US955788A

US955788A - Air-brake.

Info

Publication number: US955788A
Application number: US52303609A
Authority: US
Inventors: Charles W Frye
Original assignee: ALBERT H COCHRAN SR; JOSEPH E TURNER
Current assignee: ALBERT H COCHRAN SR; JOSEPH E TURNER
Priority date: 1909-10-16
Filing date: 1909-10-16
Publication date: 1910-04-19
Anticipated expiration: 1927-04-19

Description

G. W. FRYB.

AIR BRAKE.

APPLICATION nun 0011a, 1909.

Patented Apr. 19,1910.

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mvmdtoz Wit 0. W. FRYE.

AIR BRAKE.

APPLICATION TILED OCT. 16, 1909. I 955,788. Patented Apr. 19, 1910.

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CHARLES W. FRY E, OF ATLANTA, GEORGIA, ASSIGNOR OF ONE-THIRD TO ALBERT H. GOCHRAN, SR, AND ONE-THIRD TO JOSEPH E. TURNER, BOTH OF ATLANTA,

GEORGIA.

AIR-BRAKE.

To all whom it may concern:

Be it known that I, CHARLES IV. Farm, a citizen of the United States, residing in Atlanta, in the county of Fulton and State of Georgia, have invented certain new and useful Improvements in Air-Brakes, of which the following is a specification.

My invention relates particularly to air brakes ot' the kind known as the \Vestinghouse system, in which the brakes are normally held in a released position by compressed air supplied by the engine; are applied by a diminution of pressure in the train pipe connecting the brake mechanism with the engine and are then released by increasing this pressure. The invention is however applicable to other brake systems.

It is quite common to connect two or more engines to a train when the train is long or the burden is great and in such cases it is advisable that the brake system should be under the exclusive control of the engineman of the first or leading engine, so that he alone can apply or release the brakes. Special valve mechanism, known as doubleheader valves, have been employed for this purpose and such valves have been so constructed and arranged that the engineman of the first engine only can control the application and release of the brakes, and the arrangement has also been such that the brake equipment of the second or following engine can, under the control of the engineman of the first engine, assist in recharging the train pipe to release the brakes and bring the train pipe pressure to normal.

My invention relates to double-header valve mechanisms and systems of this kind and my object is to simplify and improve such mechanism in such manner that when the brake equipments of two engines are connected and the direct connection between the engineefis valve and the train pipe is closed on the second engine, the connection between the train pipe and the double'header valve on the second engine will be automatically closed when the brakes are applied, will be automatically opened when the brakes are released to aid in charging the train pipe, and will then be again disconnected to allow the first engine to keep up the normal or proper pressure; the mechanism also being so arranged that in. case of emergency the engineman of the second engine can apply the brakes.

Specification of Letters Patent.

Application filed October 16, 1909.

Patented Apr. 19, 1910.

Serial No. 523,036.

. In the accompanying drawings :Figure 1 is a diagram, showing my double-header valve system applied to two engines, but it will be understood that it can be applied when more than two engines are coupled together. Fig. 2 shows a vertical central section through one of my double-header valves, the parts being in the position they occupy when the brakes are released and the pressure in the train pipe is normal. Fig. 3 is a similar view, with the parts in the position they assume when the brakes are applied.

It will be understood that each engine is provided with a double-header valve properly connected in the b 'ake system and that when one engine only is used the doubleheader valve devices do not interfere in any way with the operation of the brakes. l Vhcu two or more engines are coupled to the same train, the direct connection between the engineer's valve and the train pipe is left open on the first or leading engine while on the other engine or engines this connection is closed.

In Fig. 1 the main reservoir A on each engine is shown as being connected as usual by a pipe B with an enginee1"s valve C of the ordinary kind and provided with an equalizing reservoir 0, as usual, and the enginecrs valve is connected by a pipe D with the train pipe E. Each pipe D is provided with a cock F between the train pipe and the engineers valve. When running double-heade1" the cock F on the first or leading engine is left open, while the cock F on the following engine is closed.

In Fig. 1 my doubleheader valve is shown at G. It is connected by a pipe H with the pipe I) between the cock I and the engineers valve and by a pipe I with the pipe 1) between the cock I and the train pipe. The doublc-hezulcr valve G may be placed on any convenient part of the engine, the pipes H and I being made of suitable length to connect the valve with the pipe I), in the manner be't'ore described. Each doubleheader valve is prc't'eralfly constructed in the manner shown in l igs. 2 and 3. The casing K of the main slide valve J is formed at its front end with a chamber ll; T01 the piston L and with a chamber Z2 for the slide valve J. These two chambers communicate and are closed at the rear end by the solid wall 7c of the casing and at the front end by a removable cap is.

The piston L has a rod Z, carrying at its rear end a yoke m 111 which is arranged a valve M. The rod Z lies in a groove in the pipe E by a passage 6 in the cap which connects with the pipe I, communicating with the pipe D in turn connected with the train pipe. The forward movement of the piston is limited by the cap 70 and its rearward movement is limited by a flange Z against which the piston abuts. The piston is formed with a hub Z which is adapted to strike against the front end of the slide Valve J, and thus limit the rearward movement of the piston relatively to the valve, while the forward movement of the piston relatively to the slide valve is limited by the valve M which then rests against its seat.

A plunger N is seated in a recess in the rear wall of the casing K and projects forward in the chamber is. A cap N on the .outside of the casing closes this recess and contains a spring a, engaging a flange n on the plunger and normally pressing it forward. WV hen the piston L is by high pressure moved to its rearmost position, the yoke m abuts against the plunger N and presses it rearward, but when the pressure is released or the pressure on opposite sides of the piston is equalized the spring a presses the piston forward to a limited ex tent and thus seats the valve M, the parts then occupying the position shown in Fig. 2 which is the normal running position of the mechanism. 7

To the underside of the casing K is secured the casing O of the auxiliary valve P. This casing is formed with two chambers O, O the rear casing 0 being connected by a passage 0 with the rear end of the chamber is, while the front chamber 0 is connected by

passages

0, 0 with the chamber 7c near its middle portion.

The valve P, which is in the form of a rod, carries a piston 29 located in the chamber O and the piston and rod are pressed rearward by a spring 20 The rear end of the rod is beveled to form a valve which fits a valve seat at the inner end of a passage it communicating with the pipe H leading to the pipe D, which is in turn connected with the engineers valve or with the main reservoir. In the passage 71, there is a check valve Q that is pressed towardits seat by a spring 9.

The casing K is formed with a passage R, leading from the passage 6 rearward and communicating with a lateral passage 1" communicating with the chamber 70 at its rear portion, while a passage 1 connects the front portion of this chamber with the passage An exhaust passage 6 between the passages 1" and 1" connects the chamber is with the atmosphere.

The slide valve J is formed with a recess 8, adapted to connect the passages r and 0 or the passage 0 and the exhaust passage 23 and this valve is also formed with a recess 8, adapted to connect the passages 1" and 0 or the passage 0 and the exhaust passage t. The recess 8 communicates with a passage a, which joins a port U, leading through the side of the slide valve and communicating with the chamber 70 and this passage to contains the valve M which controls the port U.

The piston L may be provided with suitable packing, as indicated at 'w, and the chambers in which the pistons and valves operate may have suitable bushings, as

shown. The bushing for the piston L is formed with a recess a: whereby when the piston is in its foremost position, as shown in Fig. 3, the pressure on .opposite sides thereof may be automatically equalized.

It will be understood that the engineers valve of the second engine is always placed at running position, except in cases of emergency, as hereinafter explained.

When the brakes are released and the train pipe pressure is normal, as while running, the parts of the double-header valve are in the position shown in Fig. 2 where the piston L is pressed back by the high train pipe pressure and holds the slide valve in such position that the chamber 0 in front of the piston 9 of the auxiliary valve connects with the exhaust by way of the passage 0 recess 8 and passage t, while the chamber 0, in rear of the piston p, connects with the train pipe by way of the passage 0, recess 8 and passages 7", R, 6, etc. At this time the valve P is open, but the valve Q is closed as the pressure on the valve from the inside of the double-header valve and the spring pressure is sufiicient to close it. Furthermore the communication between the main reservoir of the second engine and the train pipe is cut off by the valve M, which at this time closes the port U.

I would here remark that when the connection between the double-header valve and the main reservoir is made by the usual engineers valve having the usual pressure-reducing device the valve Q, may be omitted, but when a direct connection is made between the double-header valve and the main reservoir, or where the engineers Valve is not provided with pressure-reducing devices, I prefer to employ a reducing valve Q of the kind shown.

l/Vhen the pressure in the train pipe is relieved by the engineman of the first engine to apply the brakes, the parts of the doubleheader valve on the second engine assume the position shownin Fig. 3; that is to say, the pressure in the chamber is in front of the piston L being reduced, the pressure behind this piston will cause it to move forward to the position shown in Fig. 3, and when the parts are in this position the valve M remains closed, the passage 1' is covered by the slide valve J and communication of the rear portion of the chamber 0 with the exhaust passage t is established by way of the passage 0 and the recess 8. At the same time communication is established between the front portion of the chamber 0 and the passage R by way of the passage 0 the recess s and the passage 1'. When the parts are thus moved the spring p and the reduced train pipe pressure causes the piston p to move rearward and close the valve P on to its seat 72 Thus communication between the main reservoir of the second engine and the train pipe is cut off at three points, namely, by the valve P, the valve M and that part of the slide valve J which covers the passage r. Even should one of the valves leak the passage of air from the main reservoir of the second engine to the train pipe would be prevented by the other valves, and thus it is impossible for the engineman of the second engine to release the brakes while being applied at the first engine as long as the cock F on the'second engine is closed.

' After the brakes have been thus applied the engineman of the first engine can release them by operating his engineers valve to increase the pressure in the train pipe. This increased pressure, acting on the piston L (when in the position shown in Fig. 3) will first cause the piston L, its rod Z and the yoke m with the valve M, to move rearward to a limited extent without moving the slide valve J. By this movement the valve M is opened but the passage 1" remains closed. Some of the air in the chamber is can pass out through the port U, recess a and exhaust 25, thus reducing the pressure on the valve Q, and some of the air will pass through the passage 0 into the front end of the chamber 0 and tend to open the valve P. As the piston L moves farther rearward the valve J is also moved, and the passage 1" is uncovered and the valves Q and P then open and air under pressure from the main reservoir of the second engine can pass by way of the passage h, chamber 0, passage 0, the port U and the passage 1' to the train pipe, and thus the second engine assists in charging the train pipe and in bringing the pressure therein up to normal, all this being done without any attention from the engineman of the second engine but it is done automatically whenever the engineman of the first engine operates his engineers valve to charge the train pipes. After the pressure has been equalized on both sides of the piston L and the train pipe pressure is reduced at the leading engine the spring a causes the plunger N to be moved forward and to move the piston L forward to a limited extent until it assumes the position shown in Fig. 2, at which time the valve M closes the port U, thus cutting off communication from the main reservoir of the second engine and the train pipe after the train pipe has been charged, and when the engines are running, or are in running condition. When the parts are in the position shown in Fig. 2, the valve Q is closed, inasmuch as the spring assisted by the pressure in the chamber g), is sufficient to overcome the pressure from the main reservoir of the second engine, but when the pressure in the chamber 0 is reduced, as when the valve M is open, then the spring 9 is not sufficient to hold the valve Q closed, and air can enter the chamber 0, in the manner be fore described.

This valve mechanism. can be applied to brake systems already in use. Ordinary engineers valves can be employed which may be set to running, service, release, lap, or any other usual position on the first engine and the engineman of the second engine cannot possibly interfere when the first engine is applying the brakes without turning the cock F to an open position. then he does this he can either apply or release the brakes, but as it is natural only for the enginen'ian to grasp the handle of the engineers valve C it is not at all probable that he would open this cock without taking time to realize the situation and to only open the cock in case of emergency.

I t will be understood that the brake mechanisms on both engines are to be equipped with proper pressure gages so that both enginemen can know the condition of the pressure in the train pipe and in his own main reservoir.

1 claim as my invention:

1. In an automatic air brake system, the combination with a train pipe and an air reservoir of a double-header valve operated by a reduction in train pipe pressure when the b'akes are applied, which, while the brakes are applied, cuts off communication between the main reservoir with which it is connected and the train pipe, which, when the b 'akes are released, first opens communication between the main reservoir with which it is connected and the train pipe, and then after the train pipe pressure is equalized and subsequently reduced by the leading engine auton'iatically closes this connection.

2. A double-header valve, comprising a valve chamber, a piston operating therein, a connection between said chamber on one side of the iston and the train pipe, a slide valve controfiing the connection between the valve chamber on the opposite side of the piston and the train pipe, a valve connected with the piston and having a limited movement independently of the slide valve for also controlling the connection between the valve chamber on one side of the piston and the train pipe, and an auxiliary'valve for closing the connection between the main reservoir and the valve chamber in rear of the piston and the opening and closing of which is controlled by the movement of said slide valve.

3. A double-header valve, comprising a valve casing, a piston chamber therein, a slide valve chamber in rear .of said piston chamber, a piston, a slide valve connected to move therewith, a valve connected with the piston and having a limited movement independently of the slide valve, a connection between the front end of the piston chamber and the train pipe, a connection between the valve chamber in rear of the piston and the main reservoir, and a valve for opening and closing this last mentioned connection which is controlled by the movement of the slide valve.

4. A double-header valve, comprising a valve casing, having a piston chamber and a slide valve chamber, a piston operating in the piston chamber, a slide valve operating in the slide valve chamber, a valve connected with the piston and having a limited movement independently of the slide valve and which controls a port therein, a connection between the front end of the piston chamber and the train pipe, a connection between the rear end of the slide valve chamber and the main reservoir, a spring-pressed valve for opening and closing this connection, and another valve for opening and closing this connection controlled by the movement of the slide valve.

5. A double-header valve, comprising a valve casing having a piston chamber and a slide valve chamber, a piston operating in the piston chamber, a slide valve operating in the slide valve chamber, a connection between the front end of the piston chamber and the train pipe, a connection between the rear end of the slide valve chamber and the main reservoir, a chambered auxiliary valve casing, a valve carrying a piston operating in a chamber of this casing and which is adapted to close communication between the reservoir and the slide valve chamber, passages connecting said chamber on opposite sides of the piston with the slide valve chamber, connections between the train pipe and the slide valve chamber, and an exhaust passage controlled by the slide valve and which may be brought into communication with the chamber of the auxiliary valve either in front of its piston or in rear thereof, said slide valve being also adapted to open communication between the train pipe and the front end of the chamber of the auxiliary valve and to open communication between the train pipe and the slide valve chamber.

6, A double-header valve, comprising a valve casing having a piston chamber and a slide valve chamber a piston operating in the piston chamber, a slide valve operating in the slide valve chamber, a connection between the piston chamber and the train pipe, a connection between the slide valve chamber and the reservoir, a valve controlled by the movements of the slide valve for opening and closing the communication between the slide valve chamber and the reservoir, and a spring-controlled valve interposed between j the last-mentioned valve and the reservoir.

7. In an air brake system, double-header valve mechanism operated by a reduction in train pipe pressure when the brakes are applied and which normally while in running position cuts ofl communication between the main reservoir and the train pipe, which, when the pressure is reduced in the train pipe cuts .ofi communication between the main reservoir and the train pipe by a plurality .of valves, and which, when the pressure in the train pipe is raised at first admits air from the main reservoir to the train'pipe to assist in charging the train pipe but which subsequently, when the train pipe pressure is equalized and afterward reduced at the leadingengine, cuts off communication between the main reservoir and the train pipe.

8. A double-header valve, comprising a valve chamber, a piston operating therein, a groove or recess to permit air in the piston chamber to equalize in front and rear of the piston, a connection between the air chamber on one side of the piston and the train pipe, a

a slide valve controlling the connection between the valve chamber on the opposite side of the piston and the train pipe, a valve connected with the piston and having a limited movement independently of the slide valve for also controlling the connection between the valve chamber on one side of the piston and the train pipe, a spring-pressed plunger in rear of the slide valve and operating to close said independently moving valve, and

an auxiliary valve for closing the connection between the main reservoir and the valve chamber in rear of the piston, and the opening and closing of which is controlled by the movement of said slide valve.

In testimony whereof, I have hereunto subscribed my name.

CHARLES l/V. FRYE. Witnesses:

J OHN C. KNAIP, A. B. HARGRAVE.