JP2014144684A - Clutch system for hybrid system and clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a clutch system for a hybrid system and a clutch device, as an example, in which rotational fluctuation due to inertial load of a rotation electric machinery etc. hardly arises, upon starting operation of an internal combustion engine.SOLUTION: A clutch system, as an example, switches among a connection state in which a first component and a second component are pressed to each other by a pressing force, to rotate integrally, a cut-off state in which the first component and the second component are separated from each other and rotation is not transmitted between the first component and the second component, and a restriction state in which the first component and the second component are pressed to each other by a weaker pressing force than that of the connection state and torque transmission between the first component and the second component is restricted, and, upon starting operation of an internal combustion engine, the clutch system is set to be in the restriction state.

Description

  Embodiments described herein relate generally to a clutch system and a clutch device for a hybrid system.

  2. Description of the Related Art Conventionally, as a clutch device that is mounted on a hybrid vehicle or the like that includes an internal combustion engine and a rotating electrical machine as a power unit and switches connection and disconnection between the internal combustion engine and the rotating electrical machine, the clutch is in a connected state when the internal combustion engine is stopped. A so-called normally closed type clutch device is known (for example, Patent Document 1).

JP 2012-97851 A

  However, in the so-called normally closed type clutch device, depending on the environmental conditions and the like, rotation fluctuation may occur due to the inertia load of the rotating electrical machine during the starting operation of the internal combustion engine.

  The clutch system for a hybrid system according to the embodiment includes, as an example, at least one of a first member that rotates integrally with the rotating portion of the internal combustion engine, a second member that rotates integrally with the rotating portion of the rotating electrical machine, and the like. At least a part of which is movable within the cylinder part, a cylinder part provided with two hydraulic chambers, an elastic member that generates a pressing force in a direction in which the first member and the second member are pressed against each other by elasticity A piston that generates or reduces the pressing force by the hydraulic pressure of the hydraulic chamber, and a hydraulic control unit that controls the hydraulic pressure of the hydraulic chamber. A connection state in which the member and the second member are pressed against each other and rotate integrally; and the first member and the second member are separated from each other, and the first member and the second member Times between And the first member and the second member are pressed against each other by the pressing force smaller than the connected state, and the torque between the first member and the second member is reduced. The control is switched to a suppression state in which transmission is suppressed, and is set to the suppression state when the internal combustion engine is started. Therefore, according to the embodiment, as an example, during the starting operation of the internal combustion engine, transmission of torque between the first member and the second member is suppressed, thereby causing an inconvenient event such as rotational fluctuation. Is unlikely to occur.

  Further, in the clutch system for a hybrid system, as an example, during the start operation of the internal combustion engine, the elastic member generates the pressing force and the piston does not generate the pressing force or reduces the pressing force. It is possible to obtain the above suppression state in the absence of this. Therefore, as an example, even if the hydraulic pressure control unit does not adjust the hydraulic pressure in the hydraulic chamber (or is difficult or cannot be adjusted) immediately or immediately after the internal combustion engine starts the starting operation, It is easy to obtain a suppressed state.

  In the clutch system for a hybrid system, as an example, when the internal combustion engine is stopped, the elastic member generates the pressing force that obtains the suppression state during the start operation of the internal combustion engine. Therefore, as an example, it is likely to be set to a state in which inconveniences such as resonance and torque fluctuation are unlikely to occur from the start time (starting immediately after the start) of the internal combustion engine.

  Further, the hybrid system clutch system includes, as an example, a sensor that detects the rotational state of the internal combustion engine, and the hydraulic control unit obtains a detection result corresponding to a state in which the start operation is completed by the sensor. When this occurs, the hydraulic pressure in the hydraulic chamber is controlled so that the connection state is established. Therefore, as an example, when the suppression state is no longer necessary, it is easy to quickly shift to the connection state.

  In the hybrid system clutch system, as an example, at least the elastic member generates the pressing force in the connected state, and in the suppressed state, the elastic member generates the pressing force, and the piston presses the pressing force. Reduce power. Therefore, as an example, inconveniences such as resonance and torque fluctuation are unlikely to occur during the starting operation of the internal combustion engine.

  In the clutch system for a hybrid system, as an example, the hydraulic control unit includes a valve body and communicates with the hydraulic chamber that generates an oil pressure that reduces the pressing force during a start operation of the internal combustion engine. And includes a hydraulic control valve provided with a port that is opened and closed. When the internal combustion engine is stopped, the valve body closes the port. Therefore, as an example, when the internal combustion engine is restarted after being stopped, it is possible to suppress a decrease in the responsiveness of the increase in the hydraulic pressure in the hydraulic chamber, and hence the responsiveness to reduce the pressing force.

  In the clutch system for the hybrid system, as an example, the valve body is provided so as to be able to reciprocate, and the opening and closing of the port is switched by the reciprocating movement of the valve body. Two separate ports are provided adjacent to each other on both sides in the moving direction of the valve body and communicated with the drain when the internal combustion engine is stopped, and the valve body is interposed between the ports. Provided. Therefore, as an example, inconvenient events such as movement of the valve body due to a change in temperature of the hydraulic oil confined in the oil chamber of the hydraulic control valve are easily suppressed.

  In the clutch system for a hybrid system, as an example, the hydraulic control unit is configured to provide a path through which hydraulic fluid is supplied to the hydraulic chamber until the hydraulic chamber is filled with hydraulic fluid when the internal combustion engine is started. The flow path resistance is set smaller than the flow path resistance of the path after the hydraulic oil is filled in the hydraulic chamber. Therefore, according to the present embodiment, as an example, the hydraulic oil is easily supplied to the hydraulic chamber more quickly during the start operation of the internal combustion engine.

  Further, in the clutch system for a hybrid system, as an example, a housing chamber in which the first member and the second member are housed is formed, and the hydraulic control unit is configured so that the hydraulic pressure during the starting operation of the internal combustion engine is increased. The flow path resistance of another path through which hydraulic oil is supplied to the storage chamber until the hydraulic oil is filled in the chamber is larger than the flow path resistance of the other path after the hydraulic oil is filled in the hydraulic chamber. To do. Therefore, as an example, hydraulic oil is easily supplied to the hydraulic chamber more quickly during the start-up operation of the internal combustion engine. Further, as an example, after the hydraulic chamber is filled with the hydraulic oil, the hydraulic oil is easily supplied to the storage chamber more quickly.

  Moreover, the clutch apparatus used with the said clutch system for hybrid systems was provided with the said 1st member, the said 2nd member, the said cylinder part, the said elastic member, and the said piston as an example. Therefore, according to the present embodiment, as an example, inconveniences such as resonance and torque fluctuation are unlikely to occur during the starting operation of the internal combustion engine.

FIG. 1 is a diagram illustrating an example of a schematic configuration of a hybrid vehicle on which the hybrid system clutch system according to the embodiment is mounted. FIG. 2 is a cross-sectional view of one side of the rotation shaft of an example of a clutch unit included in the clutch system for a hybrid system according to the embodiment. FIG. 3 is a cross-sectional view on one side of the rotation shaft of an example of the clutch unit included in the clutch system for a hybrid system according to the embodiment. FIG. 4 is a cross-sectional view of an example of a valve unit included in the hybrid system clutch system according to the second embodiment, and is a view showing a passage configuration in a stopped state of the internal combustion engine. FIG. 5 is a cross-sectional view of an example of a valve unit included in the hybrid system clutch system according to the second embodiment, and is a diagram illustrating a passage configuration at the start of the internal combustion engine (immediately after the start). . FIG. 6 is a cross-sectional view of an example of a valve unit included in the clutch system for a hybrid system according to the second embodiment, and shows a passage configuration at the start of the internal combustion engine (at a time point after FIG. 5). It is a figure. FIG. 7 is a cross-sectional view of an example of a valve unit included in the clutch system for a hybrid system according to the second embodiment, and shows a passage configuration at the start of starting the internal combustion engine (time point after FIG. 6). It is a figure. FIG. 8 is a cross-sectional view of an example of a valve unit included in the clutch system for a hybrid system according to the second embodiment, and is a view showing a passage configuration in a shut-off state. FIG. 9 is a cross-sectional view of an example of a valve unit included in the hybrid system clutch system according to the second embodiment, and is a diagram illustrating a passage configuration at an initial stage when the state is shifted from the disconnected state to the connected state. It is. FIG. 10 is a cross-sectional view of an example of a valve unit included in the clutch system for a hybrid system according to the second embodiment, and is a view showing a passage configuration in a connected state. FIG. 11 is a cross-sectional view of an example of a valve unit included in the clutch system for a hybrid system according to the second embodiment, and the passage configuration in a state where the fourth control valve is opened and the fifth control valve is closed. FIG.

  A plurality of embodiments below includes the same configuration. Similar components are denoted by common reference numerals, and redundant description is omitted.

<First Embodiment>
The clutch system 1 for a hybrid system according to the embodiment is mounted on a hybrid vehicle 100 as shown in FIG. 1 as an example. The hybrid vehicle 100 includes an internal combustion engine 110 (engine) and a rotating electrical machine 120 (motor generator) as a generation source (power source, power device) of the rotational force. The clutch device 20 of the clutch system 1 switches the connection state between the rotating part 111 (crankshaft or the like) of the internal combustion engine 110 and the rotating part 121 of the rotating electrical machine 120 (the shaft 11 of the clutch unit 10 (see FIG. 2)). Rotation (torque) generated by at least one of the internal combustion engine 110 and the rotating electrical machine 120 is transmitted to the axle 160 and the wheels 170 via the torque converter 130, the lockup clutch 131, the transmission 140, the differential gear 150, and the like. The layout of FIG. 1 is merely an example, and the present invention can be applied to configurations other than FIG.

  In the present embodiment, as an example, the clutch system 1 includes a clutch device 20 and a hydraulic control unit 30. The hydraulic control unit 30 includes a valve unit 40, a control unit 50 (for example, an electronic control unit (ECU)) and a sensor 51. The hydraulic oil (working fluid, fluid, liquid, medium, for example, ATF (automatic transmission fluid), etc.) used in the hydraulic control unit 30 is supplied from a pump 60 that is a source of hydraulic energy. The pump 60 may be a mechanical pump that is rotated by the internal combustion engine 110 or the rotating electric machine 120, or may be an electric pump that is rotated by a motor different from the rotating electric machine 120. In the present embodiment, as an example, the pump 60 is a mechanical pump (as an example, a gear pump). In the present embodiment, as an example, the hydraulic oil also has a lubrication function, a cooling function, and the like.

  In the present embodiment, as an example, as illustrated in FIG. 2, the clutch device 20, the rotating electrical machine 120, the pump 60, and the like are included in the clutch unit 10. The clutch device 20 and the rotating electrical machine 120 are accommodated in the case 12 (accommodating chamber 12c) of the clutch unit 10. The rotating electrical machine 120 is positioned on the outer side (outer peripheral side) in the radial direction of the rotation axis Ax of the clutch device 20. Therefore, according to the present embodiment, as an example, the clutch unit 10 is prevented from increasing in size in the axial direction of the rotation axis Ax. Further, as an example, it is easy to share components compared to the case where the clutch device 20 and the rotating electrical machine 120 are configured separately. The pump 60 is configured by using a part of the case 12. Therefore, according to the present embodiment, as an example, the parts can be easily shared as compared with the case where the pump 60 is configured separately from the clutch unit 10.

  In the present embodiment, as an example, the case 12 (housing) of the clutch unit 10 is configured by combining a plurality (three in the present embodiment as an example) of members 13 to 15 (divided bodies). . The member 13 constitutes a wall portion 13a (end wall) on the input side (internal combustion engine 110 side, left side in FIG. 2). The member 14 includes a cylindrical wall portion 14a (circumferential wall, side wall) on the outer side in the radial direction and a wall portion 14b (end wall, outer portion) on the output side (torque converter 130 side, right side in FIG. 2). doing. Further, the member 15 constitutes an output-side wall portion 15a (end wall, inner portion) continuous with the wall portion 14b and a radially inner (inner peripheral side) cylindrical wall portion 15b. The wall 15b extends from the wall 15a to the input side. The members 13 to 15 are integrated by a coupler 80 (in this embodiment, a bolt as an example).

  The member 13 is provided with an opening 13b. A bearing 70 is attached to the opening 13b. The member 16 is rotatably supported by the case 12 via the bearing 70. The member 16 has a shaft 16a and wall portions 16b and 16c. The shaft 16a is coupled to the rotating part 111 (see FIG. 1) of the internal combustion engine 110. The shaft 16a is rotatably supported by the bearing 70. Moreover, the wall part 16b is extended in the radial direction outer side from the edge part of the output side of the shaft 16a, and is comprised by the disk shape. Moreover, the wall part 16c is extended in the output side from the edge part of the radial direction outer side of the wall part 16b, and is comprised by the cylindrical shape.

  In addition, a stator 124 of the rotating electrical machine 120 is fixed inside the member 14 in the radial direction. The stator 124 (armature, stator) has a stator core 122 and a coil 123 (winding). The stator core 122 is configured in a cylindrical shape. Inside the stator core 122 in the radial direction, a rotor 125 (rotating part, field, rotor) is positioned with a gap. The rotor 125 is a part of the rotating unit 121.

  The member 15 is provided with an opening 15c. The opening 15c is configured in a cylindrical shape. A bearing 71 is attached to the opening 15 c, and the member 17 is rotatably supported by the case 12 via the bearing 71. The member 17 has wall parts 17a-17e. The wall portion 17 a is configured in a cylindrical shape and is fixed to the outer periphery of the shaft 11. The wall portion 17b extends in the radial direction from the end portion on the input side of the wall portion 17a, and is configured in an annular shape and a plate shape. The wall portion 17c extends from the radially outer end of the wall portion 17b to the output side and has a cylindrical shape. The wall portion 17d extends radially outward from the output-side end of the wall portion 17c, and is configured in an annular shape and a plate shape. And in this embodiment, the rotor 125 of the rotary electric machine 120 is being fixed to the wall part 17d (member 17) as an example. The wall portion 17e extends from the radially outer end of the wall portion 17d to the input side and has a cylindrical shape. The wall portion 17 b extends between the wall portion 17 a and the wall portion 17 c on the input side of the wall portion 15 b of the member 15. Moreover, in this embodiment, the cyclic | annular groove part 17f opened to the output side is comprised by wall part 17a-17c as an example. The wall portion 15b and the bearing 71 are accommodated in the groove portion 17f. Moreover, in this embodiment, the cyclic | annular groove part 17g (recessed part) opened to the input side is comprised by wall part 17c-17e as an example. Further, the wall 18a of the member 18 that is located radially inward is positioned on the input side that is spaced from the wall 17d. The wall portion 18a extends from the input side portion of the wall portion 17c to the outside in the radial direction, and has an annular shape and a plate shape. The piston 23 is accommodated in the groove portion 17g. Two hydraulic chambers 21A and 21B defined by the piston 23 are formed in the groove portion 17g. And the cylinder part 22 is comprised by wall part 17c-17e and the wall part 18a which comprise the said groove part 17g.

  The member 16 rotates integrally with a rotating part 111 (see FIG. 1, not shown in FIG. 2) of the internal combustion engine 110. The member 17 and the shaft 11 rotate integrally with the rotor 125 (rotating part) of the rotating electrical machine 120. The clutch device 20 is provided between the member 16 and the member 17 and switches connection and disconnection with the members 16 and 17. The bearings 70 and 71 provided in the case 12 are arranged coaxially. Therefore, according to the present embodiment, as an example, the members 16 and 17, the shaft 11, the rotor 125, and the clutch device 20 all rotate around the rotation axis Ax (center axis, coaxial).

  In the present embodiment, the clutch device 20 is a wet multi-plate clutch as an example. The clutch device 20 includes a plurality of first members 24 (in the present embodiment, a friction plate as an example) and a plurality of second members 25 (in the present embodiment, a separate plate as an example). Both the first member 24 and the second member 25 are arranged in a posture orthogonal to the rotation axis Ax. The first member 24 and the second member 25 are formed in an annular and plate shape. The first member 24 and the second member 25 are alternately arranged in the axial direction.

  The first member 24 is supported by the member 16 so as to be movable in the axial direction of the rotation axis Ax, and is supported so as not to rotate in the circumferential direction of the rotation axis Ax. The first member 24 rotates integrally with the member 16 and thus the rotating portion 111 of the internal combustion engine 110. The second member 25 is supported by the member 17 so as to be movable in the axial direction of the rotation axis Ax, and is supported so as not to rotate in the circumferential direction of the rotation axis Ax.

  The piston 23 includes a wall portion 23a (a partition wall portion, a piston portion) and a protruding portion 23b (a transmission portion). The wall portion 23a divides the cylinder portion 22 into two hydraulic chambers 21A and 21B. The hydraulic oil is supplied from the valve unit 40 to the hydraulic chambers 21A and 21B via passages 12a and 12b provided in the case 12. In such a configuration, when the hydraulic pressure in the hydraulic chambers 21 </ b> A and 21 </ b> B is appropriately adjusted, the piston 23 projects from the cylinder portion 22. When the piston 23 protrudes, the first member 24 and the second member 25 are pressed against each other. In the present embodiment, as an example, the piston 23 protrudes when the hydraulic pressure in the hydraulic chamber 21B increases, and the piston 23 retracts when the hydraulic pressure in the hydraulic chamber 21A increases.

  In the present embodiment, as an example, an elastic member 26 (in the present embodiment, a coil spring as an example) is provided in the hydraulic chamber 21B. The elastic member 26 is provided between the piston 23 and the wall portion 17d on the opposite side of the piston 23. The elastic member 26 is configured as a compression spring, and gives an elastic repulsive force to the piston 23 according to the amount of compression. Therefore, in this embodiment, as an example, the elastic member 26 generates a pressing force that presses the first member 24 and the second member 25 together.

  In such a configuration, when the piston 23 protrudes from the cylinder portion 22 and pushes the first member 24 or the second member 25 (in this embodiment, the second member 25 as an example) with a required pressing force, Due to the frictional force between the first member 24 and the second member 25 corresponding to the pressing force, the first member 24 and the second member 25 are connected to rotate integrally. Further, when the piston 23 is retracted into the cylinder portion 22, the first member 24 and the second member 25 are separated from each other, and the rotation is not transmitted between the first member 24 and the second member 25. It becomes. Further, when the pressing force by the piston 23 is smaller than the connected state, the first member 24 and the second member 25 are pressed against each other, but between the first member 24 and the second member 25. A restrained state in which the transmission of torque is restrained is obtained. In the present embodiment, as an example, the pressing force that presses the first member 24 and the second member 25 together is given from the elastic member 26 and the piston 23. The pressing force by the elastic member 26 is determined by the preload (initial compression load, set load) of the elastic member 26, the compression amount (position of the piston 23), the spring constant, and the like. Further, the pressing force by the hydraulic pressure acting from the piston 23 is determined by the pressure of the hydraulic chambers 21A and 21B, the area of the piston 23, and the like. In the present embodiment, as an example, the connection state, the cutoff state, and the suppression state described above can be switched by controlling the hydraulic pressures of the hydraulic chambers 21A and 21B by the hydraulic control unit 30.

  In the present embodiment, as an example, the hydraulic control unit 30 controls the clutch device 20 to be in a restrained state during the start operation (during the start operation) of the internal combustion engine 110. Here, the starting operation of the internal combustion engine 110 is, for example, the start of rotation (cranking) of the rotating portion 111 of the internal combustion engine 110 by an external rotational drive device (drive source) such as a starter motor and ignition control. Is the operation of the internal combustion engine 110 until an idling state (operating state at no load and a relatively low constant rotation) is obtained, and the start operation time is a period during which the start operation is being executed. .

  In the present embodiment, as an example, the preload of the elastic member 26 (the pressing force by the elastic member 26 in a state where the oil pressure is not acting (stopped state of the internal combustion engine 110)) is the preload (only). Is set to a value that can obtain the suppression state. Therefore, according to the present embodiment, for example, the hydraulic pressure of the hydraulic chambers 21A and 21B is not adjusted (or adjusted) by the hydraulic control unit 30 immediately or immediately after the internal combustion engine 110 starts the starting operation such as when the hybrid vehicle 100 is started. Even if it is difficult to adjust, it is easy to obtain a restrained state by the pressing force of the elastic member 26. Moreover, at the time of low temperature start etc., the viscosity of hydraulic fluid rises and the responsiveness of the pressure rise of hydraulic chamber 21A, 21B may fall. Even in such a case, according to the present embodiment, the suppression state is easily obtained. In the suppressed state, torque transmission is suppressed between the first member 24 (the rotating part 111 of the internal combustion engine 110) and the second member 25 (the rotating part 121 of the rotating electrical machine 120). Here, if the clutch device 20 (clutch unit 10, clutch system 1) is in a connected state at the start of the starting operation of the internal combustion engine 110, for example, resonance occurs due to an inertia load of the rotating electrical machine 120. In some cases, torque fluctuation (rotational fluctuation, hunting) tends to increase. In this regard, according to the present embodiment, as an example, when the internal combustion engine 110 is started (at the start of the start operation), the clutch device 20 is set in a suppressed state, and thus the rotating portion 111 of the internal combustion engine 110 is set. Transmission of torque between the rotating part 121 and the rotating part 121 of the rotating electrical machine 120 is suppressed. Therefore, according to the present embodiment, as an example, resonance and torque fluctuation (rotational fluctuation, hunting) due to the inertial load of the rotating electrical machine 120 are less likely to occur.

  In the present embodiment, as an example, the preload of the elastic member 26 can only obtain a pressing force to be in a restrained state. Therefore, in order to obtain a connected state, the pushing force of the piston 23 by the hydraulic pressure of the hydraulic chambers 21A and 21B. Is required. Specifically, in the present embodiment, as an example, the control unit 50 of the hydraulic control unit 30 indicates that the detection result of the rotation state of the internal combustion engine 110 by the sensor 51 (see FIG. 1) corresponds to the idling state of the internal combustion engine 110. When the detection result, that is, the detection result when the starting operation is completed, the pressing force by the hydraulic pressure in the hydraulic chambers 21A and 21B is added to the pressing force by the elastic member 26 to establish a connection state. The valve unit 40 (see FIG. 1) includes one or more hydraulic control valves (eg, regulators, relief valves, switching valves, etc., not shown in FIGS. 1 and 2). The hydraulic pressure in the hydraulic chambers 21A and 21B is adjusted to a required value by electrically controlling the valve unit 40 (hydraulic control valve), the pump 60 (however, in the case of an electric pump, see FIG. 1), and the like. The sensor 51 is, for example, a rotation sensor of the rotation unit 111 of the internal combustion engine 110, a throttle sensor, a torque sensor, or the like.

  As described above, in the present embodiment, as an example, the clutch system 1 presses the first member 24 and the second member 25 with a pressing force smaller than the connected state when the internal combustion engine 110 is started. Then, a suppression state is set in which the transmission of torque between the first member 24 and the second member 25 is suppressed. Therefore, according to the present embodiment, as an example, during the start-up operation of the internal combustion engine 110, torque transmission between the first member 24 and the second member 25 is suppressed, thereby causing rotational fluctuations and the like. Inconvenient events are unlikely to occur.

  In the present embodiment, as an example, during the starting operation, the elastic member 26 generates a pressing force that presses the first member 24 and the second member 25 together, and the piston 23 does not generate a pressing force or the pressing force. Depending on the hydraulic pressure of the hydraulic chambers 21A and 21B, it is possible to obtain a restrained state without a pressing force or a force that reduces the pressing force. Thus, according to the present embodiment, as an example, the hydraulic pressure of the hydraulic chambers 21A and 21B is not adjusted (or difficult to adjust or cannot be adjusted) by the hydraulic control unit 30 immediately or immediately after the internal combustion engine 110 starts the starting operation. Even in such a case, the suppression state is easily obtained by the pressing force of the elastic member 26.

  In the present embodiment, as an example, when the internal combustion engine 110 is stopped, the elastic member 26 generates a pressing force that obtains a suppressed state during the starting operation. Therefore, according to the present embodiment, as an example, it is easy to set a state in which inconveniences such as resonance and torque fluctuation are unlikely to occur from the start point of the starting operation of the internal combustion engine 110 (immediately after starting).

  In the present embodiment, as an example, when the detection result corresponding to the state in which the start operation is completed is obtained by the sensor 51, the hydraulic control unit 30 increases the hydraulic pressure in the hydraulic chambers 21A and 21B to establish a connection state. To. Therefore, according to the present embodiment, as an example, when the suppression state is no longer necessary, it is easy to quickly shift to the connection state.

Second Embodiment
The present embodiment illustrated in FIGS. 3 to 11 also has the same configuration as that of the first embodiment. Therefore, the same result (effect) based on the same configuration can be obtained also in this embodiment. However, as shown in FIG. 3, in the clutch unit 10 </ b> A of the clutch system 1 </ b> A according to the present embodiment, as an example, a hydraulic chamber is used instead of the hydraulic chamber 21 </ b> B (see FIG. 2) that generates (increases or strengthens) a pressing force. A cancel chamber 31A for canceling the so-called centrifugal hydraulic pressure of 21A is provided. Specifically, a cancel chamber 31 </ b> A into which hydraulic oil enters is configured between the wall portions 17 c to 17 e configuring the groove portion 17 g and the piston 23. The cancel chamber 31A communicates with the storage chamber 12c in the case 12 through a passage 17h provided in the wall portion 17d. The passage 17h is opened in the cancel chamber 31A at an intermediate position between the inner peripheral surface (wall portion 17c) and the outer peripheral surface (wall portion 17e) of the cancel chamber 31A. Accordingly, the hydraulic oil that has entered the cancellation chamber 31A escapes from the passage 17h into the accommodation chamber 12c due to centrifugal force or the like, but is a region radially outside the opening edge of the passage 17h of the cancellation chamber 31A to the cancellation chamber 31A. The hydraulic oil remains in The hydraulic oil remaining in the cancel chamber 31 </ b> A gives a force corresponding to the centrifugal force to the piston 23 when centrifugal force acts with rotation. The hydraulic oil stored in the hydraulic chamber 21 </ b> A also applies a force corresponding to the centrifugal force to the piston 23 when centrifugal force is applied with rotation. Here, the direction of the force applied to the piston 23 by the hydraulic oil remaining in the cancel chamber 31A and the direction of the force applied to the piston 23 by the hydraulic oil in the hydraulic chamber 21A are opposite to each other. Therefore, according to the present embodiment, as an example, the force applied to the piston 23 by the centrifugal force acting on the hydraulic oil in the cancel chamber 31A is the force applied to the piston 23 by the hydraulic oil in the hydraulic chamber 21A. The component based on centrifugal force can be reduced. The magnitude of the force (depletion force) caused by the hydraulic oil entering the cancel chamber 31A can be adjusted by the specifications (position, flow path resistance, etc.) of the passage 17h.

  Moreover, in this embodiment, the point from which the preload of the elastic member 26 is set to the value which can acquire a connection state with the said preload (only) as an example is different from the said 1st Embodiment. ing. Therefore, in the present embodiment, as an example, in order to obtain the connected state, it is necessary to reduce the pressing force of the piston 23 by the hydraulic pressure of the hydraulic chamber 21A (for example, increasing the hydraulic pressure of the hydraulic chamber 21A).

  In the present embodiment, as an example, as shown in FIG. 4, a valve unit 40 </ b> A (hydraulic control unit 30 </ b> A) that controls the hydraulic pressure of the clutch unit 10 </ b> A in FIG. 3 is provided. The valve unit 40A is used in place of the valve unit 40 (hydraulic control unit 30) of the first embodiment. The valve unit 40A (hydraulic control unit 30A) includes a plurality of hydraulic control valves 41 to 45.

  The hydraulic control valve 41 is an example of a pressure adjustment valve (first pressure adjustment valve). The upper limit value of the line pressure in the passage 46d (passage 46a) is set by the hydraulic control valve 41. The hydraulic control valve 42 is an example of a switching valve. The hydraulic circuit can be switched by the operation of the hydraulic control valve 42. As an example, the hydraulic control valve 44 is a normally open direct acting solenoid valve (for example, a two-stage solenoid valve) that obtains a hydraulic pressure for operating the hydraulic control valve 42. The hydraulic control valve 44 allows hydraulic oil to flow through the drain in the open state where no current is supplied, and increases the pressure in the closed state where the current is supplied. The hydraulic control valve 42 is an example of a pilot electromagnetic valve that uses the hydraulic control valve 44 as a pilot valve. The hydraulic control valve 43 is an example of a second pressure regulating valve that changes (sets) the hydraulic pressure in the hydraulic chambers 21A and 21B. The hydraulic control valve 43 can change the hydraulic pressure in the hydraulic chambers 21A and 21B continuously or in a plurality of stages. As an example, the hydraulic control valve 45 is a normally open direct acting solenoid valve (for example, a linear solenoid valve) that obtains a hydraulic pressure for operating the hydraulic control valve 43. The hydraulic control valve 45 allows hydraulic oil to flow through the drain in the open state where no current is supplied, and increases the pressure in the closed state where the current is supplied. The hydraulic control valve 43 is an example of a pilot solenoid valve that uses the hydraulic control valve 45 as a pilot valve.

  The hydraulic control valve 41 is, for example, a spool valve, and includes a housing 41a (body, sleeve), a spool 41b (valve element), and a coil spring 41c. The housing 41a is provided with a hole 41d and ports 411 to 415. The hole 41d is formed in a cylindrical shape. The spool 41b is accommodated in the hole 41d so as to be able to reciprocate. Furthermore, the coil spring 41c is accommodated in the hole 41d. The coil spring 41c gives an elastic force (drag) to the spool 41b. The spool 41b is provided with a plurality of annular recesses 41b1 and 41b2 (a groove portion, a narrowed portion, a reduced diameter portion, and a small diameter portion) along the circumferential direction.

  The hydraulic control valve 42 is a spool valve, for example, and includes a housing 42a (body, sleeve), a spool 42b (valve element), and a coil spring 42c. A hole 42d and ports 421 to 427 are provided in the housing 42a. The hole 42d is formed in a cylindrical shape. The spool 42b is accommodated in the hole 42d so as to be able to reciprocate. Further, a coil spring 42c is accommodated in the hole 42d. The coil spring 42c gives an elastic force (resistance force) to the spool 42b. The spool 42b is provided with a plurality of annular recesses 42b1 to 42b3 (a groove portion, a narrowed portion, a reduced diameter portion, and a small diameter portion) along the circumferential direction.

  The hydraulic control valve 43 is a spool valve as an example, and includes a housing 43a (body, sleeve), a spool 43b (valve element), a coil spring 43c, and a sleeve 43e (movable sleeve). The housing 43a is provided with a hole 43d and ports 431 to 439. The hole 43d is formed in a cylindrical shape. The spool 43b and the sleeve 43e are accommodated in the hole 43d so as to be able to reciprocate. A concave portion 43f (inside the cylinder) is formed in the sleeve 43e. The spool 43b is also accommodated in the recess 43f so as to be able to reciprocate. Furthermore, the coil spring 43c is accommodated in the hole 43d. The coil spring 43c gives an elastic force (drag) to the spool 43b. The spool 43b is provided with a plurality of annular recesses 43b1 and 43b2 (a groove portion, a narrowed portion, a reduced diameter portion, and a small diameter portion) along the circumferential direction.

  A port 435 of the hydraulic control valve 43 is communicated with the hydraulic chamber 21A via a passage 12a (see FIG. 3) and a passage 46a (see FIG. 4), and the passage 12b (see FIG. 3) and the passages 46f and 46g (see FIG. 4), the port 413 of the hydraulic control valve 41 or the port 438 of the hydraulic control valve 43 is communicated. The hydraulic control unit 30A controls the supply of hydraulic oil to the hydraulic chamber 21A, the storage chamber 12c, and the cancel chamber 31A, and also controls the pressure of the hydraulic chamber 21A.

  FIG. 4 shows a state where the internal combustion engine 110 is stopped, the pump 60 is stopped, the hydraulic control valves 44 and 45 are not electrically controlled and opened, and no hydraulic pressure is generated in the valve unit 40A. Yes. In this state, the spools 41b to 43b and the sleeve 43e of the hydraulic control valves 41 to 43 are pushed by the coil springs 41c to 43c and are located at the left end (initial position) in FIG.

  In the present embodiment, as an example, the port 435 of the hydraulic control valve 43 communicated with the hydraulic chamber 21A via the passage 46a and the passage 12a (see FIG. 2) in the state of FIG. 4 is closed by the spool 43b. . Therefore, as an example, the hydraulic oil from the hydraulic chamber 21A is prevented from being lost, and as an example, when the internal combustion engine 110 is restarted after being stopped, the responsiveness of the increase in the hydraulic pressure in the hydraulic chamber 21A is reduced. It is suppressed. Further, two ports 434 and 436 arranged at intervals on both sides in the moving direction of the spool 43b of the port 435 are both communicated with the drain. Specifically, the port 434 communicates with the drain through the hole 43d (the recess 43b1 of the spool 43b), the port 433, and the passage 46b. The port 436 includes the passage 46c, the port 425, the hole 42d (the recess of the spool 42b). 42b3) and communicated with the drain via the port 426. Therefore, according to the present embodiment, as an example, adverse events such as a decrease in hydraulic pressure at the port 435 due to the flow of hydraulic oil between the port 435 and the adjacent ports 434 and 436 are suppressed. Cheap.

  When the start operation of the internal combustion engine 110 is started in the state of FIG. 4 and the pump 60 is operated, the pressure (hydraulic pressure) in the discharge-side passage 46d of the pump 60 increases. In addition, the control unit 50 controls (closes) the hydraulic control valves 44 and 45 from the time when the starting operation is started. As a result, the pressure at the ports 411, 414, 421, 424, 431, and 432 increases. And the hydraulic-control valves 41-43 transfer to the state of FIG. 5 from the state of FIG.

  In the hydraulic control valve 42, the hydraulic pressure of the port 421 increases, and the spool 42b moves to the right end position in FIG. 5 against the elastic force of the coil spring 42c. In this state, the discharge port of the pump 60 communicates with the ports 434 and 436 through the passage 46d, the port 424, the hole 42d (the concave portion 42b2 of the spool 42b), the port 425, and the passages 46c and 46e.

  Further, in the hydraulic control valve 43, as shown in FIG. 5, as the pressure of the ports 431 and 432 rises, the sleeve 43e resists the elastic force of the coil spring 43c, and the diameter of the enlarged portion 43d1 of the hole 43d. Move to the rightmost position. The pressure of the port 432 is adjusted by the hydraulic control valve 45. Further, the port 432 is communicated with the hydraulic chamber 43g on the left side of FIG. 5 from the spool 43b of the concave portion 43f of the sleeve 43e through a hole 43e1 (opening) provided in the diameter-expanded portion 43d1 and the sleeve 43e. The position of the spool 43b is positioned on the right side in FIG. 5 as the pressure in the hydraulic chamber 43g on the left side in FIG. 5 is higher than the spool 43b in the concave portion 43f. Therefore, in this embodiment, as an example, the position of the spool 43b can be controlled by the hydraulic control valve 45 (the degree of valve opening). Note that the greater the differential pressure between the port 431 and the port 432, the greater the oil pressure acting on the spool 43b toward the right side of FIG. 5, and the port 433 communicates with the drain in the state of FIG. The spool 43b moves from the position shown in FIG. 5 to the position shown in FIG.

  During the starting operation of the internal combustion engine 110 (during the starting operation), the hydraulic control valves 41 to 43 are in the states shown in FIGS. 5 and 6 show a state until the hydraulic chamber 21A is filled with hydraulic oil, and FIG. 7 shows a state after the hydraulic chamber 21A is filled with hydraulic oil. 5 to 7, the position of the spool 41b of the hydraulic control valve 41 or the position of the spool 43b of the hydraulic control valve 43 is different. The pressure in the hydraulic chamber 21A is a value corresponding to the pressure on the outlet side of the port 435 (for example, approximately the same value if the flow rate, flow path resistance, leakage, etc. are small). 5 and 6, as the spool 43b is positioned on the right side of FIGS. 5 and 6, the port 434 communicated with the discharge side of the pump 60 and the opening portion 433a (constriction portion) of the port 433 communicated with the drain. The flow path resistance between the port 434 and the port 433 increases due to the narrowing. 5 and 6, as the spool 43b is positioned on the right side of FIGS. 5 and 6, the opening 435a (constriction portion) of the port 435 communicating with the port 434 and the hydraulic chamber 21A is expanded, and the port 434 is expanded. And the flow path resistance between the port 435 is reduced. Therefore, in the state of FIGS. 5 and 6, the hydraulic oil is supplied to the hydraulic chamber 21 </ b> A more rapidly as the spool 43 b is positioned on the right side. In the present embodiment, as an example, a throttle portion 47 (an orifice in the present embodiment as an example) is provided in the passage 46e serving as a flow path of the hydraulic oil to the hydraulic chamber 21A and the drain. Therefore, according to the present embodiment, in the state of FIG. 5 (that is, at the time of starting operation), a rapid increase in the pressure in the hydraulic chamber 21A and an increase in the leakage of hydraulic oil through the port 433 are easily suppressed. Further, in the state of FIG. 6, the space between the port 434 and the port 433 is closed by the spool 43b. Therefore, according to this embodiment, in the state of FIG. 6 (that is, at the time of starting operation), an increase in hydraulic oil leakage through the port 433 is easily suppressed. A notch 43e3 (opening) is provided at the right end of the sleeve 43e in FIGS. As shown in FIGS. 5 to 7, when the sleeve 43e is positioned at the right end, the port 433 communicates with the inside of the hole 43f through the notch 43e3.

  In the present embodiment, as an example, in the state of FIG. 6, the port 435 communicated with the hydraulic chamber 21A communicates with both the port 434 and the port 436 through the hole 43d (the recess 43b1 of the spool 43b). The Therefore, according to the present embodiment, as an example, the hydraulic oil is more rapidly supplied to the hydraulic chamber 21A from both the passages 46c and 46e (path).

  In the present embodiment, as an example, in the state of FIG. 7, the control of the hydraulic pressure by the hydraulic control valve 45 is started as the pressure on the discharge side of the pump 60 increases. In the hydraulic control valve 41, the spool 41b moves to the right side of the position shown in FIGS. Thereby, the port 414 and the port 413 are communicated, and the supply of hydraulic oil to the storage chamber 12c and the canceller chamber 31A is started.

  After the state of FIG. 6, when the hydraulic chamber 21A is filled with hydraulic fluid and the pressure in the hydraulic chamber 21A increases, the pressure in the port 435 increases. Then, the spool 43b moves from the position of FIG. 6 to the position of FIG. In the state of FIG. 7, when the position of the spool 43 b changes due to the operation of the hydraulic control valve 45 (pressure control, valve opening amount control), the flow path resistance between the port 435 and the port 433 changes accordingly, and the port 435. , And thus the pressure in the hydraulic chamber 21A changes. That is, in the state of FIG. 7, the control unit 50 can control the pressure in the hydraulic chamber 21 </ b> A by controlling the hydraulic control valve 45.

  In the state where the spool 43b is at the position shown in FIG. 7, the port 438 communicating with the storage chamber 12c and the canceller chamber 31A via the passage 46f is connected to the port 437 via the hole 43d (the recess 43b2 of the spool 43b). Communicated. In this state, the port 413 and the passage 46f are communicated in parallel with the throttle portion 47 via a passage including the passage 46g, the ports 437 and 438, and the hole 43d (recess 43b2). Therefore, in the state of FIG. 7, hydraulic fluid is supplied more rapidly to the storage chamber 12c and the canceller chamber 31A. Therefore, according to this embodiment, as an example, heat generation, overheating, and the like of components such as the first member 24 and the second member 25 housed in the housing chamber 12c are easily suppressed.

  Further, when the spool 43b is in the position shown in FIG. 7, the hole 43d between the port 435 communicating with the hydraulic chamber 21A and the port 436 communicating with the discharge side passage 46d of the pump 60 is closed by the spool 43b. It has been. Therefore, the port 435 communicated with the hydraulic chamber 21A communicates with the port 434 connected with the passage 46e provided with the throttle 47, but with the port 436 connected with the passage 46c not provided with the throttle 47. Does not communicate. Therefore, compared with the state of FIG. 6, the flow rate of the hydraulic oil supplied to the hydraulic chamber 21A decreases, and consequently the flow rate of the hydraulic oil supplied to the storage chamber 12c and the canceller chamber 31A increases.

  FIG. 8 shows a state of the hydraulic control valves 41 to 43 in a shut-off state where the first member 24 and the second member 25 are separated from each other and rotation is not transmitted. In this state, the hydraulic pressure in the direction opposite to the elastic force due to the hydraulic pressure in the hydraulic chamber 21A (and the hydraulic chamber 21B) becomes larger than the elastic force due to the elastic member 26, and the first member 24 and The pressing force pressing the second member 25 against each other is reduced.

  In the state of FIG. 8, the position of the spool 43b is different from the state of FIG. In FIG. 8, the control unit 50 controls the hydraulic control valve 45 to further increase the pressure in the hydraulic chamber 43g (port 432), thereby positioning the spool 43b at the right end of FIG. In this case, the port 435 communicated with the hydraulic chamber 21A communicates with both the port 434 and the port 436 through the hole 43d (the recess 43b1 of the spool 43b). Therefore, the flow resistance between the ports 434, 436 and the port 435 can be made smaller than the state of FIG. 7, and the hydraulic pressure of the hydraulic chamber 21A can be made higher than the state of FIG.

  In the state of FIG. 8, in the hydraulic control valve 41, the higher the pressure of the port 411, that is, the pressure on the discharge side of the pump 60 (line pressure), the spool 41b is shown against the elastic force of the coil spring 41c. 8 on the right side. As the spool 41b is positioned on the right side of FIG. 8, the opening 415a of the port 415 expands, and the flow resistance between the port 414 and the port 415 decreases, and the pressure of the port 414, that is, the discharge side of the pump 60 is reduced. Pressure is lowered. In the state of FIG. 8, the port 413 communicated with the hydraulic chamber 21B and the accommodating chamber 12c in the case 12 of the clutch unit 10 communicates with the discharge side of the pump 60 through the hole 41d (the recess 41b1 of the spool 41b). Communicated with the connected port 414. The passage 46f that communicates with the port 413 and the canceller chamber 31A or the storage chamber 12c is provided with a throttle portion 47 (in this embodiment, an orifice as an example). Therefore, during the pressure adjustment by the hydraulic control valve 41, the hydraulic pressure reduced by the throttle 47 from the pressure on the discharge side of the pump 60 is supplied into the hydraulic chamber 21 </ b> B and the case 12.

  Moreover, as will be apparent from a comparison between FIG. 4 and FIGS. 5 to 7, in this embodiment, as an example, by setting the preload of the coil springs 41 c, 42 c, 43 c, etc. The spools 42b and 43b move to the right side in FIGS. 4 to 7 before the spool 41b of the hydraulic control valve 41. If the spool 41b of the hydraulic control valve 41 moves at an early stage of the starting operation, the pressure on the discharge side of the pump 60, and hence the pressure in the hydraulic chamber 21A, may not easily increase. In this regard, in the present embodiment, as an example, the spools 42 b and 43 b of the hydraulic control valves 42 and 43 move before the spool 41 b of the hydraulic control valve 41. Therefore, according to the present embodiment, as an example, it is easy to suppress the pressure in the hydraulic chamber 21A from increasing.

  9 shows the state of the valve unit 40A when the clutch device 20 shifts from the disconnected state (state of FIG. 8) to the engaged state, and FIG. 10 shows the state of the clutch device 20 in the engaged state. The state of the valve unit 40A is shown. As shown in FIGS. 9 and 10, when shifting from the shut-off state to the engaged state, the control unit 50 controls the hydraulic control valve 45 to move the spool 43b of the hydraulic control valve 43 to the left end of FIGS. Then, the hydraulic control valve 44 is controlled to move the spool 42b of the hydraulic control valve 42 to the left end in FIGS. FIG. 11 shows a state in which the spool 42b of the hydraulic control valve 42 is positioned at the left end of FIG. 11 and the spool 43b of the hydraulic control valve 43 is positioned at the right end of FIG. 9 and 10, unless both of the spools 42b and 43b of the hydraulic control valves 42 and 43 move to the right side of FIGS. 9 and 10, the pressure of the port 435 connected to the hydraulic chamber 21B is difficult to increase, and the clutch device 20 It can be seen that it is difficult to obtain a hydraulic pressure that cuts off.

  As described above, in the present embodiment, as an example, in the connected state, at least the elastic member 26 generates a pressing force that presses the first member 24 and the second member 25 of the clutch device 20 against each other, and is in a suppressed state. Then, the elastic member 26 generates a pressing force, and the piston 23 (the hydraulic pressure acting on the piston 23) reduces the pressing force. Therefore, also by this embodiment, as an example, at the time of starting operation of the internal combustion engine 110, problems such as resonance and torque fluctuation are unlikely to occur. Further, even in a situation where the hydraulic pressure is difficult to act on the piston 23, the connection state between the internal combustion engine 110 and the rotating electrical machine 120 can be more reliably obtained.

  In the present embodiment, as an example, when the internal combustion engine 110 is stopped, the port 435 communicated with the hydraulic chamber 21A is closed by the spool 43b. Therefore, according to the present embodiment, as an example, the hydraulic oil from the hydraulic chamber 21A is prevented from coming off, and as an example, when the internal combustion engine 110 is restarted after being stopped, a response to an increase in the hydraulic pressure in the hydraulic chamber 21A. It is suppressed that the responsiveness which reduces a property and by extension, a pressing force falls.

  In the present embodiment, as an example, two ports 434 and 436 are provided adjacent to each other with a gap on both sides of the port 435 in the moving direction of the spool 43b. When the internal combustion engine 110 is stopped, the spool 43b is interposed between the ports 434, 436 and the port 435, and the ports 434, 436 are all connected to the drain. Therefore, according to the present embodiment, as an example, inconvenient events such as movement of the spool 43b due to a temperature change of the hydraulic oil confined in the oil chamber of the hydraulic control valve 43 are easily suppressed.

  In the present embodiment, as an example, the hydraulic control unit 30A determines the flow path resistance of the path through which the hydraulic oil is supplied to the hydraulic chamber 21A until the hydraulic chamber 21A is filled with the hydraulic oil during the startup operation of the internal combustion engine 110. The flow resistance of the path after the hydraulic oil is filled in the hydraulic chamber 21A is made smaller. Therefore, according to the present embodiment, as an example, hydraulic oil is easily supplied to the hydraulic chamber 21 </ b> A more quickly when the internal combustion engine 110 is started.

  Further, in the present embodiment, as an example, the hydraulic control unit 30A is provided with another hydraulic oil supplied to the storage chamber 12c and the canceller chamber 31A until the hydraulic chamber 21A is filled with the hydraulic oil during the start operation of the internal combustion engine 110. The flow path resistance of the path is made larger than the flow path resistance of the other path after the hydraulic oil is filled in the hydraulic chamber 21A. Therefore, according to the present embodiment, as an example, the hydraulic oil is easily supplied to the hydraulic chamber 21 </ b> A more quickly during the start operation of the combustion engine 110. Further, as an example, after the hydraulic chamber 21A is filled with the hydraulic oil, the hydraulic oil is likely to be supplied more quickly to the storage chamber 12c and the canceller chamber 31A.

  As mentioned above, although embodiment and the modification of this invention were illustrated, the said embodiment and modification are an example to the last, Comprising: It is not intending limiting the range of invention. These embodiments and modifications can be implemented in various other forms, and various omissions, replacements, combinations, and changes can be made without departing from the scope of the invention. In addition, the configuration and shape of each embodiment or modification may be partially exchanged. In addition, specifications (structure, type, direction, shape, size, length, width, thickness, height, number, arrangement, position, material, etc.) of each configuration, shape, display element, etc. It can be changed and implemented. That is, the configurations of the clutch device, the hydraulic control valve, and the hydraulic circuit can be changed as appropriate.

  DESCRIPTION OF SYMBOLS 1 ... Clutch system, 110 ... Internal combustion engine, 111 ... Rotating part, 120 ... Rotating electric machine, 121 ... Rotating part, 12c ... Accommodating chamber, 21A ... Hydraulic chamber (reducing pressing force), 22 ... Cylinder part, 30, 30A ... Hydraulic control unit, 31A ... canceller chamber, 43 ... hydraulic control valve, 43b ... spool (valve element), 435 ... port, 434, 436 ... (other) port.

Claims (10)

A first member that rotates integrally with the rotating portion of the internal combustion engine;
A second member that rotates integrally with the rotating portion of the rotating electrical machine;
A cylinder portion provided with at least one hydraulic chamber;
An elastic member that generates a pressing force in a direction in which the first member and the second member are pressed against each other by elasticity; and
A piston that is at least partially movably accommodated in the cylinder portion, and that generates the pressing force or reduces the pressing force by the hydraulic pressure of the hydraulic chamber;
A hydraulic control unit for controlling the hydraulic pressure of the hydraulic chamber;
With
The connection state in which the first member and the second member are pressed against each other by the pressing force and rotate integrally with each other, and the first member and the second member are separated from each other. A blocking state in which rotation is not transmitted between the member and the second member, and the first member and the second member are pressed against each other by the pressing force smaller than the connection state, A clutch system for a hybrid system that switches between a suppression state in which transmission of torque to and from a second member is suppressed and sets the suppression state during a start operation of the internal combustion engine.   During the starting operation of the internal combustion engine, the suppression state can be obtained in a state where the elastic member generates the pressing force and the piston does not generate the pressing force or does not reduce the pressing force. The clutch system for a hybrid system according to claim 1.   3. The clutch system for a hybrid system according to claim 2, wherein the elastic member generates the pressing force for obtaining the suppression state during a start operation of the internal combustion engine when the internal combustion engine is stopped. A sensor for detecting a rotation state of the internal combustion engine;
The hydraulic control unit according to claim 1, wherein the hydraulic pressure control unit controls the hydraulic pressure of the hydraulic chamber so as to be in the connected state when a detection result corresponding to a state in which the start operation is completed is obtained by the sensor. The clutch system for hybrid systems as described in any one of them. In the connected state, at least the elastic member generates the pressing force,
The clutch system for a hybrid system according to claim 1, wherein, in the restrained state, the elastic member generates the pressing force, and the piston reduces the pressing force. The hydraulic control unit includes a hydraulic control valve having a valve body and provided with a port that is communicated with the hydraulic chamber for generating an oil pressure to reduce the pressing force during a start operation of the internal combustion engine and is opened and closed by the valve body. Including
The clutch system for a hybrid system according to claim 5, wherein the port is closed by the valve body when the internal combustion engine is stopped. The valve body is provided to be reciprocally movable,
The opening and closing of the port is switched by the reciprocating movement of the valve body,
The hydraulic control valve is provided adjacent to both sides of the port in the moving direction of the valve body with a space therebetween, and is communicated with a drain when the internal combustion engine is stopped, and is connected between the port and the valve. The clutch system for a hybrid system according to claim 6, wherein two separate ports through which a body is interposed are provided.   The hydraulic control unit fills the hydraulic chamber with a flow path resistance of a path through which the hydraulic oil is supplied to the hydraulic chamber until the hydraulic chamber is filled with the hydraulic oil during a start operation of the internal combustion engine. The clutch system for a hybrid system according to claim 6 or 7, wherein the clutch system is made smaller than a flow path resistance of the path after being applied. A storage chamber in which the first member and the second member are stored is formed,
The hydraulic control unit provides a flow path resistance of another path through which hydraulic oil is supplied to the storage chamber until the hydraulic chamber is filled with hydraulic oil during a start operation of the internal combustion engine. The clutch system for a hybrid system according to any one of claims 6 to 8, wherein the clutch resistance is set to be larger than a flow path resistance of the another path after the condition is satisfied.   It is used with the clutch system for hybrid systems as described in any one of Claims 1-9, Said 1st member, said 2nd member, said cylinder part, said elastic member, and said piston, A clutch device.

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