JP6287065B2 - Pump device with switching valve - Google Patents

Description

  The present invention relates to a pump device with a switching valve that includes a switching valve that can switch a plurality of destinations of fluid and that discharges sucked fluid to a switched destination.

  For example, in the automobile drive device described in Patent Document 1, a hydraulic control device that controls supply of hydraulic pressure to a plurality of hydraulic cylinders from a pump via a plurality of electromagnetic valves, respectively, and performs intermittent connection of a plurality of wet multi-plate clutches. Is described.

JP 2009-269605 A

  The hydraulic control device described in Patent Document 1 described above includes a plurality of actuators that respectively drive a pump and a plurality of electromagnetic valves, so that complicated drive control is required, and the number of devices tends to increase costs. It is in.

  This invention is made | formed in view of such a situation, and it aims at providing the pump apparatus with a switching valve which can respectively perform the rotational drive of a pump and a switching valve with one actuator.

(Claim 1) The pump device with a switching valve according to the present invention has one actuator that is rotationally driven, a pump that discharges the sucked fluid by the rotational drive of the actuator, and a phase that is changed by the rotational drive of the actuator. Can switch between a switching valve capable of switching a plurality of destinations of the fluid discharged from the pump chamber of the pump, and a state where the rotational driving force of the actuator is transmitted to the switching valve and a state where the switching valve is blocked. A driving force interrupting device for a valve, and a housing for housing the pump and the switching valve, wherein the rotating shaft of the actuator, the rotating shaft of the pump, and the rotating shaft of the switching valve are provided coaxially, The end face of the switching valve forms a side wall of the pump chamber of the pump, and the front end of the switching valve and the housing At least one of the surfaces facing the switching valve is provided with a circumferential groove for allowing the fluid discharged from the pump chamber to flow in, and the housing has a communication hole for communicating the pressure detection mechanism and the circumferential groove. Is provided .

As a result, the rotation drive of the pump and the rotation drive of the switching valve can be switched by the valve driving force interrupting device with one actuator, so that simple drive control of one actuator is achieved, and the high speed of the pump device with the switching valve is high. Operation is possible. In addition, since the number of devices can be reduced, significant cost reduction can be achieved. And the pump apparatus with a switching valve can be reduced in size, and the pressure for every several destinations of the fluid can be detected with one pressure detection mechanism.

(2) The valve driving force interrupting device may transmit the rotational driving force in one rotational direction of the actuator to the switching valve and block the rotational driving force in the other rotational direction with respect to the switching valve. . As a result, the switching valve can be reliably rotated and stopped.

(Claim 3) The actuator rotationally drives the pump with a rotational driving force in the other rotational direction of the actuator, and the valve driving force interrupting device generates a rotational driving force in one rotational direction of the actuator. It may be transmitted to the switching valve. As a result, the pump and the switching valve can be reliably switched and driven to rotate.

(4) The one-way clutch that transmits the rotational driving force in one rotational direction of the actuator to the switching valve and interrupts the rotational driving force in the other rotational direction. The pump device with a switching valve is a one-way clutch, transmits the rotational driving force in the other rotational direction of the actuator to the pump, and blocks the rotational driving force in the one rotational direction. A driving force interrupting device may be provided. Thereby, the rotational drive of the pump and the rotational drive of the switching valve are not operated simultaneously, and the fluid can be reliably supplied to the predetermined destination.

(5) The housing houses the switching valve in a rotatable manner , and the switching valve has a braking device capable of switching between a state in which the housing is rotationally restrained and a state in which the housing is released. When rotating in one rotational direction, the braking device may release the switching valve, and when the actuator rotationally drives in the other rotational direction, the braking device may restrain the switching valve. Thereby, the rotational phase detection and positioning of the switching valve can be performed reliably, and the switching valve can be switched reliably.

(Claim 6 ) The pump device with a switching valve includes a side plate that forms a side wall opposite to the switching valve in the pump chamber, and the pump includes an outer rotor and an inner rotor, and the outer rotor is A cam ring that is supported eccentrically with respect to the inner rotor is provided, and the switching valve, the side plate, and the cam ring may rotate integrally. As a result, the pump and the switching valve can be integrated in the direction of the rotation axis, and the pump device with the switching valve can be further downsized.

( 7 ) The side plate is accommodated in the housing, and the pump chamber is provided between the side plate on the side opposite to the pumping chamber in the rotation axis direction and the housing facing the end surface in the rotation axis direction. It is preferable that a back pressure chamber is provided to allow the fluid discharged from the fluid to flow in and to apply a pressing force toward the pump side to the side plate with the pressure of the fluid. Since the fluid becomes high pressure when the pump is operating, there is a risk of fluid leaking if there is a gap between the pump and the side plate or between the pump and the housing. Thus, the fluid can be prevented from leaking from the gap.

( 8 ) The pump device with a switching valve may include a thrust bearing disposed so as to sandwich the pump, the switching valve, and the side plate in the rotation axis direction with respect to the housing. When the switching valve is driven to rotate, there is no pump action, so it is difficult to rotate the side plate, the pump, and the switching valve integrally. However, since the thrust bearing is provided, the side plate, the pump, the switching valve, Can be rotated smoothly without play.

(Claim 9 ) The switching valve may be capable of switching a plurality of return destinations connected to the suction side of the pump chamber of the pump by changing the phase. Thereby, the fluid can be returned smoothly and reused.
(Claim 10 ) The pump device with a switching valve may include a control device that controls the rotational drive of the actuator based on the pressure of the fluid detected by the pressure detection mechanism. Thus, the actuator can be accurately driven and controlled so that the fluid pressure is appropriate.

(Claim 11 ) The pump device with a switching valve may include a phase detection mechanism capable of detecting and positioning the phase. Thereby, the several destination of the fluid discharged from the pump chamber can be switched reliably.
(Claim 12 ) The pump device with a switching valve may include a control device that controls the rotational drive of the actuator based on the phase of the switching valve detected by the phase detection mechanism. Thereby, the actuator can be accurately driven and controlled so that the destination of the fluid is accurate.

(Claim 13 ) The phase detection mechanism is fixed to a housing that rotatably accommodates the switching valve, and is provided so as to vary a protruding amount radially inward from an inner peripheral surface of the housing. And a recess formed on the outer peripheral surface of the switching valve and locked in the circumferential direction with respect to the sensor. Since a high pressure is applied to the switching valve during the operation of the pump, the switching valve may run idle only with the valve driving force interrupting device. However, since the recess for locking the sensor in the circumferential direction is provided, it is possible to prevent the switching valve from idling.

It is a figure which shows schematic structure of the drive system of the vehicle by which the pump apparatus with a switching valve which concerns on embodiment is mounted. It is a figure which shows schematic structure of the drive system of another vehicle by which the pump apparatus with a switching valve which concerns on embodiment is mounted. It is sectional drawing which shows schematic structure of an auxiliary transmission. It is sectional drawing which shows the detailed structure of the center LSD of a driving force transmission apparatus. It is a figure which shows schematic structure of the drive force transmission apparatus comprised by the center LSD, the pump apparatus with a switching valve which operates the clutch apparatus of the center LSD, and an auxiliary transmission. It is a figure which shows the axial direction cross section of the pump apparatus with a switching valve. It is a figure which shows the rotary pump and 1st pump housing of the pump apparatus with a switching valve seen from the arrow A direction of FIG. It is a figure which shows the rotary valve of the pump apparatus with a switching valve, the transmission, and the 2nd pump housing seen from the arrow B direction of FIG. It is a figure which shows only the rotary valve of FIG. It is a figure which shows only the 2nd pump housing of FIG. It is a figure which shows only the transmission of FIG. It is a figure which shows the state of the flow path at the time of the normal mode of the pump apparatus with a switching valve. It is a figure which shows the state of a flow control valve when hydraulic fluid is supplied by the normal mode of a pump apparatus with a switching valve. It is a figure which shows the state of a flow control valve when hydraulic fluid is discharged | emitted by the normal mode of a pump apparatus with a switching valve. It is a figure which shows the state of the flow path at the time of lock mode of the pump apparatus with a switching valve. It is a figure which shows the state of a non-return valve, an accumulator, and a cylinder apparatus when hydraulic fluid is supplied by the lock mode of a pump apparatus with a switching valve. It is a figure which shows the state of a non-return valve, an accumulator, and a cylinder apparatus when supply of hydraulic fluid is stopped by the lock mode of the pump apparatus with a switching valve. It is a figure which shows the state of a flow path and a cylinder apparatus at the time of sub transmission switching mode (Lo) of a pump apparatus with a switching valve. It is a figure which shows the state of a flow path and a cylinder apparatus at the time of sub transmission switching mode (Hi) of a pump apparatus with a switching valve.

(Vehicle overview)
DESCRIPTION OF EMBODIMENTS Hereinafter, an embodiment in which a pump device with a switching valve of the present invention is embodied will be described with reference to the drawings. First, a schematic configuration of a drive system of the vehicles 1 and 8 on which the pump device 100 with a switching valve of the present embodiment is mounted will be described with reference to FIGS. 1A and 1B. In FIG. 1B, the same components as those in FIG. 1A are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 1A, the vehicle 1 is a four-wheel drive vehicle, and includes an engine 2, a transmission 3, an auxiliary transmission 4, a propeller shaft 5F on the front wheels Wfl and Wfr side, and a rear wheel Wrl and Wrr side. Propeller shaft 5R, left front wheel Wfl side drive shaft 6FL, right front wheel Wfr side drive shaft 6FR, left rear wheel Wrl side drive shaft 6RL, right rear wheel Wrr side drive shaft 6RR, front LSD ( (Limited slip differential) 7F, center LSD 7C, rear LSD 7R, and three switching valve-equipped pump devices 100.

Each LSD 7F, 7C, 7R is provided with a hydraulic clutch device 7 (see FIG. 4) having a multi-plate clutch 72 for transmitting driving force and a hydraulic cylinder device 73.
The front LSD 7F distributes the driving force of the engine 2 to the drive shaft 6FL on the left front wheel Wfl side and the drive shaft 6FR on the right front wheel Wfr side, and according to the engagement force of the clutch device 7, the drive shaft on the left front wheel Wfl side This is a differential device with a differential limit that limits the differential between 6FL and the drive shaft 6FR on the right front wheel Wfr side.

The center LSD7C is a differential device with differential restriction that operates in the same manner as the front LSD7F with respect to the front wheel Wfl, Wfr side propeller shaft 5F and the rear wheel Wrl, Wrr side propeller shaft 5R.
The rear LSD 7R is a differential device with differential restriction that operates in the same manner as the front LSD 7F with respect to the drive shaft 6RL on the left rear wheel Wrl side and the drive shaft 6RR on the right rear wheel Wrr side.

  The sub-transmission 4 is provided with a hydraulic cylinder device 41 (see FIG. 4) that is driven according to the fluid pressure difference between the two divided areas 41a and 41b. The cylinder device 41 of the sub-transmission 4 is operated by a pump device 100 with a switching valve that operates the clutch device 7 of the center LSD 7C.

  Here, a schematic structure of the auxiliary transmission 4 will be described with reference to FIG. The auxiliary transmission 4 includes a planetary gear mechanism including a sun gear 43, a planetary gear 44, a planetary carrier 45 and a ring gear 46. The sun gear 43 is formed on one end side of the input shaft 31 from the transmission 3. The ring gear 46 is fixed to the inner wall of the housing 47 of the auxiliary transmission 4. The input shaft 31 and the output shaft 21 are arranged coaxially and are configured to be splined via a connecting member 48. The planetary carrier 45 and the output shaft 21 are also configured to be splined via a connecting member 48. The connecting member 48 is engaged with a shift fork 49 connected to the piston 42 of the cylinder device 41.

  For example, as shown above the one-dot chain line in FIG. 2, when the piston 42 of the cylinder device 41 is positioned on the region 41 a side, the input shaft 31 and the output shaft 21 are connected via the connecting member 48. The gear ratio of the driving force input to the shaft 31 is 1/1, which is a Hi mode that is output to the output shaft 21 without being decelerated. 2, when the piston 42 of the cylinder device 41 is located on the region 41b side, the planetary carrier 45 and the output shaft 21 are connected via the connecting member 48. The gear ratio of the driving force input to the input shaft 31 is a Lo mode in which the gear is decelerated at a reduction ratio corresponding to the number of teeth of the sun gear 43, the planetary gear 44, and the ring gear 46 and output to the output shaft. Then, by moving the position of the piston 42 from the region 41a side to the region 41b side, the mode is switched from the Hi mode to the Lo mode, and from the region 41b side to the region 41a side, the Lo mode is switched to the Hi mode.

  A driving force transmission device is configured by the front LSD 7F and the pump device 100 with a switching valve that operates the clutch device 7 of the front LSD 7F. The same applies to the rear LSD7R. The center LSD 7C, the auxiliary transmission 4, the pump device 100 with a switching valve, and the input shaft 31 from the transmission 3 constitute a driving force transmission device.

  In the vehicle 1, the driving force from the engine 2 or the like is transmitted to the center LSD 7 </ b> C via the transmission 3 and the auxiliary transmission 4. The center LSD 7C distributes the transmitted driving force to the propeller shafts 5F and 5R. Further, the differential of the propeller shafts 5F and 5R depends on the engagement force of the multi-plate clutch 72 of the clutch device 7 that is operated by hydraulic oil (corresponding to “fluid” of the present invention) supplied from the pump device 100 with a switching valve. Limit.

  The driving force distributed to the propeller shafts 5F and 5R is transmitted to the front LSD 7F and the rear LSD 7R. The front LSD 7F distributes the transmitted driving force to the drive shafts 6FL and 6FR by the same operation as the center LSD 7C. The rear LSD 7R distributes the transmitted driving force to the drive shafts 6RL and 6RR by the same action as the center LSD 7C.

  A vehicle 8 shown in FIG. 2 includes a hydraulic coupling device 9 instead of the center LSD 7C of the vehicle 1 shown in FIG. The coupling device 9 includes a clutch device 7 having a multi-plate clutch 72 and a cylinder device 73 for transmitting driving force. The coupling device 9 and the pump device 100 with a switching valve that operates the clutch device 7 of the coupling device 9 constitute a driving force transmission device.

  The coupling device 9 is provided between the propeller shaft 5F on the front wheels Wfl, Wfr side and the propeller shaft 5R on the rear wheels Wrl, Wrr side. This is a device that distributes the shaft 5F and the rear wheel Wrl, the propeller shaft 5R on the Wrr side.

  Here, as an example, the detailed structure of the center LSD 7C will be described with reference to FIG. As shown in FIG. 3, the center LSD 7C includes a planetary gear mechanism 71, a multi-plate clutch 72, a cylinder device 73, a housing 74, and the like.

  The planetary gear mechanism 71 includes a sun gear 71a, a planetary gear 71b, a carrier 71c, and an internal gear 71d. The multi-plate clutch 72 includes an inner plate 72a and an outer plate 72b. The cylinder device 73 includes a cylinder 73a, a piston 73b, and a rod 73c.

  A propeller shaft 5F on the front wheels Wfl, Wfr side is fitted in the center of the sun gear 71a. The sun gear 71a is formed with a cylindrical portion 71aa extending in the rotation axis direction. A plurality of inner plates 72a are fixed to the outer periphery of the cylindrical portion 71aa at a predetermined interval.

  The carrier 71c is integrated with the end surface 74a of the housing 74 on the propeller shaft 5F side. A cylindrical portion 74bb extending in the rotation axis direction is formed on the end surface 74b opposite to the end surface 74a on the propeller shaft 5F side in the housing 74. The output shaft 21 from the auxiliary transmission 4 is fitted to the inner periphery of the cylindrical portion 74bb.

  The internal gear 71d is formed with a cylindrical portion 71dd having a U-shaped cross section that covers the multi-plate clutch 72 and goes around the inner periphery of the sun gear 71a. A plurality of outer plates 72b are fixed to the inner periphery of the cylindrical portion 71dd facing the outer periphery of the cylindrical portion 71aa of the sun gear 71a so as to be alternately arranged with the inner plates 72a. Further, on the inner periphery of the cylindrical portion 71dd opposite to the inner periphery of the cylindrical portion 71aa of the sun gear 71a, a shaft connected to the propeller shaft 5R on the rear wheels Wrl, Wrr side via a gear mechanism (in FIG. 3, for convenience, 5R Is displayed). The shaft 5R is inserted through the hollow inner periphery of the propeller shaft 5F.

  The cylinder 73a and the piston 73b are arranged in parallel on the outer side in the rotation axis direction of the end surface 74a of the housing 74 on the propeller shaft 5R side. The rod 73c is disposed between the planetary gears 71b so as to be able to press and engage the inner plate 72a and the outer plate 72b.

(Schematic configuration of the driving force transmission device)
Next, a driving force transmission device including the center LSD 7C, the pump device 100 with a switching valve that operates the clutch device 7 of the center LSD 7C, and the auxiliary transmission 4 will be described with reference to FIG.

  As shown in FIG. 4, the pump device 100 with a switching valve includes an actuator 110, a rotary pump 120 (corresponding to the “pump” of the present invention), a rotary valve 130 (corresponding to the “switching valve” of the present invention), Transmission 140, valve driving force interrupting device 150, pump driving force interrupting device 151, phase detection mechanism 160, pressure detection mechanism 170, check valve 180, accumulator 190, control device 200, The first to fourth flow paths P1 to P4, the supply / discharge oil path P5, and the like are provided. The details of the mechanical configuration of the switching valve-equipped pump device 100 will be described later.

  The cylinder device 73 of the clutch device 7 of the center LSD 7C is connected to the pump device 100 with a switching valve by the first flow path P1 and the second flow path P2. In addition, the 1st flow path P1 and the 2nd flow path P2 are unified in the middle of piping. The cylinder device 41 of the sub-transmission 4 is pipe-connected to the pump device 100 with a switching valve by the third flow path P3 and the fourth flow path P4. In addition, the switching valve-equipped pump device 100 is connected by piping through a reservoir tank T and a supply / discharge oil passage P5.

  The first flow path P <b> 1 supplies hydraulic oil corresponding to the pressure discharged from the rotary pump 120 to the cylinder device 73 of the clutch device 7 when the rotary pump 120 is driven to rotate in the normal mode to be described later. This is a flow path for returning the hydraulic oil in the cylinder device 73 to the pump device 100 with a switching valve when driving is stopped.

  The second flow path P <b> 2 holds hydraulic oil discharged from the rotary pump 120 when the rotary pump 120 is driven to rotate in the lock mode described later, and is clutched by the hydraulic oil held when the rotary pump 120 stops rotating. This is a flow path for applying a pressing force to the cylinder device 73 of the device 7.

  The third flow path P3 supplies hydraulic oil discharged from the rotary pump 120 to the region 41a of the cylinder device 41 of the sub-transmission 4 and to the region 41b of the cylinder device 41 in the sub-transmission switching mode described later. This is a flow path for returning the hydraulic oil pushed out from the region 41a of the supply cylinder device 41 to the pump device 100 with a switching valve when the hydraulic oil is supplied.

The fourth flow path P4 supplies the hydraulic oil discharged from the rotary pump 120 to the area 41b of the cylinder device 41 of the auxiliary transmission 4 in the auxiliary transmission switching mode, and the hydraulic oil to the area 41a of the cylinder device 41. Is a flow path for returning the hydraulic oil pushed out from the region 41b of the supply cylinder device 41 to the pump device 100 with a switching valve.
The oil drainage path P5 is a flow path for returning the working oil returned from the cylinder device 73 of the clutch device 7 or the cylinder device 41 of the auxiliary transmission 4 to the reservoir tank T.

(Mechanical configuration of pump device with switching valve)
A mechanical configuration of the switching valve-equipped pump device 100 will be described with reference to the drawings. As shown in FIG. 5, the pump device 100 with a switching valve rotates the mechanical configuration such as the actuator 110 described above into an integrated hollow box-shaped motor housing Hm, first pump housing Hp1, and second pump housing Hp2. It is configured as a small device that is stored side by side in the axial direction.

  That is, the actuator 110 is housed in a hollow box-shaped motor housing Hm. The rotary pump 120, the rotary valve 130, the transmission 140, and the like are accommodated in a space formed by combining the first pump housing Hp1 and the second pump housing Hp2.

As shown in FIG. 5, the actuator 110 is a motor that is driven to rotate, and includes a stator 111, a rotor 112, a rotating shaft 113, and the like.
The stator 111 is composed of a coil or the like, and is fixed to the inner periphery of the motor housing Hm. The rotor 112 is formed in a bowl shape, a permanent magnet 112a is arranged on the outer periphery, and the end of the rotary shaft 113 is fitted in the center of the bowl so that the rotary shaft 113 protrudes from the inside of the bowl.

  The rotor 112 is disposed on the inner peripheral side of the stator 111 so as to be rotatable on the outer peripheral side of a cylindrical portion Hp1a protruding in the rotation axis direction at the center of the first pump housing Hp1. That is, the outer periphery of the inner portion 113a of the rotary shaft 113 is rotatably supported by the inner periphery of the cylindrical portion Hp1a via the radial bearing 114.

As shown in FIGS. 5 and 6, the rotary pump 120 is a pump that discharges the suctioned hydraulic oil at a high pressure by the rotational drive of the actuator 110, and includes a cam ring 121, an outer rotor 122, an inner rotor 123, and the like. ing.
The cam ring 121 is formed in a flat ring shape in which the inner periphery is eccentric with respect to the outer periphery.
The outer rotor 122 is formed in a ring shape having an outer diameter and a thickness substantially the same as the inner diameter and thickness of the cam ring 121 and having inner teeth 122 a, and is arranged rotatably on the inner periphery of the cam ring 121. The internal teeth 122a are configured by a plurality of trochoid curves.

  The inner rotor 123 is formed in a ring shape having outer teeth 123 a that are substantially the same thickness as the outer rotor 122 and can mesh with the inner teeth 122 a, and is disposed rotatably on the inner periphery of the outer rotor 122. The outer teeth 123a are configured by a plurality of trochoid curves having a smaller number of teeth than the number of teeth of the inner teeth 122a. A rotating shaft 113 of the actuator 110 is fitted to the center of the inner rotor 123 via a pump driving force interrupting device 151 so as to be integrally rotatable.

  The rotary pump 120 is recessed at the center of the second pump housing Hp2 and a side plate 125 rotatably inserted into a bottomed cylindrical space Hp1b recessed at the center of the first pump housing Hp1. It is sandwiched between a rotary valve 130 that is rotatably inserted into the bottomed cylindrical space Hp2b. Thus, the outer rotor 122 and the inner rotor 123 form a pump chamber 124 in a radially opposed region, and the plate end surface 125c and the valve end surface 130c in the rotational axis direction on the pump chamber 124 side of the side plate 125 and the rotary valve 130 124 side walls are formed.

  A step portion 125 dd is formed on the outer peripheral side of the plate end surface 125 d in the rotation axis direction on the side opposite to the pump chamber in the side plate 125. Between the step portion 125dd and the first pump housing Hp1 facing the step portion 125dd, hydraulic oil discharged from the pump chamber 124 is allowed to flow, and at the same time, rotary to the side plate 125 with the pressure of the hydraulic oil. A back pressure chamber 125e for applying a pressing force to the pump 120 side is provided.

  Since the fluid becomes a high pressure during the operation of the rotary pump 120, there is a gap between the rotary pump 120 and the side plate 125 or between the rotary pump 120 and the motor housing Hm, the first pump housing Hp1, and the second pump housing Hp2. If it occurs, fluid may leak, but the positional relationship between the side plate 125 and the motor housing Hm, the first pump housing Hp1, and the second pump housing Hp2 can be maintained by the pressing force of the back pressure chamber 125e. It is possible to prevent fluid leakage.

  The side plate 125, the cam ring 121 of the rotary pump 120, and the rotary valve 130 are coupled by a pin 127. A seal ring 125g is fitted between the plate end surface 125d and the plate peripheral surface 125f of the side plate 125 and the first pump housing Hp1. The first and second pump housings Hp1 and Hp2 are provided with a pair of thrust bearings 126 disposed so as to sandwich the side plate 125, the rotary pump 120, and the rotary valve 130 from both sides in the rotation axis direction. As a result, the side plate 125, the rotary pump 120, and the rotary valve 130 can be smoothly rotated without any play.

  On both side walls 125c, 130c of the pump chamber 124 in the side plate 125 and the rotary valve 130, crescent-shaped suction side grooves 125a, 130a and discharge side grooves 125b, 130b are provided in the circumferential direction of the side walls 125c, 130c of the pump chamber 124. Recesses are formed at predetermined intervals along the recesses. The positions where the suction side grooves 125a and 130a and the discharge side grooves 125b and 130b are formed are formed on a locus along which the space formed between the outer teeth 123a and the inner teeth 122a moves.

  The rotary valve 130 is formed with a suction passage 131 that communicates with the pump chamber 124 from the bottom of the suction side groove 130a (see FIGS. 5, 7, and 8). The position where the suction channel 131 communicates with the bottom of the suction side groove 130a is that the space formed between the outer teeth 123a and the inner teeth 122a is the start end of the suction side groove 130a that first passes through the suction side groove 130a. is there. Further, the rotary valve 130 is formed with a discharge flow path 132 that communicates with the pump chamber 124 from the bottom of the discharge side groove 130b (see FIGS. 5, 7, and 8). The position where the discharge channel 132 communicates with the bottom of the discharge side groove 130b is an intermediate portion of the discharge side groove 130b.

  In the rotary pump 120, when the actuator 110 is driven to rotate, the inner rotor 123 rotates counterclockwise in FIG. 6, and the outer rotor 122 engaged with the outer teeth 123a by the inner teeth 122a also rotates counterclockwise in FIG. . Then, the space formed between the external teeth 123a and the internal teeth 122a moves from the suction side groove 130a to the discharge side groove 130b, and the pressure on the discharge side of the pump chamber 124 is higher than the pressure on the suction side of the pump chamber 124. Therefore, the hydraulic oil is fed from the suction channel 131 to the discharge channel 132.

  The rotary valve 130 can switch a plurality of destinations of the hydraulic oil discharged from the pump chamber 124 by changing the phase by the rotational drive of the actuator 110, and a plurality of returns that communicate with the suction side of the pump chamber 124. This is a switching valve that can switch the tip. Thereby, the fluid can be returned smoothly and reused.

  The rotary valve 130 includes a normal mode in which the discharge side of the pump chamber 124 is communicated with the first flow path P1, a lock mode in which the discharge side of the pump chamber 124 is communicated with the second flow path P2, and the discharge side and suction of the pump chamber 124. This is a switching valve capable of switching between the sub-transmission switching mode for driving the cylinder device 41 by communicating the respective sides with the third and fourth flow paths P3 and P4.

As shown in FIGS. 5, 7, and 8, a hole 130 g through which a cylindrical portion 141 a extending in the rotational axis direction of the sun gear 141 of the transmission 140 is inserted with a gap is formed at the center of the rotary valve 130. ing.
Inside the rotary valve 130, the above-described suction flow path 131 and discharge flow path 132 are formed. Here, when the opening 131a in the suction side groove 130a of the suction flow path 131 and the opening 132a in the discharge side groove 130b of the discharge flow path 132 are positioned in the left-right direction shown in FIG. The path of the flow path 132 will be described.

  The suction channel 131 extends from the opening 131a in the suction side groove 130a toward the valve end surface 130d on the opposite side in the rotational axis direction to a position about half the thickness of the rotary valve 130, and is bent at a right angle diagonally downward to the right. It extends to the outer periphery and opens, and before reaching the valve outer periphery 130e, it bends and branches in the direction of the rotational axis, and extends to the valve end surface 130d to open. The branched flow path is a drain flow path 131 c for discharging hydraulic oil to the reservoir tank T.

  That is, the hydraulic oil in the reservoir tank T enters the rotary valve 130 through the opening 131d of the valve outer periphery 130e through the intake / exhaust oil passage P5, and is sucked into the pump chamber 124 through the suction passage 131. The hydraulic oil from the cylinder device 73 passes through the first flow path P1, passes through the suction flow path 131 extending from the drain flow path 131c to the valve outer periphery 130e, and passes through the intake and exhaust oil path P5 from the opening 131d of the valve outer periphery 130e. It is discharged to the reservoir tank T.

  The discharge flow path 132 extends from the opening 132a in the discharge side groove 130b toward the valve end surface 130d on the opposite side in the rotation axis direction to a position about half the thickness of the rotary valve 130, and then bends to the upper left at a right angle diagonally. Before reaching the outer periphery 130e, it bends in the direction of the rotation axis and extends to the valve end surface 130d to open. That is, the opening 131b of the valve end surface 130d of the drain flow channel 131c and the opening 132b of the valve end surface 130d of the discharge flow channel 132 are symmetric with respect to the center of the rotary valve 130 (with a 180 degree separation in the circumferential direction). ).

  A circumferential groove 133 through which hydraulic oil discharged from the pump chamber 124 flows is provided on the valve end surface 130 d of the rotary valve 130. The circumferential groove 133 is provided to detect the pressure of each of a plurality of destinations of the hydraulic oil discharged from the pump chamber 124 by the pressure detection mechanism 170 that is communicated. For this reason, the circumferential groove 133 communicates with the pressure detection flow path 132 c branched from the middle of the discharge flow path 132.

  A seal ring 134 is fitted on the outer side and the inner side of the circumferential groove 133 to prevent leakage of hydraulic oil from the circumferential groove 133. By forming such an annular groove, even if the rotary valve 130 rotates, the pressure for every destination can be detected by one pressure detection mechanism 170. As the pressure detection mechanism 170, there is a pressure detection sensor using capacitance, strain, or the like.

  Further, on the valve end surface 130d of the rotary valve 130, four convex portions 135 are provided at equal angular intervals so as to be inserted into the gaps of the four planetary gears 142 of the transmission 140 and rotate coaxially with the transmission 140. ing.

  On the valve outer periphery 130e of the rotary valve 130, recesses 161 having a wedge-shaped radial cross section constituting the phase detection mechanism 160 are provided at intervals of 45 degrees. The recess 161 is provided for detecting and positioning the rotational phase of the rotary valve 130 in cooperation with the position detection sensor 162 constituting the phase detection mechanism 160. That is, the recess 161 and the position detection sensor 162 are configured to detect the rotational phase of the rotary valve 130 and position the rotary valve 130 with respect to the first housing Hp1, and to detect the flow path 131 of the rotary valve 130, etc. For switching, the rotary valve 130 functions as a braking device capable of switching between a state in which the rotary valve 130 is released from the first housing Hp1.

  By inserting the phase detection sensor 162 into such a triangular prism-shaped recess, when the rotary valve 130 attempts to rotate counterclockwise in the figure, the phase detection sensor 162 abuts against the wall of the recess 161 and thus counterclockwise. The rotation phase of the rotary valve 130 can be detected and positioned. Thereby, the several destination of the fluid discharged from the pump chamber 124 can be switched reliably.

  As shown in FIGS. 5, 7, and 9, the second pump housing Hp2 is provided with a communication suction channel 136 that can communicate with the suction channel 131 provided in the rotary valve 130, and the drain channel 131c. A communication drain channel 136c, a first intake / exhaust channel 139a, and a second intake / exhaust channel 139b are provided. Further, a normal discharge channel 137 and a lock discharge channel 138 that can communicate with the discharge channel 132 are provided. The discharge channel 132 can also communicate with the first intake / exhaust channel 139a and the second intake / exhaust channel 139b. Further, a communication pressure detection flow path 137c (corresponding to the “communication hole” of the present invention) that is always in communication with the pressure detection flow path 132c is provided.

  On the inner periphery of the space Hp2b of the second pump housing Hp2, when the rotary valve 130 is rotated and positioned at a predetermined phase, the opening of the communication suction passage 136 that coincides with the opening 131d of the valve outer periphery 130e of the suction passage 131 136a is provided. Further, at the bottom of the space Hp2b of the second pump housing Hp2, there is an opening 136d of the communication drain channel 136c that coincides with the opening 131b of the valve end surface 130d of the drain channel 131c and the discharge channel at the time of the phase positioning. An opening 137a of the communication discharge channel 137 is provided that coincides with the opening 132b of the valve end face 130d of 132.

  That is, the positional relationship between the opening 136d of the communication drain channel 136c and the opening 137a of the normal discharge channel 137 is the same as the positional relationship between the opening 131b of the drain channel 131c and the opening 132b of the discharge channel 132. The bottom of Hp2b is drilled at a position 180 degrees apart in the circumferential direction. When the openings 136d, 131b and 137a, 132b coincide with each other, the phase detection sensor 162 is inserted into a predetermined recess 161 to detect and position the rotational phase.

  Further, at the bottom of the space Hp2b of the second pump housing Hp2, when the rotary valve 130 is rotated 90 degrees clockwise or counterclockwise from the state in which the openings 136d, 131b and 137a, 132b coincide with each other, An opening 139c of the first intake / exhaust flow path 139a and an opening 139d of the second intake / exhaust flow path 139b that coincide with the opening 131b of the valve end face 130d of the working flow path 131c and the opening 132b of the valve end face 130d of the discharge flow path 132 are provided. .

  That is, the positional relationship between the opening 139c of the first suction / discharge channel 139a and the opening 139d of the second suction / discharge channel 139b is the same as the positional relationship of the opening 131b of the drain channel 131c and the opening 132b of the discharge channel 132, Positions spaced 180 degrees in the circumferential direction at the bottom of the space Hp2b (positions shifted 90 degrees in the circumferential direction with respect to the positional relationship between the opening 136d of the communication drain channel 136c and the opening 137a of the normal discharge channel 137) Has been drilled. When the openings 139c, 131b and 139d, 132b coincide with each other, the phase detection sensor 162 is inserted into the recess 161 to detect and position the rotational phase.

  Further, at the bottom of the space Hp2b of the second pump housing Hp2, when the rotary valve 130 is rotated 45 degrees counterclockwise from the state in which the openings 136d, 131b and 137a, 132b coincide with each other, the discharge passage 132 is provided. An opening 138a of the lock discharge flow path 138 that coincides with the opening 132b of the valve end face 130d is provided. In this case, the opening 136d of the communication drain channel 136c and the opening 137a of the normal discharge channel 137 are closed by a lid 130f provided on the valve end surface 130d.

  In addition, an opening 137d of the communication pressure detection flow path 137c that always coincides with the circumferential groove 133 of the rotary valve 130 is provided at the bottom of the space Hp2b of the second pump housing Hp2.

Next, the communication suction flow path 136, the communication drain flow path 136c, the normal discharge flow path 137, the lock discharge flow path 138, the first intake / discharge flow path 139a, the second intake / discharge flow path 139b, and the communication pressure detection flow path 137c. Explain the route.
The communication suction flow path 136 is a path that extends from the inner opening 136a of the space Hp2b of the second pump housing Hp2 to the bottom surface of the second pump housing Hp2 in the radial direction.

  The communication drain flow path 136c extends from the opening 136d at the bottom of the space Hp2b of the second pump housing Hp2 toward the housing end surface opposite to the housing end surface where the space Hp2b is provided in the rotation axis direction. It extends to about half the thickness, and then bends in a right-angled right direction and bends in a right-angled upper direction before reaching the side of the housing, thereby providing a path communicating with a valve hole 137b provided in the normal discharge flow path 137. A port communicating with the valve hole 137b of the communication drain channel 136c is a drain port 136e.

  The normal discharge flow path 137 extends from the opening 137a at the bottom of the space Hp2b of the second pump housing Hp2 toward the housing end surface opposite to the housing end surface where the space Hp2b is provided in the rotation axis direction. It extends to half the thickness, where it forms a path that is bent in a right-angled right direction to a valve hole 137b formed in the side surface of the housing. The valve hole 137b is provided with a flow control valve 152 connected to the first flow path P1.

  In the state where hydraulic fluid is supplied to the flow control valve 152, the pressure of hydraulic fluid on the clutch device 7 side (first flow path P1 side) of the flow control valve 152 is set on the rotary valve 130 side (normal discharge flow path 137 side). A throttle 152a that is larger than the pressure of the hydraulic oil is provided.

  The flow control valve 152 is urged toward the normal discharge flow path 137 by the restoring force of the compression spring 152b in the valve hole 137b when the rotary valve 130 is in the normal mode and the rotary pump 120 is stopped. Further, the flow control valve 152 moves to a position where the drain port 136e is closed against the restoring force of the compression spring 152b due to the pressure difference of the hydraulic oil when the rotary valve 130 is in the normal mode and the rotary pump 120 is driven. .

  That is, the flow control valve 152 supplies the hydraulic oil from the discharge side of the rotary pump 120 to the clutch device 7 side by closing the drain port 136e, and opens the drain port 136e from the clutch device 7 side. It is a valve that can be switched between the state of discharging to the suction side. As a result, the fluid can be smoothly supplied to the switching destination, the pressure of the fluid can be rapidly reduced from the switching destination, and the driving force transmission device can be operated at high speed.

  The lock discharge passage 138 extends from the opening 138a at the bottom of the space Hp2b of the second pump housing Hp2 toward the housing end surface opposite to the housing end surface where the space Hp2b is provided in the rotation axis direction. It extends to half the thickness, and then bends upward at a right angle to provide a path to the check valve 180 provided on the upper surface of the housing and connected to the second flow path P2.

  The check valve 180 constantly presses the valve body 181 against the discharge port of the lock discharge flow path 138 by the action of the compression spring 182, and restricts the backflow of hydraulic oil to the rotary pump 120 when the rotary pump 120 is stopped. This is a valve that allows hydraulic oil to be supplied to the clutch device 7 when the rotary pump 120 is driven. Thereby, fluid leakage can be suppressed in the lock mode, and the pressure of the fluid can be maintained for a long time.

The first intake / exhaust flow path 139a and the second intake / exhaust flow path 139b are housing end faces opposite to the housing end face provided with the space Hp2b in the rotation axis direction from the openings 139c, 139d at the bottom of the space Hp2b of the second pump housing Hp2. It is a path that extends to open.
The communication pressure detection flow path 137c extends from the opening 137d at the bottom of the space Hp2b of the second pump housing Hp2 toward the housing end surface opposite to the housing end surface where the space Hp2b is provided in the rotation axis direction. It is a path that bends to the left at a right angle and extends to the side of the housing to open.

  As shown in FIG. 5, FIG. 7, and FIG. 10, the transmission 140 uses a reduction ratio when transmitting the rotational driving force of the actuator 110 to the rotary pump 120 based on a reduction ratio when transmitting to the rotary valve 130. It is a reduction gear to enlarge. The transmission 140 is provided in a bottomed cylindrical space Hp2c that is recessed further to the back than the bottomed cylindrical space Hp2b that is recessed in the center of the second pump housing Hp2 in which the rotary valve 130 is inserted. It is fitted so that it can rotate.

The transmission 140 includes a sun gear 141, four planetary gears 142, and an internal gear 143.
The sun gear 141 is formed with a cylindrical portion 141a extending in the rotation axis direction. The rotating shaft 113 of the actuator 110 is fitted to the inner periphery of the cylindrical portion 141a through the valve driving force interrupting device 150 so as to be integrally rotatable.

  The four planetary gears 142 are meshed with the sun gear 141 at equal angular intervals. And the convex part 135 of the rotary valve 130 is inserted between the planetary gears 142 so that the rotary valve 130 can rotate with the revolution of the planetary gear 142 around the sun gear 141.

  The internal gear 143 is integrally provided on the inner periphery of the space Hp2c of the second pump housing Hp2. Four planetary gears 142 are meshed with the internal gear 143 at equal angular intervals. The internal gear 143 may be provided separately from the second pump housing Hp2 and pin-coupled to the second pump housing Hp2.

  The valve driving force interrupting device 150 is a one-way clutch capable of switching between a state of transmitting the clockwise rotational driving force shown in the figure of the actuator 110 to the rotary valve 130 and a state of blocking the counterclockwise rotational driving force. It is. The pump driving force interrupting device 151 is a one-way clutch capable of switching between a state in which the counterclockwise rotational driving force shown in the figure of the actuator 110 is transmitted to the rotary pump 120 and a state in which the clockwise rotational driving force is interrupted. It is.

  Thereby, the rotary pump 120 and the rotary valve 130 can be reliably switched and driven to rotate. Then, the rotary drive of the rotary pump 120 and the rotary drive of the rotary valve 130 are not operated simultaneously, and the fluid can be reliably supplied to a predetermined destination. A friction plate type clutch may be used instead of the one-way clutch.

  As shown in FIG. 7, the phase detection mechanism 160 includes a recess 161 having a wedge-shaped radial cross section and a phase detection sensor 162. The recesses 161 are provided on the valve outer periphery 130e of the rotary valve 130 at intervals of 45 degrees. The phase detection sensor 162 is a sensor that uses eddy current, magnetism, etc., the sensor portion is fixed to the side surface of the second pump housing Hp2, and the tip portion is radial from the inner peripheral surface of the second pump housing Hp2 by a spring 163. The inward protrusion amount is provided to be variable.

  Since high pressure is applied to the rotary valve 130 during operation of the rotary pump 120, the rotary valve 130 may run idle only with the valve driving force interrupting device 150. However, since the recess 161 that locks in the circumferential direction with respect to the phase detection sensor 162 is provided, it is possible to prevent the rotary valve 130 from idling.

  As shown in FIG. 7, the check valve 180 includes a valve body 181 and a compression spring 182. The valve body 181 is always pressed against the discharge port of the lock discharge flow path 138 by the spring force of the compression spring 182 when the rotary pump 120 is stopped. Thereby, the backflow of the hydraulic oil to the lock discharge flow path 138 can be regulated.

  Further, when the rotary pump 120 is driven, the valve body 181 is separated from the discharge port of the lock discharge channel 138 against the spring force of the compression spring 182 by the hydraulic oil discharged from the lock discharge channel 138. Thereby, supply of the hydraulic fluid to the clutch device 7 side can be permitted.

  As shown in FIG. 4, the accumulator 190 is connected to the second flow path P <b> 2 and stores the hydraulic oil when the pressure of the hydraulic oil in the second flow path P <b> 2 is equal to or higher than a predetermined pressure. The pressure accumulator discharges the hydraulic oil stored in the second flow path P2 when the pressure of the hydraulic oil in the second flow path P2 decreases. Thereby, the pressure of the fluid can be maintained for a long time. Therefore, driving of the rotary pump 120 can be stopped for a long time, and current consumption of the driving force transmission device can be suppressed.

  As shown in FIG. 4, the control device 200 controls the rotation drive of the actuator 110 based on the phase of the rotary valve 130 detected by the phase detection mechanism 160 in accordance with the normal mode, the lock mode, and the auxiliary transmission switching mode. The function of controlling the rotational drive of the actuator 110 based on the pressure of the hydraulic oil detected by the pressure detection mechanism 170 is provided. Thereby, the actuator can be accurately driven and controlled so that the destination of the fluid is accurate. In addition, the actuator can be accurately driven and controlled so that the fluid pressure is appropriate.

(Operation of pump device with switching valve)
Next, operations in the normal mode, the lock mode, and the auxiliary transmission switching mode of the pump device 100 with a switching valve will be described with reference to the drawings.

  In the normal mode, as shown in FIG. 11A, the opening 131d of the suction flow path 131 of the rotary valve 130 coincides with the opening 136a of the communication suction flow path 136, and the opening 131b of the drain flow path 131c is It coincides with the opening 136d of the communication drain channel 136c. Further, the opening 132 b of the discharge passage 132 of the rotary valve 130 coincides with the opening 137 a of the normal discharge passage 137.

  When the rotary pump 120 is rotationally driven in this state, the hydraulic oil in the reserve tank T is sucked into the pump chamber 124 from the communication suction channel 136 through the suction channel 131. The hydraulic oil having a high pressure in the pump chamber 124 is discharged from the discharge passage 132 to the flow control valve 152 through the normal discharge passage 137.

  Then, as shown in FIG. 11B, the flow control valve 152 moves to a position where the drain port 136e is closed due to the pressure difference caused by the hydraulic oil passing through the throttle 152a of the flow control valve 152. The hydraulic oil that has passed through the flow control valve 152 is supplied to the cylinder device 73 of the clutch device 7 through the first flow path P1, and the multi-plate clutch 72 is engaged at a predetermined pressure according to the pressure detection signal of the pressure detection mechanism 170. . Thereafter, the rotational drive of the rotary pump 120 is controlled according to the pressure detection signal of the pressure detection mechanism 170 so that the multi-plate clutch 72 is engaged at a predetermined pressure.

  As shown in FIG. 11C, when the rotary drive of the rotary pump 120 is stopped, the pressure difference in the flow control valve 152 disappears, so the flow control valve 152 moves to a position where the drain port 136e is opened by the restoring force of the compression spring 152b. To do. The hydraulic oil in the cylinder device 73 of the clutch device 7 is returned from the first flow path P1 to the reserve tank T through the drain port 136e and the drain flow path 131c. Thus, the normal mode ends.

  In the lock mode, as shown in FIG. 12A, the opening 131b of the drain flow path 131c of the rotary valve 130 is closed by a lid 130f. Further, the opening 132 b of the discharge passage 132 of the rotary valve 130 coincides with the opening 138 a of the lock discharge passage 138.

  In this state, the first flow path P1 side, the normal discharge flow path 137 side, and the drain port 136e side of the flow control valve 152 are all closed, so that the hydraulic pressure existing in the flow control valve 152 is the cylinder of the clutch device 7. It becomes a state equal to the hydraulic pressure of the device 73 and the accumulator 190.

  When the rotary pump 120 is rotationally driven in this state, as shown in FIG. 12B, the hydraulic oil in the reserve tank T is sucked into the pump chamber 124 from the communication suction channel 136 through the suction channel 131. The hydraulic oil having a high pressure in the pump chamber 124 opens the check valve 180 from the discharge passage 132 through the lock discharge passage 138.

  Then, the hydraulic oil that has passed through the check valve 180 is supplied to the cylinder device 73 of the clutch device 7 through the second flow path P2, and the multi-plate clutch 72 is set at a predetermined pressure according to the pressure detection signal of the pressure detection mechanism 170. Engage. When the multi-plate clutch 72 is engaged at a predetermined pressure, the hydraulic oil that has passed through the check valve 180 is supplied to the accumulator 190. When the pressure of the accumulator 190 reaches a predetermined pressure according to the pressure detection signal of the pressure detection mechanism 170, the rotary drive of the rotary pump 120 is stopped.

  As shown in FIG. 12C, when the supply of hydraulic oil from the discharge flow path 132 through the lock discharge flow path 138 is stopped, the check valve 180 is closed by the restoring force of the compression spring 182. When the pressure of the multi-plate clutch 72 decreases, hydraulic oil is supplied from the accumulator 190 to engage the multi-plate clutch 72 with a predetermined pressure. And if the pressure of the accumulator 190 falls, the rotary pump 120 will be rotationally driven again and the above-mentioned operation | movement will be repeated until lock mode is complete | finished.

  In the auxiliary transmission switching mode (Hi), as shown in FIG. 13A, the opening 132b of the discharge flow path 132 of the rotary valve 130 coincides with the opening 139d of the second intake / exhaust flow path 139b, and the drain flow The opening 131b of the path 131c coincides with the opening 139c of the first intake / exhaust flow path 139a. Further, the opening 131d of the suction passage 131 of the rotary valve 130 is closed.

  When the rotary pump 120 is rotationally driven in this state, the hydraulic oil in the region 41a of the cylinder device 4 is sucked into the pump chamber 124 from the third flow path P3 through the first suction / discharge flow path 139a and the drain flow path 131c. Is done. Then, the hydraulic oil in the pump chamber 124 is supplied from the discharge flow path 132 to the area 41b of the cylinder device 4 of the auxiliary transmission 4 through the second intake / exhaust flow path 139b and the fourth flow path P4. It moves to 41a side and switches to the shift Hi. Thus, the auxiliary transmission switching mode (Hi) ends.

  In the sub-transmission switching mode (Lo), as shown in FIG. 13B, the opening 132b of the discharge passage 132 of the rotary valve 130 coincides with the opening 139c of the first intake / exhaust passage 139a, and the drain flow The opening 131b of the path 131c coincides with the opening 139d of the second intake / exhaust flow path 139b. Further, the opening 131d of the suction passage 131 of the rotary valve 130 is closed.

  When the rotary pump 120 is rotationally driven in this state, the hydraulic oil in the region 41b of the cylinder device 4 is sucked into the pump chamber 124 from the fourth flow path P4 through the second suction / discharge flow path 139b and the drain flow path 131c. Is done. Then, the hydraulic oil in the pump chamber 124 is supplied from the discharge flow path 132 to the area 41a of the cylinder device 4 of the auxiliary transmission 4 through the first intake / exhaust flow path 139a and the third flow path P3. It moves to 41b side and switches to the shift Lo. Thus, the auxiliary transmission switching mode (Lo) is completed.

  According to the pump device with a switching valve of the present embodiment, the rotation drive of the rotary pump 120 and the rotation drive of the rotary valve 130 can be switched by the actuator driving force intermittent device 150 with one actuator 110, so The drive control of the actuator 110 is simple, and the pump device 100 with a switching valve can be operated at high speed. In addition, since the number of devices can be reduced, significant cost reduction can be achieved.

(Other)
In the above-described embodiment, the cam ring 121 of the rotary pump 120 is provided separately, but the shape of the cam ring 121 may be provided on the side plate 125. Accordingly, oil leakage between the rotary pump 120 and the rotary valve 130 can be reduced, and the side plate 125 and the rotary valve 130 can be rotated more smoothly.

  In the above-described embodiment, the actuator 110, the rotary pump 120, the rotary valve 130, and the transmission 140 are integrated. However, the rotary pump 120 is directly connected to the actuator 110, and the gear mechanism (transmission 140) or belt / pulley. The actuator 110 and the rotary valve 130 may be connected via a mechanism or the like.

  In the above-described embodiment, the rotational phase of the rotary valve 130 is detected by the phase detection mechanism 160. However, the actuator 110 includes a rotary encoder, or the actuator 110 detects a rotational phase using a stepping motor. It is good. In addition, the pressure of the hydraulic oil in the rotary valve 130 is detected by the pressure detection mechanism 170, but the pressure of the hydraulic oil may be detected by the drive current of the actuator 110.

  In the above embodiment, the transmission 140 is configured to rotate the rotary valve 130 using a reduction gear. However, the transmission 140 is configured to rotate the rotary pump 120 using a speed increaser. Also good. Thereby, since the speed change apparatus 140 can be made into a simple structure, the cost reduction of the pump apparatus 100 with a switching valve can be achieved. Moreover, you may comprise so that the rotary pump 120 may be rotated using the 1st reduction gear as the transmission 140, and the rotary valve 130 may be rotated using the 2nd reduction gear with a larger reduction ratio than a 1st reduction gear. Thereby, the pump pressure of the rotary pump 120 can be increased.

  100: Pump device with switching valve, 110: Actuator, 120: Rotary pump, 125: Side plate, 130: Rotary valve, 140: Transmission, 150: Driving force interrupting device for valve, 151: Driving force interrupting device for pump, 160: phase detection mechanism, 170: pressure detection mechanism, 180: check valve, 190: accumulator, 200 control device, P1 to P4: first to fourth flow paths, P5: supply / discharge oil passage

Claims (13)

One actuator for rotational driving;
A pump that discharges the inhaled fluid by rotational driving of the actuator;
A switching valve capable of switching a plurality of destinations of the fluid discharged from the pump chamber of the pump by changing the phase by rotational driving of the actuator;
A valve driving force interrupting device capable of switching between a state in which the rotational driving force of the actuator is transmitted to the switching valve and a state in which the actuator is shut off;
A housing for housing the pump and the switching valve;
With
The rotation axis of the actuator, the rotation axis of the pump and the rotation axis of the switching valve are provided on the same axis,
The end face of the switching valve forms a side wall of the pump chamber of the pump,
At least one of the switching valve and the housing facing the switching valve is provided with a circumferential groove for allowing the fluid discharged from the pump chamber to flow therein.
The pump device with a switching valve, wherein the housing is provided with a communication hole that communicates the pressure detection mechanism and the circumferential groove .   The switching according to claim 1, wherein the valve driving force interrupting device transmits a rotational driving force in one rotational direction of the actuator to the switching valve, and blocks the rotational driving force in the other rotational direction with respect to the switching valve. Pump device with valve. The actuator rotationally drives the pump with a rotational driving force in the other rotational direction of the actuator,
The pump device with a switching valve according to claim 1, wherein the valve driving force interrupting device transmits a rotational driving force in one rotational direction of the actuator to the switching valve. The valve driving force interrupting device is a one-way clutch that transmits a rotational driving force in one rotational direction of the actuator to the switching valve and interrupts a rotational driving force in the other rotational direction,
The pump device with a switching valve is a one-way clutch, transmits a rotational driving force in the other rotational direction of the actuator to the pump, and blocks a rotational driving force in one rotational direction. The pump device with a switching valve according to claim 2 or 3, comprising an intermittent device. The housing accommodates the switching valve in a rotatable manner ,
The switching valve has a braking device capable of switching between a rotationally restrained state and a released state with respect to the housing,
When the actuator is rotationally driven in one rotational direction, the braking device releases the switching valve,
The pump device with a switching valve according to any one of claims 1 to 4, wherein when the actuator is rotationally driven in the other rotation direction, the braking device restrains the switching valve. The pump device with a switching valve includes a side plate that forms a side wall opposite to the switching valve in the pump chamber,
The pump includes an outer rotor and an inner rotor, and includes a cam ring that supports the outer rotor eccentrically with respect to the inner rotor so as to be rotatable.
The switching valve, the side plate, and the cam ring rotate integrally.
The pump apparatus with a switching valve according to any one of claims 1 to 5 . The side plate is housed in the housing;
The fluid discharged from the pump chamber is caused to flow between the side plate on the side opposite to the rotation axis in the pump chamber side of the side plate and the housing facing the end surface in the rotation axis. The pump device with a switching valve according to claim 6 , wherein a back pressure chamber is provided for applying a pressing force toward the pump side to the side plate. The pump device with a switching valve is
The pump device with a switching valve according to claim 6 or 7 , further comprising a thrust bearing disposed so as to sandwich the pump, the switching valve, and the side plate in the rotation axis direction with respect to the housing. The pump device with a switching valve according to any one of claims 1 to 8 , wherein the switching valve is capable of switching a plurality of return destinations that communicate with the suction side of the pump chamber of the pump by changing the phase. The pump device with a switching valve is
The pump device with a switching valve according to any one of claims 1 to 9 , further comprising a control device that controls the rotational drive of the actuator based on the pressure of the fluid detected by the pressure detection mechanism. The pump device with a switching valve is
The pump device with a switching valve according to any one of claims 1 to 10 , further comprising a phase detection mechanism capable of detecting and positioning the phase. The pump device with a switching valve is
The pump device with a switching valve according to claim 11 , further comprising a control device that controls rotational driving of the actuator based on the phase of the switching valve detected by the phase detection mechanism. The phase detection mechanism is
A sensor that is fixed to a housing that rotatably accommodates the switching valve, and that is provided so as to vary a protruding amount radially inward from an inner peripheral surface of the housing;
A recess formed in an outer peripheral surface of the switching valve and locked in a circumferential direction with respect to the sensor;
The pump device with a switching valve according to claim 11 or 12 , wherein

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