Integrated pump device

Abstract

An integrated pump device (10) has a motor unit (20), a pump unit (30), and a hydraulic actuator unit (60) that are integrally formed. The hydraulic actuator unit (60) operates so as to be switched between a forward state and a return state by hydraulic pressure supplied from the pump unit (30) through an oil introduction port (541, 542). A vane housing (61) has formed therein a suction port (67) and a discharge port (68), and has a vane chamber thereinside. A vane rotor (63) is accommodated in the vane housing (61), and has provided thereto a vane corresponding to the vane chamber. Formed at the bottom of a first vane chamber (621) is a chamber-bottom discharge opening (625) that is in communication with the discharge port (68). The opening area of the chamber-bottom discharge opening (625) changes according to the operating angle of a first vane accommodated in the first vane chamber (621).

Description

Integrated Pumping Unit CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Japanese Application No. 2024-043142 filed on March 19, 2024, the contents of which are incorporated herein by reference.

[0002] The present disclosure relates to an integrated pumping device.

[0003] Conventionally, there has been known a device in which an electric oil pump and a hydraulic parking lock actuator are integrally provided. For example, the actuator disclosed in Patent Document 1 includes an electric oil pump unit and a parking lock mechanism. In Patent Document 1, the pump is housed in a pump dome (30). An actuator cylinder (14) transmits power to a parking lock mechanism (18).

[0004] Patent Document 2 discloses an integrated pump device that integrates a motor, an oil pump, and a rotary hydraulic parking lock actuator. For example, the hydraulic parking lock actuator is configured as a rotary hydraulic actuator in which a vane rotor rotates within a vane housing. The oil pump can supply oil for cooling or lubrication to an oil consumer via the hydraulic parking lock actuator.

[0005] Chinese Patent Publication No. CN112912647B Specification Japanese Patent Application Laid-Open No. 2023-093012

[0006] Although Patent Document 1 does not specify the intake and discharge ports of the hydraulic unit, the following two points can be inferred from Figure 1: [1] Oil is sucked in and discharged through holes shown on the underside of the pump dome (30). [2] There are no intake or discharge ports connected to external piping, and oil circulates inside the hydraulic unit (12).

[0007] The integrated pump device of Patent Document 2 has two problems: it is necessary to reduce the size of the device for ease of installation in a vehicle, and it is also necessary to be able to adjust the discharge flow rate with a simple configuration that does not require additional components. However, the actuator of Patent Document 1 is large in size because the electric oil pump unit and the parking lock mechanism are located independently in different locations. Furthermore, there is no mention of adjusting the supply flow rate.

[0008] An object of the present disclosure is to provide an integrated pump device that includes a vane rotor rotary hydraulic actuator unit, and that is capable of adjusting the discharge flow rate with a simple configuration while reducing the size of the integrated pump device.

[0009] The integrated pump device of the present disclosure is an integrated unit comprising a motor unit, a pump unit, and a hydraulic actuator unit. The pump unit rotates by the driving force of the motor unit and discharges oil drawn in from an intake port to a discharge port. The hydraulic actuator unit operates to switch between a forward state and a reverse state by hydraulic pressure supplied from the pump unit via an oil inlet.

[0010] The hydraulic actuator includes a vane housing and a vane rotor. The vane housing has an intake port and a discharge port and has one or more vane chambers therein. The vane rotor is housed in the vane housing and has one or more vanes corresponding to the vane chambers.

[0011] An advance hydraulic chamber is formed on one side of the vane's circumference in the vane chamber, and a return hydraulic chamber is formed on the other side of the vane's circumference. When hydraulic pressure is supplied to the advance hydraulic chamber, the vane rotor rotates in one direction, resulting in an advance state. When hydraulic pressure is supplied to the return hydraulic chamber, the vane rotor rotates in the other direction, resulting in a return state.

[0012] A chamber bottom discharge opening communicating with the discharge port is formed in the bottom of a first vane chamber, which is one of the vane chambers. The opening area of ​​the chamber bottom discharge opening changes depending on the operating angle of the first vane housed in the first vane chamber.

[0013] The integrated pump device of the present disclosure has a pump unit and a hydraulic actuator unit integrated into one unit, and the vane housing of the hydraulic actuator unit has an inlet and an outlet, allowing for a reduced size. Furthermore, the bottom discharge opening is switched between closed and open depending on the operating angle of the first vane in the first vane chamber, and the opening area in the open state changes accordingly. This allows for switching between stopping and starting oil supply from the discharge opening. Furthermore, the discharge flow rate can be adjusted with a simple configuration that does not require separate components such as a flow control valve.

[0014] The above and other objects, features, and advantages of the present disclosure will become more apparent from the following detailed description taken in conjunction with the accompanying drawings, in which Fig. 1 is a perspective view of the integrated pump device of the first embodiment, Fig. 2 is an exploded perspective view of the integrated pump device of the first embodiment, Fig. 3 is a side view of the integrated pump device of the first embodiment, Fig. 4 is a schematic axial cross-sectional view of the integrated pump device of the first embodiment, Fig. 5 is a cross-sectional view taken along line V-V in Fig. 3, Fig. 6 is a cross-sectional view taken along line VI-VI in Fig. 3 that explains the operation of the vane rotor in the hydraulic actuator section, Fig. 7 is a view of the pump plate as seen from the motor section side, Fig. 8A is a schematic cross-sectional view of part VIIIa in Fig. 4, Fig. 8B is a cross-sectional view of part VIIIa in Fig. 4, Fig. 8C is a cross-sectional view of part VIIIa in Fig. 4, Fig. 8D is a cross-sectional view of part VIIIa in Fig. 4, Fig. 8E is a cross-sectional view of part VIIIa in Fig. 4, Fig. 8F is a cross-sectional view of part VIIIa in Fig. 4, Fig. 8G is a cross-sectional view of part VIIIa in Fig. 4, Fig. 8H is a cross-sectional view of part VIIIa in Fig. 4, Fig. 8H is a cross-sectional view of part VIIIa in Fig. 4, Fig. 8I is a cross-sectional view of part VIIIa in Fig. 4, Fig. 8J ...I is a cross-sectional view of FIG. 8B is a view taken in the direction of arrow VIIIb in FIG. 8A, FIG. 8C is a schematic cross-sectional view of an intake port of a modified example, FIG. 9 is a diagram explaining the shape of each part when projected in the direction of the rotational axis of the vane rotor, FIG. 10 is a schematic cross-sectional view of line X-X in FIG. 6, FIG. 11 is a configuration diagram of the integrated pump device and parking lock mechanism, FIG. 12 is a diagram explaining the relationship between the rotational position of the vane and the position of the detent spring axis, FIG. 13 is an oblique view of the integrated pump device of the second embodiment, and FIG. 14 is a schematic axial cross-sectional view of the integrated pump device of the second embodiment.

[0015] The integrated pump device of the first and second embodiments will be described with reference to the drawings. The first and second embodiments are collectively referred to as "the present embodiment." The integrated pump device of the present embodiment is an integrated device comprising a motor unit, a pump unit, and a hydraulic actuator unit. The integrated pump device of the present embodiment is primarily installed in electric vehicles such as electric vehicles and hybrid vehicles, and has both a PLA (parking lock actuator) function and an EOP (electric oil pump) function. The PLA function switches the parking lock mechanism between a locked state and an unlocked state. The EOP function supplies oil for cooling or lubrication to an oil consumer such as an MG (motor generator).

[0016] More specifically, the integrated pump device of this embodiment is mounted on, for example, an autonomous electric vehicle. When a command to start or park the vehicle is received from the vehicle's host control device, the integrated pump device activates the parking lock mechanism. The integrated pump device also adjusts the amount of oil supplied to the MG based on the MG speed, load, and other factors while the vehicle is running with the parking lock mechanism unlocked.

[0017] 1 to 4 show the overall configuration of an integrated pump device 10 according to a first embodiment. The integrated pump device 10 is mainly composed of a motor unit 20, a pump unit 30, and a hydraulic actuator unit 60, which are integrally configured. In this embodiment, the motor unit 20 and the pump unit 30 are arranged coaxially with a common motor rotation axis O. The vane rotation axis Q of the hydraulic actuator unit 60 is arranged coaxially with or parallel to the motor rotation axis O. Power and signals are input from the outside via a connector 39 provided on a pump housing 31, which is the casing of the pump unit 30.

[0018] The motor unit 20 is configured, for example, by a three-phase brushless motor, and outputs driving force for forward and reverse rotation. The pump unit 30 is configured by a gear pump equipped with a pump gear 32 consisting of an internal gear 321 and an external gear 322. The pump unit 30 rotates (forward and reverse) by the driving force of the motor unit 20, and discharges oil drawn in from an intake port 67 to an outlet port 68. The hydraulic actuator unit 60 operates to switch between an advance state and a return state by hydraulic pressure supplied from the pump unit 30 via oil inlets 541 and 542.

[0019] Regarding the basic configuration of the integrated pump device 10, the hydraulic actuator unit 60 is composed of a rotary hydraulic actuator in which a vane rotor 63 rotates within a vane housing 61. The vane housing 61 is in the shape of a substantially cylindrical container having an axial end face 611 and an outer circumferential surface 612. The rotation axis of the vane rotor 63 is connected to a detent shaft (see FIG. 11) of a detent mechanism supported on the e-Axle case.

[0020] A spool valve 40, whose position is switched by the operating pressure of the pump unit 30, is provided as a selective shutoff valve that switches between the intake oil passage and the discharge oil passage when the pump unit 30 is rotating forward and reverse. The spool valve 40 is housed in a valve hole 34 formed in the pump housing 31 and is biased in one direction by a spring (not shown). When the operating pressure of the pump unit 30 is applied to the spool valve 40, the spool valve 40 moves against the biasing force of the spring.

[0021] In this embodiment, a pump plate 50 (see FIG. 7 ) having an oil intake passage 51 and oil inlets 541, 542 on the discharge side formed therein is provided between the pump housing 31 of the pump section 30 and the vane housing 61 of the hydraulic actuator section 60. In the first embodiment, the oil intake port 67 and the oil discharge port 68 are formed to open to an end face 611 of the vane housing 61 in the axial direction.

[0022] The flow of oil will be described with reference to Figure 2. Oil is drawn into the suction port 67 from the oil tank 91 via the suction filter 92 and other components. The oil drawn into the suction port 67 is pumped through the suction oil passage 51 of the pump plate 50 and the communication space within the spool valve 40 by the rotation of the pump gear 32. The pumped oil passes through the oil inlet port 541 or 542 of the pump plate 50 depending on the rotation direction of the pump unit 30, and is introduced into the vane chamber of the vane housing 61. For example, when the pump unit 30 rotates forward, the oil passes through the oil inlet port 542, and when the pump unit 30 rotates reverse, the oil is introduced through the oil inlet port 541.

[0023] The detailed internal configuration of the vane housing 61 will be described later with reference to Figures 5 and 6. When the vane rotor 63 is at a predetermined rotational position, oil is discharged from a discharge port 68 via a discharge opening at the bottom of one of the vane chambers, and is supplied to an oil consumer such as the MG97 or a reducer.

[0024] The overall configuration of the integrated pump device 10 will be explained further with reference to the axial cross-sectional view of Figure 4. When explaining the viewing directions in the following figures, the views from the left side of Figures 3 and 4 will be referred to as "views from the motor unit 20 side," and the views from the right side of Figures 3 and 4 will be referred to as "views from the detent mechanism side."

[0025] The motor section 20 includes a stator 22, a motor rotor 23, and a shaft 24 housed in a motor housing 21. A rotating magnetic field is generated by passing current through a three-phase winding wound around the stator 22. The motor rotor 23 has multiple magnetic poles arranged circumferentially, and rotates in accordance with the rotating magnetic field of the stator 22. The shaft 24, which is fixed to the motor rotor 23, rotates together with the motor rotor 23.

[0026] The pump gear 32 is housed in a pump chamber 33 of the pump housing 31. The end of the shaft 24 on the motor housing 21 side is supported by a bearing 215. The end of the shaft 24 on the pump section 30 side is connected to an internal gear 321 of the pump gear 32, and the driving force of the motor section 20 is transmitted from the shaft 24 to the internal gear 321. When the shaft 24 rotates, the internal gear 321 rotates inside the external gear 322, and the oil in the pump chamber 33 is pumped out.

[0027] A cylindrical protrusion 37 is provided in the center of the pump housing 31 on the side facing the motor unit 20, coaxially with the motor rotation axis O, and a circuit board seat 36 is recessed around the protrusion 37. An oil seal 246 is provided inside the protrusion 37 to seal off oil that leaks from the pump chamber 33 along the outer circumferential surface of the shaft 24 toward the motor unit 20. A circuit board 26 on which a control circuit that drives the motor unit 20 is mounted is installed on the circuit board seat 36.

[0028] Next, the operation of the vane rotor 63 in the rotary hydraulic actuator unit 60 will be described with reference to Figures 5 to 7 in addition to Figures 1 to 4. Figure 5 shows a cross section of the hydraulic actuator unit 60 as viewed from the detent mechanism side. Figure 6 shows a cross section of the hydraulic actuator unit 60 as viewed from the motor unit 20 side. Figure 7 shows the pump plate 50 provided between the housing 31 and the vane housing 61 as viewed from the motor unit 20 side.

[0029] The hydraulic actuator unit 60 includes a cylindrical vane housing 61 centered on the vane rotation axis Q, and a vane rotor 63 housed coaxially in the vane housing 61. The vane housing 61 has, for example, four vane chambers 621-624 inside. The vane chambers 621-624 each have a sector shape with an arc-shaped inner wall on the radially outer side. In the figure, the lead lines of the vane chambers 621-624 are drawn out from the radially outer inner wall.

[0030] The vane rotor 63 is provided with, for example, four vanes 641-644 corresponding to the vane chambers 621-624. A seal is provided on the sliding portion of the radial outer wall of each vane 641-644. Each vane 641-644 is rotatable in the circumferential direction in the corresponding vane chamber 621-624. Lead-side hydraulic chambers 651-654 are formed on one side of the circumferential direction of the vanes 641-644 in the vane chambers 621-624. Furthermore, return-side hydraulic chambers 661-664 are formed on the other side of the circumferential direction of the vanes 641-644. Although not shown, the lead-side hydraulic chambers 651-654 are connected to each other via distribution oil passages. Similarly, the return-side hydraulic chambers 661-664 are connected to each other via distribution oil passages.

[0031] A chamber bottom discharge opening 625 communicating with the discharge port 68 is formed at the bottom of one of the four vane chambers 621. The vane chamber 621 in which the chamber bottom discharge opening 625 is formed is referred to as the "first vane chamber," and the vane 641 housed in the first vane chamber 621 is referred to as the "first vane." In FIG. 6 , the vanes are arranged clockwise from the first vane chamber 621, namely, the second vane chamber 622, the third vane chamber 623, and the fourth vane chamber 624. Similarly, in FIG. 6 , the vanes are arranged clockwise from the first vane 641, namely, the second vane 642, the third vane 643, and the fourth vane 644. For example, the circumferential inner wall of the second vane chamber 622 and the circumferential outer wall of the second vane 642 function as stoppers that restrict the rotation range of the vane rotor 63.

[0032] The hydraulic actuator unit 60 operates to switch between an advance state and a return state by hydraulic pressure supplied from the pump unit 30 via the oil inlets 541, 542 of the pump plate 50. When hydraulic pressure is supplied to the advance hydraulic chambers 651-654, the vane rotor 63 rotates in one direction (counterclockwise in FIG. 6) to enter the advance state. When hydraulic pressure is supplied to the return hydraulic chambers 661-664, the vane rotor 63 rotates in the other direction (clockwise in FIG. 6) to enter the return state. The upper diagram in FIG. 6 corresponds to the advance state, and the lower diagram in FIG. 6 and FIG. 5 correspond to the return state. The rotational operating angle is represented as θr.

[0033] Here, the terms "advance state" and "return state" are merely terms used to conveniently distinguish between two opposing polar states, and either state may be defined as the advance state or the return state. In this specification, the advance state of the vane rotor 63 corresponds to the P position, and the return state of the vane rotor 63 corresponds to the not P position. The hydraulic actuator unit 60 locks the parking lock mechanism 80 in the advance state, and unlocks the parking lock mechanism 80 in the return state.

[0034] When the vane rotor 63 is in the returning state, the chamber bottom discharge opening 625 of the first vane chamber 621 is opened, and oil is discharged from the return-side hydraulic chamber 661 to the discharge port 68. The discharged oil is supplied to the MG97 via an oil passage in the e-Axle case.

[0035] Next, a description will be given of the characteristic configuration of the integrated pump device 10 of this embodiment. In the integrated pump device 10 of this embodiment, the pump section 30 and the hydraulic actuator section 60 are integrally configured, and an intake port 67 and an outlet port 68 are formed in the vane housing 61 of the hydraulic actuator section 60. This allows the size of the integrated pump device 10 to be reduced. In particular, in the first embodiment, the intake port 67 and the outlet port 68 are formed to open to the axial end surface 611 of the vane housing 61. This allows the radial size of the integrated pump device 10 to be further reduced.

[0036] Furthermore, in the integrated pump device 10 of this embodiment, the chamber bottom discharge opening 625 is switched between closed and open states depending on the operating angle of the first vane 641 in the first vane chamber 621, and the opening area in the open state also changes. This allows the oil supply from the discharge port 68 to be stopped or started. Furthermore, the discharge flow rate can be adjusted with a simple configuration that does not require a separate component such as a flow control valve.

[0037] Intake port 67 forms an oil passage that communicates with pump section 30. As shown in Figures 5 and 6, intake port 67 is located between two circumferentially adjacent vane chambers 622, 623 in vane housing 61. By utilizing the circumferential space between adjacent vane chambers and locating intake port 67 in a radial range equal to or smaller than the inner diameters of vane chambers 621-624, the radial size of integrated pump device 10 can be reduced.

[0038] The suction port 67 also has a cylindrical connection end 671. In the first embodiment, the connection end 671 protrudes from the axial end surface 611 of the vane housing 61. As shown in FIGS. 1 and 2 , the inner and outer peripheral walls of the connection end 671 are both cylindrical. As shown by the dashed line in FIG. 4 , the inner peripheral wall of the connection end 671 is fitted with the outer peripheral wall of a mating part, such as the suction port connecting pipe 927 of the suction filter 92 (see FIG. 2 ). Providing the protruding cylindrical connection end 671 improves the ease of fitting and positioning when fitting with the mating part.

[0039] Similarly, the discharge port 68 also has a cylindrical connecting end 681 that protrudes from the axial end face 611 of the vane housing 61. The inner peripheral wall of the connecting end 681 is fitted with the outer peripheral wall of a discharge port connecting pipe that relays the discharge oil passage between, for example, the integrated pump device 10 and the e-Axle case. As with the connecting end 671 of the suction port 67, this improves workability and positioning during fitting.

[0040] 8A and 8B, the shape of the suction port 67 will be described. Inside the vane housing 61, the suction port 67 is connected to an inlet-side oil passage 673 and a pump-side oil passage 674 in a stepped configuration. In this example, the radial cross-sectional shapes of the inlet-side oil passage 673 and the pump-side oil passage 674 are both circular, and the diameter of the pump-side oil passage 674 is larger than the diameter of the inlet-side oil passage 673. Therefore, the opening area of ​​the suction port 67 on the pump side is larger than the opening area on the inlet side.

[0041] When switching from the not P position to the P position in response to a command from the vehicle's higher-level control device, the rotation direction of the pump unit 30 is reversed, and the generated operating pressure operates the spool valve 40. At this time, oil near the inlet of the spool valve 40 flows back into the suction port 67. The above-described shape of the suction port 67 makes it possible to control the pressure loss in the oil passage when oil flows back, thereby increasing the switching operating pressure of the spool valve 40. This improves switching response when the parking lock is engaged.

[0042] In order to increase pressure loss during oil backflow, it is preferable that the opening area of ​​the suction port 67 increase rapidly. In the example of Fig. 8A, the opening area increases stepwise at the connection between the inlet-side oil passage 673 and the pump-side oil passage 674. However, as in the modified example shown in Fig. 8C, the connection between the inlet-side oil passage 673 and the pump-side oil passage 674 may be tapered, so that the opening area of ​​the suction port 67 increases gradually. Furthermore, the radial cross-sectional shapes of the inlet-side oil passage 673 and the pump-side oil passage 674 are not limited to being circular, and may be oval, rounded rectangle, or the like.

[0043] 9, which is an enlarged view of FIG. 6 with additional lines added, will be used to describe the shape of each part of the vane rotor 63 when viewed in a projection in the direction of the rotational axis. Each additional line is drawn so as to extend radially from the rotational axis Q, in other words, in a radial direction centered on the rotational axis Q. Hereinafter, the "radial direction centered on the rotational axis Q" will be understood to include a range of manufacturing variation that is common sense in the technical field.

[0044] The bottom discharge opening 625 of the first vane chamber 621 is neither circular nor elliptical, but has a shape having a straight side hr extending radially from the rotation axis Q and an arc-shaped side hθ extending circumferentially. The circumferential outer wall vo1 of the first vane 641 extends radially around the rotation axis Q. When the first vane 641 rotates, the circumferential outer wall vo1 of the first vane 641 overlaps the radial side hr of the bottom discharge opening 625 at the opening / closing boundary of the bottom discharge opening 625. This makes it possible to maximize the opening area of ​​the bottom discharge opening 625 when discharging oil.

[0045] Furthermore, for example, the circumferential inner wall vi2 of the second vane chamber 622 and the circumferential outer wall vo2 of the corresponding second vane 642 function as stoppers that restrict the rotation range of the vane rotor 63. In other words, the position where the circumferential outer wall vo2 of the second vane 642 abuts against the circumferential inner wall vi2 of the second vane chamber 622 is the operating limit of the vane rotor 63. Here, the circumferential inner wall vi2 of the second vane chamber 622 and the circumferential outer wall vo2 of the corresponding second vane 642 extend in the radial direction centered on the rotation axis Q. This makes it possible to maximize the operating range of the vane rotor 63.

[0046] 6, 7, and 10, the shape of the circumferential inner wall of the first vane chamber 621 will be described. Two oil inlets 541, 542 formed in the pump plate 50 communicate with the advance hydraulic chamber 651 and the return hydraulic chamber 661, respectively, from the opening surface of the first vane chamber 621. In Figure 10, when oil is supplied from the oil inlet 542 to the return hydraulic chamber 661, the first vane 641 moves from the P position indicated by the dashed line to the not P position indicated by the solid line.

[0047] The circumferential inner walls on both sides of the first vane chamber 621 are formed as inclined walls 626 that slope inward in the circumferential direction from the opening surface toward the bottom. This reduces pressure loss in the discharge oil passage. Furthermore, reducing the oil filling volume improves switching response. Furthermore, when the vane housing 61 is manufactured using a mold, it also improves mold releasability.

[0048] 11 and 12, the relationship between the operation of the vane rotor 63 and the operation of the parking lock mechanism 80 will be described. Fig. 11 shows an example of a system configuration. The parking lock mechanism 80 includes a detent mechanism including a detent shaft 81, a detent plate 82, a detent spring 83, and a detent roller 84, as well as a parking rod 85, a cone 86, a parking lock pole 87, a parking gear 88, etc.

[0049] The detent mechanism switches between a P position and a not-P position according to the output of the hydraulic actuator unit 60. A detent shaft 81 is connected to the rotary shaft of the vane rotor 63 of the hydraulic actuator unit 60, and rotates in both directions within a predetermined angular range according to the operation of the vane rotor 63. A detent plate 82 is fixed to the detent shaft 81 and rotates together with the detent shaft 81.

[0050] For example, in a two-position detent mechanism, the detent plate 82 has two valleys 821, 822 and a peak 825 on its radially outer edge. The valley 821 is a "P valley" corresponding to the P position, and the valley 822 is a "not P valley" corresponding to the not P position. The peak 825 is disposed between the valleys 821 and 822. In other configuration examples, a detent mechanism with three or more positions, including a P position and a not P position, may be used. Generalizing to include detent mechanisms with three or more positions, the detent plate has "multiple valleys" and "one or more peaks" on its radially outer edge.

[0051] The detent roller 84, supported on the tip of the detent spring 83, fits into one of the two valleys 821, 822 due to the elastic force of the detent spring 83. When a rotational force greater than a predetermined value is applied to the detent plate 82, the detent spring 83 elastically deforms, and the detent roller 84 moves from one valley to the other, overcoming the peak 825. This switches between the P position and the not P position.

[0052] The parking rod 85 is formed in a generally L-shape, and one end 851 is fixed to the detent plate 82. A cone 86 is provided on the other end 852 of the parking rod 85, the diameter of which decreases as it approaches the other end 852. When the detent plate 82 rotates in a direction in which the detent roller 84 fits into the valley portion 821, the cone 86 moves in the direction of arrow P. When the detent plate 82 rotates in a direction in which the detent roller 84 fits into the valley portion 822, the cone 86 moves in the direction of arrow notP.

[0053] The parking lock pole 87 abuts against the conical surface of the cone 86 and is capable of swinging around a shaft 877. The parking lock pole 87 is provided with a protrusion 878 that can mesh with a parking gear 88. When the cone 86 moves in the direction of arrow P, the parking lock pole 87 is pushed up, and the protrusion 878 meshes with the parking gear 88, thereby establishing a locked state. When the cone 86 moves in the direction of arrow not P, the protrusion 878 separates from the parking gear 88, and the locked state is released.

[0054] 12 illustrates the relationship between the rotational position of the vane rotor 63, more specifically, the rotational position of the first vane 641 in the first vane chamber 621, and the position of the detent roller 84 on the detent plate 82. The vane rotor 63 in the lower diagram is shown as viewed from direction R in FIG. 11. The detent plate 82 in the upper diagram is shown as viewed from direction D in FIG. 11. In reality, the detent plate 82 rotates, but for ease of explanation, the detent plate 82 is shown fixed and the detent roller 84 is shown as moving relatively in the direction opposite to the rotational direction of the detent plate 82. This makes it easier to understand the correspondence between the operations in the upper and lower diagrams.

[0055] In the lower diagram, the left side of the first vane 641 in the first vane chamber 621 is the return hydraulic chamber 661, and the right side of the first vane 641 is the advance hydraulic chamber 651. The hydraulic pressure Po introduced into the return hydraulic chamber 661 acts on the side wall of the first vane 641, causing the vane rotor 63 to rotate counterclockwise. As the first vane 641 rotates from the advance state to the return state, the chamber bottom discharge opening 625 transitions from a closed state to an open state.

[0056] In the detent plate 82 in the upper diagram, the valley 821 on the left side of the peak 825 is a P valley, and the valley 822 on the right side is a not-P valley. A wall 827 on the left side of the valley 821 is a P wall, and a wall 828 on the right side of the valley 822 is a not-P wall. The symbol R in the circle represents the vane rotor 63. As the vane rotor 63 rotates, the detent roller 84 provided on the detent spring 83 moves relatively from the P valley to the not-P valley.

[0057] In State 1, where the first vane 641 is in the advanced state, the detent roller 84 fits into the valley 821 of the P valley, and the parking lock mechanism 80 is locked. When the vane rotor 63 rotates counterclockwise, in State 2, the detent roller 84 moves up from the valley 821 toward the peak 825.

[0058] When vane rotor 63 further rotates counterclockwise, in State 3, detent roller 84 climbs over peak 825 and begins to fall toward valley 822 of the notP valley. At this time, bottom discharge opening 625 is at the boundary where it transitions from closed to open. In other words, from the point where detent roller 84 begins to fall toward valley 822 due to the elastic force of detent spring 83, it is no longer necessary for first vane 641 to close bottom discharge opening 625.

[0059] Between State 3 and State 4, the first vane 641 approaches the return state, and the chamber bottom discharge opening 625 gradually opens. As indicated by the dashed arrow, oil in the return-side hydraulic chamber 661 is discharged from the opened chamber bottom discharge opening 625 to the discharge port. The detent roller 84 moves from the peak 825 toward the valley 822 of the notP valley. In State 4, the detent roller 84 fits into the valley 822 of the notP valley, and the parking lock mechanism 80 is unlocked.

[0060] In this way, the vane housing 61 has the bottom discharge opening 625 disposed within the operating angle range of the vane rotor 63 in which the detent roller 84 moves from the peaks 825 to the valleys 822. By determining the location of the bottom discharge opening 625 in accordance with the torque characteristics of the detent mechanism, it is possible to optimize the timing of switching between the PLA function and the EOP function.

[0061] Second Embodiment An integrated pump device 10B according to a second embodiment will be described with reference to Figures 13 and 14. The second embodiment differs from the first embodiment in the opening directions of the suction port 67 and the discharge port 68 in the vane housing 61, but the rest of the configuration is the same. Figures 13 and 14 correspond to Figures 1 and 4 of the first embodiment, respectively. In the second embodiment, components that are essentially the same as those in the first embodiment are designated by the same reference numerals, and their description will be omitted. In the integrated pump device 10B according to the second embodiment, the suction port 67 is formed to open to the outer peripheral surface 612 of the vane housing 61. A connection end 671 protrudes from the outer peripheral surface 612 of the vane housing 61. The suction oil passage inside the vane housing 61 is formed in an L-shape.

[0062] 13 and 14 , the discharge port 68 is formed to open to the axial end surface 611 of the vane housing 61, as in the first embodiment. However, instead of or in addition to the suction port 67, the discharge port 68 may be formed to open to the outer peripheral surface 612 of the vane housing 61. In other words, at least one of the suction port 67 and the discharge port 68 may be formed to open to the outer peripheral surface 612 of the vane housing 61.

[0063] (Other Embodiments) (a) The number of vane chambers in the vane housing 61 and the number of vanes in the vane rotor 63 are not limited to four. However, the configuration in which "the suction port 67 is formed between two circumferentially adjacent vane chambers" is premised on the fact that the vane housing 61 has two or more vane chambers. In a configuration with one vane chamber, the suction port 67 is formed in a circumferential position other than the vane chamber. Furthermore, in a configuration with one vane chamber, the circumferential inner wall of the first vane chamber 621, in which the chamber bottom discharge opening 625 is formed, and the circumferential outer wall of the first vane 641 also function as a stopper.

[0064] (b) In the above embodiment, as shown in Figure 4, the connection end 671 of the suction port 67 has a cylindrical inner peripheral wall into which the outer peripheral wall of the suction port connecting pipe 927 of the mating part is fitted. In other embodiments, the connection end 671 of the suction port 67 may have a cylindrical outer peripheral wall into which the inner peripheral wall of the suction port connecting pipe of the mating part is fitted. Furthermore, the outer peripheral wall or inner peripheral wall of the connection end 671 on the side not used for fitting with the suction port connecting pipe of the mating part does not necessarily have to be cylindrical. In other words, it is sufficient that at least one of the inner peripheral wall or outer peripheral wall of the connection end 671 is cylindrical.

[0065] (c) The integrated pump device 10 of the present disclosure is not limited to applications that operate the parking lock mechanism 80 of an electric vehicle and supply cooling or lubricating oil to the MG 97. The target of the rotational output of the hydraulic actuator unit 60 may be any mechanism that can be switched between an advance state and a return state. The target of the oil supply from the hydraulic actuator unit 60 may be any oil consumer.

[0066] As described above, the present disclosure is not limited to the above-described embodiment, and can be implemented in various forms without departing from the spirit of the present disclosure.

[0067] (Disclosure of Technical Ideas) This specification discloses multiple technical ideas described in the following multiple clauses. Some clauses may be described in a multiple dependent form, with the subsequent clause alternatively referring to the preceding clause. Furthermore, some clauses may be described in a multiple dependent form, with the subsequent clause referring to another multiple dependent clause. These multiple dependent clauses define multiple technical ideas.

[0068] (Technical Idea 1) A motor unit (20), a pump unit (30) that rotates by the driving force of the motor unit and discharges oil drawn in from a suction port (67) to a discharge port (68), and a hydraulic actuator unit (60) that operates to switch between an advance state and a return state by hydraulic pressure supplied from the pump unit via oil inlets (541, 542), wherein the hydraulic actuator unit comprises: a vane housing (61) in which the suction port and the discharge port are formed and which has one or more vane chambers (621-624) therein; and a vane rotor (63) that is housed in the vane housing and has one or more vanes (641-644) corresponding to the vane chambers, wherein advance-side hydraulic chambers (651-654) are formed on one side of the circumferential direction of the vanes in the vane chambers, and return-side hydraulic chambers (661-664) are formed on the other side of the circumferential direction of the vanes, An integrated pump device in which, when hydraulic pressure is supplied to the advance-side hydraulic chamber, the vane rotor rotates in one direction to enter the advance state, and when hydraulic pressure is supplied to the return-side hydraulic chamber, the vane rotor rotates in the other direction to enter the return state, and a chamber-bottom discharge opening (625) communicating with the discharge port is formed in the bottom of a first vane chamber (621), which is one of the vane chambers, and the chamber-bottom discharge opening has an opening area that changes depending on the operating angle of a first vane (641) housed in the first vane chamber. (Technical Concept 2) The integrated pump device according to Technical Concept 1, in which the vane housing has two or more vane chambers, and the suction port is disposed between two circumferentially adjacent vane chambers (622, 623) in the vane housing, forming an oil passage communicating with the pump section. (Technical Concept 3) The integrated pump device according to Technical Concept 2, in which the suction port has a cylindrical connecting end (671), and at least one of the inner circumferential wall or the outer circumferential wall of the connecting end is cylindrical. (Technical Concept 4) The integrated pump device according to Technical Concept 2, wherein the suction port has an opening area on the pump section side that is larger than the opening area on the inlet side.(Technical Idea 5) The hydraulic actuator unit locks a parking lock mechanism (80) of the vehicle in the advancing state and unlocks the parking lock mechanism in the returning state, the parking lock mechanism having a detent plate (82) having a plurality of valleys (821, 822) and one or more peaks (825) on its radial outer edge, which rotates within a predetermined angular range together with a detent shaft (81) connected to the rotary shaft of the vane rotor, and a detent roller (84) fits into one of the valleys due to the elastic force of a detent spring (83), the vane housing having the chamber bottom discharge opening arranged within the operating angle range of the vane rotor where the detent roller moves from the peak to the valley. (Technical Idea 6) The integrated pump device according to any one of Technical Ideas 1 to 5, wherein, in a projection view in the direction of the rotational axis of the vane rotor, the chamber bottom discharge opening of the first vane chamber has a side (hr) extending radially from the rotational axis of the vane rotor, and a circumferential outer wall (vo1) of the first vane (641) extends radially around the rotational axis, and a circumferential inner wall (vi2) of any of the vane chambers (622) functioning as a stopper for regulating the rotation range of the vane rotor and a circumferential outer wall (vo2) of the corresponding vane (642) extend radially around the rotational axis. (Technical Idea 7) The integrated pump device according to any one of Technical Ideas 1 to 6, wherein the two oil inlets communicate with the advance hydraulic chamber (651) and the return hydraulic chamber (661), respectively, from the opening surface of the first vane chamber, and wherein circumferential inner walls on both sides of the first vane chamber are formed as inclined walls (626) that incline circumferentially inward from the opening surface toward the bottom. (Technical Idea 8) The integrated pump device according to any one of Technical Ideas 1 to 7, wherein the suction port and the discharge port are formed to open on an axial end surface (611) of the vane housing. (Technical Idea 9) The integrated pump device according to any one of Technical Ideas 1 to 7, wherein at least one of the suction port or the discharge port is formed to open on an outer peripheral surface (612) of the vane housing.

[0069] The present disclosure has been described based on the embodiments. However, the present disclosure is not limited to the embodiments and structures. The present disclosure also encompasses various modifications and variations within the scope of equivalents. Furthermore, various combinations and forms, including only one element, more than one element, or less than one element, are also within the scope and spirit of the present disclosure.

Claims

1. Motor section (20) and A pump unit (30) rotates due to the driving force of the motor unit and discharges oil drawn in from the intake port (67) to the discharge port (68), A hydraulic actuator unit (60) is operated by hydraulic pressure supplied from the pump unit via the oil inlets (541, 542) to switch between a forward state and a reverse state, It is composed as a single unit. The aforementioned hydraulic actuator section is A vane housing (61) having the aforementioned intake port and discharge port formed therein and having one or more vane chambers (621-624) inside, The system comprises a vane rotor (63) housed in the vane housing and provided with one or more vanes (641-644) corresponding to the vane chambers, In the vane chamber, a forward hydraulic chamber (651-654) is formed on one side in the circumferential direction of the vane, and a return hydraulic chamber (661-664) is formed on the other side in the circumferential direction of the vane. When hydraulic pressure is supplied to the forward-side hydraulic chamber, the vane rotor rotates in one direction to enter the forward state, and when hydraulic pressure is supplied to the return-side hydraulic chamber, the vane rotor rotates in the other direction to enter the return state. A chamber bottom discharge opening (625) communicating with the discharge port is formed at the bottom of the first vane chamber (621), which is one of the vane chambers. The two oil inlets communicate with the forward hydraulic chamber (651) and the return hydraulic chamber (661), respectively, from the opening surface of the first vane chamber. The circumferential inner walls on both sides of the first vane chamber are formed as inclined walls (626) that slope inward in the circumferential direction from the opening surface towards the bottom. The discharge opening at the bottom of the chamber is an integrated pump device in which the opening area changes according to the operating angle of the first vane (641) housed in the first vane chamber.

2. The vane housing has two or more vane chambers, The integrated pump device according to claim 1, wherein the intake port is located between two circumferentially adjacent vane chambers (622, 623) in the vane housing and forms an oil passage communicating with the pump section.

3. The integrated pump device according to claim 2, wherein the suction port has a cylindrical connecting end (671), and at least one of the inner circumferential wall or outer circumferential wall of the connecting end is cylindrical.

4. The integrated pump device according to claim 2, wherein the opening area on the pump side of the suction port is larger than the opening area on the inlet side.

5. The hydraulic actuator locks the vehicle's parking lock mechanism (80) in the forward position and unlocks the parking lock mechanism in the return position. The parking lock mechanism includes a detent mechanism in which a detent plate (82) having a plurality of valleys (821, 822) and one or more peaks (825) on its radially outer edge rotates within a predetermined angular range together with a detent shaft (81) connected to the rotation axis of the vane rotor, and a detent roller (84) engages with one of the valleys due to the elastic force of a detent spring (83). The integrated pump device according to claim 1, wherein the vane housing has a chamber bottom discharge opening positioned within the operating angle range of the vane rotor, where the detent roller moves from the peak to the valley.

6. In the projection view of the vane rotor in the direction of the rotation axis, The discharge opening at the bottom of the first vane chamber has a side (hr) extending radially from the rotation axis of the vane rotor, and the circumferential outer wall (vo1) of the first vane (641) extends radially around the rotation axis, and The integrated pump device according to claim 1, wherein the circumferential inner wall (vi2) of any of the vane chambers (622) that functions as a stopper for restricting the rotation range of the vane rotor, and the circumferential outer wall (vo2) of the corresponding vane (642) extend radially around the axis of rotation.

7. The integrated pump device according to any one of claims 1 to 6, wherein the intake port and the discharge port are formed to open to the axial end face (611) of the vane housing.

8. The integrated pump device according to any one of claims 1 to 6, wherein at least one of the intake port or the discharge port is formed to open to the outer peripheral surface (612) of the vane housing.