JPH0526048B2 - - Google Patents

Abstract

PURPOSE:To reduce a manual unfastening control force, by a method wherein an inner surface (a first surface) making contact with a ball in the clutch engaging rotation position of a control member is formed in a slope inclined toward the inner surface (a second surface) of a recessed part allowing external displacement of a ball in the clutch disengaging rotation position of the control member. CONSTITUTION:A first surface 32 makes contact with a ball 11 when a control member 31 is situated in a clutch engaging rotation position. The first surface is formed in a slope inclined toward a recessed second surface 23 allowing displacement of the ball 11 to an external position where a press rod 2 is disengaged from a ball engaging recessed part 13 when the control member 31 is rotated to a clutch disengaging position. Thus, an enlargement force is exerted on the ball 11. With the handle of a manual release means 41 pulled outwardly, a claw engaged with a engaging part 47 of a clutch 42 is disengaged, and the control member 31 is rotated by means of a rotation force generated by the enlargement force to bring 8 clutch 30 into a disengaged state. This constitution displaces the press rod 2 leftward, and causes release of a brake force.

Description

[Detailed Description of the Invention] <Industrial Application Field> The present invention relates to a spring brake cylinder used in a railway vehicle, for example, for parking.
In particular, the present invention relates to a device having a manual release mechanism for manually releasing the spring brake force during operation.

<Conventional technology> As a conventional technology of this type, there is
There is one described in Publication No. 227848. The outline is explained in the 6th section.
This will be explained using FIGS. 8 to 8. This spring brake cylinder 1 is used by connecting a push rod 2 to a lever of a brake device (not shown). Normally, during operation, pressurized air is supplied into the pneumatic chamber 3 from the supply/discharge port 4, so the piston 6 moves to the left against the brake spring 5 from the state shown in FIG. However, when the spring brake by the spring brake cylinder 1 is applied, the air pressure chamber 3
Since the pressurized air inside is discharged, the state approximately shown in FIG. 6 is obtained. In this state, the clutch 7 is in a connected state, the push rod 2 is retracted into the cylinder body 8, and the lever is swung in a predetermined direction to act as a spring brake. When releasing this spring brake manually, the handle 15 shown in FIG.
When the clutch 7 is pulled out to the side, the clutch 7 changes from the illustrated connected state to the disconnected state.

To explain this clutch 7, the clutch 7 connects and disconnects the piston 6 and the push rod 2 for axial movement, and is held in a circular hole 9 bored in the cylindrical portion 10 of the piston 6. It consists of a ball 11, a control member 12 that controls the position of the ball 11, and a recess 13 provided in the push rod 2 with which the ball 11 engages. For manually disengaging the clutch 7, an actuating member 14 is provided in conjunction with the control member 12. Operation member 14
As shown in FIG.
An operating member 14 is installed along a cross section perpendicular to the axis of the cylinder body 8 between an end wall 18 and an end member 19 within the accommodation portion 20 so as to be movable back and forth together with a return spring 21.

When the handle 15 is pulled out to the side from the illustrated clutch engaged state, the pawl 17 rotates the control member 12 by a predetermined angle, so that the control member 12 shown in FIG.
The recess 23 provided on the inner surface 22 of the ball 11
will be located outside of. Since a tensile force by the brake spring 5 is acting between the push rod 2 and the cylindrical portion 10 of the piston 6, the ball 11 is pushed out from the recess 13 of the push rod 2 toward the recess 23, and
The clutch becomes disengaged. As a result, the push rod 2 is released from its connection to the piston 6 and moves to the left in FIG. Along with the movement, the second
The piston 24 is moved by the spring 25 to the position of the ball 11, and the hole 9 is closed so that the ball 11 does not fall inside the cylindrical part 10. This state is the state in which the spring brake is manually loosened.

<Problems to be Solved by the Invention> The spring brake cylinder is equipped with a mechanism for manually releasing the brake when the brake is applied and a parked vehicle needs to be moved quickly. is necessary. However, in railway vehicles equipped with this type of spring brake cylinder, there is often not enough space around the spring brake cylinder attached to the bogie for manual release operation, and for this reason, it is possible to release the spring brake cylinder with as little force as possible and with a simple operation. It is desirable that it can be operated from the side of the trolley.

The conventional spring brake cylinder quick release device described above has a problem in that it requires a large operating force for manual quick release operation. Considering this point, the operating force f ₁ for rotating the control member 12 during the loosening operation is expressed by the following equation (1). That is, the friction coefficient between the ball 11 and the control member 12 is μ, the rotational resistance of the control member 12 is R ₁ , and the reaction force of the return spring 21 is
W ₁ and the expansion force in the direction in which the ball 11 is pushed outward from the recess 13 is F, then f ₁ =μF+R ₁ +W ₁ (1). From this equation (1), if the acting force of the brake spring 5 is large, F becomes large and μF becomes large, so a large operating force _f1 is also required.
In fact, the brake spring 5 is very strong.

In a spring brake cylinder, this invention provides:
An object of the present invention is to make it possible to reduce the operating force _f1 even if the spring force for a spring brake is large.

<Means for Solving the Problems> The means of the present invention provides a spring brake cylinder equipped with a ball clutch as described above.
The inner surface (the first A surface) is formed into a slope inclined toward the inner surface (second surface) of the recess that allows outward displacement of the ball at the clutch disengagement position of the control member, and locks rotation of the control member in the direction caused by the rotational force. The present invention is characterized in that a locking means is provided, and a manual release means is provided for releasing the locking of the locking means by an external operation.

In this invention, the locking means includes a latch provided on the control member and a latch on the control member which is urged forward by a return spring and is in the clutch connecting rotational position in the forward position. and an engaging member having an engaging claw.

In this invention, it is preferable that the manual release means is a manual operation part that is provided on the engagement member and causes the engagement member to retreat against the return spring.

Separately, the manual release means is formed separately from the engagement member, is provided so as to be movable in a direction substantially perpendicular to the advance and retreat of the engagement member, has a manual retraction operation portion, and is advanced by a return spring. and a rotationally driven engagement portion that is biased to rotate the control member in the clutch engagement rotational position to the clutch disengagement rotational position after retracting the engagement member during manual retraction from the forward position. It can also be used as a thing.

<Function> The manual quick release device for the spring brake cylinder of the present invention has the function of controlling the first control member of the ball clutch.
Since the surface is formed as an inclined surface inclined toward the second surface, the expanding force F acting on the ball when the spring brake is applied with the clutch in the connected state causes
The control member is subjected to a force such that it is rotated in the direction of disengaging the clutch. The magnitude of that force is the first
The inclination angle of the surface is θ, the normal component force of the expanding force F to the first surface is N, the component force parallel to the first surface of the expanding force F is P,
Letting μ be the coefficient of friction between the ball and the control member, it becomes (P−μN)cosθ. In addition, P=Fsinθ,
N=Fcosθ. In order to disengage the clutch by rotating the control member, it is necessary to resist the rotational resistance R ₂ and the reaction force W ₂ of the return spring as described above, so if θ is determined according to the situation, an appropriate value can be determined. The operating force can be set to _f2 . In other words, the operating force f ₂ is expressed as f ₂ = (μN-P) cos θ + R ₂ + W ₂ (2), so if θ is determined so that f ₂ > 0 and the value of f ₂ is small, it becomes small. If θ is determined so that f ₂ >0 (it does not need to be very large), the control member can be operated with no force, and no operating force is required to rotate the control member in the clutch disengaging direction. In this case, the operating force is sufficient to release the locking means.

As mentioned above, by making the first surface an inclined surface, it is possible to generate an acting force P in a direction that cancels out the frictional resistance μN due to the expanding force F of the ball, and the magnitude of this acting force can be expressed as the inclination angle θ. can be set to a desired value by selecting .

<Example> A first example will be described with reference to FIGS. 1 to 3. This embodiment differs from the conventional spring brake cylinder shown in FIG. 6 in the control member of the clutch portion and the part for manually operating the control member, but the other parts are almost the same, so the differences will be mainly explained. Equivalent parts will be designated by the same reference numerals and the description will be omitted.

As shown in FIGS. 1 and 3, the clutch 30 has a first surface 32 that is in contact with the ball 11 when the control member 31 is in the clutch connection rotation position and extends radially outward from the center of the push rod 2. Distraction and ball 1
A plane 33 perpendicular to a straight line passing through the center of 1
It is formed into an inclined surface forming an angle θ with respect to the surface. This angle θ is determined so that f ₂ in equation (2) has a small absolute value when f ₂ <0. and control member 3
1 rotates to the clutch disengagement position, the ball 11
One end of the first surface 32 is continuous in a stepped manner with a concave second surface 23 that allows the push rod 2 to be displaced to an outward position where it is removed from the ball engaging recess 13. In the figure, 34 is a cylindrical part extending from the end wall 18, and a straight groove 35 is provided in the inner hole of the cylindrical part 34, so that the cylindrical part 10 of the piston 22 is guided through a key 36. Although this was not explained earlier, it is the same as the conventional method. Further, the right end of the control member 31 is rotatably engaged with the left end outer circumferential groove 38 of the cylindrical portion 10 by a pin 37, and the outer periphery is rotatably supported by the inner hole of the cylindrical portion 34. is also the same as before. Further, the control member 31 has a straight groove 3 on the outer surface of the cylindrical portion extending leftward in the figure.
9, and the left outer periphery is supported by an end member 19, as in the conventional case.

A locking means 40 and a manual release means 41 are provided as parts for manually operating the control member 31. The locking means 40 includes a latch 42 and an engaging member 4.
3. It consists of a forward spring 44. The latch 42 is in position between the end member 19 and the end wall 18 with respect to the moving control member 31, as seen in FIG.
9 through a sliding key 45. 4 in the diagram
6 is bushy. As seen in FIG. 2, the latch 42 has an engaging portion 47 protruding from its outer periphery, and an engaging member 43 is provided for this engaging portion 47. The engaging member 43 is urged forward by a forward spring 44 from the cylinder body 8 side, and a claw 48 at the tip engages with an engaging portion 47 of the latch 42 in the forward position. The engaged state is a state in which the control member 31 is in the clutch connection rotation position and is prevented from rotating in the clutch release direction. 49 in the figure is a support member.

The manual release means 41 is formed by extending the rear part of the engagement member 43 to the outside of the cylinder body 8, and is provided with a handle 50 as a manual operation part for backward operation, and a return spring 51 is separately provided thereon. The return spring 51 urges a stopper 53, which is provided so as to be movable toward the protrusion of the latch 42, to advance relative to the support portion 52 on the cylinder body 8 side.
As a result, a force is applied via the latch 42 to rotate the control member 31 in the direction of clutch engagement.

The manual quick loosening device configured in this way has the first
If the spring brake is acting in the state shown in the figure, an expanding force F is acting on the ball 11, and the control member 31 is thereby subjected to a rotational force in the direction of disengaging the clutch 30. In this case, the inclination angle θ is expressed as
Since f ₂ in (2) is determined so that f ₂ <0, rotation of the control member 31 in the clutch disengaging direction is stopped by the locking means 40 via the latch 42. Therefore, when the handle 50 of the manual release means 41 is pulled outward, the pawl 48 engaging the engagement portion 47 of the latch 42 is disengaged and the locking means 40 is released.
is released, the control member 31 is rotated by the rotational force of the expansion force F, and the clutch 30 is in the disengaged state. At this time, the stopper 53 is moved by the return spring 51.
is compressed and retreated to a predetermined position. Furthermore, since the clutch 30 is in a disengaged state,
The piston 22 reaches the rearward end, and the rightward pulling force of the brake spring 5 is removed, so the push rod 2 is displaced to the left by the return spring on the brake device side, and the spring braking force is released.

In order to change the spring brake from this manual quick release state to a normal release state using pneumatic pressure when the clutch 30 is connected, it is sufficient to simply supply pressurized air to the pneumatic chamber 3. That is, when the piston 22 moves to the left against the brake spring 5 due to the supply of pressurized air and the positions of the recess 13 of the push rod 2 and the ball 11 match, the stopper 53 is moved by the return spring 51 via the latch 42. Since the control member 31 is given an acting force to rotate in the clutch connecting direction, when the control member 31 tries to rotate, the ball 11
is pushed inward and engages with the recess 13 of the push rod 2, and the clutch 30 becomes connected.

A second embodiment will be explained using FIGS. 4 and 5. This embodiment differs from the first embodiment in the locking means 60 and manual release means 61, so this point will be explained.

The locking means 60 includes a latch 62, an engaging member 63,
It consists of a forward spring 64. The latch 62 is connected to the control member 3
1 is provided in the same manner as in the first embodiment, but as shown in FIG. is provided, and the engaging portions 65 are present on both sides. An engagement member 63 is provided for this engagement portion 65 . The engaging member 63 is urged forward from the cylinder body 8 by a forward spring 64, and the engaging portion 6 of the latch 62 is pushed forward in the forward position.
5 is adapted to be engaged with a claw 67 at the tip.
The claw 67 has a shape divided into two sides corresponding to the engaging portion 65, and a slope 68 is formed between the claws 67. The engagement state of the pawl 67 with the engagement portion 65 is the same as in the first embodiment, in which the control member 31 is in the clutch connection rotation position and is engaged in rotation in the clutch disengagement direction. In the figure, 69 is a support member.

The manual release means 61 includes an operating member 70 formed separately from the engaging member 63, and return springs 71a, 71.
b, a spring receiver 72, a support member 73, etc. The operating member 70 is an elongated member that passes through the groove 66 of the latch 62, and is supported by the cylinder body 8 so as to be able to move forward and backward in the longitudinal direction.As seen in FIG. A handle 74 is provided thereon as a manual retraction operation section. The return spring 71a is provided between the spring receiver 72 and the support member 73, and the return spring 71b is provided between the stepped portion 75 of the operating member 70 and the spring receiver 72, both of which face leftward toward the operating member 70. It gives you the strength to move forward. An elongated hole 76 is bored as a rotational drive engagement portion at an appropriate position in the portion where the operating member 70 passes through the groove 66, and a pin 78 is provided passing through the elongated hole 76 and penetrating both side walls of the groove 66. There is. Then, a slope 79 formed in a step shape with respect to the slope 68 between the pawls 67 of the engaging member 63 is formed in a state where the pawl 67 is engaged with the engaging portion 65 when the operating member 70 is at the forward end position. are provided on the operating member 70 so as to face each other. In the figure, 80 is a stopper that determines the forward end position of the operating member 70.

The rest of the structure is the same as that of the first embodiment, so equivalent parts are designated by the same reference numerals and their explanation will be omitted.

In this manual quick release device, the illustrated state is a state in which a spring brake is applied, and when the clutch is in a connected state, the expanding force F of the ball causes the control member 31 to disengage the clutch (clockwise in FIG. 5).
rotational force is applied, and the engagement means 60 is in a state of locking the rotation. From this state,
When the handle 74 is pulled to the right in FIG. 5, the slope 79 pushes the slope 68 and causes the engagement member 63 to retreat against the forward spring 64, so that the claw 67 moves toward the engagement portion with the stroke shown by _l1 in the figure. 65, and a subsequent stroke indicated by _l2 engages the left end of slot 76 with pin 78, rotating latch 62 to the position where the clutch is disengaged. In this case, the control member 31
Assuming that the slope θ of the first surface is determined so that f ₂ <0 as described in the first embodiment, the latch 62 begins to rotate after the stroke l has been moved _{by 1} . It follows that no manual operating force has to be applied for the movement of stroke l ₂ . In addition,
If the inclination angle θ is determined to be a small value with f ₂ >0, the entire stroke l will be moved with a small force.

Further, in order to change from the manually released state to the normal clutch-connected released state, it is sufficient to simply supply pressurized air to the pneumatic chamber as in the first embodiment. That is, by supplying pressurized air, the brake spring 5
The piston 22 moves against the
When the positions of 3 and ball 11 match,
The tip of the spring receiver 72 comes into contact with the convex portion of the latch 62, and the forward force of the return spring 71a causes the latch 62 and the control member 31 to rotate in the clutch connecting direction. When the handle 74 is released after being pulled out, the operating member 70 returns to the forward end due to the action of the return spring 71b, and when the latch 62 rotates to the clutch connection rotation position, the claw 67 of the engaging member 63
The locking means 60 is brought into a locked state.

<Effects of the Invention> The present invention has a structure in which the first surface of the control member of the ball clutch of the spring brake cylinder is inclined, so that the expanding force of the ball generates an acting force that rotates the control member in the clutch disengaging direction. Therefore, by appropriately selecting the inclination angle of the first surface, it is possible to obtain the effect that the manual loosening operation force can be made small regardless of the strength of the brake spring.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional side view of a first embodiment of the invention;
FIG. 2 is an enlarged cross-sectional view taken along line A-A in FIG. 1, FIG. 3 is an enlarged cross-sectional view taken along line B-B in FIG. 1, and FIG. Reduced cross-sectional view, 5th
The figures are an enlarged cross-sectional view taken along the line C-C in Fig. 4, Fig. 6 is a vertical sectional side view showing an example of a conventional brake cylinder, and Fig. 7 is a longitudinal sectional side view showing an example of a conventional brake cylinder.
The figure is a sectional view taken along line E-E in Figure 6, and Figure 8 is a cross-sectional view taken along line F in Figure 6.
-F cross-sectional enlarged view. 1... Spring brake cylinder, 2... Push rod, 3
... Pneumatic chamber, 5 ... Brake spring, 8 ... Cylinder body, 9 ... Circular hole, 10 ... Cylindrical part, 11 ...
...ball, 13...recess, 22...inner surface, 23...
...Concave portion (second surface), 30...Clutch, 31...
control member, 32...first surface, 40...locking means,
41... manual release means, 42... latch, 43...
...Engagement member, 44...Advance spring, 47...Engagement portion, 48...Claw, 50...Handle (manual operation part), 51...Return spring, 60...Locking means, 6
1... Manual release means, 62... Latch, 63...
Engagement member, 64... forward spring, 65... engagement portion,
67...claw, 68...slope, 70...operating member,
71a, 71b... Return spring, 76... Long hole, 7
8...Pin, 79...Slope.

Claims (1)

[Scope of Claims] 1. A piston that is pressed in one direction by the action of a brake spring, and a brake device that is connected to a brake device and is provided coaxially with the piston and moves together with the piston in the direction in which the piston is moved by the brake spring. a push rod that applies a brake to the
A ball is held in a cylindrical part formed on the piston and into which the push rod is fitted, so as to be displaceable in the radial direction, and a recess into which the ball engages is provided on the outer periphery of the push rod, and a predetermined amount of the ball is disposed at a position outside the ball. A first surface whose inner surface restrains the ball in a position engaged with the recess so as to control the ball position by forward and reverse rotation; and an outer position where the ball is continuously disengaged from the recess in a predetermined rotational direction on this first surface. a ball clutch configured to engage and disengage an axial connection between the push rod and the piston, the ball clutch having a second surface that allows displacement of the ball to The first surface is formed into a slope inclined toward the second surface so that a rotational force in the direction from the clutch connection rotational position to the clutch disengagement rotational position is generated by the outward displacement acting force, and the rotational force of the control member is A locking means for locking rotation in the direction is provided,
A manual quick release device characterized by being provided with a manual release means for releasing the lock of the locking means by an external operation. 2. The device of claim 1, wherein the locking means is biased forward by a latch on the control member and an advancement spring so that in the advanced position the locking means is in the clutch-engaged rotational position. an engagement member having a pawl that engages the latch of the control member;
A manual quick loosening device characterized by comprising: 3. The device according to claim 2, wherein the manual release means includes a manual operating portion provided on the engagement member for retracting the engagement member against the advancement spring, and a manual operation portion for driving the latch and for controlling the control member. 1. A manual quick release device comprising a return spring provided to rotate the clutch from a disconnection rotation position to a connection rotation position. 4. The device according to claim 2, wherein the manual release means is formed separately from the engagement member and is provided so as to be movable in a direction substantially perpendicular to the direction of advancement and retreat of the engagement member, and includes a manual retraction operation section. the engaging member being urged forward by a return spring and being manually retracted from the forward position, and then rotating the control member in the clutch engagement rotational position to the clutch disengagement rotational position; What is claimed is: 1. A manual quick loosening device, characterized in that it has a rotationally driven engagement portion for causing