JP5673000B2 - Clutch device - Google Patents

Description

  The present invention relates to a clutch device that intermittently transmits driving force between an input member and an output member.

  Conventionally, in a clutch device for a vehicle transmission, a piston chamber and a cancel chamber are provided on both sides of a piston that presses an engagement element, and the hydraulic pressure remaining in the piston chamber is canceled by centrifugal hydraulic pressure generated in the cancel chamber. A clutch device that prevents dragging is known. Here, the centrifugal hydraulic pressure refers to a hydraulic pressure generated in the hydraulic pressure chamber by the remaining oil when the hydraulic pressure chamber is in a rotating state.

  However, when the hydraulic pressure is not sufficiently supplied to the piston chamber under the conditions immediately after the engine is started, the centrifugal hydraulic pressure in the cancellation chamber may exceed the centrifugal hydraulic pressure in the piston chamber. For this reason, when supplying hydraulic pressure to a piston chamber and moving a piston toward a cancellation chamber, the operation | movement delay generate | occur | produced and there existed a problem that the responsiveness of a clutch apparatus fell.

  On the other hand, in order to improve the operation responsiveness, when the hydraulic pressure PC1 for advancing the piston to the cancellation chamber side is not supplied to the piston chamber, the hydraulic pressure PL2 for canceling the centrifugal hydraulic pressure is supplied to the piston chamber. There has been a conventional technique related to a clutch device to be introduced (for example, see Patent Document 1).

According to this, since the hydraulic pressure PL2 is supplied to the piston chamber in advance, for example, when the hydraulic pressure PC1 for advancing the piston to the cancellation chamber side is output immediately after starting the vehicle, the piston is responsive. You can move forward.
On the other hand, when the hydraulic pressure PC1 is supplied to the piston chamber, the hydraulic pressure PL2 is not introduced into the piston chamber. Thereby, the centrifugal hydraulic pressure generated in the piston chamber can be canceled by the operating hydraulic pressure PL2 supplied to the cancel chamber.

JP 2009-58000 A

As described above, in the clutch device disclosed in Patent Document 1, the piston can be operated with good responsiveness, and the centrifugal hydraulic pressure generated in the piston chamber can be cancelled. It plays.
However, in the clutch device disclosed in Patent Document 1, hydraulic fluid is supplied to the cancellation chamber in a state where hydraulic pressure is supplied to the piston chamber to advance the piston and press the engagement element. In order to press the engagement element with a predetermined load, it is necessary to increase the supply of the hydraulic pressure to the piston chamber by the amount of the centrifugal oil pressure due to the hydraulic oil in the cancel chamber. Therefore, the hydraulic pressure source for supplying the hydraulic pressure must be a large apparatus, the entire apparatus becomes large, and an increase in cost is inevitable.

Further, the clutch device according to Patent Document 1 requires a plurality of regulator valves for forming a predetermined hydraulic pressure in order to supply the operating oil pressure PC1 and the operating oil pressure PL2 to the piston chamber and the cancel chamber, respectively, and has a complicated configuration. In addition, the cost is inevitably increased.
Further, since the hydraulic pressure is simultaneously supplied to both the piston chamber and the cancel chamber in the state where the engaging element is being pressed, a large amount of hydraulic oil needs to be stored in the reservoir. When the reservoir is formed in the housing of the electric motor or the like, increasing the amount of hydraulic oil in the reservoir leads to an increase in the rotational resistance of the rotor, which is not easy.
The present invention has been made in view of the above circumstances, and an object thereof is to provide a clutch device that is simple in structure and excellent in responsiveness.

In order to solve the above-described problem, the structural feature of the invention of the clutch device according to claim 1 is an input member that is rotatably attached to the housing and rotated by an external drive source, and is attached to the housing. An output member that can rotate relative to the input member, a friction member that can move in the direction of the rotation axis of the input member, and that can rotate with the input member, and a friction member that can move in the direction of the rotation axis relative to the output member. A pressing member that presses the output member toward the output member, an elastic member that is attached to the output member and biases the pressing member in the rotation axis direction, and a pressure chamber that is partitioned between the pressing member and the output member , comprising a, in a state where the hydraulic pressure in the pressure chamber is discharged, the friction member is pressed by the pressing member that receives the urging force of the elastic member, by being crimped to the output member, the input unit A driving force is transmitted between the pressure member and the output member, and the hydraulic pressure is supplied from the hydraulic pressure source to the pressure chamber, so that the elastic member is deflected to release the urging force to the friction member by the pressing member; By interrupting the transmission of the driving force with the output member or by supplying the hydraulic pressure from the hydraulic pressure source to the pressure chamber, the pressing member is biased against the biasing force of the elastic member, and the biasing force In the state where the friction member is pressed by the received pressing member and is pressed against the output member , the driving force is transmitted between the input member and the output member, and the hydraulic pressure in the pressure chamber is discharged. The pressing member is urged away from the friction member by the elastic member, the transmission of the driving force between the input member and the output member is interrupted, and the rotating shaft is rotated with respect to the position where the pressure chamber is formed in the pressing member. on the opposite side in the direction A location, a release chamber which is defined and formed between the output member, is provided between the hydraulic pressure source and the pressure chamber and release chamber, if the hydraulic pressure is supplied to the pressure chamber from the hydraulic pressure source, the pressure chamber When the hydraulic pressure in the pressure chamber is discharged and the communication between the pressure chamber and the release chamber is discharged, the pressure valve and the release chamber are in communication with each other, and an operation valve that allows the supply of hydraulic fluid from the pressure chamber to the release chamber is provided. It is to prepare.

  According to a second aspect of the present invention, in the clutch device according to the first aspect, the throttle pipe for discharging the restricted hydraulic fluid from the release chamber is formed in the outer peripheral portion of the pressing member. That is.

  According to a third aspect of the present invention, in the clutch device according to the second aspect, the hydraulic fluid discharged from the release chamber via the throttle pipe is supplied to the friction member.

  According to a fourth aspect of the present invention, in the clutch device according to any one of the first to third aspects, the operating valve communicates a cylinder portion formed in the housing, the cylinder portion, and the pressure chamber. A discharge passage that communicates between the cylinder portion and the release chamber, and a valve member that is fluid-tightly fitted into the cylinder portion. The valve member opens at one end in the axial direction and passes through the inside of the cylinder portion. There is a hydraulic pressure supply path communicating with the inner peripheral surface, and a valve member to which the hydraulic pressure discharged from the hydraulic pressure source is supplied to the end on the side where the hydraulic pressure supply path is opened, and the hydraulic pressure supply to the valve member Biasing means for biasing toward the opening portion of the passage, and when the hydraulic pressure is supplied from the hydraulic pressure source to the pressure chamber, the valve member is biased by the hydraulic pressure from the hydraulic pressure source. When the cylinder moves in the axial direction against the force and the connection between the release chamber and the hydraulic pressure supply path is broken The pressure chamber is held at a position where the hydraulic pressure supply path is connected, and the hydraulic pressure discharged from the hydraulic pressure source is supplied to the pressure chamber via the hydraulic pressure supply path, and the hydraulic pressure in the pressure chamber is discharged. In this state, the valve member is urged by the urging means, and the hydraulic pressure supply path is moved to a position connected to both the discharge passage and the discharge passage on the outer peripheral surface of the valve member. Are communicated with each other via a hydraulic pressure supply path.

  According to a fifth aspect of the present invention, in the clutch device according to any one of the first to third aspects, the operating valve communicates the cylinder portion formed in the housing, the cylinder portion and the pressure chamber. A discharge passage that communicates between the cylinder portion and the release chamber, and a valve member that is fluid-tightly fitted into the cylinder portion. The valve member opens at one end in the axial direction and passes through the inside of the cylinder portion. A hydraulic pressure supply passage communicating with the inner peripheral surface, and a valve member to which the hydraulic pressure discharged from the hydraulic pressure source is supplied at an end on the side where the hydraulic pressure supply passage is opened; and the valve member in the cylinder portion An electric actuator that moves in the axial direction, and when the hydraulic pressure is supplied from the hydraulic pressure source to the pressure chamber, the electric actuator disconnects the release chamber from the hydraulic pressure supply path and Valve at the position where the hydraulic pressure supply path is connected In a state where the material is held and the hydraulic pressure discharged from the hydraulic pressure source is supplied to the pressure chamber via the hydraulic pressure supply passage and the hydraulic pressure in the pressure chamber is discharged, the hydraulic pressure supply passage is valved by the electric actuator. By moving the valve member to a position connected to both the discharge passage and the discharge passage on the outer peripheral surface of the member, the pressure chamber and the release chamber communicate with each other through the hydraulic pressure supply passage.

  According to a sixth aspect of the present invention, in the clutch device according to any one of the first to fifth aspects, a rotating electrical machine is attached in the housing, and the rotating electrical machine is a stator attached to the housing; And a rotor that is provided to face the stator in the radial direction and that can rotate with respect to the stator by generating a magnetic repulsive force or attractive force with the stator. The driving force is input, and the output member is connected to the rotor.

According to the clutch device according to claim 1, when the hydraulic pressure in the pressure chamber is discharged between the hydraulic pressure source and the pressure chamber and the release chamber, the pressure chamber and the release chamber are communicated with each other. By providing the operation valve that allows the supply of hydraulic fluid to the release chamber, the hydraulic pressure in the pressure chamber can be discharged and guided to the release chamber at the same time.
Accordingly, even if hydraulic fluid remains in the pressure chamber, the pressing member can be urged toward the pressure chamber by the centrifugal hydraulic pressure generated in the release chamber, and the clutch device is connected or disconnected. The operating responsiveness of the can be improved. Therefore, the operation time of the clutch device can be shortened.
Further, since only the hydraulic pressure in the pressure chamber is guided to the release chamber, it is not necessary to increase the size of the hydraulic pressure source, and it is not necessary to store a large amount of oil. Therefore, the entire apparatus can be reduced in size, and an increase in cost can be suppressed.

  According to the clutch device of the second aspect, the throttle pipe for discharging the restricted hydraulic fluid from the release chamber is formed on the outer peripheral portion of the pressing member, so that the hydraulic pressure source to the pressure chamber is formed. After the release of the hydraulic pressure, the centrifugal hydraulic pressure can be generated in the release chamber for a predetermined time, and thereafter, the hydraulic pressure in the release chamber can be reliably eliminated.

  According to the clutch device of the third aspect, the hydraulic fluid discharged from the release chamber through the throttle pipe is supplied to the friction member, so that the hydraulic fluid is used as cooling oil and lubricating oil for the friction member. Since it functions, wear and seizure of the friction member can be prevented.

According to the clutch device of the fourth aspect, in a state where the hydraulic pressure in the pressure chamber is discharged, the valve member is urged by the urging means, and the hydraulic pressure supply path is connected to the discharge passage and the discharge on the outer peripheral surface of the valve member. By moving to a position connected to both of the passages, the pressure chamber and the release chamber communicate with each other via the hydraulic pressure supply path.
As a result, the hydraulic pressure in the pressure chamber is discharged, and at the same time, it can be guided to the release chamber, and the centrifugal hydraulic pressure can be reliably generated in the release chamber. Further, since the operation valve is operated by the hydraulic pressure discharged from the hydraulic pressure source, a special driving force is not required and the configuration can be simplified.

  According to the clutch device of the fifth aspect, since the valve member of the operation valve is operated by the electric actuator, it can be reliably moved in the cylinder portion. Accordingly, the hydraulic pressure in the pressure chamber is discharged to the reservoir and at the same time can be reliably guided to the release chamber. When the hydraulic pressure is supplied from the hydraulic pressure source to the pressure chamber, the connection between the release chamber and the hydraulic pressure supply path And the hydraulic pressure discharged from the hydraulic pressure source can be reliably supplied to the pressure chamber.

  According to the clutch device of the sixth aspect, the driving force of the engine is input to the input member, and the output member is connected to the rotor of the rotating electrical machine, so that the connection operation or connection between the engine and the rotor is released. The responsiveness of operation can be improved.

Drive system diagram of vehicle using clutch device according to embodiment 1 of the present invention Sectional view of the front module shown in FIG. The principal part expanded sectional view of the clutch apparatus shown in FIG. FIG. 3 is an enlarged view showing a state in which hydraulic pressure is supplied to the spool valve shown in FIG. Enlarged view of spool valve according to embodiment 2 The enlarged view which showed the state which interrupted | blocked communication with a pressure chamber and a cancellation chamber in the spool valve shown in FIG.

<Embodiment 1>
A clutch device 3 according to Embodiment 1 of the present invention will be described with reference to FIGS. 1 to 4. The clutch device 3 according to the present embodiment is disposed between an electric motor 1 that is a synchronous motor for driving wheels of a hybrid vehicle and an engine 2. The electric motor 1 should not be limited to this, and can be applied to any electric motor such as a motor provided in a household electric appliance or a motor for driving a general industrial machine.
In the description, the direction of the rotation axis or the axial direction means the direction along the rotation axis C of the electric motor 1 and the clutch device 3, that is, the left-right direction in FIG. In FIG. 2, the left side may be referred to as the front of the electric motor 1 and the clutch device 3, and the right side may be referred to as the rear.

FIG. 1 shows an outline of a power train of a hybrid vehicle using an electric motor 1 (corresponding to a rotating electric machine). In FIG. 1, a thick line shows the mechanical connection of a vehicle, and a thin line shows the hydraulic piping which connects between apparatuses. A one-dot chain line indicates a power supply line, and an arrow by a broken line indicates a control signal line.
In FIG. 1, the switching valve 16, the hydraulic pump 17 and the reservoir unit 18 are described separately from the electric motor 1, but actually, the switching valve 16 and the hydraulic pump 17 together with the clutch device 3 are included in the electric motor 1. The reservoir portion 18 is formed in the motor housing 11. Thus, the front module MD is formed by the electric motor 1, the clutch device 3, the switching valve 16 and the hydraulic pump 17.

  As shown in FIG. 1, a vehicle engine 2 (corresponding to a drive source) and a rotor 13 (described later) of the electric motor 1 are connected in series via a clutch device 3 that is a wet multi-plate clutch. Yes. In addition, a vehicle transmission 4 is connected in series to the electric motor 1 for driving the hybrid vehicle, and a right drive wheel 6R and a left drive wheel 6L of the vehicle are connected to the transmission 4 via a differential device 5. Has been. Hereinafter, the right driving wheel 6R and the left driving wheel 6L are collectively referred to as driving wheels 6R and 6L.

  The engine 2 is a normal internal combustion engine that generates an output from a hydrocarbon fuel. Although the electric motor 1 is not limited to this, it is a synchronous motor for driving wheels, and the transmission 4 is a normal automatic transmission. The clutch device 3 is a normally closed type clutch device that normally connects the engine 2 and the electric motor 1, and interrupts torque transmission between the engine 2 and the electric motor 1. .

  The switching valve 16 is provided between a pressure chamber PC and a hydraulic pump 17 of the clutch device 3 described later. As shown in FIG. 1, the switching valve 16 is a two-position electromagnetic valve having three ports, and one of the ports is connected to the pressure chamber PC of the clutch device 3 by an oil passage 111a described later. The other port is connected to a discharge port of a hydraulic pump 17 (corresponding to a hydraulic pressure source), and the remaining one port is connected to a reservoir unit 18 in the electric motor 1. The suction port of the hydraulic pump 17 is always connected to the reservoir unit 18.

  When the switching valve 16 is in the operating position P1 shown in FIG. 1, the discharge port of the hydraulic pump 17 is connected to the pressure chamber PC, and the reservoir unit 18 is connected to the discharge port and the pressure chamber of the hydraulic pump 17 via the orifice. Connected to PC. At this time, the hydraulic pump 17 sucks the oil in the reservoir 18 and discharges it to the pressure chamber PC via the switching valve 16 to release the clutch device 3 from the connected state. In this state, the communication between the pressure chamber PC and the reservoir portion 18 and the supply of oil from the hydraulic pump 17 to the reservoir portion 18 are limited by the orifice, so that sufficient hydraulic pressure is generated in the pressure chamber PC. To do.

  When the switching valve 16 is in the non-operation position P 2, the discharge port of the hydraulic pump 17 and the pressure chamber PC are connected to the reservoir unit 18, and the oil (hydraulic pressure) in the pressure chamber PC returns to the reservoir unit 18. Thus, the clutch device 3 is connected. When the switching valve 16 is in the non-operation position P2, the hydraulic pump 17 is stopped.

  A stator 14 (described later) of the electric motor 1 is connected to a vehicle battery 72 via an inverter 71. The electric power of the vehicle battery 72 is converted into a three-phase alternating current by the inverter 71 and then supplied to the stator 14 to drive the rotor 13 of the electric motor 1. The electric power generated by the electric motor 1 is charged into the vehicle battery 72 via the inverter 71.

The engine ECU 81 is connected to the engine 2 and a hybrid ECU 82 described later, and controls the rotational speed of the engine 2 based on an engine output signal from the hybrid ECU 82.
The hybrid ECU 82 is electrically connected to the switching valve 16 and the hydraulic pump 17 described above, and controls their operations.

  In addition, an inverter 71 is connected to the hybrid ECU 82, and a drive signal is transmitted to the inverter 71 based on detection signals from an accelerator opening sensor (not shown), a shift position switch of the transmission 4, a vehicle speed sensor, etc. The drive torque of the motor 1 is controlled. Further, as described above, the hybrid ECU 82 transmits an engine output signal to the engine ECU 81 to control the rotational speed of the engine 2. Further, a vehicle battery 72 is electrically connected to the hybrid ECU 82, and the electric motor 1 is appropriately operated as a generator based on the state of charge of the vehicle battery 72.

The vehicle using the power train shown in FIG. 1 releases the connection of the clutch device 3 when starting, and rotates the drive wheels 6R, 6L mainly through the transmission 4 by the electric motor 1.
Further, when it is necessary to accelerate while the vehicle is traveling, the clutch device 3 is connected and the vehicle is driven by the driving force of the engine 2 in addition to the electric motor 1.
When the brake operation of the vehicle is performed, regenerative braking is performed after the clutch device 3 is disconnected. Furthermore, the electric motor 1 is driven by the engine 2 via the clutch device 3 and also functions as a generator.

As shown in FIG. 2, the motor housing 11 is integrally formed of an aluminum alloy or the like, and includes a motor cover 12 (including the motor housing 11 and the motor cover 12 in the front) with the rotor 13 and the stator 14 built-in. , Corresponding to the housing). The engine 2 is attached in front of the motor cover 12, and the transmission 4 is disposed behind the motor housing 11.
Further, a clutch device 3 that is a wet multi-plate clutch is interposed between the rotor 13 constituting the electric motor 1 and the engine 2. The clutch device 3 rotates around a rotation axis C that is also a rotation axis of the engine 2, the electric motor 1, and the transmission 4.

  An input shaft 31 (corresponding to the input member of the present invention) is connected to the flywheel of the engine 2 via a damper (both the flywheel and the damper are not shown). A clutch inner 311 forming the clutch device 3 is integrally formed on the outer peripheral surface of the input shaft 31 so that the driving force of the engine 2 can be input to the clutch inner 311. The input shaft 31 is rotatably supported on the motor cover 12 via a bearing 121.

  A plurality of spline grooves 311 a are formed on the outer peripheral surface of the clutch inner 311. A plurality of drive disks 32 (corresponding to the friction member of the present invention) are supported in the spline groove 311a in a state where they are stacked in the direction of the rotation axis. Each drive disk 32 is formed in a substantially ring shape, and a plurality of protrusions 32a are provided on the inner periphery thereof, and these protrusions 32a are engaged with the spline grooves 311a. doing. Accordingly, each drive disk 32 is configured to be movable in the direction of the rotation axis C with respect to the clutch inner 311 and to be rotatable together with the clutch inner 311. A friction material (not shown) is formed on the front and back surfaces of the drive disk 32.

On the other hand, a stator 14 of the electric motor 1 is attached to the inner peripheral portion of the motor housing 11 with a screw 144. Coils 142 for generating a rotating magnetic field are wound around the plurality of cores 141 of the stator 14. The coil 142 is connected to the inverter 71 via the bus ring 143.
Further, the rotor 13 of the electric motor 1 is disposed inward in the radial direction of the stator 14. The rotor 13 is provided to face the stator 14 while maintaining a predetermined gap. The rotor 13 is formed by caulking the end portion through the fixing member 133 in a state where the plurality of laminated steel plates 131 are sandwiched between the pair of holding plates 132a and 132b. A plurality of field pole magnets 134 are provided on the circumference of the rotor 13.

  In the electric motor 1 having the above-described configuration, for example, a three-phase alternating current is supplied to the coil 142 from the vehicle battery 72 via the inverter 71. Thereby, a rotating magnetic field is generated in the stator 14, and the rotor 13 is rotated with respect to the stator 14 by an attractive force or a repulsive force caused by the rotating magnetic field.

  One end portion of the clutch outer 33 in the axial direction is attached to the inner end of the holding plate 132a on one side of the rotor 13 by a holding bolt 135. The clutch outer 33 is formed to be rotatable relative to the clutch inner 311 around the rotation axis C. A cylindrical portion 331 is formed in the clutch outer 33, and a pressure receiving plate 332 is fixed to an end portion in the axial direction of the cylindrical portion 331. The pressure receiving plate 332 is opposed to the above-described drive disk 32 that is at the extreme end position in the axial direction.

  In addition, a plurality of driven plates 34 formed in a substantially ring shape are disposed on the inner peripheral surface side of the cylindrical portion 331. A plurality of spline grooves 331 a are formed on the circumference on the inner peripheral surface of the cylindrical portion 331. On the other hand, a plurality of protrusions 34a are provided on the outer peripheral portion of the driven plate 34, and each protrusion 34a is engaged with the spline groove 331a. As a result, the driven plate 34 can be moved in the direction of the rotation axis C with respect to the clutch outer 33 and can be rotated together with the clutch outer 33. Each driven plate 34 is alternately interposed between the plurality of drive disks 32 described above.

  The clutch outer 33 extends radially inward, and is spline-fitted with a turbine shaft 41 of a torque converter (not shown) included in the transmission 4 at the inner end. A connecting member 42 connected to a pump impeller is attached to an end of the turbine shaft 41 in the axial direction so as to be integrally rotatable. As a result, the driving force of the clutch outer 33 can be input to the torque converter of the transmission 4. An inner end portion of the clutch outer 33 is rotatably supported on the fixed wall 111 of the motor housing 11 via a bearing 38.

Further, the movable body 151 of the rotational position sensor 15 is formed in the clutch outer 33, and the rotor 13 to which the clutch outer 33 is attached is detected by a detection body 152 provided on the fixed wall 111 so as to face the movable body 151. The rotational position of is detected.
The clutch outer 33 is formed with an accommodating portion 333 bent in a U-shape. In the accommodating part 333, the plunger member 35 (corresponding to the pressing member of the present invention) is accommodated so as to be movable in the rotation axis direction. The plunger member 35 is formed in a substantially annular shape, and is fitted in a liquid-tight manner to the accommodating portion 333 at the inner peripheral end.

  Further, a contact portion 351 extending in the axial direction is formed at the outer peripheral end of the plunger member 35, and the fixing member 36 is liquid-tightly fitted to the inner peripheral surface of the contact portion 351 and the housing portion 333. ing. The fixing member 36 is formed so as not to move to the left in FIG. Thus, the pressure chamber PC is defined by the accommodating portion 333, the plunger member 35, and the fixing member 36. The fixing member 36 is provided with a check valve 361 that reduces the centrifugal hydraulic pressure generated in the pressure chamber PC. The check valve 361 is formed by a valve seat body 361a having a through hole that communicates the pressure chamber PC with the outside, and a ball 361b that can be engaged with the valve seat body 361a.

In addition, the accommodating portion 333 and the plunger member 35 define a cancellation chamber KC (corresponding to the release chamber of the present invention) in which oil can be accommodated. The cancellation chamber KC is formed on the opposite side of the pressure chamber PC in the rotation axis C direction with respect to the plunger member 35. A piston spring 37 is accommodated in the cancel chamber KC.
In addition, a bleed orifice 352 (corresponding to the throttle line of the present invention) extending in the direction of the rotation axis C is formed on the outer peripheral portion of the plunger member 35 to communicate the cancel chamber KC and the reservoir portion 18. . The bleed orifice 352 discharges restricted oil from the cancel chamber KC. A configuration including the clutch outer 33, the driven plate 34, and the fixing member 36 corresponds to the output member of the present invention.

  As shown in FIG. 2, a piston spring 37 (corresponding to the elastic member of the present invention) is interposed between the accommodating portion 333 and the plunger member 35. The piston spring 37 abuts on the side of the plunger member 35 where the pressure chamber PC is formed and the opposite side of the rotation axis direction, and urges the plunger member 35 toward the fixed member 36 (leftward in FIG. 2). Yes. The contact portion 351 of the plunger member 35 biased by the piston spring 37 presses the drive disk 32 and the driven plate 34 toward the pressure receiving plate 332.

  An oil passage 111a extending inward in the radial direction is formed in the fixed wall 111. The oil passage 111a extends obliquely in the middle, and is connected to a cylinder portion 111b extending in the axial direction to form the spool valve 39 at the tip. A stopper member 112a is fitted to the end of the oil passage 111a to seal the oil passage 111a with respect to the outside. The configuration of the spool valve 39 will be described later.

  A discharge hole 111c extending radially outward is connected to the cylinder portion 111b, and a first outer peripheral slit 111d is formed on the entire periphery of the fixed wall 111 so as to communicate with the discharge hole 111c. . In addition, a discharge hole 111e extending radially outward is connected to the cylinder portion 111b in the same manner as the discharge hole 111c, and a second outer peripheral slit 111f is connected to the fixed wall 111 so as to communicate with the discharge hole 111e. It is formed all around. The discharge hole 111e and the second outer peripheral slit 111f are formed on the rear side in the axial direction of the cylinder portion 111b (rightward in FIG. 2) with respect to the discharge hole 111c and the first outer peripheral slit 111d.

  Further, the clutch outer 33 is formed with a first through hole 334 so as to communicate the first outer peripheral slit 111d with the pressure chamber PC described above. Thereby, the hydraulic pressure supplied from the hydraulic pump 17 to the oil passage 111a is introduced into the pressure chamber PC via the spool valve 39, the discharge hole 111c, the first outer peripheral slit 111d, and the first through hole 334. In addition, what included the discharge hole 111c, the 1st outer periphery slit 111d, and the 1st through-hole 334 corresponds to the discharge passage of this invention.

Further, the clutch outer 33 is formed with a second through hole 335 so as to communicate the second outer peripheral slit 111f and the cancel chamber KC described above. Accordingly, the cancel chamber KC is connected to the oil passage 111a via the second through hole 335, the second outer peripheral slit 111f, the discharge hole 111e, and the spool valve 39. In addition, what included the discharge hole 111e, the 2nd outer periphery slit 111f, and the 2nd through-hole 335 corresponds to the discharge passage of this invention.
As shown in FIG. 2, an oil supply hole 111g passes through the upper end portion of the motor housing 11, and oil is injected into the reservoir portion 18 from the oil supply hole 111g. A sealing plug 113 is screwed into the oil supply hole 111g to block the inside of the motor housing 11 from the outside.

  The aforementioned spool valve 39 (corresponding to the operation valve of the present invention) is formed between the switching valve 16, the pressure chamber PC, and the cancel chamber KC. As shown in FIG. 3, the cylinder portion 111b forming the spool valve 39 is formed in a bag shape with one end closed. The cylinder portion 111b is formed by a small bore 111b1 at the tip and a large bore 111b2 on the inlet side, and a stepped portion 111b3 is formed at a connecting portion between the small bore 111b1 and the large bore 111b2. The aforementioned oil passage 111a communicates with the large bore 111b2. A stopper member 112b is fitted to the open end of the cylinder portion 111b, and seals the cylinder portion 111b from the outside.

  A valve body 391 (corresponding to the valve member of the present invention) is accommodated in the cylinder portion 111b so as to be movable in the axial direction. The valve body 391 has a stepped shape. The outer peripheral surface of the small diameter portion 391a is liquid-tightly fitted to the small bore 111b1, and the outer peripheral surface of the large diameter portion 391b is liquid-tightly fitted to the large bore 111b2. Yes.

  An oil supply path 391c (corresponding to the hydraulic pressure supply path of the present invention) is formed inside the valve body 391. The oil supply path 391c opens at one end portion in the axial direction of the large-diameter portion 391b, and in the small-diameter portion 391a, a vertical hole that intersects the horizontal hole 391c1 in the vertical direction in the axial direction through the inside. The hole 391c2 and a circumferential groove 391c3 formed on the outer peripheral surface of the small diameter portion 391a and communicating with the vertical hole 391c2. The circumferential groove 391c3 is formed over the entire circumference of the small diameter portion 391a and extends over a predetermined distance in the axial direction of the small diameter portion 391a. The circumferential groove 391c3 opens to the inner peripheral surface of the cylinder portion 111b, and the oil supply path 391c thereby connects the large bore 111b2 and the inner peripheral surface of the small bore 111b1.

  The first urging spring 392 (corresponding to the urging means of the present invention) is interposed between the front end of the valve body 391 and the bottom of the cylinder portion 111b in a compressed state, and the valve body 391 is placed on the large bore 111b2 side. It is biased toward (the opening portion of the oil supply path 391c). On the other hand, the second urging spring 393 is interposed in a compressed state between the rear end of the valve body 391 and the stopper member 112b, and urges the valve body 391 toward the small bore 111b1. .

  When the switching valve 16 is in the non-operating position P2 and the hydraulic pump 17 is not operating, the hydraulic pressure is not supplied from the oil passage 111a to the large bore 111b2. As shown in FIG. 3, the circumferential groove 391c3 is held at a position communicating with both the discharge hole 111c and the discharge hole 111e.

Accordingly, the pressure chamber PC is connected to the reservoir section 18 via the first through hole 334, the first outer peripheral slit 111d, the discharge hole 111c, the circumferential groove 391c3, the vertical hole 391c2, the horizontal hole 391c1, the large bore 111b2, and the oil passage 111a. Is done.
The cancel chamber KC is connected to the reservoir section 18 via the second through hole 335, the second outer peripheral slit 111f, the discharge hole 111e, the circumferential groove 391c3, the vertical hole 391c2, the horizontal hole 391c1, the large bore 111b2, and the oil passage 111a. Is done.
The pressure chamber PC and the cancel chamber KC are connected via the first through hole 334, the first outer peripheral slit 111d, the discharge hole 111c, the circumferential groove 391c3, the discharge hole 111e, the second outer peripheral slit 111f, and the second through hole 335. They are in communication with each other.

  Accordingly, in this case, no hydraulic pressure is generated in the pressure chamber PC and the cancel chamber KC, and the plunger member 35 is biased toward the fixed member 36 by the piston spring 37. As a result, the plurality of drive disks 32 and the driven plate 34 are pressed against each other between the pressure receiving plate 332 and the abutting portion 351 of the plunger member 35 to enable torque transmission. Therefore, the clutch device 3 is in the connected state, the drive disk 32 and the driven plate 34 rotate together, and the driving force is transmitted from the clutch inner 311 to the clutch outer 33.

  On the other hand, in this state, when the switching valve 16 is switched to the operating position P1 and the operation of the hydraulic pump 17 is started, the hydraulic pressure is supplied from the oil passage 111a to the large bore 111b2, and thus the cross-sectional integral of the large diameter portion 391b. The valve body 391 that has received the hydraulic pressure moves forward (leftward in FIG. 3) while compressing the first biasing spring 392. Thereby, the communication between the circumferential groove 391c3 and the discharge hole 111e is cut off, and the circumferential groove 391c3 communicates only with the discharge hole 111c (shown in FIG. 4).

  Accordingly, the connection between the pressure chamber PC and the cancel chamber KC is released, and only the pressure chamber PC includes the first through hole 334, the first outer peripheral slit 111d, the discharge hole 111c, the circumferential groove 391c3, the vertical hole 391c2, It is connected to the discharge port of the hydraulic pump 17 through the hole 391c1, the large bore 111b2, and the oil passage 111a.

  Therefore, when the hydraulic pressure from the hydraulic pump 17 is supplied to the pressure chamber PC, the piston spring 37 is bent and the plunger member 35 moves to the right in FIG. The press-bonded state with the driven plate 34 is released. Therefore, the clutch device 3 is disconnected and the transmission of the driving force from the clutch inner 311 to the clutch outer 33 is interrupted. In this state, the check valve 361 is closed because the ball 361b comes into contact with the valve seat 361a by the hydraulic pressure supplied to the pressure chamber PC.

  When the switching valve 16 is switched to the non-actuated position P2 again and the hydraulic pump 17 stops operating in the disconnected state of the clutch device 3, the supply of the hydraulic pressure to the large bore 111b2 is stopped. In response to the urging force from one urging spring 392, it moves to the right in FIG. For this reason, the pressure chamber PC and the cancel chamber KC are connected to the reservoir section 18, and the pressure chamber PC and the cancel chamber KC communicate with each other.

  Accordingly, the oil in the pressure chamber PC is stored in the reservoir portion via the first through hole 334, the first outer peripheral slit 111d, the discharge hole 111c, the circumferential groove 391c3, the vertical hole 391c2, the horizontal hole 391c1, the large bore 111b2, and the oil passage 111a. 18 to the cancel chamber KC via the first through hole 334, the first outer peripheral slit 111d, the discharge hole 111c, the circumferential groove 391c3, the discharge hole 111e, the second outer peripheral slit 111f, and the second through hole 335. Oil is supplied.

  As a result, the hydraulic pressure in the pressure chamber PC decreases due to the discharge of oil from the pressure chamber PC to the reservoir portion 18, and the plunger member 35 moves to the left in FIG. 2 by the biasing force of the piston spring 37. At the same time, centrifugal oil pressure (hydraulic pressure generated by the oil in the cancel chamber KC by rotating the cancel chamber KC) is generated in the cancel chamber KC by the supplied oil. For this reason, the movement of the plunger member 35 to the left in FIG. 2 can be accelerated, and the clutch device 3 can be brought into the connected state quickly.

  Further, in this state, since the ball 361b is separated from the valve seat body 361a due to a decrease in the hydraulic pressure in the pressure chamber PC, the check valve 361 is opened and the oil in the pressure chamber PC is discharged. The oil discharged from the check valve 361 is supplied to the engaging portion between the drive disk 32 and the driven plate 34 of the clutch device 3 as lubricating oil or cooling oil, and finally recovered in the reservoir portion 18.

  The oil supplied to the cancel chamber KC is discharged through a bleed orifice 352 formed on the outer peripheral portion of the plunger member 35 by centrifugal force. The amount of oil discharged per hour from the cancellation chamber KC is limited by the bleed orifice 352. The oil discharged from the cancel chamber KC is supplied as a lubricating oil or a cooling oil to the engaging portion between the drive disk 32 and the driven plate 34 of the clutch device 3 and finally recovered in the reservoir portion 18.

  The oil discharged by the hydraulic pump 17 is not only introduced into the pressure chamber PC but also supplied to the bearing 38 and the like as lubricating oil or cooling oil. The oil in the reservoir unit 18 is pumped up by the rotor 13 and supplied to each member in the motor housing 11 as lubricating oil or cooling oil.

  According to this embodiment, the spool valve 39 is provided between the switching valve 16 and the pressure chamber PC and the cancellation chamber KC. The spool valve 39 is configured so that the switching valve 16 applies the hydraulic pressure in the pressure chamber PC to the reservoir unit 18. When the pressure chamber PC and the cancel chamber KC are in communication with each other, the hydraulic pressure in the pressure chamber PC is discharged to the reservoir portion 18 and simultaneously led to the cancel chamber KC. be able to.

Thereby, even if oil remains in the pressure chamber PC, the plunger member 35 can be urged toward the pressure chamber PC by the centrifugal hydraulic pressure generated in the cancel chamber KC. It is possible to improve the responsiveness of the connection operation. Therefore, the operation time of the clutch device 3 can be shortened.
Further, since only the hydraulic pressure in the pressure chamber PC is guided to the cancel chamber KC, it is not necessary to increase the size of the hydraulic pump 17, and it is not necessary to store a large amount of oil in the reservoir section 18. Therefore, the entire apparatus can be reduced in size, and an increase in cost can be suppressed.

Further, since the spool valve 39 is provided in the motor housing 11 and is formed in the vicinity of the pressure chamber PC and the cancel chamber KC, the oil in the pressure chamber PC can be immediately guided to the cancel chamber KC, and the operation response is further improved. The clutch device 3 having good characteristics can be obtained.
In addition, by the bleed orifice 352 formed on the outer peripheral portion of the plunger member 35, the limited oil is discharged from the cancel chamber KC to the reservoir portion 18, so that the hydraulic pressure from the hydraulic pump 17 to the pressure chamber PC is reduced. After the release, the centrifugal hydraulic pressure can be generated in the cancellation chamber KC for a predetermined time, and thereafter, the hydraulic pressure in the cancellation chamber KC can be surely eliminated.

  Further, the oil discharged from the cancel chamber KC through the bleed orifice 352 is supplied to the engagement portion between the drive disk 32 and the driven plate 34, whereby the oil is engaged between the drive disk 32 and the driven plate 34. Therefore, it is possible to prevent the drive disk 32 and the driven plate 34 from being worn and seized.

  Further, when the switching valve 16 is in the non-operation position P2, the spool valve 39 is urged by the first urging spring 392 and the oil supply passage 391c is formed in the discharge hole 111c on the outer peripheral surface of the valve 391. And the pressure chamber PC is connected to the reservoir 18 via the oil supply path 391c, and the pressure chamber PC and the cancellation chamber KC are connected to the oil supply path. They communicate with each other via 391c.

As a result, the hydraulic pressure in the pressure chamber PC can be discharged to the reservoir section 18 and simultaneously guided to the cancellation chamber KC, and the centrifugal hydraulic pressure can be reliably generated in the cancellation chamber KC. Further, since the spool valve 39 is operated by the hydraulic pressure discharged from the hydraulic pump 17, no special driving force is required and the configuration can be simplified.
Further, the driving force of the engine 2 is input to the input shaft 31, and the clutch outer 33 is connected to the rotor 13 of the electric motor 1, thereby improving the responsiveness of the connection operation between the engine 2 and the rotor 13. Can be made.

<Embodiment 2>
A spool valve 39A according to Embodiment 2 of the present invention will be described with reference to FIGS. 5 and 6, the same reference numerals are given to the same configurations as those in the first embodiment.
In the spool valve 39A according to this embodiment, the valve body 391 is moved in the axial direction by an electromagnetic actuator 394 (corresponding to the electric actuator of the present invention). Accordingly, the first biasing spring 392 and the second biasing spring 393 are not used.

  The electromagnetic actuator 394 is formed by an actuator main body 394a including a solenoid (not shown) and a rod 394b movable in the axial direction by the actuator main body 394a. The actuator main body 394a is held between the step portion 111h of the fixed wall 111 and the stopper member 112b described above. The rod 394b is selectively moved and held between the accommodation position (shown in FIG. 5) and the protruding position (shown in FIG. 6) by the operation of the actuator body 394a.

The tip of the rod 394b is fixed to the end (the right end in FIG. 5) of the valve body 391 on the side where the oil supply passage 391c is opened. The rod 394b has a connection passage 394b1 that connects the large bore 111b2 and the oil supply passage 391c.
The actuator main body 394a is electrically connected to the hybrid ECU 82 described above. When the switching valve 16 is in the non-operation position P2, the hybrid ECU 82 controls the actuator body 394a so that the rod 394b is in the storage position, and the pressure chamber PC is controlled by the circumferential groove 391c3 as in the first embodiment. And the cancel room KC are in communication (shown in FIG. 5).

Further, when the switching valve 16 is in the operating position P1, the hybrid ECU 82 controls the actuator body 394a so that the rod 394b is in the protruding position, and as in the first embodiment, the circumferential groove 391c3 and the discharge hole The communication with 111e is cut off, and the circumferential groove 391c3 is communicated only with the discharge hole 111c (shown in FIG. 6).
Since other configurations are the same as those in the first embodiment, description thereof is omitted.

  According to the present embodiment, since the valve body 391 of the spool valve 39A is operated by the electromagnetic actuator 394, it can be reliably moved within the cylinder portion 111b. Therefore, when the switching valve 16 is in the non-operating position P2, the hydraulic pressure in the pressure chamber PC can be discharged to the reservoir portion 18 and at the same time can be reliably guided to the canceling chamber KC, and the switching valve 16 can be moved to the operating position P1. In some cases, the connection between the cancel chamber KC and the oil supply path 391c can be disconnected, and the hydraulic pressure discharged from the hydraulic pump 17 can be reliably supplied to the pressure chamber PC.

<Other embodiments>
The present invention is not limited to the above-described embodiments, and can be modified or expanded as follows.
In the spool valve 39 according to the first embodiment, when the second urging spring 393 is not used and the valve body 391 is urged only by the first urging spring 392, and no hydraulic pressure is supplied to the oil passage 111a, The rear end portion of the body 391 may be brought into contact with the fixed wall 111 of the motor housing 11.

In the spool valve 39A according to the second embodiment, an actuator or the like that converts the rotational force of the electric motor into a straight movement may be used instead of the electromagnetic actuator 394 that operates the valve body 391.
The oil discharged by the hydraulic pump 17 may function only as hydraulic oil for interrupting the clutch device 3.
The clutch device 3 may be a single plate type clutch device.

  The clutch device 3 may be a normally open type clutch device. That is, the plunger member 35 is urged away from the drive disk 32 by the urging force of the piston spring 37, and the hydraulic pressure discharged from the hydraulic pump 17 to the pressure chamber PC in the state where the switching valve 16 is in the operating position P1. , The plunger member 35 is urged against the urging force of the piston spring 37, and the drive disk 32 is pressed by the plunger member 35 that has received the urging force, so that the clutch inner 311 and the clutch outer 33 In the state where the switching force 16 is in the non-operating position P2, the plunger member 35 is urged by the piston spring 37 in the direction away from the drive disk 32, and the clutch inner 311 and the clutch outer 33 are transmitted. The transmission of the driving force between them may be cut off.

The electric motor 1 according to the present invention is applicable to a synchronous motor, an induction motor, a DC motor, or any other rotating electric machine.
Moreover, the electric motor 1 according to the present invention may be used only as an electric motor or only as a generator.

  In the drawings, 1 is an electric motor (rotary electric machine), 2 is an engine (drive source), 3 is a clutch device, 11 is a motor housing (housing), 12 is a motor cover (housing), 13 is a rotor, 14 is a stator, 17 Is a hydraulic pump (hydraulic pressure source), 31 is an input shaft (input member), 32 is a drive disk (friction member), 33 is a clutch outer (output member), 34 is a driven plate (output member), 35 is a plunger member ( (Pressing member), 36 is a fixing member (output member), 37 is a piston spring (elastic member), 39 and 39A are spool valves (actuating valves), 111b is a cylinder portion, 111c is a discharge hole (discharge passage), and 111d is a first member 1 outer slit (discharge passage), 111e is a discharge hole (discharge passage), 111f is a second outer slit (discharge passage), 334 is a first through hole (discharge passage) ) 335 is a second through hole (discharge passage), 352 is a bleed orifice (throttle conduit), 391 is a valve body (valve member), 391c is an oil supply passage (hydraulic pressure supply passage), and 392 is a first attachment. A bias spring (biasing means), 394 is an electromagnetic actuator (electric actuator), KC is a cancel chamber (release chamber), and PC is a pressure chamber.

Claims (6)

An input member rotatably attached to the housing and rotated by an external drive source;
An output member attached to the housing and rotatable relative to the input member;
A friction member movable in the direction of the rotation axis of the input member and rotatable together with the input member ;
A pressing member attached to the output member so as to be movable in the direction of the rotation axis, and pressing the friction member toward the output member ;
An elastic member attached to the output member and biasing the pressing member in the direction of the rotation axis;
A pressure chamber defined between the pressing member and the output member ;
With
In a state where the hydraulic pressure in the pressure chamber is discharged, the friction member is pressed by the pressing member that has received the urging force from the elastic member, and is crimped to the output member. Driving force is transmitted between the output member,
When the hydraulic pressure is supplied from the hydraulic pressure source to the pressure chamber, the elastic member is deflected to release the urging force to the friction member by the pressing member, and driving between the input member and the output member Cut off power transmission,
Or
When the hydraulic pressure is supplied from the hydraulic pressure source to the pressure chamber, the pressing member is biased against the biasing force of the elastic member, and the friction member is pressed by the pressing member that has received the biasing force. is, by being crimped to the output member, the driving force between said output member and the input member is transmitted,
In a state where the hydraulic pressure in the pressure chamber is discharged, the elastic member biases the pressing member in a direction away from the friction member, thereby interrupting transmission of driving force between the input member and the output member. ,
further,
A release chamber defined between the output member and a position on the opposite side in the rotation axis direction to the position where the pressure chamber is formed in the pressing member;
Provided between the hydraulic pressure source and the pressure chamber and the release chamber, and when the hydraulic pressure is supplied from the hydraulic pressure source to the pressure chamber, the communication between the pressure chamber and the release chamber is cut off, When the hydraulic pressure in the pressure chamber is discharged, the operation valve that connects the pressure chamber and the release chamber and allows the supply of hydraulic fluid from the pressure chamber to the release chamber;
A clutch device comprising: In the outer periphery of the pressing member,
The clutch device according to claim 1, wherein a throttle pipe for discharging a restricted hydraulic fluid from the release chamber is formed.   The clutch device according to claim 2, wherein the hydraulic fluid discharged from the release chamber via the throttle pipe is supplied to the friction member. The actuating valve is
A cylinder portion formed in the housing;
A discharge passage communicating the cylinder part and the pressure chamber;
A discharge passage communicating the cylinder part and the release chamber;
A valve member that is fluid-tightly fitted into the cylinder portion, and has a hydraulic pressure supply passage that opens at one end portion in the axial direction and communicates with the inner peripheral surface of the cylinder portion through the inside; A valve member to which the hydraulic pressure discharged from the hydraulic pressure source is supplied to the end on the side where the pressure supply path is opened;
Biasing means for biasing the valve member toward the opening of the hydraulic pressure supply path;
With
When hydraulic pressure is supplied from the hydraulic pressure source to the pressure chamber, the valve member moves in the axial direction in the cylinder portion against the urging force of the urging means by the hydraulic pressure from the hydraulic pressure source. The release chamber and the hydraulic pressure supply path are disconnected, and the hydraulic pressure discharged from the hydraulic pressure source is held at a position where the pressure chamber and the hydraulic pressure supply path are connected. Supplied to the pressure chamber via the hydraulic pressure supply path;
In a state where the hydraulic pressure in the pressure chamber is discharged, the valve member is urged by the urging means, and the hydraulic pressure supply path is provided on both the discharge passage and the discharge passage on the outer peripheral surface of the valve member. 4. The pressure chamber and the release chamber communicate with each other through the hydraulic pressure supply path by moving to a connected position. 5. Clutch device. The actuating valve is
A cylinder portion formed in the housing;
A discharge passage communicating the cylinder part and the pressure chamber;
A discharge passage communicating the cylinder part and the release chamber;
A valve member that is fluid-tightly fitted into the cylinder portion, and has a hydraulic pressure supply passage that opens at one end portion in the axial direction and communicates with the inner peripheral surface of the cylinder portion through the inside; A valve member to which the hydraulic pressure discharged from the hydraulic pressure source is supplied to the end on the side where the pressure supply path is opened;
An electric actuator for moving the valve member in the axial direction in the cylinder portion;
With
When hydraulic pressure is supplied from the hydraulic pressure source to the pressure chamber, the electric actuator disconnects the release chamber and the hydraulic pressure supply path, and the pressure chamber and the hydraulic pressure supply path The valve member is held at a position where the hydraulic pressure is connected, and the hydraulic pressure discharged from the hydraulic pressure source is supplied to the pressure chamber via the hydraulic pressure supply path.
In a state where the hydraulic pressure in the pressure chamber is discharged, the valve member is placed at a position where the hydraulic pressure supply path is connected to both the discharge passage and the discharge passage on the outer peripheral surface of the valve member by the electric actuator. 4. The clutch device according to claim 1, wherein the pressure chamber and the release chamber communicate with each other through the hydraulic pressure supply path by being moved. 5. A rotating electric machine is mounted in the housing,
The rotating electric machine is
A stator attached to the housing;
A rotor that is provided opposite to the stator in the radial direction, and that is capable of rotating with respect to the stator by generating a magnetic repulsive force or attractive force with the stator;
Have
The clutch device according to any one of claims 1 to 5, wherein a driving force of an engine is input to the input member, and the output member is connected to the rotor.

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