WO2012005149A1

WO2012005149A1 - Brake cylinder device and disc brake device

Info

Publication number: WO2012005149A1
Application number: PCT/JP2011/064883
Authority: WO
Inventors: 大野智也; 中村丈一
Original assignee: ナブテスコ株式会社
Priority date: 2010-07-05
Filing date: 2011-06-29
Publication date: 2012-01-12
Also published as: JP5344729B2; TW201211416A; CN102985718A; CN102985718B; JPWO2012005149A1; TWI407024B

Abstract

Disclosed is a compact brake cylinder device which, while avoiding increases in the size of the device, is capable of increasing the braking force outputted from a brake output unit which moves together with a rod. A rod (22) is provided inside of a cylinder body (20) so as to freely move in the advancing and retracting directions of the cylinder shaft direction. A piston (24) partitions a pressure chamber (44) inside of the cylinder body (20), surrounding the circumference of the rod (22), and moves in a linear direction parallel to the movement direction of the rod (22). By supplying a pressure fluid to the pressure chamber (44), the piston (24) resists the biasing force of a biasing spring (23) and moves in the retracting direction relative to the cylinder body (20). At that time, a force-multiplication mechanism (25) converts the linear direction drive force generated by the piston (24) to a rotational direction, moves the rod (22) in the advancing direction, and multiplies the drive force from the piston (24) to act on the rod (22). A brake output unit (21) moves together with the rod (22) in the advancing direction and outputs a braking force.

Description

Brake cylinder device and disc brake device

The present invention relates to a brake cylinder device that is operated by pressure fluid to move a rod, and a disc brake device including the brake cylinder device.

Conventionally, as a disc brake device for a railway vehicle equipped with a brake cylinder device, the one disclosed in Patent Document 1 is known. The disc brake device disclosed in Patent Document 1 is configured to advance the rod in the brake cylinder device by air pressure. Further, in this disc brake device, a pair of brake levers in a caliper body mounted so as to be relatively displaceable in the axle direction with respect to the vehicle is a rod side in the brake cylinder device and a cylindrical member side constituting the cylinder body Are connected to each other at one end side. And a pair of brake levers are driven because a brake cylinder device operates as mentioned above. Further, the disc brake device is configured to generate a braking force by sandwiching the disc on the axle side by a pair of brakes driven as described above and a brake provided on the other end side.

Further, a brake cylinder device disclosed in Patent Document 2 is known. In the brake cylinder device disclosed in Patent Document 2, a piston is fixed to a rod provided as a push rod. The piston is urged by supplying compressed air to the pressure chamber in the cylinder body, and the piston and the rod are advanced. When the rod advances, a braking force is output from a brake output portion that is provided so as to be movable together with the rod.

JP-A-61-175330 JP 2007-131203 A

In the disc brake device disclosed in Patent Document 1, the length of the brake is set so that a necessary braking force is generated. However, when a large braking force is required, there is a problem that the length of the brake lever becomes long and the caliper body becomes large, and the entire disc brake device becomes large.

On the other hand, in the brake cylinder device disclosed in Patent Document 2, the diameter of the cylinder body is determined so that a desired output brake force can be obtained. As described above, the setting of the diameter of the cylinder main body is adjusted so that a necessary braking force is generated. However, when a large braking force is required, there is a problem that the diameter of the cylinder body is increased and the entire brake cylinder device is enlarged. Further, when the brake cylinder device is enlarged, there is a problem that the disc brake device is also enlarged.

In view of the above circumstances, the present invention provides a small brake cylinder device capable of increasing a braking force output from a brake output unit that moves together with a rod while suppressing an increase in size of the device. Objective. Another object of the present invention is to provide a disc brake device including the brake cylinder device.

In order to achieve the above object, a brake cylinder device according to a first aspect of the present invention includes a cylinder body having a hollow interior, a cylinder body disposed inside the cylinder body, and a linear direction along a cylinder axial direction. In the cylinder body, a rod provided movably in an advancing direction that advances from the main body and a retracting direction that retracts in the opposite direction, a rod biasing spring that can bias the rod in the retracting direction, and The pressure chamber is partitioned and is disposed so as to surround the rod axis in the circumferential direction so as to be movable along a linear direction parallel to the movement direction of the rod, and pressure fluid is supplied to the pressure chamber. A piston that moves in the retracting direction with respect to the cylinder body against the biasing force of the rod biasing spring, and the piston is retracted When the movement is performed, the linear driving force generated in the piston is converted into the rotation direction, and the rod is moved in the advance direction to increase the driving force from the piston and act on the rod. It is provided with a boosting mechanism, and a brake output unit that is movably provided together with the rod, and that can output a braking force when the rod moves in the advance direction.

According to the present invention, the rod and the piston are configured to advance and retract in a linear direction along the cylinder axis direction, and further, the piston is disposed so as to surround the axis of the rod. For this reason, the arrangement space of the piston and the rod inside the cylinder body can be made efficient, and in particular, the arrangement space of the piston and the rod can be greatly reduced in the cylinder axial direction. Furthermore, a force-increasing mechanism for converting the linear driving force from the piston into the rotational direction and increasing the force to act on the rod can be arranged in the area secured by the efficiency of the arrangement space of the piston and the rod. Then, the braking force is output from the brake output unit that moves together with the rod on which the increased driving force acts. As described above, it is possible to reduce the size of the brake cylinder device by increasing the efficiency of the arrangement space of the piston and the rod and to reduce the size of the brake cylinder device, and it is possible to increase the braking force by the force increasing mechanism.

Therefore, according to the present invention, it is possible to provide a small brake cylinder device capable of increasing the braking force output from the brake output unit that moves together with the rod while suppressing an increase in the size of the device.

A brake cylinder device according to a second invention is the brake cylinder device according to the first invention, wherein the force-increasing mechanism is provided in the piston and extends along a circumferential direction centering on an axial center of the piston and moves the piston. An inclined surface provided to be inclined with respect to a direction, and a rotation that is urged by the inclined surface when the piston moves in the retracting direction and rotates in a predetermined rotation direction about the axial center of the rod. The rod is connected to the cylinder body so as to be restricted from displacement in a rotational direction around the axial center of the rod, and the rotational portion is moved in a predetermined rotational direction. It moves in the said advance direction with rotation, It is characterized by the above-mentioned.

According to the present invention, when the piston moves in the retracting direction along the linear direction, the rotating portion urged by the inclined surface inclined in the moving direction of the piston rotates. Then, by the rotation of the rotation unit, the rod whose displacement in the rotation direction is regulated moves in the advance direction, and a braking force is output. Therefore, the simple structure of providing the inclined surface and the rotating portion can efficiently convert the driving force generated in the retracting direction by the piston and generate the braking force in the rod advance direction.

A brake cylinder device according to a third invention is the brake cylinder device according to the second invention, wherein the force-increasing mechanism is formed integrally with the rod or fixed to the rod, and provided in the receiver. The rod-side receiving surface arranged so as to extend along the circumferential direction centering on the axial center of the rod, and the rotation arranged so as to face the receiving portion in a direction parallel to the axial direction of the rod. A rotating part-side receiving surface provided in the moving part and arranged so as to extend along a circumferential direction centering on an axial center of the rotating part; the rod-side receiving surface; and the rotating part-side receiving surface A rolling member disposed between the rod-side receiving surface and the rotating portion-side receiving surface; At least one of the locks Characterized in that provided for so as to be inclined with respect to the axial direction.

According to the present invention, the rolling member is disposed between the rod side receiving surface and the rotating portion side receiving surface facing each other, and at least one of the rod side receiving surface and the rotating portion side receiving surface is in the axial direction of the rod. To be inclined. For this reason, the structure which moves a rod to an advancing direction via rolling of a rolling member with rotation of a rotation part is realizable with a simple structure. The driving force converted from the retracted direction to the rotating direction between the inclined surface and the rotating part can be efficiently converted from the rotating direction to the advance direction between the rotating part and the rod. Furthermore, the ratio of increasing force can be easily adjusted by setting the inclined surfaces and the rolling members in the radial direction of the cylinder body (or the radial direction of the rod).

A brake cylinder device according to a fourth invention is the brake cylinder device according to the third invention, wherein a plurality of the rolling members are provided so as to be positioned along one circumference centering on an axial center of the rod. It is characterized by that.

According to the present invention, a plurality of rolling members to which a rotational force is transmitted from the rotating portion are provided along one circumference. For this reason, in the rolling members arranged in the rotation direction, the transmitted force can be efficiently shared and burdened, and the force acting on one rolling member can be reduced. Thereby, since a general rigid rolling member with good availability can be used, it becomes inexpensive. In addition, in order to use a commonly available rolling member with high rigidity, compared with the case of trying to reduce the contact surface pressure of one rolling member, one Since it is not necessary to enlarge a rolling member, it can suppress that a rolling member enlarges. Therefore, the increase in size of the brake cylinder device can be further suppressed.

A brake cylinder device according to a fifth invention is the brake cylinder device according to the third or fourth invention, wherein both the rod side receiving surface and the rotating portion side receiving surface are inclined with respect to the axial direction of the rod. The rolling member is provided as a plurality of roller cam members that are rotatably supported, and a side surface of the roller cam member extends in the circumferential direction so as to form a part of a conical curved surface and is on the rod side. It is provided as a rolling surface which rolls with respect to a receiving surface and the said rotation part side receiving surface.

According to the present invention, both the rod side receiving surface and the rotating portion side receiving surface are provided so as to be inclined in the axial direction of the rod, and as a roller cam member having a rolling surface that forms part of a conical curved surface therebetween. A rolling member is disposed. For this reason, the contact surface pressure which acts on one rolling member can be reduced compared with the case where a rolling member is provided as a spherical ball member. Furthermore, when the rod is moved in the advancing direction via the rolling member in accordance with the rotation of the rotating part, the advancing stroke (advancing distance) is achieved when a larger advancing stroke is achieved with a smaller amount of rotation of the rotating part. However, when a ball member is used as the rolling member, a large-diameter member is required. However, in the roller cam member, the rod side receiving surface and the rotating portion side receiving member that are inclined in the axial direction of the rod without being enlarged. The slope of the surface inclination can be set to a steeper slope. Therefore, the advance stroke can be ensured arbitrarily and easily while efficiently suppressing an increase in size of the brake cylinder device.

A brake cylinder device according to a sixth aspect of the present invention is the brake cylinder device according to any one of the first to fifth aspects of the present invention, further comprising a parking brake mechanism used when the vehicle equipped with the brake cylinder device is parked. The mechanism includes a plurality of parking brake springs arranged so as to be arranged along the circumferential direction of the cylinder body, and a second pressure chamber for releasing the parking brake that is different from the pressure chamber inside the cylinder body. The pressure fluid is discharged from the second pressure chamber so as to be partitioned and disposed so as to surround the rod axis in the circumferential direction so as to be movable along a direction parallel to the movement direction of the rod. The parking brake moves in the retracting direction with respect to the cylinder body by the biasing force of the parking brake spring and biases the piston. Characterized in that it comprises a piston for a rk, a.

According to this invention, the parking brake spring that generates the braking force of the parking brake, the parking brake piston that is biased by the parking brake spring and biases the piston, the second pressure chamber for releasing the parking brake, , A parking brake mechanism can be incorporated in the brake cylinder device. Since the parking brake piston that moves parallel to the rod movement direction is arranged so as to surround the rod axis, the parking brake piston can be arranged more efficiently, especially in the cylinder axis direction. Piston arrangement space can be greatly reduced. Further, according to the present invention, even when a large braking force is required as the braking force of the parking brake, the necessary braking force can be easily ensured by the plurality of parking brake springs. Since a plurality of parking brake springs are arranged along the circumferential direction of the cylinder body, the parking brake springs can be easily installed in a compact space while avoiding interference with other parts such as the brake output part. Can be arranged. For this reason, size reduction (namely, short axis and diameter reduction) can be achieved in the axial direction and radial direction of the brake cylinder device.

In addition, when one or two large coil springs arranged concentrically with respect to the cylinder body are provided as parking brake springs, the wire diameter of the coil springs is increased in order to ensure the necessary braking force. The compression length will be long. For this reason, it will be difficult to reduce the size of the brake cylinder device incorporating the parking brake mechanism. In addition, since it is necessary to avoid the interference with other parts such as the brake output portion, when the above coil spring is provided, this coil spring will be disposed on the outer side in the radial direction of the cylinder body, In the brake cylinder device, the diameter increases, and it becomes difficult to reduce the size. On the other hand, according to the above-described invention, the plurality of parking brake springs are arranged along the circumferential direction of the cylinder body, and it is easy to make a compact space by avoiding interference with other parts such as the brake output part. The parking brake spring can be disposed on the brake cylinder device, and the axial and radial dimensions of the brake cylinder device can be reduced.

The brake cylinder device according to a seventh aspect of the present invention is the brake cylinder device according to the sixth aspect, wherein the plurality of parking brake springs are disposed outside the cylinder body.

According to the present invention, since the parking brake spring is disposed outside the cylinder body, the cylinder body can be prevented from being enlarged. And since the several parking brake spring is arrange | positioned so that it may align along the circumferential direction in the outer side of a cylinder main body, each parking brake spring can be arrange | positioned compactly in the space which has the allowance in the outer side of a cylinder main body. Therefore, further downsizing of the brake cylinder device can be achieved. The present invention is configured as a brake cylinder device in which the piston and the parking brake piston move in the retracting direction and the rod moves in the opposite advancing direction during the braking operation. The structure which arrange | positions to the outer side of a cylinder main body can be implement | achieved more easily.

The brake cylinder device according to an eighth invention is the brake cylinder device according to the sixth or seventh invention, wherein the plurality of parking brake springs are parallel to the radial direction of the cylinder body with respect to the brake output portion. And are arranged on both sides on the side.

According to the present invention, the plurality of parking brake springs are arranged in parallel to the radial direction of the cylinder body on both sides of the brake output portion. For this reason, a plurality of parking brake springs can be arranged in a space-efficient and compact manner while avoiding interference with the brake output portion. Moreover, the dead space in the side of a brake output part can be utilized effectively, and several springs for parking brakes can be efficiently arrange | positioned partially along the circumferential direction of a cylinder main body. Therefore, the size can be further reduced in the axial direction and the radial direction of the brake cylinder device (that is, the shaft can be further shortened and the diameter can be further reduced).

A brake cylinder device according to a ninth invention is the brake cylinder device according to any one of the first invention to the eighth invention, wherein the screw shaft is connected to the brake output portion and has a screw formed on the outer periphery thereof; A guide tube that is attached to a force-increasing mechanism and is arranged so that the screw shaft can be urged toward the advance direction with respect to the cylinder body or a portion fixed to the cylinder body. A pusher spring, a clutch nut threadedly engaged with a tip end side of the screw shaft disposed on the brake output portion side with respect to the cylinder body, and the clutch nut so as to restrict movement of the clutch nut with respect to the guide tube It is arranged so as to be able to come into contact with the nut from the front side which is the brake output part side, and the guide tube A front stopper capable of urging the clutch nut and the screw shaft in the retraction direction along with the movement in the avoiding direction, and the front stopper from the rear side opposite to the brake output portion side with respect to the clutch nut. A first clutch disposed so as to be able to contact the clutch nut via an interval, and disposed so as to be relatively movable along an axial direction of the screw shaft with respect to the clutch nut and the guide tube, An adjustment stopper in which a movable range is restricted with respect to a member fixed to the cylinder body, and a second clutch in which the adjustment stopper is fixed and arranged to come into contact with the clutch nut from the rear side; The one end side contacts or is connected to the adjustment stopper or the second clutch, and the clutch nut is retracted. And adjusting spring capable biased toward the direction, characterized in that it further comprises a.

According to the present invention, during the braking operation, the pressure fluid is supplied to the pressure chamber, so that the force from the piston against the urging force of the rod urging spring is transmitted via the force-increasing mechanism, and the rod moves. The brake output unit moves in the advancing direction through the guide tube, the first clutch, the clutch nut, and the screw shaft, and the braking force is output. On the other hand, when the pressure fluid in the pressure chamber is discharged, the rod is moved in the retracting direction by the biasing force of the rod biasing spring, and the brake output portion is retracted through the guide tube, the front stopper, the clutch nut, and the screw shaft. And the brake is released. When the gap to the brake operation position in the released state becomes large due to wear of the brake pad, etc., the clutch nut, the first and second clutches, the screw shaft, the guide tube, the pusher spring, the front stopper, The gap is automatically adjusted by a gap adjusting mechanism including an adjustment stopper and an adjustment spring.

When the clearance adjustment is performed, first, during the braking operation, the movement range of the adjustment stopper is restricted, so that in the adjustment spring, the force that can urge the clutch nut in the retracting direction is accumulated as the accumulated force of the adjustment spring. . Further, at this time, the contact between the second clutch to which the adjustment stopper is fixed and the clutch nut is released, and a gap is formed between the second clutch and the clutch nut. When the guide tube starts moving in the retracting direction during the brake release operation, the screw shaft is urged in the advancing direction by the pusher spring. A state occurs in which the clutch nut is biased in the retracting direction by the accumulated force of the spring. At this time, the clutch nut is released from contact with the first clutch and is not in contact with the front stopper, and the clutch nut is not in contact with the second clutch. The nut becomes rotatable with respect to the screw shaft. Then, the clutch nut rotates with respect to the screw shaft so as to move in the retracting direction by the accumulated force of the adjustment spring. Thereafter, there is no gap between the clutch nut and the second clutch, the clutch nut and the second clutch come into contact with each other, the clutch nut becomes non-rotatable, and as the guide tube moves in the retracting direction, the front stopper, The brake output unit moves in the retracting direction together with the clutch nut and the screw shaft, and the brake is released. In this way, the clutch nut moves relative to the screw shaft in the retracting direction in the middle of the brake releasing operation, so the brake releasing operation is performed with the screw shaft moved in the advance direction from the state before the brake releasing operation. Will end. That is, the screw shaft and the brake output portion are moved to a position where they are advanced with respect to the cylinder body as compared with the state before the brake operation. As a result, the gap to the brake operation position in a state where the brake is released is automatically adjusted.

As described above, according to the present invention, the gap adjusting mechanism includes the clutch nut, the first and second clutches, the screw shaft, the guide tube, the pusher spring, the front stopper, the adjustment stopper, and the adjustment spring. For this reason, the clearance adjustment is not performed by elastic deformation of rubber or the like as in the brake cylinder device disclosed in Patent Document 2, and a configuration that is not easily affected by the surrounding environment such as temperature and humidity is realized at low cost. Can do.

Therefore, according to the present invention, in a brake cylinder device having a clearance adjustment mechanism for automatically adjusting the clearance to the brake operation position in a state where the brake is released, the brake cylinder device is not easily affected by the surrounding environment such as temperature and humidity. A small brake cylinder device can be provided at low cost.

According to the brake cylinder device of the present invention, in the state where the automatic clearance adjustment operation by the clearance adjustment mechanism is not performed, the second clutch and the clutch are engaged regardless of whether the brake operation is being performed or the brake is being released. The state in which the clutch nut is in contact with the clutch nut is maintained, and the second clutch and the clutch nut are prevented from being detached. That is, in a state where the clearance adjustment operation is not performed, the clutch nut is biased in the retracting direction by the adjustment spring whose one end is in contact with or connected to the adjustment stopper or the second clutch. The state in contact with the nut is maintained. Accordingly, the clutch nut is prevented from rotating with respect to the screw shaft at a timing other than the gap adjusting operation, and the clutch nut is prevented from being displaced with respect to the screw shaft due to vibration or the like.

Also, as another aspect of the invention, an invention of a disc brake device including any one of the above-described brake cylinder devices can be configured. That is, the disc brake device according to the tenth invention is equipped with the brake cylinder device according to any one of the first to ninth inventions and the brake cylinder device so as to be capable of relative displacement in the axle direction with respect to the vehicle. And a caliper body attached thereto, and when the brake cylinder device is operated, a disc on the axle side is sandwiched between a pair of brake pads attached to the caliper body to generate a braking force.

According to the present invention, it is possible to provide a small disc brake device capable of increasing the braking force while suppressing an increase in the size of the device.

According to the present invention, it is possible to provide a small brake cylinder device capable of increasing the braking force output from the brake output unit that moves together with the rod while suppressing an increase in the size of the device. Moreover, a disc brake device provided with the brake cylinder device can be provided.

1 is a side view of a disc brake device according to an embodiment of the present invention. FIG. 2 is a plan view of the disc brake device shown in FIG. 1. It is a perspective view of a brake cylinder device concerning one embodiment of the present invention, and is a figure showing an internal structure in a notch section. It is sectional drawing of the brake cylinder apparatus shown in FIG. It is sectional drawing of the brake cylinder apparatus shown in FIG. FIG. 4 is an exploded perspective view showing a rod, a guide tube, and a part of a boosting mechanism in the brake cylinder device shown in FIG. 3. It is a perspective view which expands and shows the rod and guide tube which are shown in FIG. It is the perspective view of the piston in the brake cylinder apparatus shown in FIG. 3, and the figure which looked at the piston from the booster mechanism side. It is the perspective view of the rotation part in the brake cylinder apparatus shown in FIG. 3, and the figure which looked at the rotation part from the rod side. It is the figure seen from the brake output part about the brake cylinder apparatus shown in FIG. FIG. 4 is a perspective view showing a roller cam member and a roller retainer in the brake cylinder device shown in FIG. 3. It is the figure seen from the brake output part side about the brake cylinder apparatus shown in FIG. It is an expanded sectional view which expands and shows a part of FIG. It is a perspective view for demonstrating the action | operation of the brake cylinder apparatus shown in FIG. 3, Comprising: It is a figure which shows an internal structure in a notch cross section. It is a perspective view for demonstrating the action | operation of the brake cylinder apparatus shown in FIG. 3, Comprising: It is a figure which shows an internal structure in a notch cross section. It is a perspective view for demonstrating the action | operation of the brake cylinder apparatus shown in FIG. 3, Comprising: It is a figure which shows an internal structure in a notch cross section. It is a perspective view for demonstrating the action | operation of the brake cylinder apparatus shown in FIG. 3, Comprising: It is a figure which shows an internal structure in a notch cross section.

Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings. The brake cylinder device of the present invention and the disc brake device including the brake cylinder device will be described by taking as an example a case of being used for a railway vehicle. The drawings are created with an accuracy equivalent to a design drawing.

FIG. 1 is a side view of a disc brake device 1 according to an embodiment of the present invention as viewed from the axle direction. FIG. 2 is a plan view of the disc brake device 1 shown in FIG. 1 as viewed from above. A disc brake device 1 shown in FIGS. 1 and 2 includes a brake cylinder device 2, a caliper body 11 equipped with the brake cylinder device 2 and attached to the vehicle body 100 so as to be relatively displaceable in the axle direction. A pair of back plates (12, 12), which are control members holding parts that respectively hold a pair of brake pads (13, 13), which are control wheels, are provided.

The pair of brake pads (13, 13) are attached to the caliper body 11 via the back plate 12. The disc brake device 1 is a disc on the axle side that rotates in conjunction with the rotation of the wheels (not shown) of the railway vehicle by the pair of brake pads (13, 13) when the brake cylinder device 2 is operated. The disc-shaped brake disc 101 is sandwiched to generate a braking force. The brake disc 101 is formed in a disc shape having front and back braking surfaces (101a, 101a) formed so as to be orthogonal to the rotation axis. When the brake cylinder device 2 is operated, the brake pads (13, 13) move the brake discs 101 on both sides from a direction substantially parallel to the rotation axis direction of the brake disc 101 with respect to the braking surfaces (101a, 101a). It is pressed so that it may be pinched.

The caliper body 11 includes a coupling member 14 and a pair of brake levers (15, 15). The coupling member 14 is attached to a bracket 100a fixed to the bottom surface of the vehicle main body 100 via a swing pin 14a so as to be swingable about an axis parallel to the traveling direction of the vehicle. Then, a pair of brake levers (15, 15) are installed so as to be swingable via a pair of fulcrum pins 15a in a substantially symmetrical manner with respect to the coupling member 14. The fulcrum pin 15 a is installed so as to extend in a direction perpendicular to the axial direction of the swing pin 14 a when viewed from the rotational axis direction of the disc brake 101.

The brake cylinder device 2 is attached to one end side of the pair of brake levers (15, 15) via a cylinder support pin 15b, and one end side is driven by the brake cylinder device 2. The pair of brake levers (15, 15) is a pair of back plates (12, 12) that hold the brake pad 13 on the other end side via the fulcrum pin 15a with respect to the one end side to which the brake cylinder device 2 is attached. ) Are attached. The back plate 12 is swingably attached to the brake lever 15 via a support pin 12a extending in parallel with the fulcrum pin 15a.

In the above-described disc brake device 1, as will be described later, the cylinder body 20 of the brake cylinder device 2 is attached to one brake lever 15, and the brake output portion 21 is attached to the other brake lever 15. As a result of the operation, the brake output unit 21 moves forward (moves away from the cylinder body 20) or retreats (moves close to the cylinder body 20). Thereby, the cylinder support pin 15b vicinity in a pair of brake levers (15, 15) is driven so that it may mutually separate or adjoin.

By being driven as described above, the disc brake device 1 operates such that the pair of brake levers (15, 15) operate with the fulcrum pin 15a as the support shaft and the brake pad 13 is sandwiched between the brake pads 13. become. At this time, in the pair of brake levers (15, 15), one brake pad 13 provided on one brake lever 15 comes into contact with the braking surface 101a of the brake disc 101 first. Further, the other brake lever 15 presses the other brake pad 13 against the braking surface 101 a of the brake disc 101 by using a reaction force received from one brake pad 13 in contact with the braking surface 101 a. As a result, the brake disc 101 is sandwiched between the pair of brake pads (13, 13), and the rotation of the brake disc 101 is caused by the frictional force generated between the brake pads (13, 13) and the braking surfaces (101a, 101a). The wheel is braked and the rotation of the wheels of the railway vehicle provided coaxially with the brake disk 101 is braked.

Next, the brake cylinder device 2 according to an embodiment of the present invention will be described in detail. FIG. 3 is a perspective view of the brake cylinder device 2 and shows the internal structure in a cut-away cross section. 4 and 5 are cross-sectional views of the brake cylinder device 2. FIG. 4 and 5, cross sections including the central axis P (the central axis indicated by the alternate long and short dash line P in FIGS. 4 and 5) in the brake cylinder device 2 are illustrated at different positions. FIG. 5 shows cross sections at different angles in the circumferential direction around the central axis P on both sides of the central axis P. The brake cylinder device 2 shown in FIGS. 3, 4, and 5 is configured in the same manner as the brake cylinder device 2 shown in FIGS. 1 and 2, but a part of the outer shape is changed and illustrated.

Both ends of the brake cylinder device 2 in the brake operation direction are connected to the cylinder support pins 15b. The brake cylinder device 2 includes a cylinder body 20, a brake output unit 21, a rod 22, a rod biasing spring 23, a piston 24, a boosting mechanism 25, a parking brake mechanism 26, a screw shaft 27, a guide tube 28, and a pusher spring 29. A clutch nut 30, a front stopper 31, a first clutch 32, an adjustment stopper 33, an adjustment spring 34, a second clutch 35, an adjustment sleeve 36, a spring receiver 37, a pusher spring guide 38, a cover 39, and the like. Yes. Of the above-described components, parts other than the adjustment sleeve 36 are made of, for example, a metal material such as an iron-based material, and the adjustment sleeve 36 is made of, for example, a resin material. 4 and 5, the predetermined components are not shown in cross section but are shown in outline.

The cylinder body 20 is composed of a first case portion 40 and a second case portion 41, and the inside is formed to be hollow. Inside the cylinder body 20, there are a rod 22, a rod urging spring 23, a piston 24, a booster mechanism 25, a part of a screw shaft 27, a guide tube 28, a pusher spring 29, an adjustment stopper 33, an adjustment spring 34, and a second clutch. 35, an adjustment sleeve 36, a spring receiver 37, a pusher spring guide 38, and the like are arranged. Further, the first case portion 40 is formed in a substantially cup shape having a bottom portion, and the second case portion 41 is fixed to the open end portion of the first case portion 40 with a bolt. The end portion of the first case portion 40 is connected to one brake lever 15 by a cylinder support pin 15b.

The second case portion 41 includes a cylindrical portion 41a formed in a cylindrical shape that is fixed to the end portion of the first case portion 40, and an axial direction of the cylindrical portion 41a (a direction parallel to the central axis P). ) And a flat plate-like portion 41b formed in a flange shape that protrudes inward and extends along the circumferential direction. A through hole is formed in the central portion in the radial direction of the flat plate portion 41b so that the rod 22 and the like are disposed therethrough. In addition, the first case of the cylindrical portion 41a is provided at the end of the cylindrical portion 41a of the second case portion 41 opposite to the side fixed to the first case portion 40 as a flat cover member. A cover 39 covering the opening on the side opposite to the part 40 side is fixed. A through hole is formed in the central portion of the cover 39 in the radial direction. The through hole is arranged with the screw shaft 27 and the guide tube 28 penetrating therethrough.

FIG. 6 is an exploded perspective view showing the rod 22, the guide tube 28, and a part of the force-increasing mechanism 25. FIG. 7 is an enlarged perspective view showing the rod 22 and the guide tube 28 shown in FIG. As shown in FIGS. 3 to 7, the rod 22 is provided as a cylindrical member disposed inside the cylinder body 20. The rod 22 is movable in a linear direction along the cylinder axis direction (a direction parallel to the central axis P) and in an advancing direction that advances from the cylinder body 20 and a retreating direction that retreats in the opposite direction. Is provided. As shown in FIGS. 4 and 5, the advance direction is referred to as “advance direction X1” (the direction indicated by arrow X1 in the figure), and the above retract direction is referred to as “retreat direction X2” (in the figure). The direction will be described below.

The rod 22 is formed as a large-diameter cylindrical portion 22a that is a large-diameter cylindrical portion on the advancing direction X1 side, and is formed as a small-diameter cylindrical portion 22b that is a small-diameter cylindrical portion on the retracting direction X2 side ( (See FIGS. 6 and 7). On the inner side of the large-diameter cylindrical portion 22a and the small-diameter cylindrical portion 22b, a step portion that is reduced in steps toward the retracting direction X2 is formed in two stages (see FIGS. 4 and 5). And the edge part of the rod urging | biasing spring 23 is contact | abutted and arrange | positioned at the step part by the side of the advancing direction X1. Further, the end portion on the retracting direction X2 side of the guide tube 28 is fixed to the stepped portion on the advancing direction X1 side and the stepped portion on the retracting direction X2 side in a state of being fitted over both of these stepped portions. Has been. A plurality of spline grooves 42 formed so as to extend along the axial direction of the rod 22 (direction parallel to the central axis P) are formed on the inner periphery of the small diameter cylindrical portion 22b.

As shown in FIGS. 3 and 4, the rod urging spring 23 is provided as a coiled spring disposed inside the rod 22 around the guide tube 28, and the edge of the through hole at the center of the cover 39. It arrange | positions between the cylindrical support member 43 fixed with respect to the part, and the step part by the side of the advancing direction X1 in the rod 22. FIG. The end of the rod biasing spring 23 on the advancing direction X1 side is formed as a cylindrical member, and the end of the cylindrical support member 43 on the inner periphery of which the side surface of the guide tube 28 is slidably contacted Against and is supported. On the other hand, the end of the rod biasing spring 23 on the retracting direction X2 side is in contact with and supported by the stepped portion of the rod 22 on the advancing direction X1 side. Accordingly, the rod biasing spring 23 is configured to bias the rod 22 in the retracting direction X2 with respect to the cover 39 and the cylindrical support member 43 which are members fixed to the cylinder body 20.

FIG. 8 is a perspective view of the piston 24 (FIG. 8A) and a view of the piston 24 viewed from the booster mechanism 25 (FIG. 8B). As shown in FIG. 3 to FIG. 5 and FIG. 8, the piston 24 is arranged so as to partition the inside of the cylinder body 20, and is in airtight sliding contact with the inner peripheral surface of the second case portion 41 of the cylinder body 20. The two case portions 41 are provided so as to be slidable in the axial direction. A pressure chamber 44 is formed in the cylinder body 20 by a space defined by the piston 24 and the second case portion 41. The pressure chamber 44 is configured such that compressed air as a pressure fluid is supplied and discharged through the communication passage 44a (see FIG. 5).

Further, the piston 24 is provided with a disk-like portion 45 and a pair of plate-like portions (46, 46). The disk-shaped portion 45 is provided as a disk-shaped portion that is in sliding contact with the inner periphery of the second case portion 41 in the sealing member fitted on the outer periphery. The disc-like portion 45 has a through hole 45a at the center. The disk-shaped part 45 is arranged so as to be in sliding contact with the outer periphery of the rod 22 through a seal member fitted into the inner periphery of the through hole 45a. Accordingly, the piston 24 is disposed so as to surround the axis of the rod 22 in the circumferential direction, and is provided so as to be movable along a linear direction parallel to the moving direction of the rod 22.

A plurality (four in this embodiment) of guide shaft holes 45b are provided around the through-hole 45a in the disc-like portion 45 so as to penetrate the disc-like portion 45, respectively. A guide shaft 47 formed in a round bar shape is inserted through each guide shaft hole 45b (see FIGS. 3 to 5). The guide shaft 47 is supported at both ends and midway portions in the cylinder body 20 and the cover 39, the end portion on the side in the advance direction X 1 is supported with respect to the inner wall of the cover 39, and the midway portion of the second case portion 41 The flat part 41b is fitted and fixed, and the end on the retracting direction X2 side is fitted and fixed to the first case part 40. The inner periphery of each guide shaft hole 45 b of the disk-shaped portion 45 is configured to be in sliding contact with the outer periphery of each guide shaft 47.

By providing the disk-like portion 45 configured as described above, the piston 24 is supplied with compressed air, which is a pressure fluid, into the pressure chamber 44, and thereby the rod biasing spring 23 via the force-increasing mechanism 25 described later. The cylinder body 20 is configured to move in the retracting direction against the urging force.

The pair of plate-like portions (46, 46) in the piston 24 extend in a curved manner along the circumferential direction centered on the axial center of the piston 24 and project from the disc-like portion 45 toward the retreat direction X2 side. It is provided as a part of. An inclined surface 48 is provided on the end surface of each plate-like portion 46 on the retracting direction X2 side. The inclined surface 48 is provided so as to extend along the circumferential direction centering on the axial center of the piston 24 and to be inclined with respect to the moving direction of the piston 24.

The brake output unit 21 is connected to the rod 22 via a screw shaft 27, a guide tube 28, and the like, which will be described later, and is provided so as to be movable together with the rod 22. As a result, the brake output unit 21 is movably provided in the advance direction X1 that advances from the cylinder body 20 and the retreat direction X2 that retracts so as to approach the cylinder body 20, and the rod 22 moves in the advance direction X1. The brake force can be output. Moreover, the brake output part 21 is connected with the other brake lever 15 by the cylinder support pin 15b.

When the piston 24 moves in the retracting direction X2, the force increasing mechanism 25 shown in FIGS. 3 to 6 converts the linear driving force generated in the piston 24 into the rotational direction and moves the rod 22 in the advancing direction X1. , A mechanism for increasing the driving force from the piston 24 to act on the rod 22 is provided. The force-increasing mechanism 25 includes the inclined surface 48, the receiving portion 49, the rotating portion 50, the roller cam member 51, the roller retainer 52, the spline shaft 53, the rod-side receiving surface 54, and the rotating portion-side receiving surface provided on the piston 24. 55 and the like.

As shown in FIGS. 3 to 7, the receiving portion 49 is formed integrally with the large-diameter cylindrical portion 22a of the rod 22, and is provided as an end portion on the retracting direction X2 side in the large-diameter cylindrical portion 22a. ing. In addition, a plurality of rod-side receiving surfaces 54 (six in this embodiment) are provided in the receiving portion 49 and are formed as end surfaces on the retreating direction X2 side in the receiving portion 49. The plurality of rod-side receiving surfaces 54 are arranged in order along the circumferential direction around the axial center of the rod 22, and each rod-side receiving surface 54 is also centered on the axial center of the rod 22. It is arranged so as to extend along the circumferential direction. Each rod side receiving surface 54 is provided so as to be inclined with respect to the axial direction of the rod 22.

FIG. 9 is a perspective view of the rotating unit 50 (FIG. 9A) and a view of the rotating unit 50 viewed from the rod 22 side (FIG. 9B). FIG. 10 is a view of the brake cylinder device 2 as viewed from the side opposite to the brake output unit 22. In FIG. 10, a part of the internal configuration of the cylinder body 20 is indicated by a broken line.

3 to 6, 9, and 10 are disposed so as to face the receiving portion 49 in a direction parallel to the axial direction of the rod 22. The rotating portion 50 is rotatable with respect to the rotating main body member 57 formed in a cylindrical shape whose axial length is shorter than the radial length, and the rotating main body member 57 via the rotating shaft. A pair of attached rollers (58, 58), etc. are provided. An end of the rotating main body member 57 on the retracting direction X2 side is rotatably supported with respect to the first case portion 40 of the cylinder main body 20 via a bearing 56. Thereby, the rotation part 50 is supported in the cylinder body 20 so as to be rotatable about the axis center of the rod 22.

Further, each of the pair of rollers (58, 58) is supported so as to be rotatable with respect to the respective rotation shafts arranged along the diameter direction of the rotating main body member 57. The side surface of each roller 58 is provided as a rolling surface that extends in the circumferential direction (in the circumferential direction of each roller 58) so as to constitute a part of a conical curved surface and rolls with respect to each inclined surface 48. ing. By providing the rotating main body member 57 and the pair of rollers (58, 58), the rotating portion 50 has a rolling surface of each roller 58 when the piston 24 moves in the retracting direction X2. It is configured to be urged by the inclined surface 48 to rotate in a predetermined rotation direction (a direction in which the rotation main body member 57 rotates clockwise as viewed from the piston 24 side) around the axial center of the rod 22. .

Rotating part side receiving surfaces 55 are provided in the rotating part 50 in a plurality (six in this embodiment), and are formed as end faces on the advancing direction X1 side in the rotating part 50. And the some rotation part side receiving surface 55 is arrange | positioned in order along the circumferential direction centering on the axial center of the rod 22 and the rotation part 50, and each rod side receiving surface 55 is also a rod. 22 and the rotation part 50 are arranged so as to extend along the circumferential direction centered on the axial center. Further, each rotating portion side receiving surface 55 is provided so as to be inclined with respect to the axial direction of the rod 22. Therefore, in the force-increasing mechanism 25, both the rod-side receiving surface 54 and the rotating portion-side receiving surface 55 are provided so as to be inclined with respect to the axial direction of the rod 22.

FIG. 11 is a perspective view showing the roller cam member 51 and the roller retainer 52. The roller cam member 51 shown in FIGS. 3 to 6 and FIG. 11 constitutes a rolling member in the present embodiment, and is provided in plural (six in the present embodiment) and is rotatable with respect to the roller retainer 52. It is supported. The roller retainer 52 includes an inner ring member 52a and an outer ring member 52b provided as ring-shaped members disposed concentrically. The inner ring member 52a and the outer ring member 52b are connected and fixed to each other by a plurality of (six in this embodiment) rotating shaft members extending in the radial direction. Each roller cam member 51 is rotatably supported with respect to each rotation shaft member.

The plurality of roller cam members 51 are disposed between the rod side receiving surface 54 and the rotating portion side receiving surface 55 while being rotatably held by the roller retainer 52. The roller cam members 51 are arranged so as to be able to roll with respect to the rod-side receiving surfaces 54 and the rotating portion-side receiving surfaces 55 that are arranged to face each other. That is, the side surface of each roller cam member 51 extends in the circumferential direction (in the circumferential direction of each roller cam member 51) so as to form a part of a conical curved surface, and is opposed to the rod side receiving surface 54 and the rotating portion side receiving surface 55. It is provided as a rolling surface that rolls. Further, the plurality of roller cam members 51 are provided so as to be positioned along one circumference centered on the axial center of the rod 22, and are arranged at equal angular positions in the circumferential direction of the roller retainer 52.

The spline shaft 53 shown in FIGS. 4 to 6 is fixed to the first case portion 40 at the end portion on the retracting direction X2 side, and is supported by the cylinder body 20 in a state of protruding in a cantilevered manner toward the advancing direction X1 side. It is provided as a shaped member. A plurality of spline teeth 53a are formed on the outer periphery of the portion of the spline shaft 53 on the advancing direction X1 side. Each spline tooth 53a is formed so as to extend along the axial direction of the spline shaft 53 (a direction parallel to the central axis P), and is axial with respect to each spline groove 42 on the inner periphery of the small-diameter cylindrical portion 22b of the rod 22. It is provided to fit in a slidably movable state in the direction. As described above, the rod 22 is connected to the spline shaft 53 so as to be movable in the axial direction while sliding, so that the rod 22 rotates about the axis center of the rod 22 with respect to the cylinder body 20. It is connected so that the displacement of the direction is restricted, and is configured to be movable in the advance direction X1 in accordance with the rotation of the rotation unit 50 in a predetermined rotation direction. The spline shaft 53 is provided with a screw shaft insertion hole 53b that opens toward the advancing direction X1 side and into which a later-described screw shaft 27 is inserted.

As shown in FIGS. 3 to 5, in the force-increasing mechanism 25, the pair of inclined surfaces (48, 48) and the pair of pairs are more than the distance from the central axis P at the position where the plurality of roller cam members 51 are disposed. The distance from the central axis P of the position where the rollers (58, 58) are arranged is set larger. As a result, the driving force generated by the piston 24 is increased so that it can be output from the rod 22.

FIG. 12 is a view of the brake cylinder device 2 as viewed from the brake output unit 21 side. A brake mechanism that generates a braking force by operating the piston 24, the boosting mechanism 25, the rod 22 and the like by supplying compressed air to the pressure chamber 44 is used during normal operation of the railway vehicle. On the other hand, the parking brake mechanism 26 shown in FIGS. 3 to 5 and 12 is provided as a brake mechanism used when parking a railway vehicle equipped with the brake cylinder device 2. The parking brake mechanism 26 includes a plurality of parking brake springs 59, a parking brake piston 60, and the like.

A plurality (10 in this embodiment) of parking brake springs 59 are provided as coil springs, and each of the two parking brake spring support portions 39a provided on the cover 39 has a half (five). ) Is arranged. The parking brake spring support portion 39a is a portion that extends along the circumferential direction and protrudes toward the advancing direction X1 side in the cover 39 fixed to the cylinder body 20, and divides a hollow region inside. Two are provided. A plurality of parking brake springs 59 are supported inside each parking brake spring support portion 39a. Thereby, the plurality of parking brake springs 59 are arranged along the circumferential direction of the cylinder body 20.

Further, in each parking brake spring support portion 39 a, the end portion of each parking brake spring 59 on the advancing direction X 1 side is in contact with and supported by the inner wall of the parking brake spring support portion 39. On the other hand, the end of each parking brake spring 59 on the retracting direction X2 side is in contact with and biased against a parking brake piston 60 described later. The plurality of parking brake springs 59 are disposed on the parking brake spring support portion 39 a of the cover 39, and are disposed outside the cylinder body 20. Further, the parking brake spring support portions 39a are arranged in the direction parallel to the radial direction of the cylinder body 20 with respect to the brake output portion 21, and are disposed on both sides on the side. Therefore, the plurality of parking brake springs 59 are also arranged with respect to the brake output portion 21 in a direction parallel to the radial direction of the cylinder body 20 and arranged on both sides on the side.

The parking brake piston 60 is disposed on the inner side of the cylinder body 20, and hermetically slidably contacts the inner peripheral surface of the second case portion 41 of the cylinder body 20 on the side in the advance direction X1 with respect to the flat plate portion 41b. The second case portion 41 is provided so as to be slidable in the axial direction. A parking brake releasing pressure chamber 61 is formed inside the cylinder body 20 by a space defined by the parking brake piston 60 and the second case portion 41. In addition, the parking brake releasing pressure chamber 61 is configured so that compressed air as pressurized fluid is supplied and discharged through a communication path (not shown). The parking brake releasing pressure chamber 61 is provided for releasing the parking brake different from the pressure chamber 44, and constitutes a second pressure chamber in the present embodiment.

Further, the parking brake piston 60 is provided with a disk-shaped portion 60a and a cylindrical portion 60b. The disc-shaped portion 60a is provided as a disc-shaped member that is in sliding contact with the inner periphery of the second case portion 41 in a seal member fitted on the outer periphery. A through hole is formed in the central portion of the disc-shaped portion 60a. And the cylindrical part 60b provided as a cylindrical member is connected with respect to the edge part of this through-hole via the connection member 62 formed in the ring shape. That is, the connecting member 62 is provided so as to be able to engage with the inner peripheral side of the disc-shaped portion 60a and the outer peripheral side of the cylindrical portion 60b, and the connecting member 62 is provided with the disc-shaped portion 60a and the cylindrical portion 60b. The disk-shaped part 60 a and the cylindrical part 60 b are integrally connected via the connecting member 62.

In addition, a plurality of guide shaft holes formed so as to penetrate the disk-shaped part 60a are provided around the through-holes in the disk-shaped part 60a. Each guide shaft hole is inserted with a guide shaft 47 protruding from the flat plate portion 41a toward the advance direction X1 (see FIG. 4). The inner periphery of each guide shaft hole of the disc-shaped portion 60 a is configured to be in sliding contact with the outer periphery of each guide shaft 47.

Moreover, the cylindrical part 60b is arrange | positioned on the outer peripheral side so that it may slidably contact with the flat part 41a via the sealing member fitted by the edge part of the through-hole of the flat part 41a of the 2nd case part 41. As shown in FIG. ing. And the cylindrical part 60b is arrange | positioned so that the outer periphery of the rod 22 may be slidably contacted in the inner peripheral side in which the sealing member was engage | inserted. Further, the end portion on the retracting direction X2 side of the cylindrical portion 60b is disposed so as to contact the end surface of the piston 24 on the advancing direction X1 side. Accordingly, the parking brake piston 60 is disposed so as to surround the axis of the rod 22 in the circumferential direction, and is provided so as to be movable along a linear direction parallel to the moving direction of the rod 22, and moves in the retreat direction X2. The piston 24 is sometimes configured to be biased.

Since the parking brake mechanism 26 is configured as described above, when the compressed air is supplied to the parking brake release pressure chamber 61, the parking brake piston 60 resists the biasing force of the parking brake spring 59. The state where the brake force of the parking brake is not generated by the parking brake spring 59 (the state where the parking brake is released) is maintained by being biased in the advancing direction X1. On the other hand, when the compressed air is discharged from the parking brake release pressure chamber 61, the parking brake piston 60 moves in the retracting direction X 2 with respect to the cylinder body 20 by the biasing force of the parking brake spring 59. The braking force is generated as a parking brake.

In the brake cylinder device 2, as shown in FIG. 12, a parking brake release operation ring 63 is provided on the cover 39 side. The parking brake release operation ring 63 is provided as an operation part for manually releasing the parking brake. In the brake cylinder device 2, when the parking brake release operation ring 63 is pulled, a link mechanism (not shown) is driven so that the connecting member 62 formed in a ring shape expands in the radial direction. It is configured to operate. Thereby, in the parking brake piston 60, the engagement between the cylindrical portion 60b and the connecting member 62 is released, and the connection between the disc-like portion 60a and the cylindrical portion 60b is released.

When the connection between the disc-shaped portion 60a and the cylindrical portion 60b is released as described above, the piston 24 is moved in the advance direction X1 by the urging force from the rod urging spring 23 acting via the rod 22 and the force-increasing mechanism 25. The cylindrical portion 60b moves in the advancing direction X1 together with the piston 24 without changing the position of the disc-shaped portion 60a biased by the parking brake spring 59. Thereby, the brake output part 21 moves with the rod 22 in the retracting direction X2, and the parking brake is released. Therefore, in the brake cylinder device 2, the parking brake can be operated even when compressed air is not supplied to the parking brake release pressure chamber 61 in a state where the parking brake is operated due to the braking force of the parking brake spring 59. When the release operation ring 63 is pulled, the parking brake can be released.

Next, the clearance adjustment mechanism in the brake cylinder device 2 will be described with reference to FIGS. 4, 5 and 13. 13 is an enlarged cross-sectional view showing a part of FIG. 4 in an enlarged manner, and is an enlarged view showing a main part of the gap adjusting mechanism. When the gap to the brake operation position in the released state is increased due to wear of the brake pad 13 in the disc brake device 1, the clutch nut 30, the first clutch 32, the second clutch 35, the screw shaft 27, The gap is automatically adjusted by a gap adjustment mechanism including the guide tube 28, the pusher spring 29, the front stopper 31, the adjustment stopper 33, the adjustment spring 34, and the like.

The screw shaft 27 is provided as a shaft-like member that is connected to the brake output portion 21 and has a screw 27a formed on the outer periphery. The screw shaft 27 is formed to be hollow so as to open toward the side opposite to the brake output portion 21 (in this embodiment, on the side of the booster mechanism 25). That is, the hollow region inside the screw shaft 27 is provided as an axial hole 27b extending along the axial direction, and is opened only on the side opposite to the brake output portion 21 (retracting direction X2 side). The end of the screw shaft 27 on the retracting direction X2 side is inserted into the screw shaft insertion hole 53b of the spline shaft 53.

The guide tube 28 is formed as a cylindrical member, and is attached so that the end portion on the retreat direction X2 side is fixed and attached to the step portion inside the rod 22 and penetrates the cylindrical support member 43. . The guide tube 28 has a screw shaft 27 disposed in an inner space area. In addition, the peripheral wall of the guide tube 28 is provided with a pair of slit holes (28a, 28a) penetratingly formed in a slit shape at a midway position in the cylindrical axis direction. The pair of slit holes (28a, 28a) are provided so as to be arranged at positions along the diameter direction of the cylindrical guide tube 28, and an adjustment stopper 33 described later penetrates from the inside toward the outside. It is formed as an opening arranged so as to.

The pusher spring 29 is provided as a coiled spring and is disposed in the axial hole 27 b in the screw shaft 27. The axial hole 27b is provided with a step portion whose diameter decreases stepwise toward the back side (the advance direction X1 side). The pusher spring 29 is provided as a compression spring, the end on the advancing direction X1 side abuts on the stepped portion on the axial hole 27b, and the end on the retracting direction X2 side is a screw shaft insertion hole of the spline shaft 53. It arrange | positions so that it may contact | abut to the bottom part of 53b. Thereby, the pusher spring 29 is arranged so that the screw shaft 27 can be urged from the inside toward the advance direction X1 with respect to the spline shaft 53 of the force-increasing mechanism 25 which is a portion fixed to the cylinder body 20.

The pusher spring guide 38 is formed as a shaft-like portion fixed to the spline shaft 53 at the bottom portion of the screw shaft insertion hole 53b. The pusher spring guide 38 is disposed so as to protrude toward the axial hole 27 b of the screw shaft 27 and is inserted inside the pusher spring 29. Thereby, the pusher spring guide 38 is configured to restrict deformation of the pusher spring 29 in the buckling direction. Further, the pusher spring guide 38 is inserted in a state in which a tip portion thereof is in sliding contact with a hole portion whose diameter is reduced on the back side (the advance direction X1 side) in the axial hole 27b of the screw shaft 27. As a result, the pusher spring guide 38 has a distal end portion slidable with respect to the inside of the screw shaft 27.

The clutch nut 30 is provided as a cylindrical member having a female screw portion formed on the inner periphery, and is screwed to the tip end side of the screw shaft 27 disposed on the brake output portion 21 side with respect to the cylinder body 20. It is configured. Further, the outer periphery of the clutch nut 30 at the midway position in the axial direction is formed so as to extend in the circumferential direction and to protrude outward in the radial direction, with respect to the front stopper 31 and the first clutch 32 described later. A convex portion 30a that can be brought into contact with each other is provided. Since the clutch nut 30 is provided as described above, the pusher spring 29 urges the clutch nut 30 screwed to the screw shaft 27 toward the front stopper 31 by urging the screw shaft 27 from the inside. Is configured to do.

The front stopper 31 includes a cylindrical member having a male screw portion formed on the outer periphery and a short axial length, and a bearing that is fitted and integrated inside the cylindrical member. . The front stopper 31 is threadedly engaged with a female screw portion formed on the inner periphery of the tip portion of the guide tube 28 facing the brake output portion 21 in the male screw portion. That is, the front stopper 31 is fixed to the inner periphery of the guide tube 28 by screw connection. A groove extending in the circumferential direction is formed on the inner periphery of the distal end portion of the guide tube 28 on the brake output portion 21 side with respect to the front stopper 31. A snap ring 64 that engages with the end of the front stopper 31 on the brake output portion 21 side is fitted into the groove, thereby preventing the front stopper 31 from coming off.

Further, the front stopper 31 is concentrically arranged on the outer side with respect to the end of the clutch nut 30 on the brake output portion 21 side and the screw shaft 27 (so that the center positions in the radial direction coincide with each other). And the front stopper 31 is arrange | positioned so that the convex part 30a can be contact | abutted with respect to the clutch nut 30 from the front side which is the brake output part 21 side so that the movement with respect to the guide tube 28 of the clutch nut 30 may be controlled. Thereby, the front stopper 31 is configured to be able to bias the clutch nut 30 and the screw shaft 27 to which the clutch nut 30 is screwed in the retracting direction X2 as the guide tube 28 moves in the retracting direction X2.

The first clutch 32 is provided as a cylindrical member having a short axial length, and is formed as an integral member that is a separate member from the front stopper 31. The first clutch 32 is press-fitted inside the guide tube 28 and fixed. The end portion of the first clutch 32 is positioned in contact with a portion formed in a step shape on the inner periphery of the guide tube 28. Further, the first clutch 32 is disposed concentrically outside the clutch nut 30 and the screw shaft 27 (so that the radial center positions coincide). The first clutch 32 can come into contact with the convex portion 30a of the clutch nut 30 through a predetermined distance from the front stopper 31 from the rear side opposite to the brake output portion 21 side with respect to the clutch nut 30. Has been placed.

The adjustment stoppers 33 are provided as a pair, and are respectively fixed to a second clutch 35 described later formed as a ring-shaped member or a cylindrical member having a short axial length. Each adjustment stopper 33 is provided as a block-like member that protrudes outward in the radial direction of the second clutch 35. The pair of adjustment stoppers (33, 33) are fixed to the second clutch 35 so as to be disposed at positions along the diameter direction of the guide tube 28 and the screw shaft 27. The pair of adjustment stoppers (33, 33) are arranged so as to protrude through the pair of slit portions (28b, 28b) in the guide tube.

A stopper stroke formed on the cylindrical support member 43, which is a member fixed to the cylinder body 20 via the cover 39, is formed as an annular protrusion extending in the circumferential direction at the end on the retracting direction X2 side. A restricting portion 65 is provided. And each adjustment stopper 33 is arrange | positioned so that it can contact | abut with respect to the stopper stroke control part 65 in the protruded edge part, when moving to the advancing direction X1. The adjustment stopper 33 is a member fixed to the cylinder body 20 so as to be relatively movable along the axial direction of the screw shaft 27 with respect to the clutch nut 30 and the guide tube 28 by being provided as described above. The movable range is restricted with respect to the cylindrical support member 43.

As described above, the second clutch 35 to which the adjustment stopper 33 is fixed is formed as a ring-shaped member or a cylindrical member having a short axial length, and around the screw shaft 27 and the adjustment sleeve 36 described later around the guide tube. 28 is arranged inside. The second clutch 35 is disposed so as to be capable of coming into contact with the clutch nut 30 from the rear side at the end in the advance direction X1, and is in contact with an adjustment spring 34 described later at the end in the retracting direction X2. Further, teeth 35a are formed on the surface of the second clutch 35 on the side in the advance direction X1 and facing the clutch nut 30 in the circumferential direction. On the other hand, teeth 30b are formed on the surface of the clutch nut 30 on the side of the retracting direction X2 and facing the second clutch 35 in the circumferential direction. The teeth 35 a on the second clutch 35 side and the teeth 30 b on the clutch nut 30 side are formed as teeth that can engage the second clutch 35 and the clutch nut 30.

The adjusting sleeve 36 is provided as a flexible cylindrical member by being formed of resin, and is arranged around the screw shaft 27. The adjustment sleeve 36 is provided with an engaging portion 36a formed as an uneven portion on the outer periphery of the end portion on the advancing direction X1 side. The clutch nut 30 is provided with an engaged portion 30c formed as an uneven portion that fits with the uneven portion of the engaging portion 36a on the inner periphery of the end portion on the retracting direction X2 side. The adjustment sleeve 36 and the clutch nut 30 are integrally formed by engaging an engagement portion 36a on the adjustment sleeve 36 side and an engaged portion 30c on the clutch nut 30 side.

The engaging portion 36a of the adjustment sleeve 36 is provided so as to engage from the inside with an engaged portion 30c formed on the inner peripheral side of the clutch nut 30. The dimension in the radial direction of the adjustment sleeve 36 between the inner periphery of the adjustment sleeve 36 and the top of the thread 27 of the screw 27a on the screw shaft 27 is determined by the engagement portion 36a and the engaged portion 30c. Are configured to be smaller than the dimension in the radial direction of the adjustment sleeve 36 (the overlapping margin of the uneven parts in the radial direction of the adjustment sleeve 36).

The adjustment spring 34 is provided as a coiled spring disposed around the adjustment sleeve 36. The adjustment spring 34 has one end abutted (or connected) to the end of the second clutch 35 on the retracting direction X2 side, and the other end attached to the end of the adjusting sleeve 36 on the retracting direction X2 side. It arrange | positions so that the spring receiver 37 which has a bearing may be urged | biased. As a result, the adjustment sleeve 36 is configured such that one end side is urged in the retracting direction X2 by the other end side of the adjustment spring 34 that contacts the second clutch 35. The adjustment spring 34 is configured to be able to urge the clutch nut 30 that is engaged and integrated with the adjustment sleeve 36 in the retracting direction X2.

Further, the spring receiver 37 is disposed between the outer periphery of the adjustment sleeve 36 and the inner periphery of the guide tube 28, and is formed in a flange shape formed on the outer periphery of the end portion in the retracting direction X 2 of the adjustment sleeve 36 over the circumferential direction. The adjustment sleeve 36 is attached by engaging with the protrusion. The spring receiver 37 is disposed so that the dimension in the radial direction of the guide tube 28 in the gap formed between the outer periphery thereof and the inner periphery of the guide tube 28 is substantially zero. The spring receiver 37 may be disposed so that its outer periphery and the inner periphery of the guide tube 28 are in sliding contact. Since the spring receiver 37 is provided with a bearing, the adjustment sleeve 36 is configured to be rotatable with respect to the adjustment spring 34.

Next, the operation of the brake cylinder device 2 will be described with reference to FIGS. 3 and 14 to 17, which are perspective views of the brake cylinder device 2 and showing the internal structure in a cutaway cross section. FIG. 3 is a diagram illustrating a state corresponding to the cross-sectional views of FIGS. 4 and 5, in which compressed air is not supplied to the pressure chamber 44 and compressed air is supplied to the parking brake releasing pressure chamber 61. State. That is, the brake cylinder device 2 in the state shown in FIG. 3 is in a state where no braking force is generated.

When the supply of compressed air to the pressure chamber 44 is started from the state shown in FIG. 3, the state shown in FIG. 3 is shifted to the state shown in FIG. 14, and the state shown in FIG. The state shown in FIG. Note that the state shown in FIG. 14 shows a state in which the piston 24 has advanced through about one-third of all the steps (full stroke) in the retreat direction X2. Moreover, the state shown in FIG. 15 shows a state in which the piston 24 has advanced in the retreat direction X2 through about two-thirds of all the steps. Further, the state shown in FIG. 16 shows a state in which the piston 24 proceeds through the entire process in the retracting direction X2 and the braking force is output from the brake output unit 21.

As shown in FIGS. 14 to 16, when compressed air is supplied to the pressure chamber 44, the piston 24 resists the urging force transmitted from the rod urging spring 23 via the rod 22 and the booster mechanism 25. The guide shaft 47 moves in the retracting direction X2 while being guided in the moving direction. Each inclined surface 48 presses each roller 58 in the rotation unit 50. As a result, the roller 58 rolls on the inclined surface 48 while rotating, and the rotating body member 57 rotates together with the roller 58 in a predetermined rotation direction (a direction rotating clockwise as viewed from the piston 24 side). Then, with the rotation of the rotation main body member 57, the rotation part side receiving surface 55 also rotates about the axis center of the rod 22. As a result, the roller cam member 51 rotates while rolling with respect to the rotating portion side receiving surface 55 and the rod side receiving surface 54.

When the roller cam member 51 rotates as the rotating main body member 57 rotates, the roller cam member 51 advances while rotating along the rotating portion side receiving surface 55 provided to be inclined with respect to the axial direction of the rod 22. It will move in the direction X1. At this time, the rod-side receiving surface 54 provided to be inclined with respect to the axial direction of the rod 22 is further pushed in the advancing direction X1 as the roller cam member 51 rotates. As a result, the rod 22, whose displacement in the rotational direction is restricted by the connection with the spline shaft portion 53 and allowed to move only in the axial direction, moves in the advance direction X 1.

When the rod 22 moves in the advancing direction X1, the guide tube 28 and the first clutch 32 move together with the rod 22 in the advancing direction X1, and are further screwed into the clutch nut 30 and the clutch nut 30 that contact the first clutch 32. The threaded shaft 27 and the brake output unit 21 connected to the threaded shaft 27 also move in the advancing direction X1. Then, the brake output unit 21 moves together with the rod 22 in a predetermined amount in the advancing direction X1, and the piston 24 moves to the retracting direction X2 and stops until the state shown in FIG. 13) presses the brake disc 101, and the necessary braking force is output.

When the brake is released from the state shown in FIG. 16 in which the brake is activated, the reverse operation is performed. That is, the compressed air is discharged from the pressure chamber 44, the rod 22 starts to move in the retracting direction X2 by the urging force of the rod urging spring 23, and the roller cam member 51 pushed by the rod side receiving surface 54 is in a brake operation state. Rotates in the opposite direction. Then, the roller cam member 51 moves in the retracting direction X2 while rolling on the rotating portion side receiving surface 55, and the rotating main body member 57 rotates in the direction opposite to the direction of brake operation (counterclockwise when viewed from the piston 24 side). In the direction of rotation). As a result, the inclined surface 48 is pushed in the advance direction X1 while the roller 58 rotates, and the piston 24 moves in the advance direction X1. And in the state which discharge of the compressed air from the pressure chamber 44 was completed, it will return to the state shown in FIG. When the rod 22 moves in the retracting direction X2, the guide tube 28 and the front stopper 31 also move in the retracting direction X2. Then, the clutch nut 30 that contacts the front stopper 31, the screw shaft 27 that is screwed into the clutch nut 30, and the brake output portion 21 that is connected to the screw shaft 27 also move in the retracting direction X2.

Note that the above-described brake operation and brake release operation are operations during normal operation, and the state where compressed air is always supplied to the parking brake release pressure chamber 61 is maintained. On the other hand, when the railway vehicle is parked and the parking brake mechanism 26 is used, the compressed air is discharged from the pressure chamber 61 for releasing the parking brake. FIG. 17 shows a state where the parking brake mechanism 26 is activated and a braking force is generated as a parking brake.

When the compressed air is discharged from the parking brake release pressure chamber 61, the parking brake piston 60 is biased in the retracting direction X2 by the biasing force of the parking brake spring 59. When the parking brake piston 60 moves in the retracting direction X2, the piston 24 biased by the parking brake piston 60 also moves in the retracting direction X2. When the piston 24 moves in the retreat direction X2, the rod 22 moves in the advancing direction X1 via the force-increasing mechanism 25, and the brake output unit 21 also moves in the advancing direction X1, similarly to the brake operation in the normal operation described above. As a result, a braking force as a parking brake is generated.

As described above, according to the brake cylinder device 2, the rod 22 and the piston 24 are configured to advance and retract in a linear direction along the cylinder axis direction, and the piston 24 is configured around the axis of the rod 22. It is arranged to surround. For this reason, the arrangement space of the piston 24 and the rod 22 inside the cylinder main body 20 can be made efficient, and in particular, the arrangement space of the piston 24 and the rod 22 can be greatly reduced in the cylinder axial direction. In addition, a force-increasing mechanism 25 that converts the linear driving force from the piston 24 into the rotational direction to increase the force and act on the rod 22 is disposed in an area secured by the efficiency of arrangement space of the piston 24 and the rod 22. be able to. Then, the braking force is output from the brake output unit 21 that moves together with the rod 22 on which the increased driving force acts. As described above, the efficiency of the arrangement space of the piston 24 and the rod 22 can suppress the size of the brake cylinder device 2 and reduce the size, and the force increasing mechanism 25 can increase the braking force.

Therefore, according to the present embodiment, it is possible to provide a small brake cylinder device 2 that can increase the braking force output from the brake output unit 21 that moves together with the rod 22 while suppressing an increase in the size of the device. it can.

Further, according to the brake cylinder device 2, when the piston 24 moves in the receding direction X 2 along the linear direction, the rotating portion 50 urged by the inclined surface 48 that is inclined in the moving direction of the piston 24. Rotate. Then, by the rotation of the rotation unit 50, the rod 22 whose displacement in the rotation direction is regulated moves in the advance direction X1 and a braking force is output. Therefore, with the simple structure of providing the inclined surface 48 and the rotating portion 50, the driving force generated in the retracting direction X2 by the piston 24 can be efficiently converted to generate the braking force in the advance direction X1 of the rod 22. it can.

Further, according to the brake cylinder device 2, the roller cam member 51, which is a rolling member, is disposed between the rod side receiving surface 54 and the rotating portion side receiving surface 55 facing each other, and the rod side receiving surface 54 and the rotating portion are arranged. The side receiving surface 55 is provided so as to be inclined in the axial direction of the rod 22. For this reason, the structure which moves the rod 22 to the advancing direction X1 via rolling of the roller cam member 51 with rotation of the rotation part 50 is realizable with a simple structure. Then, the driving force converted from the retraction direction X2 to the rotation direction between the inclined surface 48 and the rotation unit 50 is efficiently converted from the rotation direction to the advance direction X1 between the rotation unit 50 and the rod 22. Can do. Further, the ratio of increasing force can be easily adjusted by setting the arrangement of the inclined surface 48 and the roller cam member 51 in the radial direction of the cylinder body 20 (or the radial direction of the rod 22).

Further, according to the brake cylinder device 2, a plurality of roller cam members 51 to which the rotational force is transmitted from the rotating portion 50 are provided along one circumference. For this reason, in the roller cam members 51 arranged in the rotation direction, the transmitted force can be efficiently shared and burdened, and the force acting on one roller cam member 51 can be reduced. As a result, a commonly available rolling member (roller cam member 51) having high availability can be used, and the cost becomes low. In addition, in order to use a commonly available rolling member with high rigidity, compared with the case of trying to reduce the contact surface pressure of one rolling member, one Since it is not necessary to enlarge a rolling member, it can suppress that a rolling member enlarges. Therefore, the enlargement of the brake cylinder device 2 can be further suppressed.

Further, according to the brake cylinder device 2, both the rod side receiving surface 54 and the rotating portion side receiving surface 55 are provided so as to be inclined in the axial direction of the rod 22, and the rolling that forms part of the conical curved surface therebetween. A rolling member as a roller cam member 51 having a surface is disposed. For this reason, the contact surface pressure which acts on one rolling member can be reduced compared with the case where a rolling member is provided as a spherical ball member. Further, with respect to the advance stroke (advance distance) when the rod 22 is moved in the advance direction X 1 through the rolling member along with the rotation of the rotary portion 50, a larger advance stroke with a smaller rotation amount of the rotary portion 50. When the ball member is used as the rolling member, a large-diameter member is required. However, in the rolling member provided as the roller cam member 51, the axial direction of the rod 22 is not increased. It is possible to set the gradient of the inclination of the rod-side receiving surface 54 and the rotating portion-side receiving surface 55 that is inclined to a steeper gradient. Therefore, the advance stroke can be ensured arbitrarily and easily while efficiently suppressing an increase in size of the brake cylinder device 2.

Also, according to the brake cylinder device 2, the parking brake spring 59 that generates the braking force of the parking brake, the parking brake piston 60 that is biased by the parking brake spring 59 and biases the piston 24, and the parking brake release The parking brake mechanism 26 including the pressure chamber 61 can be incorporated in the brake cylinder device 2. Since the parking brake piston 60 that moves parallel to the moving direction of the rod 22 is arranged so as to surround the axis of the rod 22, the arrangement space of the parking brake piston 60 can be made more efficient. The space for disposing the parking brake piston 60 can be greatly reduced. Further, according to the present embodiment, even when a large braking force is required as the braking force of the parking brake, the necessary braking force can be easily ensured by the plurality of parking brake springs 59. Since the plurality of parking brake springs 59 are arranged along the circumferential direction of the cylinder body 20, the parking brake can be easily parked in a compact space while avoiding interference with other parts such as the brake output part 21. A spring 59 can be arranged. For this reason, size reduction (namely, short axis and diameter reduction) can be achieved in the axial direction and radial direction of the brake cylinder device 2.

Further, according to the brake cylinder device 2, since the parking brake spring 59 is disposed outside the cylinder body 20, it is possible to prevent the cylinder body 20 from becoming large. Since a plurality of parking brake springs 59 are arranged on the outside of the cylinder body 20 along the circumferential direction, the parking brake springs 59 are compactly arranged in a space with a margin on the outside of the cylinder body 20. it can. Therefore, the brake cylinder device 2 can be further reduced in size. The present embodiment is configured as a brake cylinder device 2 in which the piston 24 and the parking brake piston 60 move in the retracting direction X2 and the rod 22 moves in the opposite advancing direction X1 during the braking operation. Therefore, the configuration in which the parking brake spring 59 is disposed outside the cylinder body 20 can be realized more easily.

Further, according to the brake cylinder device 2, a plurality of parking brake springs 59 are arranged in parallel to the radial direction of the cylinder body 20 on both sides lateral to the brake output portion 21. For this reason, the plurality of parking brake springs 59 can be arranged in a space-efficient and compact manner while avoiding interference with the brake output portion 21. Moreover, the dead space in the side of the brake output part 21 can be utilized effectively, and the several parking brake springs 59 can be efficiently arranged partially along the circumferential direction of the cylinder body 20. Therefore, the size can be further reduced in the axial direction and the radial direction of the brake cylinder device 2 (that is, the shaft can be further shortened and the diameter can be further reduced).

Further, according to the brake cylinder device 2, during the braking operation, the compressed air is supplied to the pressure chamber 44, so that the force from the piston 24 against the urging force of the rod urging spring 23 is transmitted via the force-increasing mechanism 25. As a result, the rod 22 moves, and the brake output portion 21 moves in the advancing direction X1 via the guide tube 28, the first clutch 32, the clutch nut 30, and the screw shaft 27, and the braking force is output. On the other hand, when the compressed air in the pressure chamber 44 is discharged, the rod 22 moves in the retracting direction X2 by the biasing force of the rod biasing spring 23, and the guide tube 28, the front stopper 31, the clutch nut 30 and the screw shaft 27 are moved. Thus, the brake output unit 21 moves in the retreat direction X2 and the brake is released. When the gap to the brake operation position in the released state becomes large due to wear of the brake pad 13 or the like, the clutch nut 30, the first clutch 32, the second clutch 35, the screw shaft 27, the guide tube 28 The gap is automatically adjusted by a gap adjustment mechanism including the pusher spring 38, the front stopper 31, the adjustment stopper 33, the adjustment spring 34, and the like.

When the clearance adjustment is performed, first, during the braking operation, the movement range of the adjustment stopper 33 is restricted, so that the force that can bias the clutch nut 30 in the retracting direction X2 is stored in the adjustment spring 34 in the adjustment spring 34. Accumulated as power. Further, at this time, the contact between the second clutch 35 to which the adjustment stopper 33 is fixed and the clutch nut 30 is released, and a gap is formed between the second clutch 35 and the clutch nut 30. . When the guide tube 28 starts moving in the retracting direction X2 during the brake releasing operation, the screw shaft 27 and the brake output unit 21 are moved in the retracting direction because the screw shaft 27 is urged by the pusher spring 29 in the advancing direction X1. A state in which the clutch nut 30 is urged in the retracting direction X2 by the stored force of the adjustment spring 34 without moving to X2 occurs. At this time, the clutch nut 30 is released from contact with the first clutch 32 and is not in contact with the front stopper 31, and the clutch nut 30 is also in contact with the second clutch 35. Therefore, the clutch nut 30 can rotate with respect to the screw shaft 27. Then, the clutch nut 30 rotates with respect to the screw shaft 27 so that the clutch nut 30 moves in the retracting direction X2 by the accumulated force of the adjustment spring 34. Thereafter, the gap between the clutch nut 30 and the second clutch 35 disappears, the clutch nut 30 and the second clutch 35 come into contact with each other, the clutch nut 30 becomes non-rotatable, and the guide tube 28 moves in the retracting direction X2. Along with the movement, the brake output unit 21 moves in the retracting direction X2 together with the front stopper 31, the clutch nut 30, and the screw shaft 27, and the brake is released. Thus, since the clutch nut 30 moves relative to the screw shaft 27 in the retracting direction X2 during the brake releasing operation, the position of the screw shaft 27 is moved in the advance direction X1 from the state before the brake releasing operation. This completes the brake release operation. That is, the screw shaft 27 and the brake output unit 21 are moved to a position where they are advanced with respect to the cylinder body 20 as compared with the state before the brake operation. As a result, the gap to the brake operation position in a state where the brake is released is automatically adjusted.

As described above, according to the present embodiment, the clearance adjustment mechanism includes the clutch nut 30, the first clutch 32, the second clutch 35, the screw shaft 27, the guide tube 28, the pusher spring 29, the front stopper 31, the adjustment stopper 33, An adjustment spring 34 is provided. For this reason, the clearance adjustment is not performed by elastic deformation of rubber or the like as in the brake cylinder device disclosed in Patent Document 2, and a configuration that is not easily affected by the surrounding environment such as temperature and humidity is realized at low cost. Can do.

Therefore, according to the present embodiment, in the brake cylinder device having a clearance adjustment mechanism for automatically adjusting the clearance to the brake operation position when the brake is released, the brake cylinder device is affected by the surrounding environment such as temperature and humidity. A difficult-to-use small brake cylinder device 2 can be provided at low cost.

Note that, according to the brake cylinder device 2 according to the present embodiment, in the state where the automatic gap adjustment operation by the gap adjustment mechanism is not performed, regardless of whether the brake operation is being performed or the brake is being released, the second The state in which the clutch 35 and the clutch nut 30 are in contact with each other is maintained, and the second clutch 35 and the clutch nut 30 are prevented from being detached. That is, in a state where the clearance adjustment operation is not performed, the clutch nut 30 is biased in the retracting direction X2 by the adjustment spring 34 whose one end is in contact with the second clutch 35, so that the second clutch 35 and the clutch nut The state where 30 is in contact is maintained. This prevents the clutch nut 30 from rotating with respect to the screw shaft 27 at timings other than the clearance adjustment operation, and prevents the position of the clutch nut 30 from being displaced with respect to the screw shaft 27 due to vibration or the like. Is done.

Further, according to the present embodiment, it is possible to provide a small disc brake device 1 that can increase the braking force while suppressing an increase in the size of the device.

As mentioned above, although embodiment of this invention was described, this invention is not limited to the above-mentioned embodiment, As long as it described in the claim, it can implement variously. For example, the following modifications can be implemented.

(1) In the above-described embodiment, an example in which compressed air is used as the pressure fluid for operating the brake cylinder device has been described as an example. However, the present invention is not limited to this, and other pressure fluid (for example, pressure oil) It may operate.

(2) In the above-described embodiment, the configuration in which the receiving portion in the force-increasing mechanism is formed integrally with the rod has been described as an example, but this need not be the case. The receiving portion may be configured as a member separate from the rod and fixed to the rod. Moreover, about a force increase mechanism, you may implement not only the form illustrated by said embodiment but various changes. For example, the force-increasing mechanism includes the receiving portion fixed to the rod as described above, and the rotating portion is provided so as to be screwed into a screw thread formed on the outer peripheral surface of the receiving portion. The configuration may be such that the receiving portion moves in the advance direction by rotating in the direction.

(3) In the above-described embodiment, the embodiment in which the roller cam member is used as the rolling member has been described as an example. However, this need not be the case. For example, a form in which a rolling member configured as a spherical ball member may be used. In this case, the rod-side receiving surface and the rotating portion-side receiving surface are formed in the form of an inclined groove that is formed in a curved surface according to the shape of the ball member and has a surface that is inclined with respect to the axial direction of the rod. It may be. Further, the arrangement and the number of rolling members and the arrangement and the number of inclined surfaces provided on the piston are not limited to the form exemplified in the above-described embodiment, and various changes may be made.

(4) In the above-described embodiment, both the rod-side receiving surface and the rotating portion-side receiving surface have been described by taking the example in which the rod-side receiving surface and the rotating portion-side receiving surface are inclined with respect to the axial direction of the rod. It does not have to be. You may implement the form provided so that at least any one of a rod side receiving surface and a rotation part side receiving surface might incline with respect to the axial direction of a rod.

(5) In the above embodiment, the mode in which the guide tube is attached to the rod has been described as an example, but this need not be the case, and the mode in which the guide tube is attached to the force-increasing mechanism may be used. In the above embodiment, the pusher spring is described as an example in which the screw shaft is arranged to be urged toward the advance direction with respect to the spline shaft of the force-increasing mechanism which is a portion fixed to the cylinder body. However, this may not be the case, and the pusher spring may be arranged so as to be able to urge the screw shaft toward the advancing direction with respect to a portion other than the cylinder body or the spline shaft fixed to the cylinder body. Good.

(6) In the above embodiment, an example has been described in which the movable stopper is restricted with respect to the member fixed to the cylinder main body. However, this need not be the case. The movable range may be regulated with respect to the main body. In the above-described embodiment, an example in which one end side of the adjustment spring is in contact with or connected to the second clutch has been described as an example, but this need not be the case, and one end side of the adjustment spring may be against the adjustment stopper. It may be in the form of contact or connection. In addition, about the shape and arrangement | positioning of an adjustment spring, an adjustment stopper, a front stopper, an adjustment sleeve, and a spring receiver, it may change and implement not only what was illustrated in embodiment. Moreover, you may change and implement also about the shape of a clutch nut, a 1st clutch, and a 2nd clutch.

(7) In the above-described embodiment, an example in which only the front stopper is fixed to the inner periphery of the guide tube by screw connection has been described as an example. It may be fixed to the inner periphery of the guide tube by screw connection. The front stopper may be fixed by press-fitting with respect to the inner periphery of the guide tube. In the above embodiment, teeth that can engage the second clutch and the clutch nut are formed on both the surface of the second clutch that faces the clutch nut and the surface of the clutch nut that faces the second clutch. Although the description has been made taking the formed form as an example, this need not be the case, and a form in which teeth are formed on any one of the surfaces facing each other may be used.

The present invention can be widely applied to a brake cylinder device that is actuated by a pressure fluid to move a rod and a disc brake device including the brake cylinder device.

2 Brake cylinder device 20 Cylinder body 21 Brake output part 22 Rod 23 Rod biasing spring 24 Piston 25 Boosting mechanism 44 Pressure chamber

Claims

A cylinder body having a hollow interior;
A rod disposed inside the cylinder body, and is provided so as to be movable in a linear direction along the cylinder axis direction and in an advancing direction that advances from the cylinder body and a retracting direction that retracts in the opposite direction;
A rod biasing spring capable of biasing the rod in the retracting direction;
In the cylinder body, the pressure chamber is partitioned and is disposed so as to surround the rod axis in the circumferential direction, and is provided so as to be movable along a linear direction parallel to the movement direction of the rod. A piston that moves in the retraction direction with respect to the cylinder body against a biasing force of the rod biasing spring by being supplied with a pressure fluid;
When the piston moves in the retraction direction, the linear driving force generated in the piston is converted into a rotation direction, the rod is moved in the advance direction, and the driving force from the piston is increased to increase the driving force. A force-increasing mechanism that acts on the rod;
A brake output unit provided so as to be movable together with the rod, and capable of outputting a braking force by the rod moving in the advance direction;
A brake cylinder device comprising:
The brake cylinder device according to claim 1,
The force-increasing mechanism is
An inclined surface provided on the piston, extending along a circumferential direction centered on the axial center of the piston and inclined with respect to the moving direction of the piston;
A rotating part that is urged by the inclined surface when the piston moves in the retracting direction and rotates in a predetermined rotating direction around the axial center of the rod;
With
The rod is connected to the cylinder body so as to be restricted from displacement in a rotational direction around the axial center of the rod, and the advancement is performed in accordance with the rotation of the rotating portion in a predetermined rotational direction. Brake cylinder device characterized by moving in a direction.
The brake cylinder device according to claim 2,
The force-increasing mechanism is
A receiving part formed integrally with the rod or fixed to the rod;
A rod-side receiving surface provided in the receiving portion and disposed so as to extend along a circumferential direction centering on an axial center of the rod;
Provided in the rotating portion disposed so as to face the receiving portion in a direction parallel to the axial direction of the rod, and extends along a circumferential direction centering on the axial center of the rotating portion. The rotating part side receiving surface arranged;
A rolling member disposed between the rod side receiving surface and the rotating portion side receiving surface and capable of rolling with respect to the rod side receiving surface and the rotating portion side receiving surface;
Further comprising
At least one of the rod side receiving surface and the rotating portion side receiving surface is provided so as to be inclined with respect to the axial direction of the rod.
The brake cylinder device according to claim 3, wherein
The brake cylinder device according to claim 1, wherein a plurality of the rolling members are provided so as to be positioned along one circumference centered on an axial center of the rod.
The brake cylinder device according to claim 3 or claim 4, wherein
Both the rod side receiving surface and the rotating part side receiving surface are provided so as to be inclined with respect to the axial direction of the rod,
The rolling member is provided as a plurality of roller cam members that are rotatably supported,
A side surface of the roller cam member is provided as a rolling surface that extends in the circumferential direction so as to constitute a part of a conical curved surface and rolls with respect to the rod side receiving surface and the rotating portion side receiving surface. Brake cylinder device characterized by
The brake cylinder device according to any one of claims 1 to 5,
A parking brake mechanism used when parking a vehicle equipped with the brake cylinder device;
The parking brake mechanism is
A plurality of parking brake springs arranged so as to be aligned along the circumferential direction of the cylinder body;
Inside the cylinder body, a second pressure chamber for releasing the parking brake that is different from the pressure chamber is defined, and is arranged so as to surround the axis of the rod in the circumferential direction, and is parallel to the moving direction of the rod. It is provided so as to be movable along the direction, and when the pressure fluid is discharged from the second pressure chamber, it moves in the retraction direction with respect to the cylinder body by the biasing force of the parking brake spring, and the piston is moved. An energizing parking brake piston;
A brake cylinder device comprising:
The brake cylinder device according to claim 6, wherein
The brake cylinder device according to claim 1, wherein the plurality of parking brake springs are disposed outside the cylinder body.
The brake cylinder device according to claim 6 or 7,
The plurality of parking brake springs are arranged in a direction parallel to the radial direction of the cylinder body with respect to the brake output portion, and are arranged on both sides on the side.
The brake cylinder device according to any one of claims 1 to 8,
A screw shaft connected to the brake output part and having a screw formed on the outer periphery;
A guide tube attached to the rod or the force-increasing mechanism and having the screw shaft disposed inside;
A pusher spring disposed so as to be able to bias the screw shaft toward the advance direction with respect to the cylinder body or a portion fixed to the cylinder body;
A clutch nut that is screwed to the tip end side of the screw shaft that is disposed on the brake output portion side with respect to the cylinder body;
The clutch nut is disposed so as to be able to contact the clutch nut from the front side which is the brake output portion side so as to restrict the movement of the clutch nut with respect to the guide tube. And a front stopper capable of urging the screw shaft in the retracting direction;
A first clutch disposed so as to be able to contact the clutch nut from the rear side opposite to the brake output unit side with respect to the clutch nut via a predetermined distance from the front stopper;
An adjustment stopper that is disposed so as to be relatively movable along the axial direction of the screw shaft with respect to the clutch nut and the guide tube, and in which the movable range is restricted with respect to the cylinder body or a member fixed to the cylinder body. When,
A second clutch fixed to the adjustment stopper and arranged so as to be able to contact the clutch nut from the rear side;
One end side contacts or connects to the adjustment stopper or the second clutch, and an adjustment spring capable of biasing the clutch nut toward the retracting direction;
A brake cylinder device, further comprising:
A brake cylinder device according to any one of claims 1 to 9, and a caliper body equipped with the brake cylinder device and attached so as to be relatively displaceable in the axle direction with respect to the vehicle. Prepared,
The disc brake device is characterized in that when the brake cylinder device is operated, a disc on the axle side is sandwiched between a pair of brake pads attached to the caliper body to generate a braking force.