JP5841454B2 - Twin clutch cylinder device and twin clutch operating device having the same - Google Patents

Description

  The present invention relates to a twin clutch cylinder device, and more particularly to a cylinder device for hydraulically driving first and second bearing units of a twin clutch device. The present invention also relates to an operating device for a twin clutch provided with this cylinder device.

  BACKGROUND ART A vehicle clutch device is provided with a hydraulic clutch release cylinder device that is operated by a clutch pedal. This clutch release cylinder device includes a slave cylinder and a release fork. The slave cylinder is driven by a hydraulic pressure generated by a master cylinder directly connected to the clutch pedal. By operating the slave cylinder, the release bearing unit is moved via the release fork, and the clutch is released.

  Here, it is necessary to increase the torque transmission capacity of the clutch as the engine output increases. When the clutch torque transmission capacity increases, the release operation force of the clutch increases accordingly. For this reason, for example, as shown in Patent Document 1 and Patent Document 2, there is provided an operating device that directly drives a bearing unit by a driving mechanism including a cylinder and a piston without using a conventional release fork or the like. Already provided.

  Further, Patent Document 3 also shows an operating device for a twin clutch device having a configuration basically similar to the configuration shown in these patent documents.

U.S. Pat. No. 4,328,883 Japanese Patent Laid-Open No. 8-105459 JP 2005-201452 A

  In the devices disclosed in the above patent documents, a plurality of pistons and cylinders for driving the bearing unit are arranged around the input shaft of the transmission. In the device of Patent Document 1, a plurality of cylinders are configured by one component, and in the device of Patent Document 2, a plurality of pistons are configured by one component. Moreover, in the apparatus of Patent Document 3, one annular member is driven by a plurality of pistons. In the device of Patent Document 3, one clutch operating member and the other clutch operating member are arranged at different radial positions.

  In such a conventional apparatus, one part in which a plurality of cylinders or pistons are formed can be formed by resin molding or die casting. I don't get it. For this reason, the manufacturing cost including the mold cost is high. Furthermore, since one component becomes large, it is difficult to manufacture with high accuracy.

  In the configuration shown in Patent Document 3, it is difficult to reduce the size in the axial direction and the radial direction.

  An object of the present invention is to provide a compact and inexpensive configuration in a cylinder device in which a bearing unit for a twin clutch is directly driven by hydraulic pressure.

  A cylinder device for a twin clutch according to a first invention is a device for hydraulically driving the first and second bearing units of the twin clutch device, and includes an annular hydraulic chamber, a plurality of first cylinders, and a plurality of A first piston, a plurality of second cylinders, a plurality of second pistons, and a hydraulic pressure supply unit are provided. The hydraulic chamber has a first oil chamber and a second oil chamber divided in the axial direction. The plurality of first cylinders are separately disposed in the hydraulic chamber and communicated with the first oil chamber. The plurality of first pistons are movably disposed in each of the plurality of first cylinders, and are coupled to the first bearing unit. The plurality of second cylinders are separately disposed in the hydraulic chamber and communicated with the second oil chamber. The plurality of second pistons are movably disposed in each of the plurality of second cylinders and are coupled to the second bearing unit. The hydraulic supply unit supplies hydraulic oil for operating the plurality of first and second pistons to the hydraulic chamber.

  In this apparatus, the hydraulic oil is supplied from the hydraulic supply unit to the plurality of first cylinders via the first oil chamber of the hydraulic chamber, and the hydraulic oil is supplied to the plurality of second cylinders via the second oil chamber. The Then, the first and second pistons provided in each cylinder slide to operate the first and second bearing units. Thereby, each clutch of a twin clutch can be joined or can be released.

  Here, a plurality of cylinders and pistons are independently provided in the hydraulic chamber. The hydraulic chamber can be easily and inexpensively manufactured by sheet metal processing or the like. For this reason, the whole apparatus becomes cheap compared with the case where a plurality of cylinders and pistons are formed as one component as in the conventional apparatus. Further, since each component is small, it is easy to increase the dimensional accuracy. Furthermore, even if the size of the bearing unit is changed, it is not necessary to change the type of cylinder or piston that is expensive and difficult to obtain, unlike the conventional device, and it can be handled only by changing the inexpensive hydraulic chamber. Is possible.

  In addition, since the first oil chamber and the second oil chamber for supplying hydraulic oil to the first and second cylinders are formed in the hydraulic chamber so as to be divided in the axial direction, the hydraulic chamber can be reduced in size. it can.

  The twin clutch cylinder device according to the second invention is the device according to the first invention, wherein the plurality of first cylinders are arranged at equal angular intervals on the same circumference, and the plurality of second cylinders are on the same circumference. They are arranged at equiangular intervals.

  Here, since the respective cylinders for operating the two clutch devices are arranged at the same position in the radial direction, it is possible to prevent the device from being enlarged in the radial direction.

  A cylinder device for a twin clutch according to a third aspect is the device according to the first or second aspect, wherein each of the hydraulic chambers has an annular base plate, a cover member, and a separate plate. The cover member is formed in a C-shaped cross section, and the opening is closed by the base plate to constitute an oil chamber inside. The separate plate is disposed in the oil chamber and separates the oil chamber into a first oil chamber and a second oil chamber.

  Here, since the hydraulic chamber is configured by an annular base plate, a cover member, and a separate plate, the hydraulic chamber can be formed with a simple configuration and at low cost.

  A twin clutch cylinder device according to a fourth invention is the device according to the third invention, wherein the cover member has an opening at a position where the plurality of first cylinders and the second cylinder are arranged, and the plurality of first cylinders Each of the second cylinder protrudes in the axial direction through the opening of the cover member. Each of the plurality of first pistons and second pistons protrudes outside the first cylinder and the second cylinder, and the first bearing unit and the second bearing unit are connected to the tip portions.

  The twin clutch cylinder device according to a fifth aspect is the device according to the fourth aspect, wherein the hydraulic pressure supply section includes a first oil supply pipe and a second oil supply pipe for supplying hydraulic pressure from the outside, a first oil supply socket, 2 oil supply sockets. The first oil supply socket is provided on the cover member and is connected to the first oil supply pipe, and introduces hydraulic oil from the first oil supply pipe into the first oil passage of the hydraulic chamber. The second oil supply socket is provided in the cover member and connected to the second oil supply pipe, and introduces hydraulic oil from the second oil supply pipe into the second oil passage of the hydraulic chamber.

  A twin clutch cylinder device according to a sixth aspect of the present invention is the device according to any one of the first to fifth aspects of the present invention, wherein the twin clutch cylinder device is provided in the hydraulic chamber and discharges air inside the first oil chamber and the second oil chamber. A discharge part is further provided.

  Here, the air in each oil chamber can be extracted through the air discharge unit. Therefore, it can suppress that operating efficiency falls.

  The twin clutch cylinder device according to a seventh aspect of the present invention is the device of the sixth aspect, wherein the air discharge portion includes a first discharge pipe and a second discharge pipe for discharging air to the outside, a first discharge socket, 2 discharge sockets. The first discharge socket is provided on the cover member and connected to the first discharge pipe, and discharges the air in the first oil chamber to the outside. The second discharge socket is provided on the cover member and connected to the second discharge pipe, and discharges the air in the second oil chamber to the outside.

  The twin clutch cylinder device according to an eighth aspect of the present invention is the device of the seventh aspect, wherein the air discharge portion is disposed above each cylinder and the hydraulic pressure supply portion in the vehicle mounted state. The hydraulic chamber has a spacer disposed in at least a portion above the air discharge portion in the first oil chamber and the second oil chamber to avoid air remaining in the first oil chamber and the second oil chamber. Yes.

  Here, if a part of the oil chamber exists above the air discharge part, air remains in this part, and the remaining air cannot be discharged from the air discharge part.

  Therefore, in the apparatus according to the eighth aspect of the present invention, in each oil chamber of the hydraulic chamber, a spacer is disposed at a portion located above the air discharge portion. By this spacer, it is possible to eliminate residual air in a portion above the air discharge portion in the oil chamber.

  The twin clutch cylinder device according to a ninth aspect of the present invention is the device according to any one of the first to eighth aspects of the present invention, provided between the first cylinder and the first piston and between the second cylinder and the second piston. A dust seal is further provided that prevents foreign matter from entering the first cylinder and the second cylinder.

  An operation device for a twin clutch according to a tenth aspect of the invention is a device for operating the first pressing member and the second pressing member of the twin clutch device, and moves along the rotation axis of the twin clutch device and depends on each pressing member. A first clutch unit and a second bearing unit for releasing the pressing; a twin clutch cylinder device according to any one of the first to ninth inventions for driving the first bearing unit and the second bearing unit by hydraulic pressure; It has.

  The twin clutch actuator according to the eleventh aspect of the present invention is the apparatus of the tenth aspect, wherein the first bearing unit has a first bearing and a first bearing mounting plate. The first bearing has an inner ring and an outer ring, and presses the first pressing member via the inner ring. The first bearing mounting plate has an outer peripheral portion that holds the outer ring of the first bearing, and an inner peripheral portion to which the tip of the first piston is connected. The second bearing unit has a second bearing and a second bearing mounting plate. The second bearing has an inner ring and an outer ring, and presses the second pressing member via the outer ring. The second bearing mounting plate has an inner peripheral portion that holds the inner ring of the second bearing, and an outer peripheral portion to which the tip of the second piston is connected.

  Here, it becomes easy to arrange | position a 1st cylinder and a 2nd cylinder on the same periphery, respectively.

  In the present invention as described above, a small and inexpensive cylinder device for a twin clutch can be realized.

1 is a front view of a clutch actuator according to an embodiment of the present invention. FIG. 2 is a cross-sectional view taken along line A-O-A ′ in FIG. 1. FIG. 2 is a cross-sectional view taken along line B-O-B ′ and C-O-C ′ in FIG. 1. FIG. The enlarged view of FIG. The figure which removed the cover member of FIG. FIG. 2 is a rear view of FIG. 1 with a base plate removed.

[overall structure]
1 to 4 show a clutch operating device according to an embodiment of the present invention. 1 is a front view of the present apparatus, FIG. 2 is a cross-sectional view taken along line AO-A ′ of FIG. 1, FIG. 3 is a cross-sectional view taken along BO-B ′ and CO—C ′ of FIG. .

  The clutch operating device 1 includes a first bearing unit 11 and a second bearing unit 12, and a hydraulic clutch cylinder device 2. Although not shown, the twin clutch device is disposed on the left side of the clutch operating device 1 in FIGS. This twin clutch device includes two clutch devices. The two clutch devices have the same configuration, and each clutch device mainly includes a clutch disk that is pressed against the flywheel, a pressure plate that presses the clutch disk against the flywheel, and a diaphragm that applies a pressing force to the pressure plate. A spring (pressing member). The clutch actuating device 1 applies a pressing force to the pressure plate by pushing the inner peripheral end portion of the diaphragm spring of each clutch device toward the engine.

[Bearing units 11, 12]
As apparent from FIGS. 1 and 2, the first and second bearing units 11 and 12 are arranged at different positions in the radial direction and at positions overlapping in the axial direction. Specifically, the first bearing unit 11 is disposed on the outer peripheral side of the second bearing 12, and is shifted to the side away from the clutch device at substantially the same position as the second bearing unit 12 in the axial direction. .

  In FIG. 2, the first bearing unit 11 and its drive mechanism are shown above the rotation axis OO, and the second bearing unit 12 and its drive mechanism are shown below. FIG. 2 shows a state in which both the bearing units 11 and 12 are disengaged.

-First bearing unit 11-
The first bearing unit 11 includes a first bearing 4, a first bearing mounting plate 5, and a first bearing support member 6.

  The first bearing 4 includes an inner ring 4a, an outer ring 4b, and a plurality of balls 4c. The inner ring 4a protrudes toward the clutch device, and the tip of the protrusion can abut on the inner peripheral end of a diaphragm spring (not shown) of the first clutch device.

  The first bearing mounting plate 5 is a disk-shaped plate and is a member for mounting the first bearing 4 to the clutch cylinder device 2. A first bearing support member 6 is fixed to the outer peripheral portion of the first bearing mounting plate 5, and a piston mounting hole 5a is formed in the inner peripheral portion.

  The first bearing support member 6 is a cylindrical member extending to the clutch device side, and supports the outer ring 4b of the first bearing 4 on the inner peripheral side. The end of the first bearing support member 6 opposite to the clutch device is fixed to the outer periphery of the first bearing mounting plate 5.

-Second bearing unit 12-
The second bearing unit 12 includes a second bearing 7, a second bearing mounting plate 8, and a second bearing support member 9.

  The second bearing 7 includes an inner ring 7a, an outer ring 7b, and a plurality of balls 7c. The outer ring 7b protrudes toward the clutch device, and the tip of the protrusion can abut on the inner peripheral end of a diaphragm spring (not shown) of the second clutch device.

  The second bearing mounting plate 8 is a disk-shaped plate and is a member for mounting the second bearing 7 to the clutch cylinder device 2. A second bearing support member 9 is fixed to the inner peripheral portion of the second bearing mounting plate 8, and a piston mounting hole 8a is formed on the outer peripheral portion.

  The second bearing support member 9 is a cylindrical member extending to the clutch device side, and supports the inner ring 7a of the second bearing 7 on the outer peripheral side. The end of the second bearing support member 9 opposite to the clutch device is fixed to the inner periphery of the second bearing mounting plate 8.

[Clutch cylinder device 2]
The clutch cylinder device 2 includes a hydraulic chamber 15, three integrated cylinders 16a, 16b, and 16c, a plurality of pistons 17, a hydraulic pressure supply unit 18, and an air discharge unit 19.

<Hydraulic chamber 15>
The hydraulic chamber 15 includes an annular base plate 21, an annular cover member 22 having a C-shaped cross section, an annular separate plate 23, and first and second spacers 24 and 25 (see FIG. 3). .

-Base plate 21-
The inner peripheral edge and the outer peripheral edge of the base plate 21 are welded to the inner peripheral edge and the outer peripheral edge of the opening of the cover member 22 by a laser beam, respectively. Thereby, the opening part of the cover member 22 is block | closed by the baseplate 21, and the oil chamber is formed in the inside. Further, the separate plate 23 is disposed inside the cover member 22. The inner peripheral edge and the outer peripheral edge of the separate plate 23 are welded to the inner peripheral wall surface and the outer peripheral inner wall surface of the cover member 22 by a laser beam, respectively. The oil chamber formed by the base plate 21 and the cover member 22 by the separate plate 23 is connected to the first oil chamber R1 on the base plate 21 side (right side in FIGS. 2 to 4) and the clutch device side (in FIGS. 2 to 4). It is divided into a second oil chamber R2 on the left side).

-Cover member 22-
On the side of the cover member 22 on the side of the clutch device, there are three portions where the integrated cylinders 16a to 16c are arranged, first and second cylinder holes 22a and 22b, and mounting holes 22c (FIGS. 1 and 4). Similarly, on the side of the cover member 22 on the clutch device side, as shown in FIG. 3, two socket holes 22d are formed in the portion where the hydraulic pressure supply unit 18 is provided, and the air discharge unit 19 is provided. Two socket holes 22e are formed in the formed portion.

-First spacer 24 and second spacer 25-
The first spacer 24 is an annular resin member disposed in the first oil chamber R1, and has a plurality of grooves (details of the grooves will be described later) on the surface on the base plate 21 side. An annular groove S0 is secured between the inner peripheral portion of the first spacer 24 and the inner wall on the inner peripheral side of the cover member 22. A first oil passage P1 is formed by these grooves. Details of the first oil passage P1 will be described later.

  The 2nd spacer 25 is arrange | positioned at a part of 2nd oil chamber R2, and the shape is shown by the cross hatching of FIG. FIG. 6 is a view showing a state where the cover member 22 is removed. The second spacer 25 is a resin member, and is provided in the second oil chamber R <b> 2 to prevent air from remaining on the upper portion of the air discharge portion 19. That is, the second spacer 25 is mainly disposed in a space above the air discharge part 19 in the second oil chamber R2.

<Integrated cylinders 16a to 16c>
The three integrated cylinders 16a, 16b, and 16c all have the same configuration, and the clutch operating device 2 is mounted on the vehicle, and the position (16a) at the bottom of the hydraulic chamber 15 is spaced 120 ° from this position. It is arranged at two positions (16b, 16c) with a gap. Since all the three integrated cylinders 16a to 16c have the same configuration, the integrated cylinder 16a positioned at the lowermost part will be described below.

  As shown in FIG. 5 in which FIG. 2 is enlarged, the integrated cylinder 16a includes a cylinder base 30, a first cylinder part 31, a second cylinder part 32, and a mounting collar part 33 (see FIG. 4). It is an integrally molded resin member. The first cylinder part 31 and the second cylinder part 32 are arranged at equiangular intervals.

-Cylinder base 30-
As shown in FIG. 1 (broken line) and FIG. 6, the cylinder base 30 is formed in an arc shape. The cylinder base 30 is disposed in the second oil chamber R <b> 2 and is sandwiched between the cover member 22 and the separate plate 23. Thereby, the movement of the integral cylinder 16a in the axial direction is restricted. The 1st cylinder part 31 and the 2nd cylinder part 32 are formed in the both ends of the circumferential direction of the cylinder base 30, and the collar part 33 for attachment is formed among these.

-First cylinder part 31-
The first cylinder part 31 is formed in a cylindrical shape. The first end 31a on the base plate 21 side of the first cylinder portion 31 protrudes from the cylinder base 30 and extends into the first oil chamber R1, and the second end 31b on the opposite side passes through the first cylinder hole 22a. Extending to the clutch device side. A through hole 31c is formed in the second end 31b.

  Note that the first end portion 31 a of the first cylinder portion 31 is not in contact with the side surface of the base plate 21. Accordingly, a gap 31d is secured between the end surface of the first end portion 31a and the base plate 21, and hydraulic oil is introduced from the first oil chamber R1 into the first cylinder portion 31 through the gap 31d. . Further, on both side surfaces of the cylinder base 30, O-rings are disposed on the outer peripheral portion of the first cylinder portion 31 to prevent the hydraulic oil inside the second oil chamber R2 from leaking to the outside. Further, on the outer periphery of the first cylinder portion 31, an O-ring is similarly arranged between the separate plate 23 and the base plate 21. Furthermore, a dust seal 28 is provided between the piston 17 and the tip of the second end portion 31 b of the first cylinder portion 31. A cap 29 for fixing the dust seal 28 is provided on the outer peripheral portion of the second end portion 31b.

-Second cylinder part 32-
The second cylinder part 32 is formed on the same circumference as the first cylinder part 31 and is formed in a cylindrical shape. The second cylinder part 32 is formed to protrude from the cylinder base 30 to the clutch device side, and a through hole 32c is formed at the tip part.

  As shown in FIG. 6, a plurality of notches 32a are formed on the side surface (the surface on the side of the separate plate 23) of the cylinder base 30 on which the second cylinder portion 32 is formed. The hydraulic oil is introduced from the second oil chamber R2 into the second cylinder part 32 through the second oil chamber R2. In addition, an O-ring is disposed between the side surface of the cylinder base 30 and the cover member 22 on the outer periphery of the second cylinder portion 32. A dust seal 28 is provided between the piston 17 and the tip of the second cylinder portion 32. A cap 29 for fixing the dust seal 28 is provided on the outer periphery of the tip.

-Mounting collar part 33-
As shown in FIG. 4, the mounting collar portion 33 has a cylindrical shape and is formed so as to protrude from both side surfaces of the cylinder base 30. The end face on the clutch device side of the mounting collar portion 33 is flush with the surface of the cover member 22, and the end face on the base plate 21 side is flush with the side face of the base plate 21.

  On the outer periphery of the mounting collar portion 33, O-rings are disposed on both side surfaces of the cylinder base 30, between the separation plate 23 and the first spacer 24, and between the separation plate 23 and the base plate 21. Yes.

  The clutch operating device 1 is assembled to the vehicle by the bolts penetrating the inside of the mounting collar portion 33 as described above.

<Piston 17 and spring 36>
The plurality of pistons 17 have the same configuration. The piston 17 is movably disposed in the first cylinder portion 31 and the second cylinder portion 32, and includes a piston main body 17a, a seal mounting portion 17b formed on the base plate 21 side of the piston main body 17a, and a piston main body 17a. And a connecting portion 17c formed on the other end side.

  The piston body 17a passes through through holes 31c and 32c formed in the cylinder portions 31 and 32, and protrudes toward the clutch device. The piston 17 has a bottomed hole 17d formed therein. Further, a guide portion 17e is formed between the piston main body 17a and the seal attachment portion 17b, and a collar portion 17f is formed at an end portion of the seal attachment portion 17b. The guide portion 17e can contact the inner walls of the cylinder portions 31 and 32, and guides the movement of the piston 17. A seal member 34 and a washer 35 are mounted between the guide portion 17e and the flange portion 17f.

  The connecting portion 17c is formed so as to protrude from the end surface of the piston body 17a toward the clutch device. And this connection part 17c is inserted in the holes 5a and 8a formed in the bearing attachment plates 5 and 8 of each bearing unit 11 and 12, and the head part of the front-end | tip is crushed and fixed by melting caulking.

  A spring 36 is disposed in a hole 17 d formed in the piston 17. The spring 36 provided in the first cylinder part 31 is compressed and mounted between the base plate 21 and the bottom surface of the hole 17d. The spring 36 provided in the second cylinder part 32 is compressed and mounted between the separate plate 23 and the bottom surface of the hole 17d. With such a configuration, the piston 17 is biased by the spring 36 so as to protrude from the cylinder portions 31 and 32 toward the clutch device.

<Hydraulic supply part 18 and air discharge part 19>
The hydraulic pressure supply unit 18 supplies hydraulic oil for operating the plurality of pistons 17 to the cylinder units 31 and 32 via the hydraulic chamber 15. Moreover, the air discharge part 19 is provided in order to extract the air of each oil chamber R1, R2. As shown in FIG. 1, the hydraulic pressure supply unit 18 is disposed between the lowermost integrated cylinder 16a and the upper integrated cylinder 16b. Further, the air discharge unit 19 is disposed so as to be positioned at the uppermost part of the hydraulic chamber 15 in a state where the present apparatus is mounted on the vehicle.

  The hydraulic pressure supply unit 18 and the air discharge unit 19 have different connection destinations, but basically have the same configuration, and include a pipe 38 and integrated sockets 39a and 39b (see FIG. 3).

<Pipe 38>
In the hydraulic pressure supply unit 18, the pipe 38 is connected to a hydraulic pressure supply source (not shown), and the tip is coupled to the integrated socket 39a. Moreover, in the air discharge part 19, the pipe 38 is connected to the bleeder 41 via the connector 40, and the front-end | tip is connected with the integrated socket 39b.

<Integrated sockets 39a, 39b>
As shown in FIG. 3, the integrated sockets 39a and 39b are resin members in which a socket base 50, a first socket portion 51, and a second socket portion 52 are integrally molded. The integrated socket 39a of the hydraulic pressure supply unit 18 is disposed between the lowermost integrated cylinder 16a and the upper integrated cylinder 16b. The integrated socket 39b of the air discharge unit 19 is disposed between the upper two integrated cylinders 16b and 16c.

-Socket base 50-
As shown in FIG. 1 (broken line) and FIG. 6, the socket base 50 is formed in a substantially elliptical shape. The socket base 50 is disposed in the second oil chamber R <b> 2 and is sandwiched between the cover member 22 and the separate plate 23. Thereby, the movement of the socket base 50 in the axial direction is restricted. The first socket part 51 and the second socket part 52 are formed at both ends of the socket base 50 in the circumferential direction.

-First socket part 51-
The first socket part 51 is formed in a cylindrical shape. The first end portion of the first socket portion 51 on the base plate 21 side protrudes from the socket base 50 and extends into the first oil chamber R1, and the second end portion on the opposite side penetrates through the socket holes 22d and 22e to engage the clutch. It extends to the device side. A pipe 38 is inserted and fixed from the second end.

  A notch 51 a is formed on the end surface of the first end portion of the first socket portion 51 so that a gap is formed between the first socket portion 51 and the side surface of the base plate 21. On the hydraulic pressure supply unit 18 side, hydraulic oil is introduced from the first oil chamber R1 into the first socket unit 51 through the notch 51a. On the air discharge part 19 side, hydraulic oil and air from the first oil chamber R1 are introduced into the first socket part 51 through the notch 51a.

  In addition, on both side surfaces of the socket base 50, O-rings are disposed on the outer peripheral portion of the first socket portion 51 to prevent the hydraulic oil inside the second oil chamber R2 from leaking to the outside. Further, on the outer periphery of the first socket portion 51, an O-ring is similarly disposed between the separate plate 23 and the base plate 21.

-Second socket part 52-
The second socket part 52 is formed in a cylindrical shape. The second socket portion 52 is formed so as to protrude from the socket base 50 to the clutch device side. And the pipe 38 is inserted and fixed from this front-end | tip part.

  A notch 52 a is formed on the end surface (the surface on the side of the separate plate 23) of the socket base 50 in which the second socket portion 52 is formed so that a gap is formed between the second base plate 52 and the separate plate 23. On the hydraulic pressure supply unit 18 side, hydraulic oil is introduced from the second oil chamber R2 into the second socket 52 through the notch 52a. On the air discharge part 19 side, hydraulic oil and air from the second oil chamber R2 are introduced into the second socket part 52 through the notch 52a.

  Note that an O-ring is disposed between the side surface of the socket base 50 and the cover member 22 on the outer periphery of the second socket portion 52.

<Oil passages P1, P2>
-First oil passage P1-
The 1st oil path P1 which supplies hydraulic fluid to the 1st cylinder part 31 is demonstrated. FIG. 7 is a rear view of FIG. 1 with the base plate 21 removed. Therefore, in this FIG. 7, the 1st spacer 24 seen mainly from the right side of FIG. 1 appears. Further, FIG. 7 is in a positional relationship reversed from that of FIG.

  As shown in this figure, grooves S1 to S8 are formed on the surface of the first spacer 24 on the base plate 21 side. Further, as described above, the groove S0 is secured between the inner peripheral end of the first spacer 24 and the inner wall surface of the inner peripheral portion of the cover member 22, and between the first cylinder portion 31 and the base plate 21. A gap 31d is secured. A first oil passage P1 is formed by the grooves S0 to S8 and the gap 31d and the notch 51a formed on the end face of the first socket portion 51 of the hydraulic pressure supply portion 18 and the air discharge portion 19.

  More specifically, the groove S1 communicates with the notch 51a of the first socket portion 51 and the groove S0. The groove S2 communicates with the notch 51a and the bottom gap 31d of the first cylinder portion 31 of the integrated cylinder 16a. The groove S3 communicates with the bottom notch 51a of the first socket part 51 of the integrated socket 39a and the groove S0. The grooves S4 and S5 communicate with the bottom gap 31d of the first cylinder part 31 of the integrated cylinder 16c and the groove S0. The groove S6 communicates with the bottom gap 31d of the first cylinder part 31 of the integral cylinder 16b and the groove S0. The groove S7 communicates with the bottom gap 31d of the first cylinder part 31 of the integrated cylinder 16b and the notch 51a of the first socket part 51 of the air discharge part 19. The groove S8 communicates with the notch 51a of the first socket portion 51 and the groove S0.

-Second oil passage P2-
The 2nd oil path P2 which supplies hydraulic oil to the 2nd cylinder part 32 is demonstrated using FIG. As described above, FIG. 6 is a view showing a state where the cover member 22 is removed. Therefore, in FIG. 6, the integrated cylinders 16a to 16c, the integrated sockets 39a and 39b, and the second spacer 25, which are arranged in the second oil chamber R2, mainly appear.

  As shown in this figure, as described above, a cutout 32a communicating with the inside of the second cylinder portion 32 is formed on the side surface of the cylinder base 30 of the three integrated cylinders 16a to 16c. A notch 52 a is formed on the end surface of the second socket portion 52 of the hydraulic pressure supply unit 18 and the air discharge unit 19. These notches 32a and 52a communicate with the second oil chamber R2, and a second oil passage P2 is formed by the notches 32a and 52a and the second oil chamber R2.

[Operation]
First, the operation when operating (engaging) the first clutch device will be described in detail.

  In a state where hydraulic oil is not supplied to the clutch operating device 1, the bearing 4 of the first bearing unit 11 is in contact with the inner peripheral end portion of the diaphragm spring of the first clutch device.

  When the clutch device is joined, the hydraulic oil is supplied to the first socket portion 51 via the hydraulic pressure supply pipe 38 of the hydraulic pressure supply portion 18. The hydraulic oil supplied to the first socket portion 51 is supplied to the three first cylinder portions 31 via the first oil passage P1. Thereby, the piston 17 protrudes to the clutch device side. Due to the protrusion of the piston 17, the first clutch bearing unit 11 moves to the clutch device side and presses the inner peripheral end of a diaphragm spring (not shown). For this reason, the pressing force of the diaphragm spring is applied and the clutch is engaged.

  The operation at the time of joining the second clutch device is exactly the same as the operation at the time of joining the first clutch device, except that hydraulic oil is supplied to the three second cylinder portions 32 via the second oil passage P2. It is.

  Here, air may be mixed in the hydraulic path in the initial stage of assembly or the like. In this case, the bleeder 41 provided at the tip of the pipe 38 of the air discharge unit 19 is loosened and the hydraulic pressure supply unit 18 is hydraulically applied. Thereby, the air mixed in the hydraulic path of the present apparatus can be removed together with the hydraulic oil. At this time, since there is no space above the socket parts 51 and 52 of the air discharge part 19 in the hydraulic chamber 15 due to the presence of the first spacer 24 and the second spacer 25, the air enters the hydraulic chamber 15. It will not remain.

[Feature]
(1) A plurality of cylinders 16a to 16c and a piston 17 are independently provided in the hydraulic chamber 15, and the hydraulic chamber 15 can be easily and inexpensively manufactured by sheet metal processing or the like, a base plate 21, a cover member 22, And a separate plate 23. For this reason, the whole apparatus becomes cheap. Further, even when the size of the bearing unit is changed, it is possible to cope with the change only by changing the inexpensive hydraulic chamber.

  (2) The first oil chamber R1 and the second oil chamber R2 for supplying hydraulic oil to the first cylinder portion 31 and the second cylinder portion 32 are formed in the hydraulic chamber 15 so as to be divided in the axial direction. The hydraulic chamber 15 can be reduced in size.

  (3) Since the 1st cylinder part 31 and the 2nd cylinder part 32 are arrange | positioned on the same periphery, it can avoid that the radial direction dimension of an apparatus enlarges.

  (4) Since the second spacer 25 is disposed above the air discharge portion 19, it is possible to prevent air from remaining in the first oil chamber R1 and the second oil chamber R2.

[Other Embodiments]
The present invention is not limited to the above-described embodiments, and various changes or modifications can be made without departing from the scope of the present invention.

  (A) In the above embodiment, the cylinder is an integral cylinder, but the first cylinder and the second cylinder may be formed separately. The same applies to the hydraulic pressure supply unit and the air discharge unit, and is not limited to an integrated socket.

  (B) The configuration of the air discharge unit is not limited to the previous embodiment, and the air discharge unit may not be provided in some cases.

  (C) In the above-described embodiment, the plurality of first cylinders and the second cylinders are arranged on the same circumference, but the plurality of first cylinders are arranged on the same circumference, and the plurality of second cylinders are different from each other. It may be arranged on the circumference.

  (D) The mounting collar 33 is not necessarily provided in the hydraulic chamber, and the clutch operating device can be fixed to the vehicle in another direction.

  (E) In the above embodiment, the clutch actuating device of the present invention is used for clutch engagement operation. However, the present invention can be similarly applied to an operation when releasing (disengaging) the clutch.

  (F) The number of cylinders and pistons is not limited to the above embodiment.

DESCRIPTION OF SYMBOLS 1 Clutch actuator 2 Clutch cylinder apparatus 4, 7 Bearing 5, 8 Bearing mounting plate 11, 12 Bearing unit 15 Hydraulic chamber 16a-16c Integrated cylinder 17 Piston 18 Hydraulic supply part 19 Air discharge part 21 Base plate 22 Cover member 23 Separate plate 24, 25 Spacer 31, 32 Cylinder part 38 Pipe 39a, 39b Integrated socket 51, 52 Socket part

Claims (10)

A cylinder device for hydraulically driving first and second bearing units for operating a twin clutch device,
An annular hydraulic chamber having a first oil chamber and a second oil chamber divided in an axial direction;
A plurality of first cylinders arranged separately in the hydraulic chamber and communicating with the first oil chamber;
A plurality of first pistons movably disposed in each of the plurality of first cylinders and coupled to the first bearing unit;
A plurality of second cylinders that are separately disposed in the hydraulic chamber and communicate with the second oil chamber;
A plurality of second pistons movably disposed in each of the plurality of second cylinders and coupled to the second bearing unit;
A hydraulic pressure supply section that supplies hydraulic oil for operating the plurality of first and second pistons to the hydraulic chamber;
Equipped with a,
The hydraulic chamber is
An annular base plate;
A cover member for forming an oil chamber in an annular shape and having a C-shaped cross section, the opening being closed by the base plate;
An annular separate plate disposed in the oil chamber for separating the oil chamber into the first oil chamber and the second oil chamber;
Having
Twin clutch cylinder device. The plurality of first cylinders are arranged at equiangular intervals on the same circumference,
The plurality of second cylinders are arranged at equiangular intervals on the same circumference,
The cylinder device for twin clutch according to claim 1. The cover member has an opening at a position where a plurality of the first cylinder and the second cylinder are disposed,
Each of the plurality of first cylinders and the second cylinder protrudes in the axial direction through the opening of the cover member,
Each of the plurality of first pistons and second pistons has tips protruding outside the first cylinder and the second cylinder, and the first bearing unit and the second bearing unit are connected to the tips.
The cylinder device for twin clutch according to claim 1 . The hydraulic pressure supply unit
A first oil supply pipe and a second oil supply pipe for supplying hydraulic pressure from the outside;
A first oil supply socket provided on the cover member and connected to the first oil supply pipe, for introducing hydraulic oil from the first oil supply pipe into the first oil passage of the hydraulic chamber;
A second oil supply socket provided on the cover member and connected to the second oil supply pipe, for introducing hydraulic oil from the second oil supply pipe into the second oil passage of the hydraulic chamber;
Having
The cylinder device for twin clutch according to claim 3 . The twin clutch cylinder according to any one of claims 1 to 4 , further comprising an air discharge portion provided in the hydraulic chamber for discharging air inside the first oil chamber and the second oil chamber. apparatus. The air discharge part is
A first discharge pipe and a second discharge pipe for discharging air to the outside;
A first discharge socket provided on the cover member and connected to the first discharge pipe, for discharging the air in the first oil chamber to the outside;
A second discharge socket provided on the cover member and connected to the second discharge pipe, for discharging the air in the second oil chamber to the outside;
Having
The cylinder device for a twin clutch according to claim 5 . The air discharge unit is disposed above each cylinder and the hydraulic pressure supply unit in a vehicle-mounted state,
The hydraulic chamber is disposed at least above the air discharge portion in the first oil chamber and the second oil chamber, and is a spacer for avoiding air remaining in the first oil chamber and the second oil chamber. have,
The twin clutch cylinder device according to claim 6 . Provided between the first cylinder and the first piston, and between the second cylinder and the second piston, respectively, to prevent foreign matter from entering the first cylinder and the second cylinder. The twin clutch cylinder device according to any one of claims 1 to 7 , further comprising a dust seal. An operating device for a twin clutch for operating the first pressing member and the second pressing member of the twin clutch device,
A first bearing unit and a second bearing unit for moving along the rotation axis of the twin clutch device and releasing the pressing by each pressing member;
The twin clutch cylinder device according to any one of claims 1 to 8 , wherein the first bearing unit and the second bearing unit are driven by hydraulic pressure,
Actuator for twin clutch. The first bearing unit includes:
A first bearing having an inner ring and an outer ring and pressing the first pressing member via the inner ring;
A first bearing mounting plate having an outer peripheral portion for holding an outer ring of the first bearing, and an inner peripheral portion to which a tip of the first piston is coupled;
Have
The second bearing unit includes:
A second bearing having an inner ring and an outer ring, and pressing the second pressing member via the outer ring;
A second bearing mounting plate having an inner peripheral portion for holding an inner ring of the second bearing, and an outer peripheral portion to which a tip of the second piston is coupled;
Having
The actuator for a twin clutch according to claim 9.

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