HK1172674B - Brake cylinder device and disk brake device - Google Patents

Description

Brake cylinder device and disc brake device

Technical Field

The present invention relates to a brake cylinder device having a clearance adjustment mechanism for automatically adjusting a clearance from an end of a brake output portion in a brake released state to a brake operation position, and a disc brake device having the same.

Background

There is known a brake cylinder device disclosed in patent document 1 having a clearance adjustment mechanism for automatically adjusting a clearance from an end of a brake output unit in a brake released state to a brake operation position (a position where a braking force can be generated). The brake cylinder device disclosed in patent document 1 includes an ejector having an uneven surface formed on an outer surface thereof, and a guide member movable together with the ejector. An O-ring engaged with the concave-convex surface is disposed in a space between the guide member and the lift pin, and when a predetermined force or more is applied to the guide member, the O-ring goes over the convex portion of the concave-convex surface, thereby automatically adjusting a gap from an end portion of the brake output portion in a state where the brake is released to the brake operation position. In this way, since the clearance adjustment mechanism is constituted by the concave-convex surface and the O-ring engaged with the concave-convex surface, the brake cylinder device having the clearance adjustment mechanism which is easy to adjust and manage the sliding resistance can be realized with a simple structure.

On the other hand, a brake cylinder device having a clearance adjustment mechanism without using an O-ring, which is different from the above-described one, is known from patent document 2. The clearance adjustment mechanism of the brake cylinder device disclosed in patent document 2 is provided with a cylindrical sheath rod supported rotatably with respect to a piston via a bearing, and having a linear key groove and a spiral key groove formed in an outer periphery thereof, and a push rod attached to a push rod base screwed to an inner periphery of the sheath rod. Further, teeth of a gear of a ratchet mechanism whose rotation direction is regulated by engagement with the pawl are fitted into the respective key grooves of the sheath rod. Therefore, when the stroke of the piston is equal to or greater than a predetermined stroke during the braking operation, the engagement position between the pawl and the ratchet gear is shifted. Thereby, the gap from the end of the brake output unit in the brake released state to the brake operating position is automatically adjusted.

Prior art documents

Patent document

Patent document 1: japanese laid-open patent publication No. 2007-131203

Patent document 2: japanese Kokai publication Sho-61-59158

Since the clearance adjustment mechanism in the brake cylinder device disclosed in patent document 1 utilizes elastic deformation of the O-ring, the clearance adjustment mechanism is susceptible to the influence of the surrounding environment such as temperature and humidity during operation. Therefore, it is necessary to construct the gap adjusting mechanism using an O-ring made of a special material that is not easily affected by the surrounding environment such as temperature and humidity, which leads to an increase in cost. On the other hand, since the clearance adjustment mechanism in the brake cylinder device disclosed in patent document 2 does not use an O-ring, the cost for suppressing the influence of the surrounding environment such as temperature and humidity is hardly required. However, in the case of the gap adjustment mechanism disclosed in patent document 2, a bearing for rotatably supporting the sheath rod is required on the side opposite to the brake output portion disposed on the front side, which is the tip end side of the jack rod, that is, on the rear side, which is the piston side. Therefore, the diameter of the rear side of the cylinder main body in which the piston is disposed is limited to be small.

Disclosure of Invention

In view of the above circumstances, an object of the present invention is to provide, at low cost, a brake cylinder device having a clearance adjustment mechanism for automatically adjusting a clearance from an end of a brake output portion in a brake released state to a brake operation position, which is less susceptible to an influence of an ambient environment such as temperature and humidity, and which is capable of reducing a radial dimension of a cylinder main body. Another object of the present invention is to provide a disc brake device having the brake cylinder device.

The brake cylinder device according to claim 1 for achieving the above object is characterized in that

Transmitted by a force increasing mechanism. On the other hand, by discharging the pressure fluid in the pressure chamber, the piston moves in the opposite direction by the biasing force of the piston spring, and the brake output portion moves in the anti-braking direction via the guide pipe, the front clutch, the clutch nut, and the threaded shaft, thereby releasing the brake. When the clearance between the end of the brake output unit in the brake released state and the brake operating position becomes large due to wear of the brake pads or the like, the clearance is automatically adjusted by a clearance adjustment mechanism including a clutch nut, a front clutch, a rear clutch, a threaded shaft, a guide tube, a thrust spring, a stopper, and an adjustment spring.

When adjusting the clearance, first, by limiting the movement range of the stopper at the time of braking operation, the biasing force that can be applied to the clutch nut in the anti-braking direction is accumulated in the adjustment spring as the accumulated force of the adjustment spring. When the guide pipe starts moving in the anti-braking direction during the brake release operation, the screw shaft is biased in the braking direction by the thrust spring, and therefore, the following state occurs: the threaded shaft and the brake output portion do not move in the anti-braking direction, and the clutch nut is biased in the anti-braking direction by the stored force of the adjustment spring. At this time, the clutch nut is released from contact with the rear clutch and is not in contact with the front clutch, and the clutch nut is rotatable with respect to the threaded shaft. Then, the clutch nut is rotated relative to the threaded shaft so as to move in the anti-braking direction by the stored force of the adjustment spring. Then, the clutch nut comes into contact with the front clutch to be in a state where the clutch nut cannot rotate, and the brake output portion moves in the anti-braking direction together with the front clutch, the clutch nut, and the threaded shaft as the guide pipe moves in the anti-braking direction, and the brake is released. In this way, since the clutch nut moves in the reverse braking direction with respect to the screw shaft during the braking release operation, the braking release operation is terminated when the position of the screw shaft is in a state of being moved in the braking direction from the state before the braking release operation. That is, the state is shifted to a state where the threaded shaft and the brake output portion are moved to a position protruding from the cylinder main body, compared to the state before the braking operation. Thereby, the gap from the end of the brake output unit in the brake released state to the brake operating position is automatically adjusted.

As described above, according to the present invention, the clearance adjustment mechanism includes the clutch nut, the front and rear clutches, the threaded shaft, the guide tube, the thrust spring, the stopper, and the adjustment spring. Therefore, a brake cylinder device in which the clearance is adjusted by elastic deformation of rubber or the like is not used, and a structure that is not easily affected by the surrounding environment such as temperature and humidity can be realized at low cost. Further, since the structure in which the guide pipe is attached to the piston or the force increasing mechanism does not require the provision of a bearing, the diameter dimension of the rear side of the cylinder main body can be reduced.

Therefore, according to the present invention, it is possible to provide at low cost a brake cylinder device having a clearance adjustment mechanism for automatically adjusting a clearance from an end portion of a brake output portion in a brake released state to a brake operation position, which is less susceptible to an influence of an ambient environment such as temperature and humidity, and which is capable of reducing a radial dimension of a cylinder main body.

The brake cylinder device according to claim 2 of claim 1 is characterized in that the threaded shaft is hollow so as to open to a side opposite to the brake output portion, and the thrust spring biases the clutch nut screwed to the threaded shaft toward the front clutch by biasing the threaded shaft from inside.

In the present invention, the thrust spring for urging the screw shaft is disposed inside the screw shaft formed in the hollow structure, and urges the clutch nut screwed to the screw shaft toward the front clutch. Therefore, the thrust spring can be disposed by efficiently utilizing the space of the brake cylinder device. This improves the space efficiency of the brake cylinder device, and further reduces the size of the brake cylinder device.

The brake cylinder device according to claim 3 of claim 2 is characterized by further comprising a thrust spring guide formed as a shaft-like portion provided so as to be movable together with the guide pipe, the thrust spring guide being inserted into an inner side of the thrust spring provided as a coil spring to restrict deformation of the thrust spring in a buckling direction, a tip end portion of the thrust spring guide being opposed to the thrust spring, and the thrust spring guide being provided so as to be movable together with the guide pipe

A brake cylinder device according to any one of claims 1 to 12, wherein a caliper body equipped with the brake cylinder device and mounted to be displaceable in an axle direction relative to a vehicle is operated by the brake cylinder device, and a pair of brake pads mounted to the caliper body sandwich a disc on the axle side to generate a braking force.

The present invention can provide a disc brake device including a brake cylinder device provided with a clearance adjustment mechanism for automatically adjusting a clearance from an end of a brake output portion in a brake released state to a brake operation position, which is less susceptible to an influence of ambient environments such as temperature and humidity, and which can reduce a radial dimension of a cylinder main body at low cost.

The present invention can provide a brake cylinder device at low cost that has a clearance adjustment mechanism for automatically adjusting a clearance from an end of a brake output portion in a brake released state to a brake operation position, that is less susceptible to the influence of ambient environments such as temperature and humidity, and that can reduce the radial dimension of a cylinder main body. Further, a disc brake device having the brake cylinder device can be provided at low cost.

Drawings

Fig. 1 is a side view of a disc brake apparatus according to an embodiment of the present invention.

Fig. 2 is a plan view of the disc brake apparatus shown in fig. 1.

Fig. 3 is a sectional view of a brake cylinder device according to embodiment 1 of the present invention.

Fig. 4 is a diagram showing a state in which the brake output portion, the nut member, and the distal end portion of the threaded shaft of the brake cylinder device shown in fig. 3 are viewed from the direction of arrow C.

Fig. 5 is an enlarged cross-sectional view showing a part of the brake cylinder device shown in fig. 3 in an enlarged manner.

Fig. 6 is a sectional view of the brake cylinder device shown in fig. 3, which is a sectional view for explaining a case where the brake cylinder device is operated without automatically adjusting the clearance by the clearance adjusting mechanism.

Fig. 7 is a sectional view of the brake cylinder device shown in fig. 3, which is a sectional view for explaining a case where the brake cylinder device is operated without automatically adjusting the clearance by the clearance adjusting mechanism.

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

The pair of brake levers (15, 15) are attached with the brake cylinder device 2 at one end thereof via a cylinder support pin 15b, and the one end is driven by the brake cylinder device 2. Further, a pair of backing plates (12, 12) for holding the brake pad 13 are attached to the other end side of the pair of brake levers (15, 15) with the fulcrum pin 15a interposed therebetween from the one end side to which the brake cylinder device 2 is attached. The backing 12 is swingably attached to the brake lever 15 via a support pin 12a extending parallel to the fulcrum pin 15a with respect to the brake lever 15.

In the 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, the brake output portion 21 is attached to the other brake lever 15, and the brake output portion 21 is operated to protrude or approach from the cylinder body 20 by the operation of the brake cylinder device 2. Thereby, the cylinder support pins 15b of the pair of brake levers (15, 15) are driven to be close to or separate from each other.

By driving as described above, the disc brake device 1 operates such that the pair of brake levers (15, 15) operate with the fulcrum pins 15a as support shafts, and the brake disc 101 is sandwiched by the brake pads 13. At this time, in the pair of brake levers (15, 15), the one brake pad 13 provided in the one brake lever 15 first contacts the braking surface 101a of the brake disc 101. The other brake lever 15 presses the other brake pad 13 against the braking surface 101a of the brake disc 101 by a reaction force received from the one brake pad 13 that is in contact with the braking surface 101 a. Thus, the brake disc 101 is sandwiched by the pair of brake pads (13, 13), and the rotation of the brake disc 101 is braked by the frictional force generated between the brake pads (13, 13) and the braking surfaces (101 a ), thereby braking the rotation of the wheel of the railway vehicle disposed coaxially with the brake disc 101.

Next, a brake cylinder device 2 according to embodiment 1 of the present invention will be described in detail. Fig. 3 is a sectional view of the brake cylinder device 2. The brake cylinder device 2 shown in fig. 3 is configured similarly to the brake cylinder device 2 shown in fig. 1 and 2, but a part of the external shape is modified and shown in the drawings. Both ends of the brake cylinder device 2 in the braking operation direction are coupled to cylinder support pins 15b, respectively. The brake cylinder device 2 includes a cylinder body 20, a brake output portion 21, a piston 22, a piston spring 23, a threaded shaft 24, a guide pipe 25, a thrust spring 26, a clutch nut 27, a front clutch 28, a rear clutch 29, a stopper 30, an adjustment spring 31, a thrust spring guide 32, an adjustment sleeve 33, a spring stopper 34, a nut member 38, a bearing 40, and the like. Of the above-described components, the members other than the adjustment sleeve 33 are made of a metal material such as an iron-based material, and the adjustment sleeve 33 is made of a resin material, for example. In fig. 3, a part of the threaded shaft 24, a part of the stopper 30, the nut member 38, and the like are not illustrated in cross section but illustrated in external form.

The cylinder main body 20 is constituted by a 1 st shell portion 35 and a 2 nd shell portion 36, and the inside thereof is formed to be hollow. The cylinder body 20 houses a piston 22, a piston spring 23, a part of a threaded shaft 24, a guide pipe 25, a thrust spring 26, a clutch nut 27, a front clutch 28, a rear clutch 29, a stopper 30, an adjustment spring 31, a thrust spring guide 32, an adjustment sleeve 33, a spring stopper 34, and the like. The 1 st housing part 35 is formed in a substantially cup shape having a bottom, and the 2 nd housing part 36 is fixed by bolts so as to close the open side of the 1 st housing part 35. Further, the end of the 1 st housing portion 35 is connected to one brake lever 15 by a cylinder support pin 15 b. In addition, the 2 nd casing part 36 is provided with a flat plate-like portion 36a and a cylindrical portion 36b, the flat plate-like portion 36a is formed in a flange shape so as to close the 1 st casing part 35, and the cylindrical portion 36b is formed in a cylindrical shape protruding perpendicularly to the flat plate-like portion 36 a.

The opposite side of the portion 21, that is, the rear side, is disposed so as to be able to contact the convex portion 27a with a predetermined gap from the front clutch 28.

The surface of the rear clutch 29 facing the clutch nut 27 is a tapered surface formed to be inclined with respect to the axial direction so as to form a part of a conical curved surface having the axial direction of the screw shaft 24 as a center line. Further, the surface of the convex portion 27a of the clutch nut 27 facing the rear clutch 29 is also provided as a tapered surface formed obliquely with respect to the axial direction so as to constitute a part of a conical curved surface having the axial direction of the threaded shaft 24 as a center line. The surfaces of the rear clutch 29 and the clutch nut 27 facing each other are inclined at substantially the same angle in the axial direction of the threaded shaft 24, and are provided so as to abut against and fit each other.

The stopper 30 includes: a ring portion 30a formed in a ring shape; and a pair of protruding portions (30 b ) fixed to the ring portion 30a and provided in a block shape protruding outward in the radial direction of the ring portion 30 a. The ring portion 30a is disposed around the threaded shaft 24 and an adjustment sleeve 33 described later and inside the guide pipe 25. The ring portion 30a has an end in the braking direction abutting against the adjustment sleeve 33, and an end in the anti-braking direction abutting against an adjustment spring 31 described later.

The pair of protruding portions (30 b ) of the stopper 30 are provided so as to be disposed at positions along the diameter direction of the ring portion 30a, and are disposed so as to protrude so as to penetrate the pair of slit holes (25 b ) of the guide tube 25. Further, a pair of stopper stroke limiting portions (39, 39) are provided in the cylindrical portion 36b of the 2 nd housing portion 36 of the cylinder body 20 at positions along the diameter direction of the cylindrical portion 36b, and the pair of stopper stroke limiting portions (39, 39) are provided as holes extending parallel to the axial direction of the screw shaft 24 and formed to penetrate in a slit shape. The projecting end portions of the projecting portions 30b are disposed so as to be movable along the stopper stroke restricting portion 39, and are disposed so as to be capable of abutting against an end portion of the stopper stroke restricting portion 39 in the braking direction and an end portion of the stopper stroke restricting portion 39 in the anti-braking direction, respectively.

By providing the stopper 30 as described above, the stopper is disposed so as to be movable relative to the clutch nut 27 and the guide pipe 25 in the axial direction of the threaded shaft 24, and the movable range relative to the cylinder main body 20 is limited.

The adjustment sleeve 33 is a flexible cylindrical member formed of resin, and is disposed around the threaded shaft 24. An engaging portion 33a formed as a concave-convex portion is provided on the outer periphery of the end portion of the adjustment sleeve 33 in the braking direction. An engaged portion 27c formed as an uneven portion to be engaged with the uneven portion of the engaging portion 33a is provided on the inner periphery of the end portion of the clutch nut 27 in the anti-braking direction. The adjustment sleeve 33 and the clutch nut 27 are integrated by engaging the engagement portion 33a on the adjustment sleeve 33 side with the engaged portion 27c on the clutch nut 27 side.

The engaging portion 33a of the adjustment sleeve 33 is provided so as to engage with an engaged portion 27c formed on the inner peripheral side of the clutch nut 27 from the inside. Further, the dimension of the gap formed between the inner periphery of the adjustment sleeve 33 and the crest of the thread 24a of the threaded shaft 24 in the radial direction of the adjustment sleeve 33 is smaller than the dimension of the concave-convex portion where the engaging portion 33a and the engaged portion 27c are fitted to each other in the radial direction of the adjustment sleeve 33 (the amount of overlap of the concave-convex portion in the radial direction of the adjustment sleeve 33).

The adjustment spring 31 is provided as a spiral spring disposed around the adjustment sleeve 33. The adjustment spring 31 is disposed such that one end side thereof is in contact with (or connected to) an end portion of the ring portion 30a of the stopper 30 in the anti-braking direction and the other end side thereof biases the spring stopper 34 and the bearing 40, and the spring stopper 34 and the bearing 40 function as spring seats disposed at the end portion of the adjustment sleeve 33 in the anti-braking direction. Thereby, the adjustment sleeve 33 is biased in the anti-braking direction by the other end side of the adjustment spring 31, one end side of which abuts against the stopper 30. The adjustment spring 31 can bias the clutch nut 27 engaged with the adjustment sleeve 33 and integrated with the adjustment sleeve 33 in the anti-braking direction.

The bearing 40 is disposed between the outer periphery of the adjustment sleeve 33 and the inner periphery of the guide pipe 25, and is engaged with the adjustment sleeve 33 formed in the entire circumferential direction

(D3 < D2). That is, since the clutch nut 27 is relatively moved in the anti-braking direction with respect to the threaded shaft 24 in the middle of the brake release operation, the brake release operation is ended at a position where the threaded shaft 24 is moved in the braking direction from the state before the brake release operation. Then, the state is shifted to a state in which the threaded shaft 24 and the brake output portion 21 are moved to a position protruding from the cylinder main body 20 compared to the state before the braking operation and the braking release operation are performed. This makes it possible to automatically adjust the gap from the end 21c of the brake output unit 21 in the brake released state to the brake operating position P.

Next, with reference to fig. 17 to 20, the operation of the brake cylinder device 2 in a case where the clearance adjusting operation is forcibly performed in a state where the brake pad 13 is not in contact with the brake disc 101 and no braking force is generated, that is, in a so-called idling state (since the clearance adjustment is performed by a force generated when the brake pad 13 is in contact with the brake disc 101, the clearance cannot be adjusted if the brake pad is not in contact with the brake disc) will be described. Fig. 17 is a sectional view showing a state before compressed air is supplied to the pressure chamber 37 in the idling state (i.e., a state corresponding to the brake released state). For example, a state in which the clearance adjusting operation is to be performed after the replacement operation of the brake pads 13 of the disc brake device 1 is performed is shown.

In the above case, by supplying compressed air to the pressure chamber 37, first, the state shown in the cross-sectional view of fig. 17 is transited to the state shown in the cross-sectional view of fig. 18. That is, as the compressed air is supplied to the pressure chamber 37, the piston 22 moves in the braking direction together with the guide pipe 25 against the biasing force of the piston spring 23. The threaded shaft 24 moves in the braking direction together with the guide tube 25 and the thrust spring 26, the stopper 30 and the adjustment spring 31 also move in the braking direction together with the adjustment sleeve 33, and the adjustment sleeve 33 engages with the clutch nut 27 screwed to the threaded shaft 24. As shown in the sectional view of fig. 18, the protruding portion 30b of the stopper 30 abuts on the end of the stopper stroke limiting portion 39 in the braking direction. Thereby, the stopper 30 reaches the forward limit, and the movement of the stopper 30 in the forward direction (braking direction) with respect to the cylinder body 20 is restricted.

In the state shown in fig. 18, the stopper 30 is moved relative to the cylinder main body 20

As described above, if the clutch nut 27 is not in contact with both the front clutch 28 and the rear clutch 29 and is in a rotatable state with respect to the threaded shaft 24, the clutch nut 27 rotates with respect to the threaded shaft 24 so as to move in the anti-braking direction by the stored force of the adjustment spring 31 corresponding to the dimension F2. With the clutch nut 27 thus rotated relative to the threaded shaft 24, the dimension F2 shown in fig. 20 is reduced. Further, the state in which the clutch nut 27 is not in contact with both the front clutch 28 and the rear clutch 29 and is rotated relative to the threaded shaft 24 continues until the dimension F2 becomes zero. The rotation of the clutch nut 27 until the dimension F2 becomes zero is not limited to being completed in a period in which the operation corresponding to the braking operation and the braking release operation is performed 1 time, and may be completed in a period in which the operation corresponding to the braking operation and the braking release operation is performed a plurality of times.

As described above, even in the idle state, the clutch nut 27 moves relatively in the anti-braking direction with respect to the threaded shaft 24 during the operation corresponding to the braking operation, and therefore, the operation corresponding to the braking operation is ended at a position where the threaded shaft 24 is moved in the braking direction than the state before the operation corresponding to the braking operation. Then, the state is shifted to a state in which the threaded shaft 24 and the brake output portion 21 are moved to a position protruding from the cylinder main body 20 compared to the state before the operation corresponding to the braking operation. Thus, when maintenance work such as replacement work of the brake pads 13 is completed and the brake is enabled from the idling state, the gap from the end 21c of the brake output unit 21 in the brake released state to the brake operating position P is automatically adjusted.

As described above, with the brake cylinder device 2, the clearance adjustment mechanism is constituted by the clutch nut 27, the front clutch 28, the rear clutch 29, the threaded shaft 24, the guide pipe 25, the thrust spring 26, the stopper 30, the adjustment spring 31, and the like. Therefore, a structure that is not a brake cylinder device in which the clearance is adjusted by elastic deformation of rubber or the like can be realized that is not easily affected by the surrounding environment such as temperature and humidity. Further, in the structure in which the guide pipe 25 is attached to the piston 22, the bearing 40 is not required, and therefore, the diameter size of the rear side (the end side in the anti-braking direction) of the cylinder body 20 can be reduced.

Thus, according to the present embodiment, there is provided the brake cylinder device 2 having the clearance adjustment mechanism for automatically adjusting the clearance from the end portion 21c of the brake output portion 21 in the brake released state to the brake operating position P, which is less susceptible to the influence of the surrounding environment such as temperature and humidity, and which can reduce the radial dimension of the cylinder main body 20 at low cost.

Further, with the brake cylinder device 2, the thrust spring 26 that biases the threaded shaft 24 is disposed inside the threaded shaft 24 formed in the hollow structure, and biases the clutch nut 27 screwed to the threaded shaft 24 toward the front clutch 28. Therefore, the thrust spring 26 can be disposed by efficiently utilizing the space of the brake cylinder device 2. This can improve the space efficiency of the brake cylinder device 2, and can achieve further downsizing.

Further, with the brake cylinder device 2, the thrust spring guide 32 is provided, and the thrust spring guide 32 extends inside the spiral thrust spring 26 to restrict deformation of the thrust spring 26 in the buckling direction. Therefore, even when the size of the gap to be adjusted is increased and a long thrust spring 26 is required as the gap adjustment mechanism, buckling of the thrust spring 26 can be prevented efficiently. Further, a tip end portion of a thrust spring guide 32 provided movably together with the guide pipe 25 is slidably disposed inside the screw shaft 24. Therefore, with a simple structure in which the shaft-shaped thrust spring guide 32 is provided, a structure in which the positional relationship between the screw shaft 24 and the piston 22 is maintained in a shifted relationship on the same axis can be easily realized.

In addition, with the brake cylinder device 2, the front clutch 28 and the rear clutch 29 are provided as separate integral members and are fixed to the guide pipe 25 independently of each other. Therefore, it is not necessary to provide the front clutch 28 and the rear clutch 29 disposed in front of and behind the clutch nut 27 in a split structure and to couple them with a separate coupling member. Similarly, it is not necessary to provide the clutch nut 27, in which the front clutch 28 and the rear clutch 29 are arranged in the front and rear, with a split structure and to couple them with a separate coupling member. This enables the front clutch 28, the rear clutch 29, and the clutch nut 27 to be engaged

Since the female screw 27 is engaged by the teeth (27 b, 28 a) formed on the surfaces facing each other, the rotation of the clutch nut 27 due to vibration or the like can be prevented. Even when the gap adjustment operation is repeated to bring about a state in which the adjustment amount of the gap is increased and the biasing force of the thrust spring 26 is reduced (a state in which the thrust spring 26 is extended), it is possible to prevent the clutch nut 27 from rotating due to vibration or the like when braking is not performed.

Further, in the brake cylinder device 2, the threaded shaft 24 is engaged with the brake output portion 21 by screwing the nut member 38 to the distal end portion of the threaded shaft 24, and the distal end portion of the threaded shaft 24 is disposed so as to penetrate the brake output portion 21 to face outward and is provided with a hexagonal hole 24c as an engagement portion for operation. Therefore, the nut member 38 is loosened to release the engagement between the threaded shaft 24 and the brake output portion 21, and the threaded shaft 24 is rotated by a tool for operation, so that the threaded shaft 24 can be manually rotated, and the positional relationship between the threaded shaft 24 and the clutch nut 27 can be easily restored to the state before the clearance adjustment, that is, the initial state.

Further, according to the present embodiment, there is provided a disc brake device 1 including a brake cylinder device 2, in which the brake cylinder device 2 is provided with a clearance adjustment mechanism for automatically adjusting a clearance from an end portion 21c of a brake output portion 21 in a brake released state to a brake operating position P, and which is capable of reducing the radial dimension of a cylinder main body 20 while being less susceptible to an influence of an ambient environment such as temperature and humidity at low cost.

Embodiment 2

Next, a brake cylinder device 3 according to embodiment 2 of the present invention will be described. Fig. 21 is a sectional view of the brake cylinder device 3 of embodiment 2. The brake cylinder device 3 shown in fig. 21 is provided as a brake cylinder device provided in the disc brake device 1, similarly to the brake cylinder device 2 of embodiment 1. In fig. 21, some components of the brake cylinder device 3 are not shown in cross section but are shown in outer diameter.

The brake cylinder device 3 includes a cylinder body 20, a brake output portion 21, a piston 50, a piston spring 23, a threaded shaft 24, a guide pipe 25, a thrust spring 26, a clutch nut 27, a front clutch 28, a rear clutch 29, a stopper 30, an adjustment spring 31, a thrust spring guide 32, an adjustment sleeve 33, a spring stopper 34, a nut member 38, a bearing 40, and the like, as in the brake cylinder device 2 of embodiment 1. Of the above-described components, the members other than the adjustment sleeve 33 are formed of a metal material such as an iron-based material, and the adjustment sleeve 33 is formed of a resin material, for example.

As described above, the brake cylinder device 3 is configured in the same manner as the brake cylinder device 2 according to embodiment 1. However, the brake cylinder device 3 is different from the brake cylinder device 2 according to embodiment 1 in that a force increasing mechanism 51 is further provided, and the moving direction of the piston 50 is opposite to the moving direction of the piston 22 according to embodiment 1. In the following description of the brake cylinder device 3, a structure different from that of embodiment 1 will be described, and elements configured to have the same functions as those of embodiment 1 will be denoted by the same reference numerals and will not be described.

The piston 50 includes a disk-shaped portion 52 and a pair of plate-shaped portions 53 (only one plate-shaped portion 53 is shown in fig. 21), and the pair of plate-shaped portions 53 protrude from the disk-shaped portion 52 in parallel with the threaded shaft 24 and the guide pipe 25 in the anti-braking direction (the direction indicated by the arrow B in fig. 21). Further, a cylindrical portion 54 extending toward the 1 st housing portion 35 side (i.e., in the anti-braking direction) is formed inside the 2 nd housing portion 36 of the cylinder main body 20. A through hole 52a is formed in the center of the disk-shaped portion 52, and a cylindrical portion 54 of the cylinder main body 20 is inserted through the through hole 52 a. Thus, the piston 50 is disposed between the outer peripheral surface of the cylindrical portion 54 and the inner peripheral surface of the 2 nd housing portion 36. That is, the piston 50 is disposed so as to divide a space between the outer peripheral surface of the cylindrical portion 54 and the inner peripheral surface of the 2 nd housing portion 36 into two parts, and is relatively movable in the axial direction with respect to the cylinder main body 20. Further, a pressure chamber 37 is defined between the piston 50 and the 2 nd housing portion 36.

Further, a pair of guide shafts 55 (only one guide shaft 55 is illustrated in fig. 21) extending in parallel with the axial directions of the threaded shaft 24 and the guide pipe 25 are provided in the cylinder body 20. The disc-shaped portion 52 of the piston 50 is provided with guide holes 52b through which the guide shafts 55 are inserted. Further, a piston spring 23 is disposed around each guide shaft 55

The brake output unit 21 moves in the anti-braking direction. Also, during the brake release operation, the 1 st support member 57 is biased in the anti-braking direction by the spring 62, and therefore the 1 st rolling member 59 rolls in the 1 st inclined groove, and the 2 nd rolling member 60 rolls in the 2 nd inclined groove.

Further, the gap adjustment mechanism constituted by the clutch nut 27, the front clutch 28, the rear clutch 29, the threaded shaft 24, the guide tube 25, the thrust spring 26, the stopper 30, the adjustment spring 31, and the like operates in the same manner as in the case of embodiment 1. Therefore, in the present embodiment, as in embodiment 1, there is also provided a brake cylinder device 3 including a clearance adjustment mechanism for automatically adjusting a clearance from an end portion 21c of a brake output portion 21 in a brake released state to a brake operation position, which is less susceptible to an influence of an ambient environment such as temperature and humidity, at a low cost, and which is capable of reducing the radial dimension of a cylinder main body 20.

Modification example

While the embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and can be implemented by being variously modified within the scope of the claims. For example, the following modifications can be implemented.

(1) In embodiment 1, the description has been given taking as an example a case where the thrust spring is disposed on the guide pipe so as to be able to bias the screw shaft in the braking direction. The thrust spring may be disposed on the piston so as to bias the threaded shaft in the braking direction.

(2) The shapes and arrangements of the adjustment spring, the stopper, the adjustment sleeve, and the spring stopper are not limited to those illustrated in the embodiments, and may be modified. The shapes of the clutch nut, the front clutch, and the rear clutch may be modified.

(3) In the above-described embodiment, the description has been given by taking as an example the case where only the front clutch is fixed to the inner periphery of the guide pipe by screwing, but this need not be the case, and the rear clutch may also be fixed to the inner periphery of the guide pipe by screwing. The front clutch may be fixed to the inner periphery of the guide tube by press fitting.

(4) In the above-described embodiment, the description has been given taking as an example the case where teeth capable of engaging the front clutch and the clutch nut are formed on both the surface of the front clutch that faces the clutch nut and the surface of the clutch nut that faces the front clutch, but this need not be the case, and teeth may be formed on either of the surfaces that face each other.

(5) In the above-described embodiment, the case where compressed air is used as the pressure fluid for operating the brake cylinder device has been described as an example, but the present invention is not limited to this, and other pressure fluids (for example, pressure oil) may be used for operation.

(6) The case where the force-increasing mechanism is provided in the brake cylinder device is not limited to the embodiment illustrated in embodiment 2, and the embodiment of the force-increasing mechanism may be variously modified. For example, the following method is also possible: the force increasing mechanism includes a support member fixed to the guide pipe, and the rotating member is provided so as to be screwed into a thread formed on an outer peripheral surface of the support member, and the support member is moved in a braking direction by rotating the rotating member in a predetermined rotating direction.

Industrial applicability

The present invention is widely applicable to a brake cylinder device having a clearance adjustment mechanism for automatically adjusting a clearance from an end of a brake output portion in a brake released state to a brake operation position, and a disc brake device having the brake cylinder device.

Description of the reference numerals

2. A brake cylinder device; 20. a cylinder main body; 21. a brake output section; 22. a piston; 23. a piston spring; 24. a threaded shaft; 25. a guide tube; 26. a thrust spring; 27. a clutch nut; 28. a front clutch; 29. a rear clutch; 30. a stopper; 31. the spring is adjusted.

Claims (13)

1. A brake cylinder device is characterized in that,

the brake cylinder device includes:

a cylinder main body, the interior of which is formed to be hollow;

a piston which is partitioned into a pressure chamber in the cylinder main body, receives an urging force of a piston spring, and moves relative to the cylinder main body against the urging force of the piston spring by supplying a pressure fluid to the pressure chamber;

a brake output portion that is provided so as to be movable together with the piston or so as to be movable by a force increasing mechanism that increases a force generated in the piston in accordance with the movement of the piston, and that is movable in a braking direction protruding from the cylinder body and a counter-braking direction approaching the cylinder body;

a threaded shaft coupled to the brake output unit and having a thread formed on an outer periphery thereof;

a guide tube attached to the piston or the force increasing mechanism and having the threaded shaft housed therein;

a thrust spring disposed on the guide tube or the piston so as to be capable of biasing the threaded shaft in the braking direction;

a clutch nut screwed to a distal end side of the threaded shaft, the distal end side of the threaded shaft being disposed closer to the brake output portion than the cylinder body;

a front clutch disposed so as to be able to contact the clutch nut at a position on the brake output side, i.e., on the front side of the clutch nut;

a rear clutch disposed so as to be able to come into contact with the front clutch nut at a predetermined interval on a rear side opposite to the brake output side with respect to the clutch nut;

a stopper that is disposed so as to be movable relative to the clutch nut and the guide pipe in an axial direction of the threaded shaft, and that limits a movable range relative to the cylinder body;

and an adjustment spring having one end abutting or coupled to the stopper and capable of biasing the clutch nut in the reverse braking direction.

2. Brake cylinder arrangement according to claim 1,

the screw shaft is formed hollow so as to open toward the side opposite to the brake output portion,

the thrust spring biases the clutch nut screwed to the threaded shaft toward the front clutch by biasing the threaded shaft from inside.

3. Brake cylinder arrangement according to claim 2,

the brake cylinder device further includes a thrust spring guide formed as a shaft-like portion provided so as to be movable together with the guide pipe, the thrust spring guide being inserted into an inner side of the thrust spring provided as a coil spring to restrict deformation of the thrust spring in a buckling direction,

the tip end portion of the thrust spring guide is disposed inside the threaded shaft so as to be slidable with respect to the inside of the threaded shaft.

4. Brake cylinder device according to one of the claims 1 to 3,

the front clutch and the rear clutch are provided as integrally formed independent members, and are fixed to the guide pipe.

5. Brake cylinder arrangement according to claim 4,

at least one of the front clutch and the rear clutch is fixed to an inner periphery of the guide pipe by screwing.

6. Brake cylinder device according to one of the claims 1 to 3,

the brake cylinder device further includes an adjustment sleeve that is provided as a flexible cylindrical member disposed around the threaded shaft and is biased in the anti-braking direction by the other end side of the adjustment spring having one end side abutting against or coupled to the stopper,

the clutch nut and the adjustment sleeve are integrated by engaging an engaging portion formed on the adjustment sleeve with an engaged portion formed on the clutch nut.

7. Brake cylinder arrangement according to claim 6,

the engaging portion of the adjustment sleeve engages with the engaged portion formed on the inner peripheral side of the clutch nut from the inside,

a dimension of a gap formed between an inner periphery of the adjustment sleeve and a crest of a thread of the threaded shaft in a radial direction of the adjustment sleeve is smaller than a dimension of a concave-convex portion in which the engagement portion and the engaged portion are fitted to each other in the radial direction of the adjustment sleeve.

8. Brake cylinder arrangement according to claim 7,

the adjusting spring is disposed so that the other end side thereof biases a spring seat attached to the adjusting sleeve,

the spring seat is disposed such that a dimension of a gap formed between an outer periphery of the spring seat and an inner periphery of the guide pipe in a radial direction of the guide pipe is almost zero, or such that the outer periphery of the spring seat is in sliding contact with the inner periphery of the guide pipe.

9. Brake cylinder arrangement according to claim 8,

the spring seat contains a bearing.

10. Brake cylinder device according to one of the claims 1 to 3,

the brake cylinder device further includes a spring stopper for limiting a displacement amount, by which the other end side of the adjustment spring is displaced relative to the one end side of the stopper that is in contact with or coupled to the adjustment spring and the adjustment spring is elastically deformed, to a predetermined amount or less.

11. Brake cylinder device according to one of the claims 1 to 3,

teeth that can engage the front clutch with the clutch nut are formed on at least one of a surface of the front clutch that faces the clutch nut and a surface of the clutch nut that faces the front clutch.

12. Brake cylinder device according to one of the claims 1 to 3,

the threaded shaft is provided at a distal end portion thereof with an operation engagement portion engageable with an operation tool, and the distal end portion is disposed so as to penetrate the brake output portion and face outward,

the brake cylinder device is further provided with a nut member for engaging with the outer periphery of the distal end portion of the threaded shaft and for engaging the threaded shaft with the brake output portion.

13. A disc brake device, characterized in that,

the disc brake device includes the brake cylinder device as defined in any one of claims 1 to 12, a caliper body equipped with the brake cylinder device and mounted displaceably in an axle direction with respect to a vehicle,

the brake cylinder device is operated to sandwich a disc on the axle side by a pair of brake pads attached to the caliper body, thereby generating a braking force.