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Emergency portion for a brake control valve |
| RE31059 |
Emergency portion for a brake control valve
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| Patent Drawings: | |
| Inventor: |
Hart |
| Date Issued: |
October 19, 1982 |
| Application: |
06/171,603 |
| Filed: |
July 23, 1980 |
| Inventors: |
Hart; James E. (Trafford, PA)
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| Assignee: |
American Standard Inc. (Wilmerding, PA) |
| Primary Examiner: |
Reger; Duane A. |
| Assistant Examiner: |
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| Attorney Or Agent: |
Falce; G. J. |
| U.S. Class: |
303/38; 303/82 |
| Field Of Search: |
303/35; 303/36; 303/37; 303/38; 303/39; 303/69; 303/80; 303/81; 303/82; 303/83 |
| International Class: |
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| U.S Patent Documents: |
2106491; 3018138; 3160447; 3175871; 3208801; 3232678; 3240540; 3716276 |
| Foreign Patent Documents: |
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| Other References: |
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| Abstract: |
An inexpensve emergency valve device embodies a cycling-type continual quick service valve operative by an abutment, subject on its respective opposite sides to the pressure in a train brake pipe and in a quick action chamber, in response to a service rate of reduction of the pressure of the fluid in a train brake pipe to repeatedly vent and supply fluid under pressure from and to a quick service volume disposed on one side of a diaphragm-type valve that is operatively responsive to the venting of fluid under pressure from this volume to effect the release of fluid under pressure from the quick action chamber to atmosphere at a rate faster than a service rate to cause joint cyclic operation of the continual quick service valve and the diaphragm valve to successively supply fluid under pressure from the brake pipe to and thereafter release fluid under pressure from the quick service volume at a certain rate and from the quick action chamber at a faster rate so long as fluid under pressure is released from the train brake pipe at a service rate. An emergency piston disposed within the quick service volume cooperates with the diaphragm valve in response to an emergency rate of reduction of the pressure in the brake pipe to effect operation of a brake pipe vent valve and a poppet-type valve that effects the supply of fluid under pressure from an emergency reservoir to a brake cylinder jointly with the supply from an auxiliary reservoir to cause an emergency brake application. |
| Claim: |
Having now described the invention, what I claim as new and desire to secure by Letters Patent, is:
1. For use in a brake apparatus including a brake pipe, .[.an auxiliary reservoir,.]. anemergency reservoir and a quick action chamber each normally charged to a certain chosen pressure, a brake cylinder and a fluid-pressure-operated service valve device, a fluid-pressure-operated emergency valve device operative in conjunction with saidservice valve device in response to a reduction of the pressure in the brake pipe at an emergency rate to effect .[.the supply of fluid under pressure from said reservoirs to said brake cylinder to cause.]. an emergency brake application, said emergencyvalve device comprising:
(a) a quick service volume chamber,
(b) a continual quick service valve device operable jointly by the pressure in the quick action chamber and in the brake pipe in response to a continuing reduction of the pressure in the brake pipe at a service rate to effect repeated successiverelease of fluid under pressure from said quick service volume chamber to atmosphere and thereafter recharge of said quick service volume chamber from the brake pipe to the reduced pressure present in the brake pipe,
(c) restricted means enabling flow of fluid under pressure from the brake pipe to the quick action chamber to provide for charging the quick action chamber from the brake pipe to the pressure in the brake pipe, and
(d) fluid-pressure-operated means operably responsive to the release of fluid under pressure from the brake pipe to atmosphere to so cooperate with said continual quick service valve device and said restricted means as to cause the release offluid under pressure from the quick action chamber to atmosphere at a rate in excess of said service rate, whereby said continual quick service valve device is rendered sequentially operative to terminate the release of fluid under pressure from saidquick service volume chamber to atmosphere and thereafter effect recharging of said quick service volume chamber from the brake pipe to the reduced pressure in the brake pipe, and said fluid-pressure-operated means is rendered sequentially operative inconjunction with said continual quick service valve device to terminate the release of fluid under pressure from the quick action chamber to atmosphere at said rate that is in excess of said service rate to enable the flow of fluid under pressure fromthe brake pipe to the quick action chamber until the pressure in the quick action chamber is the same as that in the brake pipe.
2. The emergency valve device, as recited in claim 1, further characterized in that said continual quick service valve device comprises:
(a) a first annular valve seat,
(b) a second annular valve seat coaxial with and spaced apart from said first annular valve seat,
(c) valve means disposed between said first and second valve seats, for, while in engagement with said first valve seat, establishing a communication for the recharge of said quick service volume chamber from the brake pipe, while disengaged fromboth of said valve seats, establishing a communication through which fluid under pressure can flow from both said quick service volume chamber and the quick action chamber to atmosphere, and, while in engagement with said second valve seat, establishingan unrestricted communcation through which fluid under pressure can flow from said quick service volume chamber to atmosphere and a restricted communication through which fluid under pressure can flow from the quick action chamber to atmosphere, and
(d) a movable abutment subject on its respective opposite sides to the pressure in the quick action chamber and in the brake pipe and so operably connected to said valve means as to enable shifting of said valve means into engagement with saidfirst valve seat in response to equal pressures in the quick action chamber and in the brake pipe, to cause disengagement of said valve means from both of said valve seats in response to a reduction of the pressure in the brake pipe at said service rate,and to cause engagement of said valve means with said second valve seat in response to a reduction of the pressure in the brake pipe at an emergency rate.
3. The emergency valve device, as recited in claim 1, further characterized in that said emergency valve device further comprises:
(a) a check valve device providing flow of fluid under pressure in the direction from the brake cylinder to the brake pipe, and
(b) valve means operable by said continual quick service valve device is response to the supply of fluid under pressure to the brake pipe in the absence of fluid under pressure in the quick action chamber for effecting flow of fluid underpressure from said check valve device to the brake pipe whereby fluid under pressure in the brake cylinder flows to the brake pipe until equalization of pressure between the brake cylinder and the brake pipe occurs.
4. The emergency valve device, as recited in claim 2, further characterized by means whereby said communication established, while said valve means is in engagement with said first valve seat, comprises two parallel communications one of whichis restricted, and the other of which may be closed without effecting closing of said restricted communication.
5. The emergency valve device, as recited in claim 2, further characterized by means providing, while said valve means is disengaged from both of said valve seats, a restricted communication between the brake pipe and atmosphere for causing aquick service reduction of the pressure in the brake pipe.
6. The emergency valve device, as recited in claim 2, further characterized in that, while said valve means is in engagement with said second valve seat, said continual quick service valve device comprises:
(a) a first means providing a restricted communication through which fluid under pressure flows from the brake pipe to atmosphere, and
(b) a second means providing said restricted communication through which fluid under pressure can flow from the quick action chamber to atmosphere.
7. For use in a brake apparatus including a brake pipe, .[.an auxiliary reservoir,.]. an emergency reservoir and a quick action chamber each normally charged to a certain chosen pressure, a brake cylinder and a fluid-pressure-operated servicevalve device, a fluid-pressure-operated emergency valve device operative in conjunction with said service valve device in response to a reduction of the pressure in the brake pipe at an emergency rate to efect .[.the supply of fluid under pressure fromsaid reservoirs to said brake cylinder to cause.]. an emergency brake application, said emergency valve device comprising:
(a) a quick service volume chamber,
(b) a continual quick service valve device operable jointly by the pressure in the quick action chamber and in the brake pipe in response to a continuing reduction of the pressure in the brake pipe at a service rate to effect repeated successiverelease of fluid under pressure from said quick service volume chamber to atmosphere and thereafter recharge of said quick service volume chamber from the brake pipe to the reduced pressure present in the brake pipe,
(c) restricted means enabling flow of fluid under pressure between said quick service volume chamber and the quick action chamber to provide for charging the quick action chamber from said quick service volume chamber to the pressure in saidquick service volume chamber, and
(d) fluid-pressure-operated means operatively responsive to the release of fluid under pressure from said quick service volume chamber to atmosphere to so cooperate with said continual quick service valve device and said restricted means as tocause the release of fluid under pressure from the quick action chamber to atmosphere at a rate in excess of said service rate, whereby said continual quick service valve device is rendered sequentially operative to terminate the release of fluid underpressure from said quick service volume chamber to atmosphere and therefter recharge said quick service volume chamber from the brake pipe to the reduced pressure therein, and said fluid-pressure-operated means is rendered sequentially operative inconjunction with said continual quick service valve device to terminate the release of fluid under pressure from the quick action chamber to atmosphere at said rate that is in excess of said service rate and thereafter effect the recharging of the quickaction chamber from said quick service volume chamber to the reduced pressure in the brake pipe.
8. The emergency valve device, as recited in claim 1, further characterized in that said continual quick service valve device comprises:
(a) a valve,
(b) a stop,
(c) biasing means normally biasing said valve against said stop,
(d) a valve seat so arranged that when engaged by said valve as to close an unrestricted communication between the brake pipe and said quick service volume, and
(e) an abutment subject on one side to the pressure in the quick action chamber and on the other side to the pressure in the brake pipe and effective upon a reduction of brake pipe pressure on said other side to effect shifting of said valve intoseating contact with said valve seat to close said unrestricted communication.
9. The emergency valve device, as recited in claim 1, further characterized in that said continual quick service valve device comprises:
(a) a hollow cylindrical member having a valve seat at each end thereof,
(b) a stop member,
(c) a first valve cooperating with one of said valve seats to control flow of fluid under pressure from the brake pipe to the interior of said hollow cylindrical member,
(d) a first biasing means normally biasing said first valve against said stop member,
(e) a second biasing means so interposed between said hollow cylindrical member and said stop member as to normally bias said first valve seat out of seating engagement with said first valve to establish a communication through which fluid underpressure may flow from the brake pipe to the interior of said hollow cylindrical member,
(f) a second valve cooperating with the other of said valve seats to control flow of fluid under pressure from the interior of said hollow cylindrical member to said quick service volume chamber,
(g) means providing a restricted communication through which fluid under pressure may flow from the interior of said hollow cylindrical member to said quick service volume chamber while said second valve is seated on said other valve seat, and
(h) an abutment subject on one side to the pressure in the quick action chamber and on the other side to the pressure in the brake pipe and so arranged with respect to said second valve whereby a reduction of brake pipe pressure on said otherside of said abutment renders said abutment effective to, first, seat said second valve on said other valve seat whereby flow of fluid under pressure from the brake pipe to said quick service volume chamber is only via said restricted bypasscommunication and thereafter shift said hollow cylindrical member to effect seating of said one valve seat on said first valve to terminate flow from the brake pipe to said quick service volume chamber.
10. The emergency valve device, as recited in claim 1, further characterized in that said continual quick service valve device is operative to control the supply of fluid under pressure from the brake pipe to said quick service volume chamberand the release of fluid under pressure from both said quick service volume chamber and the quick action chamber to atmosphere, said continual quick service valve device comprising:
(a) a hollow stop member having at one end an annular valve seat and intermediate its ends a port,
(b) two integral hollow cylindrical members of unequal diameter, the larger of which is provided at each end with a valve seating surface and the smaller of which is mounted for reciprocation in said hollow stop member and is provided at itsouter end with a valve seat and intermediate its ends with an elongated peripheral annular groove that is of sufficient length so as to always communicate with said port as said cylindrical members reciprocate within said hollow stop member,
(c) a first valve cooperating with said valve seat at the outer end of said smaller cylindrical member to control flow of fluid under pressure from the brake pipe to the interior of said two hollow cylindrical members,
(d) a first biasing means normally biasing said first valve against the other end of said stop member,
(e) a stationary annular exhaust valve seat,
(f) a second biasing means so interposed between the cylindrical member of larger diameter and said stop member as to normally bias said valve seat at the outer end of said smaller cylindrical member out of seating engagement with said firstvalve to establish a communication through which fluid under pressure may flow from the brake pipe to the interior of said two hollow cylindrical members, the seating surface at one end of said larger cylindrical member out of seating engagement withsaid valve seat at said one end of said stop member to establish a communication through which fluid under pressure may be released from the quick action chamber to atmosphere upon operation of said fluid-pressure-operated means in response to therelease of fluid under pressure from said quick service volume chamber to atmosphere, and the seating surface at the other end of said larger cylindrical member into seating engagement with said stationary exhaust valve seat to close communicationbetween said quick service volume chamber and atmosphere,
(g) a second valve cooperating with said seating surface at the other end of said larger cylindrical member to control flow of fluid under pressure from the interior of said hollow cylindrical members to said quick service volume chamber,
(h) means providing a restricted bypass communication through which fluid under pressure may flow from the interior of said hollow cylindrical members to said quick service volume chamber while said second valve is seated on said seating surfaceat the other end of said larger cylindrical member, and
(i) an abutment subject on one side to the pressure in the quick action chamber and on the other side to the pressure in the brake pipe and so arranged with respect to said valves whereby a reduction of brake pipe pressure at a service rate onsaid other side of said abutment renders said abutment effective to, first, seat said second valve on said seating surface at the other end of said larger cylindrical member whereby flow of fluid under pressure from the interior of said hollowcylindrical member to said quick service volume chamber is only via said restricted bypass communication, and thereafter shift said hollow cylindrical member to a position in which said seating surface at the other end of said larger cylindrical memberis unseated from said stationary exhaust valve seat whereupon fluid under pressure can flow from both the brake pipe and the quick service volume chamber to atmosphere, and said seating surface at the one end of said larger cylindrical member is unseatedfrom said valve seat at one end of said hollow stop member whereby fluid under pressure can flow from the quick action chamber to atmosphere via said port, said groove and past said valve seat upon operation of said fluid-pressure-operated means.
11. The emergency valve device, as recited in claim 9, further characterized in that said means providing a restricted communication through which fluid under pressure may flow from the interior of said hollow cylindrical member to said quickservice volume chamber, while said second valve is seated on said other valve seat, is carried by said second valve.
12. The emergency valve device, as recited in claim 9, further characterized in that said means providing a restricted communication through which fluid under pressure may flow from the interior of said hollow cylindrical member to said quickservice volume chamber is carried within said hollow cylindrical member and constitutes the sole communication through which fluid under pressure may flow to said quick service volume chamber.
13. The emergency valve device, as recited in claim 10, further characterized by a casing member having a first bore at one end of which is formed said stationary annular exhaust valve seat, and a second bore coaxial with said first bore, saidsecond bore having said hollow stop member so disposed therein that said annular valve seat at one end thereof is so spaced apart from said stationary annular exhaust valve seat as to enable the larger of said hollow cylindrical members to be disposedbetween said valve seats so as to be movable from a position in which it engages neither valve seat to a position in which it engages either of said valve seats, said first valve being so constructed as to be also mounted in said second bore in such aposition as to be normally biased by said first biasing means against said other end of said stop member and movable away from said other end subsequent to shifting of said valve seat at the outer end of said smaller cylindrical member into engagementwith said first valve.
14. The emergency valve device, as recited in claim 10, further characterized in that said abutment carries thereon said restricted means enabling flow of fluid under pressure from the brake pipe to the quick action chamber to provide forcharging the quick action chamber.
15. The emergency valve device, as recited in claim 1, further characterized in that said restricted means comprises a pair of chokes so arranged as to provide for the flow therethrough in series of fluid under pressure from said quick servicevolume chamber to the quick action chamber, one of said pair of chokes being so arranged and of such size as to provide for the release of fluid under pressure from the quick action chamber to atmosphere at said rate in excess of said service rateindependently of the other of said pair of chokes.
16. The emergency valve device, as recited in claim 15, further characterized in that the diameter of said one choke is greater than the diameter of the other of said pair of chokes.
17. The emergency valve device, as recited in claim 15, further characterized in that the diameter of said one choke is 0.0760 inch, and the diameter of the other of said pair of chokes is 0.0210 inch.
18. The emergency valve device, as recited in claim 1, further characterized in that said fluid-pressure-operated means comprises:
(a) an annular valve seat, and
(b) a diaphragm-type valve subject on one side to the pressure of fluid in said quick service volume chamber to bias the other side into seated engagement with said annular valve seat whereby said diaphragm-type valve, while in seated engagementwith said annular valve seat, closes communication between the quick action chamber and atmosphere,
and said restricted means comprises a pair of chokes so arranged and of such size as to enable the release of fluid under pressure from the quick action chamber through said pair of chokes in parallel to atmosphere at a rate in excess of saidservice rate in response to the release of fluid under pressure from said quick service volume chamber to atmosphere by operation of said quick service valve device.
19. The emergency valve device, as recited in claim 1, further characterized in that said fluid-pressure-operated means comprises:
(a) an annular valve seat, and
a diaphragm-type valve subject on one side to the pressure of fluid in said quick service volume chamber to bias the opposite side into seated engagement with said annular valve seat whereby said diaphragm-type valve, while in seated engagementwith said annular valve seat, closes communication between the quick action chamber and atmosphere,
and said restricted means comprises a pair of chokes, one of which is carried by said diaphragm-type valve and so arranged as to enable flow of fluid under pressure therethrough in series with the other of said pair of chokes from said quickservice volume chamber to the quick action chamber while said diaphragm-type valve is biased into seated engagement with said valve seat, and the other of said chokes being of such size and so arranged as to provide for the release of fluid underpressure from the quick action chamber to atmosphere past said valve seat at a rate in excess of said service rate independently of said one choke upon unseating of said diaphragm-type valve from said valve seat in response to the release of fluid underpressure from said quick service volume chamber to atmosphere by operation of said continual quick service valve device.
20. The emergency valve device, as recited in claim 15, further characterized in that said fluid-pressure-operated means comprises a diaphragm-type valve, and the other of said pair of chokes is mounted on said diaphragm-type valve to provide arestricted communication between one side thereof and the other to provide for the charging of the quick action chamber from said quick service volume chamber.
21. The emergency valve device, as recited in claim 1, further characterized in that said emergency valve device further comprises:
(a) a fluid-pressure-operated brake pipe vent valve means operable upon the release of fluid under pressure .Iadd.therefrom .Iaddend.to cause the release of fluid under pressure from the brake pipe to atmosphere at an emergency rate, .Iadd.and.Iaddend.
(b) valve means for effecting the release of fluid under pressure from said fluid-pressure-operated brake pipe vent valve means to cause the operation thereof, .[.and .]. .Iadd.in response to said emergency rate of brake pipe reduction. .Iaddend.
.[.(c) abutment means disposed in said quick service volume chamber and operable by said fluid-pressure-operated means only in response to an emergency rate of reduction of pressure in the brake pipe to operate said valve means to effect therelease of fluid under pressure from said fluid-pressure-operated brake pipe vent valve means..].
22. The emergency valve device, as recited in claim 21, further characterized in that said fluid-pressure-operated brake pipe vent valve means comprises:
(a) an annular valve seat the area within which is open to atmosphere, and
(b) an abutment having a chamber on each side thereof subject to the pressure in the brake pipe, said abutment being so arranged as to engage said valve seat so long as equal pressures are present in each of said chambers and movable out ofengagement with said seat to release fluid under pressure from the chamber on the side thereof adjacent said seat to atmosphere at an emergency rate in response to the release of fluid under pressure from the other of said chambers by operation of saidvalve means.
23. The emergency valve device, as recited in claim .[.21.]. .Iadd.22.Iaddend., further characterized in that said valve means comprises:
(a) an annular valve seat the area within which is open to said quick service volume chamber and the area without which is open to said fluid-pressure-operated brake pipe vent valve means,
(b) a valve cooperating with said valve seat and having a fluted stem extending in the direction of said abutment means, and
(c) biasing means normally biasing said valve into seating engagement with said valve seat,
(d) the operation of said abutment .[.means.]. by said fluid-pressure-operated means being effective to cause said fluted stem to unseat said valve from said valve seat to release fluid under pressure from said fluid-pressure-operated brake pipevent valve means to cause operation thereof.
24. The emergency valve device, as recited in claim 1, further characterized in that said emergency valve device further comprises:
(a) valve means for effecting the flow of fluid under pressure from the emergency reservoir to the brake cylinder, and
(b) abutment means disposed in said quick service volume chamber and operable by said fluid-pressure-operated means only in response to an emergency rate of reduction of pressure in the brake pipe to operate said valve means to effect the flow offluid under pressure from the emergency reservoir to the brake cylinder.
25. The emergency valve device, as recited in claim 1, further characterized in that said emergency valve device further comprises:
(a) a fluid-pressure-operated brake pipe vent valve means operable upon the release of fluid under pressure therefrom to cause the release of fluid under pressure from the brake pipe to atmosphere at an emergency rate,
(b) a first valve means for effecting the release of fluid under pressure from said fluid-pressure-operated brake pipe vent valve means to cause the operation thereof,
(c) a second valve means for effecting the flow of fluid under pressure from the emergency reservoir to the brake cylinder, and
(d) an abutment subject on one side to the pressure in the quick action chamber and one the other side to the pressure in the brake pipe and operable in response to a reduction of the pressure in the brake pipe at only an emergency rate to causesimultaneous operation of said first and second valve means.
26. The emergency valve device, as recited in claim 1, further characterized in that said emergency valve device further comprises:
(a) an annular valve seat the area within which is open to the emergency reservoir and the area without which is open to the brake cylinder,
(b) a valve cooperating with said valve seat and having an operating stem extending from one side thereof through said annular valve seat,
(c) abutment means subject on one side to the pressure in the quick action chamber and on the other side to the pressure in the brake pipe and so disposed with respect to said continual quick service valve device and said operating stem wherebysaid abutment means is responsive to a reduction of pressure in the brake pipe at a service rate to operate said continual quick service valve device without effecting operation of said valve via said operating stem, and said abutment means is responsiveto a reduction of pressure in the brake pipe at only an emergency rate to effect via said valve stem unseating of said valve from said valve seat to cause flow of fluid under pressure from the emergency reservoir to the brake cylinder.
27. The emergency valve device, as recited in claim 24, further characterized in that said valve means comprises:
(a) an annular valve seat the area within which is open to the brake cylinder and the area without which is open to the emergency reservoir,
(b) a valve cooperating with said valve seat and having a fluted stem extending in the direction of said abutment means,
(c) sealing means carried by said fluted stem and providing a seal between said quick service volume chamber and the brake cylinder, and
(d) biasing means normally biasing said valve into seating engagement with said valve seat to close communication between the emergency reservoir and the brake cylinder,
(e) the operation of said abutment means by said fluid-pressure-operated means being effective to cause said fluted stem to unseat said valve from said valve seat to cause flow of fluid under pressure from the emergency reservoir to the brakecylinder until equalization therebetween occurs.
28. The emergency valve device, as recited in claim 1, further .[.characterized by a brake-cylinder-pressure-operated inshot valve device.]. comprising: .Iadd.
(a) an auxiliary reservoir; and
(b) an inshot valve device comprising: .Iaddend.
.[.(a).]. .Iadd.(i) .Iaddend.two parallel flow communications through which fluid under pressure is supplied from the auxiliary reservoir and the emergency reservoir to the brake cylinder,
.[.(b).]. .Iadd.(ii) .Iaddend.a first valve means for controlling flow of fluid under pressure through one of said two parallel flow communications,
.[.(c).]. .Iadd.(iii) .Iaddend.a first biasing means for operating said first valve means to cut off flow through said one communication,
.[.(d).]. .Iadd.(iv) .Iaddend.an abutment operable in response to the supply of fluid under pressure to one side thereof to operate said first valve means against the yielding resistance of said biasing means to establish said one communicationand subject on the other side to the pressure of the fluid supplied to the brake cylinder, and
.[.(e).]. .Iadd.(v) .Iaddend.brake-pipe-pressure-operated valve means for controlling the flow of fluid under pressure to said one side of said abutment whereby said abutment in response to the flow of fluid under pressure to said one sideoperates said first valve means to effect the flow of fluid under pressure through said one of said two communications so long as fluid under pressure is supplied to said one side of said abutment, said brake-pipe-pressure-operated valve means beingeffective in response to the release of all fluid under pressure therefrom to trap fluid at a chosen pressure on said one side of said abutment whereby said abutment, in response to brake cylinder pressure on said other side exceeding said chosenpressure, renders said biasing means effective to operate said first valve means to cut off flow through said one communication, so that further flow of fluid under pressure to the brake cylinder is only via the other of said two parallel flowcommunications thereby providing a two-stage buildup of pressure in the brake cylinder.
29. The emergency valve device, as recited in claim 1, further .[.characterized by an inshot valve device.]. comprising: .Iadd.
(a) an auxiliary reservoir; and
(b) an inshot valve device comprising: .Iaddend.
.[.(a).]. .Iadd.(i) .Iaddend.two parallel flow communications through which fluid under pressure is supplied from the auxiliary reservoir and the emergency reservoir to the brake cylinder,
.[.(b).]. .Iadd.(ii) .Iaddend.a first valve means for controlling flow of fluid under pressure through one of said two communications,
.[.(c).]. .Iadd.(iii) .Iaddend.a first biasing means for operating said first valve means to cut off flow through said one communication,
.[.(d).]. .Iadd.(iv) .Iaddend.a first abutment subject on one side to the fluid under pressure supplied to the brake cylinder,
.[.(e).]. .Iadd.(v) .Iaddend.a second biasing means so disposed on the other side of said first abutment as to operate said valve means against the yielding resistance of said first biasing means as to establish said one communication,
.[.(f).]. .Iadd.(vi) .Iaddend.a second valve means for controlling the flow of fluid under pressure from the brake cylinder to said other side of said first abutment whereby, only while both sides of said first abutment are subject to the fluidunder pressure in the brake cylinder, said second biasing means is rendered effective to operate said valve means to establish said one communication, and
.[.(g).]. .Iadd.(vii) .Iaddend.means operable only in response to an emergency rate of reduction in the brake pipe pressure to cause said second valve means to cut off flow of fluid under pressure from the brake cylinder to said other side ofsaid first abutment whereby only said one side of said first abutment is subject to brake cylinder pressure thereby enabling said first biasing means to operate said first valve means to cut off flow through said one communication upon brake cylinderpressure establishing on said one side of said first abutment a fluid pressure force in excess of the force exerted on said other side of said abutment by second biasing means, so that further flow of fluid under pressure to the brake cylinder is onlyvia the other of said two parallel flow communications thereby providing a two-stage buildup of pressure in the brake cylinder.
30. The emergency valve device, as recited in claim 28, further characterized by means for restricting the flow of fluid under pressure through the other of said two parallel flow communications in said inhot valve device.
31. The emergency valve device, as recited in claim 28, further characterized in that said first valve means comprises:
(a) a valve seat, and
(b) a disc valve biased in the direction of said valve seat by said biasing means.
32. The emergency valve device, as recited in claim 28, further characterized in that said brake-pipe-pressure-operated valve means comprises:
(a) a conduit through which fluid under pressure supplied to the brake cylinder may flow to said one side of said abutment,
(b) an annular valve seat to the inner area of which fluid under pressure is supplied via said conduit,
(c) a valve cooperable with said seat to control flow of fluid under pressure from the brake cylinder to said one side of said abutment, and
(d) a second abutment operably connected to said valve and effective to unseat said valve from said valve seat in response to the supply of fluid under pressure from the brake pipe to said second abutment,
(e) said valve, valve seat and second abutment being so arranged with respect to said first abutment as to enable said first abutment to effect seating of said valve on said valve seat in response to the buildup of brake cylinder pressure on saidother side of said first abutment only in the absence of the supply of fluid under pressure from the brake pipe to said second abutment whereby further flow of fluid under pressure to the brake cylinder is only via the other of said two parallel flowcommunications thereby providing a two-stage buildup of pressure in the brake cylinder.
33. The emergency valve device, as recited in claim 28, further characterized in that said brake-pipe-pressure-operated valve means comprises:
(a) a conduit through which fluid under pressure may be supplied from the brake pipe to said one side of said abutment,
(b) a stop member,
(c) a first hollow cylindrical member having a stop at one end and an out-turned flange at the other end,
(d) a second biasing means for normally biasing said out-turned flange at the other end of said first hollow cylindrical member against said stop member,
(e) a second hollow cylindrical member longer than said first cylindrical member in which it is slidably and sealably mounted and having a valve seat at one end and an out-turned flange at the other end,
(f) a third biasing means for normally biasing said second mentioned out-turned flange into abutting relationship with said first mentioned out-turned flange whereby said valve seat at said one end of said second hollow cylindrical memberprotrudes beyond said stop at said one end of said first hollow cylindrical member, and
(g) a valve so carried on said one side of said abutment as to normally be disengaged from both of said valve seats whereby fluid under pressure supplied from the brake pipe to said conduit flows via said second hollow cylindrical member to saidone side of said abutment,
(h) said first and second biasing means being of such strength that said valve is moved into engagement with said stop at said one end of said first hollow cylindrical member only in response to a reduction of the pressure in the brake pipe to avalue that is a chosen amount less than that required to effect a full service brake application whereby brake pipe pressure at said reduced value is trapped on said one side of said abutment to provide a fluid pressure force on said one side of saidabutment of sufficient magnitude to prevent the brake cylinder pressure acting on said other side from deflecting said abutment in the direction to render said first biasing means effective to operate said valve means to cut off flow of fluid underpressure through said one communication.
34. The emergency valve device, as recited in claim 29, further characterized in that said second valve means comprises:
(a) a pair of spaced-apart annular valve seats,
(b) a diaphragm-type valve disposed between said seats and shiftable into engagement with each of said annular valve seats to, while in engagement with each respective seat, form within the respective seat a first chamber and without saidrespective seat a second chamber,
(c) biasing means normally biasing one side of said diaphragm-type valve into contact with one of said pair of annular valve seats,
(d) a first conduit means through which fluid under pressure is supplied from the brake cylinder to the first chamber within said one valve seat and the second chamber without the other of said pair of valve seats,
(e) choke means so disposed in said first conduit as to restrict the flow of fluid under pressure from the brake cylinder to said second chamber without said other valve seat without restricting flow to said first chamber within said one valveseat, and
(f) a second conduit means through which said means operably only in response to an emergency rate of reduction in brake pipe pressure supplies fluid under pressure to said second chamber without said one valve seat whereby said diaphragm-typevalve is shifted against the yielding resistance of said biasing means out of contact with said one annular valve seat and into contact with the other of said pair of annular valve seats to cut off flow of fluid under pressure to said other side of saidfirst abutment only in response to the operation of said means to supply fluid under pressure to said second conduit.
35. The emergency valve device, as recited in claim 3, further characterized in that said valve means comprises:
(a) an annular valve seat disposed in concentric relation to said continual quick service valve device,
(b) an annular valve member disposed in concentric relation to said continual quick service valve device and having an annular valve formed on one end for engaging said annular valve seat,
(c) a spring seat,
(d) a spring interposed between said spring seat and said annular valve member for normally biasing said annular valve at the one end of said valve member into engagement with said annular valve seat, and
(e) a lost-motion connection between said annular valve member and said continual quick service valve device so constructed and arranged that said annular valve at the one end of said valve member is unseated from said annular valve seat byoperation of said continual quick service valve device only upon the supply of fluid under pressure from the brake pipe to said continual quick service valve device subsequent to the release of all fluid under pressure from the quick action chamber asthe result of effecting an emergency brake application.
36. The emergency valve device, as recited in claim 1, further characterized in that said emergency valve device further comprises:
(a) a movable abutment subject on one side to the pressure in the quick action chamber and on the other side to the pressure in the brake pipe,
(b) a check valve device providing flow of fluid under pressure in the direction from the brake cylinder to the brake pipe,
(c) valve means so arranged with respect to said abutment, said check valve device and said continual quick service valve device as to be operable by said abutment in response to the supply of fluid under pressure to the brake pipe in the absenceof fluid under pressure in the quick action chamber to effect flow of fluid under pressure from said check valve device to the brake pipe whereby fluid under pressure in the brake cylinder flows to the brake pipe until equalization of pressure betweenthe brake cylinder and the brake pipe occurs, said abutment being effective in response to a reduction of the pressure in the brake pipe at a service rate to cause said continual quick service valve device to repeatedly release fluid under pressure fromsaid quick service volume chamber to atmosphere and thereafter recharging said volume chamber from the brake pipe. |
| Description: |
BACKGROUND OF THE INVENTION
In U.S. Pat. No. 3,232,678, issued Feb. 1, 1966 to William G. Wilson, and assigned to the assignee of the present application, there is shown and described a brake control valve device that is substantially the same in function and operationas the brake control valve device included in the standard fluid pressure brake apparatus now in use on railway freight cars owned and operated by American railroads. The brake control valve device shown in the above-mentioned U.S. Pat. No. 3,232,678comprises a service valve portion embodying therein a plurality of slide, spool and disc type valves, and an emergency valve portion that has a slide-type emergency valve slidable on a flat ported valve seat and a graduating valve slidably mounted on aflat ported surface provided therefor on the side of the emergency slide valve opposite the side thereof that engages the flat ported valve seat. This emergency valve portion is operative in response to a service rate of reduction of pressure in a trainbrake pipe to release fluid under pressure from a quick action chamber to atmosphere at a service rate thereby rendering this emergency valve portion effective to cause an emergency brake application only in response to an emergency rate of reduction ofpressure in the train brake pipe.
The manufacture and production of these slide-type valves and valve seats of this emergency valve portion require considerable accurate and skillful machining which, as is readily apparent, increases the cost of the emergency valve portion ofwhich they are an essential component.
Moreover, in U.S. Pat. No. 3,716,276, issued Feb. 13, 1973 to Richard L. Wilson et al, and assigned to the assignee of the present application, there is shown and described a brake control valve device that is substantially the same infunction and operation as the latest design of brake control valve devices now being offered to the railway industry as the brake control valve device included in the standard fluid pressure brake apparatus installed on any new freight cars builtsubsequent to Jan. 1, 1977. In this brake control valve device, the fluid under pressure released from the quick action chamber, when effecting a service brake application, is used to operate a continual quick service valve device that effects a "quickservice" transmission through a train brake pipe of a pressure reduction wave.
The above-mentioned continual quick service valve device operates repeatedly in cycles to release locally on each railway vehicle provided with this valve device fluid under pressure from the brake pipe to atmosphere so long as a relay valvedevice embodied in a brake valve device on the locomotive effects a release of fluid under pressure from the train brake pipe to atmosphere via a choke at a normal rate of brake pipe pressure reduction.
However, if the rate of release of fluid under pressure from the train brake pipe exceeds a normal service rate and approaches, but is less than, an emergency rate, this continual quick service valve device is ineffective to operate in repeatedcycles for the reasons given below.
The emergency slide valve and the emergency graduating valve, which are operated by an abutment subject on one side to the pressure in the brake pipe and on the other side to the pressure in the quick action chamber, are so constructed as torelease fluid under pressure from the quick action chamber at the same rate as fluid under pressure is released from the train brake pipe.
Consequently, when the rate of release of fluid under pressure from the train brake pipe is greater than the normal rate but less than an emergency rate, the quantity or amount of fluid under pressure supplied from the quick action chamber to thecontinual quick service valve device via the emergency graduating valve for operating this continual quick service valve device is correspondingly increased. This increased amount of fluid under pressure is supplied through the pipe 13, passageway 115and bore 120 to the lower side of the diaphragm 77 shown in FIG. 3 of the above-mentioned U.S. Pat. No. 3,716,276 to deflect this diaphragm upward to unseat it from the annular valve seat 119. It is apparent from FIG. 3 that upon the unseating of thisdiaphragm 77 from the valve seat 119, fluid under pressure flows from the bore 120 into the chamber 125 below the diaphragm 77 and thence to atmosphere via the passageway 122 and choke 123 at a rate determined by the size of this choke which in the brakecontrol valve device now being sold for installation on freight cars used by American railroads has an actual diameter of 0.015625 inch. This being a choke of small size, it so restricts the flow of fluid under pressure from the chamber 125 shown inFIG. 3 that, upon an excessive supply of fluid under pressure to this chamber 125, the continual quick service valve device becomes inoperative to operate in cycles to locally release fluid under pressure from the train brake pipe to atmosphere so longas fluid under pressure is being released from the train brake pipe by the relay valve device embodied in the brake valve device on the locomotive.
Furthermore, it is apparent that when this continual quick service valve device operates in repeated cycles in response to a normal rate of brake pipe reduction, this cyclic operation produces excessive wear of the various elements, especiallythe valves and valve seats, of this valve device which wear, of course, is undesirable.
Accordingly, it is the general purpose of this invention to provide a railway car brake control valve device with a novel emergency valve portion that embodies a first movable abutment, subject on its respective opposite sides to the pressure ina train brake pipe and in a quick action chamber that is effective, upon a normal service rate of reduction of the pressure in the train brake pipe, to unseat a poppet-type valve from one of two coaxial spaced-apart valve seats between which it is sodisposed that, while unseated from both seats, fluid under pressure is released from a quick service volume previously charged from the train brake pipe and disposed on one side of a diaphragm-type valve that is operatively responsive to the venting offluid under pressure from this quick service volume to effect the release of fluid under pressure from the quick action chamber and the chamber on one side of the first abutment to atmosphere at a rate faster than a normal service rate to cause jointcyclic operation of the abutment-operated poppet valve and the diaphragm-type valve to successively release fluid under pressure from the quick service volume at a certain rate and from the quick action chamber at a faster rate and thereafter rechargethis quick service volume from the brake pipe so long as fluid under pressure is released from the train brake pipe at a normal service rate.
An emergency piston disposed within the quick service volume cooperates with the diaphragm valve in response to an emergency rate of reduction of the pressure in the train brake pipe to effect operation of a second movable abutment thatconstitutes a brake pipe vent valve and a poppet-type valve which effects the supply of fluid under pressure from an emergency reservoir to a brake cylinder simultaneously with the supply from an auxiliary reservoir by operation of the service portion ofthe control valve device to cause an emergency brake application.
SUMMARY OF THE INVENTION
According to the present invention, a railway freight car brake control valve device that includes a service valve portion and a pipe bracket that are substantially the same as the service valve portion and pipe bracket shown in theabove-mentioned U.S. Pat. No. 3,232,678, and a novel emergency valve portion which is secured to this pipe bracket whereby there is provided a brake control valve device, the novel emergency portion of which embodies therein a cycling-type continualquick service valve device having a hollow poppet-type valve operated sequentially by a first movable abutment, subject on its respective opposite sides to the pressure in a train brake pipe and in a quick action chamber, between a first position, inwhich it is seated on one of two coaxial spaced-apart valve seats and a quick service volume is charged from a train brake pipe via the hollow poppet valve, and a second position in which it is unseated from both valve seats and fluid under pressure isvented from the quick service volume to atmosphere at a certain rate.
This novel emergency portion further comprises a diaphragm-type valve on one side of which is disposed the quick service volume the opposite side being normally pressed against an annular valve seat by fluid under pressure in the quick servicevolume to close communication between the quick action chamber and atmosphere via the other one of the two spaced-apart valve seats while the poppet-type valve is unseated therefrom.
Furthermore, this emergency portion also embodies an emergency piston disposed within the quick service volume on the one side of the diaphragm valve. When an emergency rate of brake pipe reduction is effected, a sufficient differential fluidpressure force is developed on the first movable abutment to cause it to shift the poppet-type valve into engagement with the other one of the two spaced-apart valve seats to limit the rate of flow of fluid under pressure from the quick action chamber toatmosphere via a choke of a chosen size thus enabling the fluid under pressure in the quick action chamber to establish, on the diaphragm valve when unseated from the annular valve seat, a fluid pressure force of sufficient magnitude that, whentransmitted to the emergency piston, enables this piston to effect the release of fluid under pressure from the second abutment whereupon it is unseated from a vent valve seat to release fluid under pressure from the train brake pipe at an emergencyrate.
Furthermore, this emergency piston at the same time unseats a poppet-type valve from its seat to effect the supply of fluid under pressure from an emergency reservoir to a brake cylinder simultaneously with the supply to this cylinder from anauxiliary reservoir by operation of the service portion of this brake control valve device whereby fluid under pressure from the two reservoirs establish a higher pressure in the brake cylinder than obtained therein when a service brake application iseffected.
In the accompanying drawings:
FIGS. 1A, 1B and 1C, when taken together such that the lower edge of FIG. 1A is matched with the upper edge of FIG. 1B and the right-hand edge of FIG. 1B is matched with the left-hand edge of FIG. 1C, constitute a diagrammatic view, in section,of an improved brake control valve device embodying the invention.
FIG. 2 is a partial diagrammatic view, in section, of an emergency valve portion constructed in accordance with a second embodiment of the invention.
FIG. 3 is a diagrammatic view, in section, of an inshot valve device that may be used in place of the inshot valve device shown in FIG. 1B.
FIGS. 1A, 1D and 1C, when taken together such that the lower edge of FIG. 1A is matched with the upper edge of FIG. 1D and the right-hand edge of FIG. 1D is matched with the left-hand edge of FIG. 1C, constitute a diagrammatic view in section, ofan improved brake control valve device that embodies an inshot valve device that is somewhat different in construction and operation than the inshot valve devices shown in FIGS. 1B and 3.
FIGS. 1E and 1C when taken together such that the right-hand edge of FIG. 1E is matched with the left-hand edge of FIG. 1C, constitute a diagrammatic view in section, of an improved brake control valve device constructed in accordance with afifth embodiment of the invention.
DESCRIPTION - FIGS. 1A, 1B and 1C
As shown in FIGS. 1A, 1B and 1C of the drawings, when the lower edge of FIG. 1A is placed above the upper edge of FIG. 1B and the right-hand edge of FIG. 1B is placed along the side of the left-hand side of FIG. 1C, an improved freight carfluid-pressure-operated brake apparatus constituting a first embodiment of the invention comprises a brake pipe 1 that extends from one end of the car to the other, a brake cylinder 2, an emergency or supplemental reservoir 3, an auxiliary reservoir 4,and a brake control valve device 5 connected to the brake pipe 1 through a combined cut-out cock and centrifugal dirt collector 6 and a branch pipe 7.
The brake control valve device 5 may comprise a pipe bracket 8 having gasket faces 9 and 10 disposed opposite each other, a service or triple valve device or portion 11 and a novel emergency valve device or portion 12.
The service valve portion 11 and pipe bracket 8 shown in FIG. 1C of the drawings may be substantially the same in construction and operation as the service valve portion 7 and pipe bracket 6 shown and described in the above-mentioned U.S. Pat. No. 3,232,678. Since reference may be had to this patent for a complete description of the structure and operation of this service valve portion and pipe bracket, it is deemed unnecessary to describe them in detail herein. Briefly, however, the servicevalve portion 11 comprises a sectionalized casing 13 between which and a cover member 14, secured thereto by any suitable means (not shown), is clamped the outer periphery of a diaphragm 15 subject opposingly on its opposite sides to brake pipe pressurein a chamber 16 at the upper side of this diaphragm and to the pressure in the auxiliary reservoir 4 connected to a chamber 17 at the lower side of this diaphragm by a pipe and correspondingly numbered passageway 18 that extends through the pipe bracket8 and the sectionalized casing 13. Operatively connected to the diaphragm 15 is a service graduating valve 19 and a service slide valve 20 for respectively controlling the release of fluid under pressure from the brake pipe 1 to a quick service volume21 and the supply of fluid under pressure from the auxiliary reservoir 4 to the brake cylinder 2 in response to variations in brake pipe pressure, as disclosed in the above-mentioned U.S. Pat. No. 3,232,678.
The novel emergency valve portion 12 shown in FIGS. 1A and 1B of the drawings, when the lower edge of FIG. 1A is placed above the upper edge of FIG. 1B, has a sectionalized casing comprising an upper casing section 22, a pair of center casingsections 23 and 24 and a lower casing section 25. The upper casing section 22 is secured to the upper end of the left-hand center casing section 23 by any suitable means (not shown) and the right-hand center casing section 24 is disposed between theright-hand side of the casing section 23 and the gasket face 9 (FIG. 1C) on the left-hand side of the pipe bracket 8 it being noted that these casing sections 23 and 24 (FIG. 1B) are secured to the pipe bracket 8 (FIG. 1C) by any suitable means (notshown) and that a ported gasket 26 is disposed between the gasket face 9 and a gasket face 27 formed on the right-hand side of the center casing section 24. Likewise, the upper end of the lower casing section 25 is secured to the lower end of theright-hand center casing section 24 by any suitable means (not shown).
As shown in FIGS. 1A and 1B of the drawings, the emergency valve portion 12 comprises an emergency piston 28, an emergency brake pipe vent valve device 29, and a high pressure valve device 30 operated by the emergency piston 28 that is disposedin a quick service volume chamber 31 which is formed by the cooperative relationship of the upper casing section 22 and a diaphragm-type quick action chamber breather valve 32 the outer periphery of which is clamped between the left-hand side of thisupper casing section 22 and a first cover member 33 that is secured to this casing section 22 by any suitable means (not shown).
As is shown in FIG. 1B, the emergency valve portion 12 further comprises a continual quick service valve device 34 for controling in cycles the flow of fluid under pressure from the brake pipe 1 to the quick service volume chamber 31 (FIG. 1A)and the subsequent release of this fluid under pressure from this chamber 31 to atmosphere, an emergency accelerated release valve mechanism 35 that is so embodied in the continual quick service valve device 34 as to connect the brake cylinder 2 and theauxiliary reservoir 4 to the brake pipe 1 when effecting a brake release subsequent to an emergency brake application, an emergency accelerated release check valve device 36, a spill over check valve device 37 and an inshot valve device 38.
The emergency brake pipe vent valve device 29 comprises an annular diaphragm 39, the outer periphery of which is clamped between the right-hand side of the upper casing section 22 and a second cover member 40 that is secured to the casing section22 by any suitable means (not shown). Extending through the cover member 40 is a bore 41 of large diameter that has an annular valve seat 42 formed at its left-hand end against which the diaphragm 39 is normally biased by a spring 43 that is interposedbetween a plate 44 to which the diaphragm 39 is bonded and the bottom of a bottomed bore 45 provided in the casing section 22. The diaphragm 39 and cover member 40 cooperate to form a chamber 46 into which opens one end of a passageway 47 that extendsthrough the cover member 40 and the casing sections 22, 23 and 24 to the gasket face 27 on the casing section 24 where it registers with a port in the ported gasket 26 (FIG. 1C). This port in the gasket 26 establishes a communication between thepassageway 47 in the casing section 24 and a passageway 48 in the pipe bracket 8 to which fluid under pressure is supplied from the brake pipe 1 through the branch pipe 7 and the combined cut-out cock and dirt collector 6. Accordingly, it is apparentthat fluid under pressure is supplied from the brake pipe 1 to the passageway 47 and thence to the chamber 46.
As shown in FIG. 1A, the diaphragm 39 and the casing section 22 cooperate to form on the left-hand side of this diaphragm 39 a chamber 49 to which fluid under pressure is supplied from the brake pipe 1 in a manner hereinafter described.
As is also shown in FIG. 1A, the casing section 22 is provided with a bore 50 and a coaxial counterbore 51. An annular valve seat 52 is provided at that end of the bore 50 that opens into the counterbore 51. The other end of the bore 50 opensinto the quick service volume chamber 31 and the other end of the counterbore 51 opens into the chamber 49.
In order to effect the release of fluid under pressure from the chamber 49 to the chamber 31 and thence to atmosphere in a manner hereinafter described, a flat disc valve 53 having a fluted stem 54 extending through the bore 50 into the chamber31 is normally biased against the valve seat 52 by a spring 55 interposed between the disc valve 53 and a hollow cylindrical spring seat 56 disposed in the counterbore 51 and retained therein by a snap ring 57 that is inserted in an annular grooveprovided therefor in the wall surface of the counterbore 51.
A spring 58 interposed between a shoulder 59 formed between one end of a bore 60 and a coaxial counterbore 61 provided in the emergency piston 28 and the end of a bottomed bore 62 provided in the casing section 22 normally biases an annular bead63 on the left-hand face of the piston 28 against the right-hand side of the diaphragm-type valve 31 so that the right-hand face of this piston 28 is disposed a short distance from the end of the fluted stem 54.
As shown in FIG. 1A, the diaphragm-type breather valve 32 is constructed of some suitable resilient material, such as, for example, rubber, that is bonded to a plate 64 that is provided with a quick action chamber charging choke 65 that restrictsthe flow of fluid under pressure from the quick service volume chamber 31 and, therefore, the brake pipe 1, to a chamber 66 disposed about the outside of an annular valve seat 67 formed on the first cover member 33 against which valve seat 67 thediaphragm-type breather valve 32 is normally biased by the fluid under pressure in the quick service volume chamber 31. Opening into this chamber 66 is one end of a passageway 68 that extends through the cover member 31 and the casing sections 22, 23and 24, the ported gasket 26 (FIG. 1C) and the pipe bracket 8 to a quick action chamber 69 formed in this pipe bracket. Disposed in the one end of the passageway 68 (FIG. 1A) that opens into the chamber 66 is a screw-threaded choke 70. Consequently,the quick action chamber 69 (FIG. 1C) is charged with fluid under pressure from the quick service volume chamber 31 wich is supplied with fluid under pressure from the brake pipe 1, via the two chokes 65 and 70 in series. If the diameter of the choke 65is selected to be 0.0210 inch, and the diameter of the choke 70 is selected to be 0.0760 inch, then the quick action chamber 69 will be charged at substantially the same rate as the quick action chamber in the brake control valve devices presently usedon freight cars owned and operated by American railroads.
The high pressure valve device 30 comprises a valve 71 that is normally biased against an annular valve seat 72 by a spring 73 that is interposed between this valve 71 and the second cover member 40. This valve seat 72 is formed at one end of abore 74 that extends through the casing section 22 from the quick service volume chamber 31 to a chamber 75 into which opens one end of a passageway 76 that extends through the casing sections 22 and 23, ported gasket 26 (FIG. 1C) and pipe bracket 8 andis connected by a correspondingly numbered pipe to the emergency reservoir 3.
In order to effect unseating of the valve 71 from its seat 72 by operation of the piston 28, a valve stem 77 is slidably mounted in the bore 74. This stem 77 is provided with a peripheral annular groove in which is disposed an O-ring seal 78 andwith an elongated peripheral annular groove 79 to enable, when the valve 71 is unseated from its seat 72, flow of fluid under pressure from the chamber 75 to a passageway 80 one end of which opens at the wall surface of the bore 74. This passageway 80extends through the casing sections 22 and 23 to the gasket face 27 on the casing section 23 and thence the ported gasket 26 (FIG. 1C) to a passageway in the pipe bracket 8 that corresponds to the passageway 72 shown in the hereinbefore-mentioned U.S. Pat. No. 3,232,678. As explained in this patent, fluid under pressure is supplied from the auxiliary reservoir 2 (in the patent) to this passageway 72 (in the patent) whenever a service brake application is effected. Accordingly, it is apparent that,likewise, fluid under pressure is supplied from the auxiliary reservoir 4 (FIG. 1C) to the passageway 80 (FIGS. 1A and 1B) by operation of the service portion 11 (FIG. 1C) in response to a reduction of the pressure in the brake pipe 1 at a service rate.
Referring now to FIG. 1B of the drawings, it will be seen that the continual quick service valve device 34 comprises a valve stem 81 that is slidably mounted in a bore 82 formed in the casing section 23. Near its left-hand end, the valve stem 81has formed integral therewith a first collar 83 against which abuts a sleeve member 84 that is provded with an outturned flange 85 to which is bonded a diaphragm 86. Intermediate the collar 83 and the left-hand end of the valve stem 81 there is provideda peripheral annular groove in which is disposed an O-ring seal 87. The left-hand end of the stem 81 has screw threads for receiving a nut 88 which, when tightened, forces the sleeve member 84 against the collar 83 to operatively connect the diaphragm86 to the stem 81. The outer periphery of the diaphragm 86 is clamped between the casing section 23 and a third cover member 89 that is provided with a bottomed bore 90 into which extends the threaded portion of the stem 81 on which is mounted the nut88. The cover member 89 is secured to the casing section 23 by any suitable means (not shown).
The diaphragm 86 cooperates with the casing section 23 and cover member 89 to form within the continual quick service valve device 34 and on opposite sides of the diaphragm 86 two chambers 91 and 92. Opening into the chamber 91 is one end of apassageway 93 that extends through the cover member 89 and casing section 23 and opens into the hereinbefore-mentioned passageway 68 that is connected to the quick action chamber 69 (FIG. 1C), as hereinbefore stated. The chamber 92 is connected to thebrake pipe 1 in a manner which will now be explained.
Opening into the chamber 92 is one end of a passageway 94 that extends through the casing sections 23 and 24 and at its other end opens at the wall surface of a bore 95 in the casing section 24 it being noted that this bore 95 is coaxial with thebore 82 in the casing section 23. A fluted cup-shaped accelerated application cut-off valve 96 is slidably mounted in the bore 95 into which opens one end of a passageway 97 that extends through the casing 24 and at its other end opens into a chamber 98(FIG. 1C) formed in the pipe bracket 8. Also opening into the chamber 98 is one end of a passageway 99 that is connected to the brake pipe 1 in the manner described in the hereinbefore-mentioned U.S. Pat. No. 3,232,678.
As shown in FIG. 1B, the continual quick service valve device 34 further comprises a poppet-type valve member 100 that has some suitable resilient material such as, for example, rubber, bonded to each side thereof to provide seating surfaces forengagement with a left-hand annular valve seat 101 or a right-hand annular valve seat 102. The valve seat 101 is formed on the casing section 23 at the right-hand end of the hereinbefore-mentioned bore 82 in this casing section and the valve seat 102 isformed on the inside of an annular cup-shaped exhaust valve seat member 103 that is disposed in a first counterbore 104 in the casing section 23 and coaxial with the bore 82, and a second counterbore 105 in the casing section 24 and coaxial with the bore95, it being noted that the counterbores 104 and 105 have the same diameter which is somewhat greater than the outside diameter of the exhaust valve seat member 103 to enable a spring 106 to bias an out-turned flange 107 that is integral with theleft-hand end of this exhaust valve member 103 against the bottom of the counterbore 104, this spring 106 being interposed between the out-turned flange 107 and the right-hand end of the counterbore 105.
As shown in FIG. 1B, the cup-shaped exhaust valve member 103 is formed integral with the right-hand end of a bushing 108 disposed in the bore 25 on the left-hand side of the accelerated application cut-off valve 96 and is provided with aplurality of arcuately arranged ports 109 two of which appear in FIG. 1B. When the valve member 100 is unseated from the seat 101, fluid under pressure can flow from the quick service volume chamber 31 to atmosphere via a passageway 110 that at one endopens into this chamber 31 and at the other at the wall surface of the bore 82, this bore 82, past the valve seat 101, ports 109, counterbores 104 and 105, and a passageway 111 in the casing section 24 that at one end opens at the wall surface of thecounterbore 105 and at the other end at the exterior surface of the casing section 24.
The poppet-type valve member 100 is formed integral with the left-hand end of a hollow cylindrical member 112 that is slidably mounted in the bushing 108 and has an annular supply valve seat 113 formed on its right-hand end, as viewed in FIG. 1B. This cylindrical member 112 adjacent the valve seat 113 thereon is provided with a peripheral annular groove in which is disposed an O-ring seal 114 that forms a seal with the inside wall surface of the bushing 108. This bushing 108 in turn is providedwith a pair of spaced-apart peripheral annular grooves in each of which is disposed an O-ring seal 115 that forms a seal with the wall surface of the bore 95 on the respective opposite sides of a port 116 in bushing 108 which port 116 is disposed betweenthese O-ring seals 115. This port 116 is in alignment with one end of a passageway 117 that extends through the casing sections 23 and 22 and the first cover member 33 (FIG. 1A) and at its other end opens within the annular valve seat 67.
As shown in FIG. 1B, the port 116 is also in alignment with an elongated peripheral annular groove 118 provided on the cylindrical member 112 between the O-ring seal 114 carried thereon and a fluted collar 119 that is integral therewith. Thisfluted collar 119 cooperates with the O-ring 114 to guidably support the cylindrical member 112 within the bushing 108. This bushing 108 is provided with an internal shoulder 108a between which and the poppet-type valve member 100 is interposed a spring120 that is normally effective to bias the left-hand seating surface on this valve member 100 into seating engagement with the valve seat 101 and the right-hand seating surface out of seating enagagement with the valve seat 102, as shown in FIG. 1B.
As can be seen from FIG. 1B, a spring 121 is interposed between the accelerated application cut-off valve 96 and an annular spring seat 122 that is retained in the bore 95 by a snap ring 123 which is inserted in a groove provided therefor in thewall surface of the bore 95. This spring 121 normally biases a pair of slotted and diametrically arranged bosses 124 provided on the left-hand end of the accelerated application cut-off valve 96 against the right-hand end of the bushing 108 so that adisc 125 constructed of some suitable resilient material such as, for example, rubber and bonded to the left-hand end of this valve 96 is disposed out of seating engagement with the valve seat 113.
Since the passageway 99 (FIG. 1C) is connected to the brake pipe 1 in the manner described in the hereinbefore-mentioned U.S. Pat. No. 3,232,678, the fluid under pressure supplied from the brake pipe 1 to the passageway 99 will flow to thechamber 92 (FIG. 1B) at the right-hand side of the diaphragm 86 via chamber 98 (FIG. 1C), passageway 97 (FIG. 1B), bore 95, the flutes on the accelerated application cut-off valve 96 and passageway 94. The fluid under pressure thus supplied to thechamber 92 is effective to bias the diaphragm 86 against a plurality of arcuately-arranged stops 126 provided on the third cover member 89, two of these stops 126 appearing in FIG. 1B, so that an annular valve 127 formed on the right-hand end of thevalve stem 81 is unseated from the resilient seating surface on the left-hand side of the valve member 100 which is biased against the valve seat 101 by the spring 120, as hereinbefore stated.
As shown in FIG. 1B, the valve 127 is formed at the right-hand end of a bottomed bore 128 that extends into the valve stem 81 from the right-hand end thereof to substantially the location of a collar 129 integral with the stem 81 and providedwith a groove in which is disposed an O-ring seal 130 that forms a seal with the wall surface of the bore 82 on the left-hand side of the hereinbefore-mentioned other end of the passageway 110 that opens at the wall surface of this bore 82. The valvestem 81 is provided with a cross-bore 131 of small diameter so as to constitute a choke that at one end opens into the bottom bore 128 and at the other end at the peripheral surface of the valve stem 81 on the right-hand side of the collar 129 and theO-ring seal 130 carried thereby.
Referring to FIGS. 1A and 1B, it will be seen that some of the fluid under pressure supplied from the brake pipe 1 to the interior of the bore 95, in the manner explained above, will flow to the quick service volume 31 via the slotted andarcuately arranged bosses 124, the interior of bushing 108, past valve seat 113, hollow cylindrical member 112, past unseated valve 127 to the bore 82, and also to this bore 82 via the bottomed bore 128 and choke 131, and thence through the passageway110 so that the quick service volume 31 is charged to the pressure carried in the brake pipe 1.
As shown in FIG. 1B, the exhaust valve seat member 103 is provided with a bore 132 and a coaxial counterbore 133. The bore 132 constitutes a quick action chamber blowdown choke and in actual practice, as in heretofore constructed railway freightcar brake control valve devices, has a diameter of 0.020 inch.
The emergency accelerated release valve mechanism 35, which is embodied in the continual quick service valve device 34, as hereinbefore stated, comprises a resilient annular valve seat 134 that abuts a shoulder 135 formed on the casing section 23and a cup-shaped piston valve member 136 that is normally biased against the valve seat 134 by a spring 137 which is interposed between this piston valve member 136 and a spring seat 138. The piston valve member 136 is provided with a peripheral annulargroove in which is disposed an O-ring seal 139 that forms a seal with the wall surface of a counterbore 140 which is coaxial with the bore 82 in the casing section 23 and with a perforated sleeve member 141 that is integral with the bottom of thiscup-shaped piston member and disposed about the valve stem 81 on the inside of the spring 137. The outer end of the sleeve member 141 is provided with internal screw threads that have screw-threaded engagement with external screw threads formed on anannular member 142 the inside diameter of which is slightly greater than the outside diameter of the first collar 83 that is integral with valve stem 81 but substantially less than the outside diameter of a second collar 143 that is also integral withthe valve stem 81 and spaced apart from the first collar 83 on the right-hand side thereof, as viewed in FIG. 1B.
The check valve devices 36 and 37 are identical in construction. Hence, a description of the elements of one will suffice for the corresponding elements of the other. However, the elements of the spill-over check valve device 37 will bedistinguished from those of the emergency accelerated release check valve device 36 by the addition of a prime (') to the numeral for each respective corresponding element of the check valve device 37.
Referring to FIG. 1B, the check valve device 36 comprises an annular valve seat 144 and an annular disc valve 145 normally biased against the valve seat 144 by a spring 146.
Opening within the annular valve seat 144 is one end of a short passageway 147 that extends through the casing section 23 and at its opposite end opens into the passageway 80. Consequently, the spring 146 normally biases the disc valve 145against its seat 144 to cut off flow from the passageway 147 to a chamber 148 into which opens one end of a passageway 149 that extends through the casing section 23 and at its opposite end opens into an annular chamber 150 that is on the outside of theannular valve seat 134.
Opening within the annular valve seat 144' is one end of a short passageway 151 that extends through the casing section 23 and at its opposite end opens into the passageway 68. Consequently, the spring 146' normally biases the disc valve 145'against its seat 144' to cut off flow from the passageway 151 to a chamber 152 into which opens one end of a passageway 153 that extends through the casing section 23 and at its opposite end opens into the hereinbefore-mentioned passageway 76intermediate the ends thereof.
The inshot valve device 38 shown in FIG. 1B comprises a disc valve 154 mounted in a chamber 155 and yieldingly urged by means of a spring 156 toward an annular valve seat 157. This valve seat 157 is formed at one end of a bore 158 that at itsopposite end opens into a chamber 159 that is constantly connected to the brake cylinder 2 (FIG. 1C) by a passageway and correspondingly numbered pipe 160.
The chamber 155 is connected by a passageway 161 to the passageway 80. A choke 162 and a short passageway 163 connect the passageways 160 and 161.
A resilient flat abutment 164, constructed of, for example, rubber is bonded to one side of a disc or plate 165 and has its outside periphery clamped between a casing section 166 and the casing section 25 of the inshot valve device 38, the casingsection 25 being secured by any suitable means (not shown) to a flat face 167 on the casing section 23. This abutment 164 cooperates with the casing sections 166 and 25 to form on its respective opposite sides a chamber 168 and the above-mentionedchamber 159.
The casing section 166 is provided with a bore 169 that at one end opens into the chamber 168 and at the other end into a chamber 170 formed by the cooperative relationship of the casing section 166 and a cover member 171 secured to this casingsection 166 by any suitable means (not shown).
A hollow cylindrical spring seat member 172 is slidably mounted in the bore 169 and is provided at one end with an outturned flange 173 that is normally biased against a shoulder 174 formed between the bore 169 and a coaxial counterbore 175 by aspring 176 that is stronger than the spring 156 and is interposed between this flange 173 and the cover member 171. This spring seat member 172 is further provided with a peripheral annular groove in which is disposed an O-ring seal 177 that forms aseal with the wall surface of the bore 169 to prevent leakage of fluid under pressure from the chamber 168 to the chamber 170 and vice versa.
As shown in FIG. 1B, a hollow cylindrical valve seat member 178 that has an annular valve seat 179 formed at one end and an out-turned flange 180 at the other is so slidably mounted in the hollow cylindrical spring seat member 172 that theout-turned flange 180 is normally biased against the out-turned flange 173 by a spring 181 that is lighter than the spring 156 and is interposed between this flange 180 and the cover member 171, it being noted that the length of this valve seat member178 is such that the valve seat 179 is disposed outside of the hollow cylindrical spring seat member 172, within the chamber 168 and a short distance away from the left-hand side of the abutment 164.
As further shown in FIG. 1B, opening into the chamber 170 is one end of a passageway 182 that extends through the casing sections 166, 25 and 23 and at its opposite end opens into the chamber 92 which is connected to the brake pipe 1 in a mannerhereinbefore described. Consequently, fluid under pressure is supplied from the brake pipe 1 to the chamber 170 from whence it flows to the chamber 168 via the hollow valve seat member 178. Since the chamber 159 is connected to the brake cylinder 2 inthe manner hereinbefore described, it is apparent that the abutment 164 may be subject on one side to brake cylinder pressure present in the chamber 159 and on the other to brake pipe pressure present in the chamber 168.
Referring to FIG. 1B, it will be noted that opening into the passageway 182 intermediate the ends thereof is one end of a passageway 183 that extends through the casing sections 23 and 22 (FIG. 1A) and at its opposite end opens into thehereinbefore-mentioned chamber 49 via a choke 184 disposed in this opposite end of the passageway 183. Since fluid under pressure is supplied from the brake pipe 1 to the chamber 92, as noted above, it is apparent that fluid under pressure applied fromthe brake pipe 1 to the chamber 92 can flow to the chamber 49 via the passageways 182 and 183 and the choke 184 in addition to flow past valve 53 from chamber 31.
It may be further noted that fluid under pressure can flow from the chamber 49 to the brake pipe 1 at a rate determined by the diameter of the choke 184, and from the chamber 46 to the brake pipe 1 at an unrestricted rate. Consequently, when aservice brake application is effected, a higher pressure is maintained in the chamber 49 to prevent unseating of the diaphragm 39 from the valve seat 42 which would cause an undesired emergency brake application.
OPERATION - FIGS. 1A, 1B and 1C
Initial Charging
Let it be assumed that a railway freight car provided with the brake control valve device 5 shown in FIGS. 1A, 1B and 1C of the drawings has been coupled into a train of cars, and that a handle of an engineer's brake valve device (not shown)located on the locomotive coupled to the head end of the train is in its release position. Therefore, while the handle of the engineer's brake valve device is in its release position, the relay valve device of this brake valve device will effect thesupply of fluid under pressure to the train brake pipe and therefore to the brake pipe 1 to charge the train brake pipe to a preselected normal charged value which, for example, may be seventy pounds per square inch.
Fluid under pressure supplied to the brake pipe 1 (FIG. 1C) will flow via the branch pipe 7 and combined cut-out cock and dirt collector 6 to the brake control valve device 5 to cause the service valve portion 11 of this control valve device 5 tooperate in the usual well-known manner of railway freight car brake control valves to effect a release of fluid under pressure from the brake cylinder 2 thereby releasing the brakes on the car and to charge the emergency reservoir 3 and auxiliaryreservoir 4 to the pressure carried in the brake pipe 1.
Fluid under pressure supplied to the brake pipe 1 will flow therefrom through the branch pipe 7 and combined cut-out cock and dirt collector 6 to the passageway 48 in the pipe bracket 8 and thence from this passageway 48 to: (1) the chamber 46(FIG. 1A) via the ported gasket 26 and the passageway 47, (2) the chamber 92 (FIG. 1B) via a passageway 185, a chamber 186, a strainer device 187, passageway 99, chamber 98, passageway 97 (FIG. 1B), bore 95, and passageway 94 (3) the chamber 170 from thechamber 92 via passageway 182, (4) the quick service volume chamber 31 from the bore 95 via the slotted and diametrically arranged bosses 124, the interior of bushing 108, past valve seat 113, hollow cylindrical member 112, past unseated valve 127 to thebore 82, and also to this bore 82 via the bottomed bore 128 and the choke 131, and thence from the bore 82 through the passageway 110, (5) the chamber 49 (FIG. 1A) from the passageway 182 (FIG. 1B) via the passageway 183, and choke 184, and (6) thechamber 49 from the quick service volume chamber 31 past the disc valve 53 and through the counterbore 51.
It may be noted that the bore 60 in the emergency piston 28 enables both sides of this piston to be subject to the pressure in the quick service volume chamber 31.
Furthermore, fluid under pressure will flow from the quick service volume chamber 31 at a restricted rate determined by the size of the chokes 65 and 70 to: (1) the quick action chamber 69 (FIG. 1C) via the choke 65, chamber 66, choke 70, andpassageway 68, and (2) the chamber 91 from the passageway 68 via the passageway 93.
It will be noted that the chamber 91 is charged with fluid under pressure via the chokes 65 and 70 in series whereas no choke restricts the flow of fluid under pressure from the brake pipe 1 to the chamber 92. Consequently, the pressure in thechamber 92 will build up faster than in the chamber 91 so that the left-hand side of the diaphragm 86 is maintained against the stops 126 so that the valve 127 is held unseated from the seating surface on the left-hand side of valve member 100 to enableflow of fluid under pressure to the passageway 110 past the unseated valve 127 and also through the choke 131 in parallel.
Assuming that no fluid under pressure is present in the brake cylinder 2 (FIG. 1C) at the time the freight car is coupled into the train, there is no flow of fluid under pressure from this brake cylinder 2 to the brake pipe 1 via the emergencyacclerated release check valve device 36 (FIG. 1B) and the emergency accelerated release valve mechanism 35.
SERVICE APPLICATION
A service application of the brakes is initiated by the locomotive engineer moving the handle of the engineer's brake valve device on the locomotive arcuately from its release position to a position in its application zone corresponding to thedegree of brake application desired, whereupon the relay valve device of this brake valve device will effect a gradual reduction in brake pipe pressure at a service rate in the usual well-known manner. The service portion 11 (FIG. 1C) of the brakecontrol valve device 5 will operate in the usual manner of the service portion of heretofore known railway freight car brake control valve devices to effect the supply of fluid under pressure from the auxiliary reservoir 4 to the brake cylinder 2 tocause a service brake application on the freight car provided with this control valve device 5.
As the pressure in the brake pipe 1 is reduced at a service rate, the pressure in the chamber 92 (FIG. 1B) on the right-hand side of the diaphragm 86 will be correspondingly reduced at a service rate.
Since the chokes 65 and 70 restrict the rate of flow of fluid under pressure from the chambers 91 and 66 and quick action chamber 69 (FIG. 1C) to the brake pipe 1, it is apparent that the pressure in the chamber 92 at the right-hand side of thediaphragm 86 is reduced faster than the pressure in the chamber 91 at the left-hand side of this diaphragm 86. Consequently, a differential fluid pressure force is established which acts in the direction to deflect the diaphragm 86 in the direction ofthe right-hand and thereby effect shifting of the stem 81 in this same direction.
As the stem 81 is thus shifted in the direction of the right hand, as viewed in FIG. 1B, the valve 127 on the right-hand end of this stem 81 is shifted into engagement with the resilient seating surface on the left-hand side of the valve member100 to close communication between the brake pipe 1 and the quick service volume chamber 31 except for the restricted communication provided by the choke 131.
As the diaphragm 86 is further deflected in the direction of the right hand, the stem 81, valve 127 and valve member 100 are shifted in the direction of the right hand in response to the increasing differential fluid pressure force. Therefore,the resilient seating surface on the left-hand side of the valve member 100 is unseated from the valve seat 101.
While the resilient seating surfaces on the opposite sides of valve member 100 are unseated from the spaced-apart valve seats 101 and 102, fluid under pressure will flow from the quick service volume chamber 31 (FIG. 1A) to atmosphere viapassageway 110, interior of bore 82 (FIG. 1B), past valve seat 101, ports 109, counterbore 105 and passageway 111.
Since the volume of the chamber 31 is comparatively small, the pressure therein is quickly reduced so that quick action chamber pressure, which is present in the chamber 66 and acting on the left-hand side of the diaphragm-type valve 32, unseatsthis valve 32 from the valve seat 67.
Upon the unseating of diaphragm valve 32 from the valve seat 67, fluid under pressure will flow from the chamber 91 (FIG. 1B) at the left-hand side of the diaphragm 86 and the quick action chamber 69 (FIG. 1C) to atmosphere via passageways 93(FIG. 1B) and 68, choke 70 (FIG. 1A), chamber 66, past seat 67, passageway 117, port 116 (FIG. 1B), groove 118, fluted collar 118, past valve seat 102, ports 109, counterbore 105 and passageway 111.
It will be noted that at this time fluid under pressure will flow from the brake pipe 1 (FIG. 1C) to atmosphere via branch pipe 7, combined cut-out cock and dirt collector 6, passageways 48 and 185, chamber 186, strainer 187, passageway 99,chamber 98, passageway 97 (FIG. 1B), bore 95, the slotted and diametrically arranged bosses 124, the interior of bushing 108, past valve set 113, hollow cylindrical member 112, bottomed bore 128, choke 131, bore 82, past valve seat 101, ports 109,counterbore 105 and passageway 111 at a rate determined by the size of the choke 131. This flow of fluid under pressure from the brake pipe 1 to atmosphere at a rate determined by the size of the choke 131 provides an initial quick service reduction ofthe pressure in the brake pipe 1.
The diameter of the choke 70 (FIG. 1A) is 0.0760 inch, as hereinbefore stated, which size is such that fluid under pressure can now flow from the chamber 91 (FIG. 1B) and the quick action chamber 69 (FIG. 1C) to atmosphere via the pathwaydescribed above faster than fluid under pressure can flow from the chamber 92 (FIG. 1B) and the train brake pipe to atmosphere via the relay valve device of the engineer's brake valve device on the locomotive and from the brake pipe 1 to atmosphere viathe choke 131 in the manner described above. Consequently, when the pressure in the chamber 91 becomes less than that in the chamber 92, a differential fluid pressure force will be established on the diaphragm 86 to deflect this diaphragm in thedirection of the left-hand, as viewed in FIG. 1B. Accordingly, this deflection of the diaphragm 86 in the direction of the left hand is effective to shift the valve stem 81 and valve 127 in this same direction. As the valve 127 is thus shifted in thedirection of the left hand, the spring 120 will shift the valve member 100 in this direction until the resilient seating surface on the left-hand side thereof engages the valve seat 101, it being noted that this seating surface also engages the valve127.
Upon this resilient seating surface on the valve member 100 engaging the valve seat 101, the flow of fluid under pressure from the chamber 92 to atmosphere via the passageway 111 is cut off, it being noted that the flow of fluid under pressurefrom the quick sevice volume chamber 31 (FIG. 1A) to atmosphere past the valve seat 101 is likewise cut off.
It will be noted that fluid under pressure will continue to flow from the chamber 91 (FIG. 1A) to atmosphere via passageways 93 and 68, choke 70, chamber 66, passageway 117, port 116, groove 118, fluted collar 119, past valve seat 102, ports 109,counterbore 105, and passageway 111.
Accordingly, the pressure in the chamber 91 and the quick action chamber 69 (FIG. 1C) will quickly be reduced below the pressure in the chamber 92 (FIG. 1B). Therefore, this pressure in the chamber 92 will establish a differential fluid pressureforce which acts in the direction of the left hand, as viewed in FIG. 1B, on the diaphragm 86.
It is apparent that this differential fluid pressure force deflects the diaphragm 86 in the direction of the left hand which in turn shifts the valve stem 81 and valve 127 in the same direction so that this valve 127 is moved out of seatingengagement with the resilient seating surface on the left-hand side of the valve member 100.
Upon this unseating of the valve 127 from the seating surface on the left-hand side of the valve member 100, fluid under pressure will flow from the brake pipe 1 to the quick service volume chamber 31 via the pathway hereinbefore described, itbeing noted that this pathway includes flow past the unseated valve 127 and through the choke 131 in parallel notwithstanding that fluid under pressure is being released from the train brake pipe to atmosphere via the relay valve device of the engineer'sbrake valve device on the locomotive. Accordingly, the quick service volume chamber 31 will be recharged to the reduced pressure remaining in the train brake pipe.
Fluid under pressure is now flowing from the chamber 91 to atmosphere via choke 70 and the chamber 66, as stated above. Consequently, the supply of fluid under pressure from the brake pipe 1 to the quick service volume chamber 31 to rechargethis chamber will quickly establish a differential fluid pressure force that acts in the direction of the left hand on the diaphragm valve 32 to deflect it into engagement with the valve seat 67.
This engagement of the diaphragm valve 32 with the valve seat 67 cuts off further flow from the chamber 91 (FIG. 1B) and the quick action chamber 69 (FIG. 1C) to atmosphere. Consequently, the remaining fluid under pressure in these chambers istrapped therein.
Since the handle of the engineer's brake valve device is still in the position in its application zone to which it was moved by the locomotive engineer, fluid under pressure continues to be released from the train brake pipe to atmosphere via therelay valve device of the engineer's brake valve device. Consequently, fluid under pressure will continue to flow from the chamber 92 (FIG. 1B) to atmosphere via the passageway 94, bore 95, passageway 97, chamber 98 (FIG. 1C), passageway 99, strainer187, chamber 186, passageways 185 and 48, combined cut-out cock and dirt collector 6, branch pipe 7, the train brake pipe and the relay valve device of the engineer's brake valve device.
When the flow of fluid under pressure from the chamber 92 (FIG. 1B) to atmosphere via the relay valve device of the engineer's brake valve device has reduced the pressure in this chamber 92 to a value less than the trapped pressure in the chamber91 and the quick action chamber 69 (FIG 1C), the continual quick service valve device 34 (FIG. 1B) and the diaphragm valve (FIG. 1A) will operate the cycle hereinbefore described to vent the fluid under pressure in the quick service volume chamber 31(FIG. 1A) to atmosphere, thereafter release fluid under pressure from the chamber 91 (FIG. 1B) and the quick action chamber 69 (FIG. 1C) to atmosphere until the pressure in these chambers is reduced sufficiently to cause the continual quick service valvedevice 34 (FIG. 1B) to effect the recharge of the quick service volume chamber 31 with fluid under pressure from the train brake pipe which fluid under pressure in chamber 31 is effective to cause reseating of the diaphragm valve 32 on the valve seat 67thereby trapping fluid under pressure in the chamber 91 (FIG. 1B) and the quick action chamber 69 (FIG. 1C) to cause the continual quick service valve device 34 (FIG. 1B) and diaphragm valve 32 (FIG. 1A) to again repeat the above-described cycle ofoperation. Therefore, the continual quick service valve device 34 and the diaphragm valve 32 operate in successive repeated cycles to release fluid under pressure from the chambers 31, 69 and 91 to atmosphere and recharge the chamber 31 from the trainbrake pipe during each cycle so long as fluid under pressure is being released from the train brake pipe via the relay valve device of the engineer's brake valve device located on the locomotive.
It should be noted that the repeated recharge of the quick service volume chamber 31 (FIG. 1A) from the train brake pipe effects a local quick service reduction of the pressure in the train brake pipe, and that the repeated release of fluid underpressure from the chamber 91 (FIG. 1B) and the quick action chamber 69 (FIG. 1C) to atmosphere causes the pressure in these chambers to be reduced substantially simultaneously as the pressure in the train brake pipe is reduced when a service brakeapplication is effected, whereby the emergency piston 28 (FIG. 1A) is rendered ineffective to operate the vent valve device 29 to cause an undesired emergency brake application.
It should be understood that when the relay valve device of the engineer's brake valve device has released fluid under pressure from the train brake pipe to atmosphere until the pressure in the train brake pipe has been reduced to a valuecorresponding to the position in its application zone to which the handle of the brake valve device was moved by the engineer, this relay valve device will cease to release fluid under pressure from the train brake pipe and, therefore, from the chamber92 (FIG. 1B) in the continual quick service valve device 34.
Moreover, it should be further understood that upon the termination of the release of fluid under pressure from the chamber 92 and the train brake pipe to atmosphere via the relay valve device of the engineer's brake valve device, the continualquick service valve device 34 and the diaphragm valve 32 will cease to operate in cycles to release fluid under pressure from the train brake pipe to atmosphere to cause a local quick service reduction of the pressure of the fluid in the train brakepipe.
SERVICE LAP
When the relay valve device of the engineer's brake valve device terminates the release of fluid under pressure from the train brake pipe, the release of fluid under pressure from the chamber 92 (FIG. 1B) is likewise terminated, whereupon thecontinual quick service valve device 34 and the diaphragm valve 32 cease to operate in successive cycles to release fluid under pressure from the train brake pipe and the quick action chamber 69 (FIG. 1C) to atmosphere.
Furthermore, when the release of fluid under pressure from the train brake pipe, and, therefore, the brake pipe 1 (FIG. 1C) is terminated, the service valve device 11 will move to a lap position to cut off flow of fluid under pressure from theauxiliary reservoir 4 to the brake cylinder 2.
EMERGENCY APPLICATION
To effect an emergency application of the brakes, fluid under pressure is suddenly vented at a rapid rate from the brake pipe 1. Upon this rapid rate of reduction of pressure in the brake pipe 1, the service valve device 11 will operate tosupply fluid under pressure from the auxiliary reservoir 4 (FIG. 1C) to the passageway 80 (FIG. 1B).
Moreover, the emergency valve device 12 operates in the manner explained above to release fluid under pressure from the chamber 91 and quick action chamber 69 (FIG. 1C) to atmosphere via the choke 70 (FIG. 1A). This rate of release of fluidunder pressure from the chamber 91 (FIG. 1B) on the left-hand side of diaphragm 86 is less than the emergency rate of release of fluid under pressure from the chamber 92 on the right-hand side of this diaphragm 86 via the brake pipe 1 and the train brakepipe.
Therefore, it is apparent that a differential of pressure is quickly established on the diaphragm 86 which acts in the direction of the right hand to deflect this diaphragm in this same direction and thereby shift the stem 81, valve 127 and valvemember 100 toward the right.
As the stem 81 and valve member 100 are thus further shifted in the direction of the right hand, the seating surface on the right-hand side of the valve member 100 will be seated on the valve seat 102.
Upon this seating of the valve member 100 on valve seat 102, fluid under pressure will no longer flow from the chamber 91 at the left-hand side of the diaphragm 86 and the quick action chamber 69 (FIG. 1C) to atmosphere via passageways 93 (FIG.1B) and 68, choke 70 (FIG. 1A) and the pathway described above. However, fluid under pressure may flow from the chamber 91 (FIG. 1B) and the quick action chamber 69 (FIG. 1C) to atmosphere at a restricted rate via passageways 93 (FIG. 1B) and 68, choke70 (FIG. 1A), chamber 66, passageway 117, port 116 (FIG. 1B), groove 118, fluted collar 119, quick action chamber blowdown choke 132, counterbores 133 and 105 and passageway 111. This restricted flow of fluid under pressure from the chamber 66 (FIG. 1A)to atmosphere causes a buildup of pressure in this chamber which acts on the entire effective area of the left-hand side of the diaphragm valve 32 to shift this diaphragm valve 32 and the emergency piston 28 in the direction of the right hand, as viewedin FIG. 1A, against the yielding resistance of the spring 58 to an emergency position in which the disc valve 53 is unseated from its seat 52 by the fluted stem 54, and the valve 71 is unseated from its seat 72 by the stem 77 and shifted in the directionof the right hand, as viewed in FIG. 1A, until this valve 71 abuts the second cover member 40.
Upon the unseating of the valve 53 from its seat 52, fluid under pressure in the chamber 49 will flow to atmosphere via hollow spring seat 56, counterbore 51, past valve seat 52, bore 50, chamber 31, passageway 110, bore 82 (FIG. 1B), past valveseat 101, ports 109, counterbore 105 and passageway 111.
Brake pipe pressure which is present in the chamber 46 (FIG. 1A) will now unseat diaphragm 39 from valve seat 42.
Fluid under pressure will now flow from the brake pipe 1 and the train brake pipe to atmosphere via the bore 41 of large diameter for the purpose of serially transmitting an emergency rate of reduction of pressure in the train brake pipeextending through the train in the usual well-known manner.
As the stem 77 is shifted in the direction of the right hand, the O-ring seal 78 on the stem 77 is moved to a position in which it forms a seal with the wall surface of the bore 74 at a location that is on the left-hand side of the location atwhich the hereinbefore-mentioned one end of the passageway 80 opens at the wall surface of this bore 74. Therefore, fluid under pressure will flow from the emergency reservoir 3 (FIG. 1C) to the passageway 80 (FIG. 1A) via pipe and passageway 76,chamber 75, past valve seat 75 and groove 79. Fluid under pressure thus supplied to the passageway 80 from the emergency reservoir 3 combines with that supplied to this passageway 80 from the auxiliary reservoir 4 by operation of the service valvedevice 11 and flows therefrom to the passageway 161 (FIG. 1B) and thence to a pressure chamber (not shown) within the brake cylinder 2 (FIG. 1C) via a chamber 188 (FIG. 1B) and a passageway 189 in the inshot valve device 38, the chamber 155, past thevalve 154 which is unseated from the valve seat 157, the bore 158, chamber 159, and passageway and pipe 160.
The fluid under pressure thus supplied to the pressure chamber within cylinder 2 will act on one side of the piston (not shown) therein and move this piston outward against the yielding resistance of the brake cylinder release spring (not shown)that acts on the other side of this piston. As this piston is thus moved, it increases the volume of the pressure chamber to which fluid under pressure is being supplied from the chamber 159 (FIG. 1B) below the abutment 164.
It will be noted that when an emergency brake application is made, all fluid under pressure is vented from the chambers 168 and 170 on the left-hand side of the abutment 164. Therefore, as the pressure in the chamber 168 is reduced to zero, thisabutment 164 is deflected in the direction of the left hand by the spring 156 acting through the valve 154, a fluted stem 154a and the disc 165 until the abutment 164 engages valve seat 179 on the right-hand end of the valve seat member 178.
The spring 156 continues to deflect the abutment 164 in the direction of the left hand to shift the valve seat member 178 in this direction against the yielding resistance of the spring 181 until the abutment 164 is moved into abuttingrelationship with the right-hand end of the spring seat member 172, the out-turned flange 173 of which is biased against the shoulder 174 by the spring 176 which, as hereinbefore stated, is stronger than the spring 156. The length of the fluted stem154a is such that the disc valve 154 is still unseated from the valve seat 157.
Consequently, the fluid under pressure supplied to the passageway 161 will flow through the choke 162 and passageway 163 to the passageway 160 and also to this passageway 160 via the chamber 188, passageway 189, chamber 155, past the valve seat157, between the fluted valve stem 154a and the wall of the bore 158 and the chamber 159. Therefore, fluid under pressure is supplied from the passageway 161 to the passageway and pipe 160 which is connected to the brake cylinder 2 via the choke 162 andthe bore 158 in parallel until the pressure in the chamber 159 on the right-hand side of the abutment 164 is increased sufficiently to overcome the yielding resistance of the two springs 181 and 176.
The strength of the two springs 181 and 176 may be so selected that when the pressure in the chamber 159 is increased to a chosen value, such as, for example, fifteen pounds per square inch, the abutment 164 will be deflected in the direction ofthe left hand against the yielding resistance of the springs 176 and 181 whereupon the spring 156 will shift the valve 154 into seating engagement with the valve seat 157 thereby closing off the rapid flow of fluid under pressure to the brake cylinder 2by way of the annular valve seat 157. With the valve 154 thus seated on valve seat 157, fluid under pressure continues to flow from the passageway 161 to the brake cylinder 2 (FIG. 1C) via the chamber 188, choke 162 (FIG. 1B), passageway 163 andpassageway and pipe 160 (FIGS. 1B and 1C), the choke 162 forming a by-pass communication around the valve 154 which is now seated on the valve seat 157. The choke 162 provides for the second stage of increase in brake cylinder pressure at a slower rate. The pressure in the brake cylinder 2 will now continue to build up at this slower rate determined by the size of the choke 162 until equalization of the pressure in the auxiliary reservoir 4, emergency reservoir 3 and brake cylinder 2 occurs.
From the foregoing, it is apparent that the emergency valve device 12 of the brake control valve device 5 provides a two-stage buildup of pressure in the brake cylinder 2.
Since fluid under pressure is supplied from both the auxiliary reservoir 4 and the emergency reservoir 3 to the brake cylinder 2 when an emergency brake application is effected, it is apparent that a higher pressure is obtained in the brakecylinder 2 than is the case when a service brake application is effected.
It will be noted that the fluid under pressure trapped in the chamber 91 (FIG. 1B) on the left-hand side of diaphragm 86 and in the quick action chamber 69 (FIG. 1C) upon seating of the seating surface on the right-hand side of valve member 100on valve seat 102 in the manner described above may flow to the atmosphere via the passageways 93 and 68, choke 70, chamber 66, passageway 117, port 116, groove 118, fluted collar 119, choke 132, counterbore 133, counterbore 105 and passageway 111.
As hereinbefore stated, when an emergency brake application is effected, the diaphragm valve 32 and the emergency piston 28 are shifted in the direction of the right hand by quick action chamber pressure present in the chamber 66 to unseat valve53 from its seat 52 to release fluid under pressure from the chamber 49 to atmosphere to cause unseating of the vent valve diaphragm 39 from its seat 42 by brake pipe pressure in the chamber 46. This vent valve diaphragm 39 cannot be reseated on itsseat 42 as long as the chamber 49 is open to atmosphere past the valve 53 which is held unseated from its seat 52 by the emergency piston 28 and diaphragm valve 32 that is subject on its right hand side to quick action chamber pressure in the chamber 66.
It being noted, as explained above, that fluid under pressure is being released from the quick action chamber to atmosphere via the chokes 70 and 132 in series, it is apparent that the size of these chokes determine how long the vent valvediaphragm 39 remains unseated from its seat 42. Accordingly, the size of the chokes 70 and 132 is so selected as to prevent the spring 43 from reseating the vent valve diaphragm 39 on its seat 42 until a sufficient period of time has elapsed as isnecessary for the emergency brake application to bring the train to a stop.
When all fluid under pressure is released from the quick action chamber 69 (FIG. 1C) and the brake pipe 1 and, therefore, from the chambers 91 (FIG. 1B) and 92 (FIG. 1B), the diaphragm 86, stem 81 and valve 127 thereon and diaphragm valve 32 willbe returned to the position shown in FIGS. 1B and 1A by the resiliency of the diaphragm 86 and the diaphragm valve 32.
RELEASE OF THE BRAKES AFTER AN EMERGENCY APPLICATION
To effect a release of the brakes after an emergency application, fluid under pressure is supplied to the brake pipe 1 from whence it flows to the chamber 92 on the right-hand side of diaphragm 86 (FIG. 1B), the quick service volume chamber 31 onthe right-hand side of the diaphragm valve 32 (FIG. 1A) and the chamber 170 on the left-hand side of the abutment 164 (FIG. 1B).
Moreover, fluid under pressure flows from the brake pipe 1 to the chamber 16 (FIG. 1C) above the diaphragm 15 in the service valve device 11 at a restricted rate determined by the size of a choke 190.
It will be noted from FIGS. 1A and 1B of the drawings that fluid under pressure flows at an unrestricted rate to the chambers 92 and 31 in the emergency valve device 12 since there are no chokes in the passageways 97, 94 and 110.
Furthermore, it will be noted from FIG. 1A that the chokes 65 and 70 restrict the rate of flow of fluid under pressure from the quick service volume chamber 31 to the chamber 66, the chamber 91 on the left-hand side of the diaphragm 86, and thequick action chamber 69 (FIG. 1C). Accordingly, it is apparent that the pressure in the chamber 92 on the right-hand side of the diaphragm 86 (FIG. 1B) will increase more rapidly than will the pressure in the chamber 91 on the left-hand side of thisdiaphragm.
Moreover, it is apparent that the more rapid rate of increase of pressure in the chamber 92 quickly establishes a fluid pressure differential force which is effective to deflect the diaphragm 86 in the direction of the left hand, as viewed inFIG. 1B, and shift the valve stem 81 in this same direction.
As the valve stem 81 is thus shifted in the direction of the left hand, collar 143 thereon first abuts the annular member 142 and thereafter, via the sleeve member 141 that is integral with the piston valve member 136, shifts this piston valvemember 136 in the direction of the left hand against the yielding resistance of spring 137 to unseat valve member 136 from valve seat 134, it being noted that the spring seat 138 limits the distance that the piston valve member 136 may be shifted in thedirection of the left hand.
When the piston valve member 136 is thus unseated from its seat 134, fluid under pressure will flow from the brake cylinder 2 (FIG. 1C), and the auxiliary reservoir 4 connected thereto via the service valve device 11 which is still in its serviceapplication position to the brake pipe 1 via pipe and passageway 160, chamber 159 (FIG. 1B), past valve seat 157 and through choke 162, chamber 155, passageways 189, 161, and 147, past valve seat 144, check valve 145 being unseated against the yieldingresistance of the spring 146, chamber 148, passageway 149, chamber 150, past valve seat 134, through sleeve member 141 of valve member 136, chamber 92, passageway 94, bore 95, passageway 97, chamber 98 (FIG. 1C), passageway 99, strainer device 187,chamber 186, the passageway 185 and 48 in the pipe bracket 8, combined cut-out cock and dirt collector 6 and branch pipe 7.
The above-mentioned flow of fluid under pressure from the brake cylinder 2 and auxiliary reservoir 4 to the brake pipe 1 acclerates the rate of recharge of the brake pipe. This action naturally occurs first at the head end of the train when theincrease in brake pipe pressure is first effected, and the sudden increase in brake pipe pressure on one car causes the emergency valve device on the next car to function in the same manner, so that this back dump operation is rapidly transmittedserially from car to car throughout the length of the train.
It will be noted from FIG. 1B that some of the fluid under pressure supplied from the brake cylinder 2 and auxiliary reservoir 4 to the passageway 94, in the manner described above, flows from this passageway 94 to the quick service volumechamber 31 and chamber 49 (FIG. 1A) via bore 95, the slotted and diametrically arranged bosses 124, interior of bushing 108, past valve seat 113, hollow cylindrical member 112, past now unseated valve 127 to the bore 82, and also to this bore 82 via thebottomed bore 128 and choke 131, and passageway 110.
As the pressure in the quick service volume chamber 31 increases, the diaphragm valve 32 will be deflected in the direction of the left hand into seating engagement with the valve seat 67.
As the diaphragm valve 32 is thus deflected in the direction of the left hand by the increasing pressure in the quick service volume chamber 31, the spring 58 shifts the emergency piston 28 in this direction which allows spring 55 to seat valve53 on its seat 52 and the spring 73 to seat valve 71 on its seat 72 subsequent to the chambers 31 and 49 becoming charged to the normal fully charged pressure carried in the train brake pipe.
Subsequent to the seating of diaphragm valve 32 on the valve seat 67, fluid under pressure will flow from the quick service volume chamber 31 to the chamber 91 (FIG. 1B) and the quick action chamber 69 (FIG. 1C) via choke 65, chamber 66, choke70, and passageways 68 and 93 until these chambers are charged to the pressure carried in the train brake pipe.
As the pressure in the chamber 91 (FIG. 1B) is thus charged to the pressure in the train brake pipe and in the chamber 92 on the opposite side of the diaphragm 86, the spring 137 is rendered effective to shift valve member 136, collar 143 andstem 82 in the direction of the right hand until the valve member 136 engages the valve seat 134.
The elements of the continual quick service valve device 34, the emergency accelerated release valve mechanism 35, the vent valve device 29, the high pressure valve device 30 and diaphragm valve 32 now occupy their release position in which theyare shown in FIGS. 1A and 1B.
As fluid under pressure is supplied to the chamber 16 (FIG. 1C) in the manner described above, the resulting increase in pressure in this chamber 16 will deflect the diaphragm 15 downward to thereby return the graduating valve 19 and the servicevalve 20 of the service valve device 11 to the position shown. The fluid under pressure now remaining in the brake cylinder 2 will flow to atmosphere via pipe and passageway 160, chamber 159 (FIG. 1B), past valve seat 157, bore 158, choke 162 inparallel therewith, chamber 155, passageways 189, 161, 80 and passageways and ports in the service valve device 11 it being understood that these passageways and ports correspond to ports and passageways in the service valve device 7 of the brake controlvalve device 1 shown in hereinbefore-mentioned U.S. Pat. No. 3,232,678 through which fluid under pressure may flow from the brake cylinder 7 shown in this patent to atmosphere.
With the release of all fluid under pressure from the brake cylinder 2 (FIG. 1C), the brakes on the car will be completely released.
Furthermore, the emergency reservoir 3 and the auxiliary reservoir 4 will now be charged from the brake pipe 1 to the normal fully charged train brake pipe pressure.
DESCRIPTION - FIG. 2
In FIG. 2 of the drawings, there is shown a partial diagrammatic view, in vertical cross section, of a portion of a continual quick service valve device 191 constructed in accordance with a second embodiment of the invention. According to thissecond embodiment of the invention, the other elements comprising the continual quick service valve device 191 are identical to those of the continual quick service valve device 34 shown in FIG. 1B.
Moreover, it should be understood that this continual quick service valve device 191 may be substi | | | |
