Integrated pump device

Abstract

An integrated pump device forms a module in which a motor (10), an oil pump (30) that rotates using a driving force of the motor (10), and a hydraulic actuator (60) that operates using hydraulic pressure supplied from the oil pump (30) are integrated. The hydraulic actuator (60) includes a housing (61) having one or more vane chambers (621 to 624) and a vane rotor (63) housed in the housing (61) and provided with one or more vanes (641 to 644) corresponding to the vane chambers. An advance-side hydraulic chamber (651 to 654) is formed on one circumferential side of the vanes in the vane chamber, and a return-side hydraulic chamber (661 to 664) is formed on the other circumferential side of the vanes. When hydraulic pressure is supplied to the advance-side hydraulic chamber (651 to 654), the vane rotor (63) rotates in one direction to become an advance state, and when hydraulic pressure is supplied to the return-side hydraulic chamber (661 to 664), the vane rotor (63) rotates in the other direction to become a return state.

Description

[0001] Cross-reference to related applications

[0002] This application is based on Japanese Patent Application No. 2020-209129, filed on December 17, 2020, the contents of which are incorporated herein by reference. Technical Field

[0003] This invention relates to integrated pump devices. Background Technology

[0004] Previously, hydraulic systems integrating a motor, an electric oil pump, and a hydraulic actuator were known. For example, the automotive hydraulic system disclosed in Patent Document 1 integrates a motor, an electric oil pump, a hydraulic parking lock actuator, and a clutch engagement control circuit. When the motor rotates forward, the hydraulic parking lock actuator and clutch are activated. When the motor rotates in reverse, oil for cooling the electric generator is supplied from the oil pump.

[0005] Existing technical documents

[0006] Patent documents

[0007] Patent Document 1: International Publication No. 2020 / 043235 Summary of the Invention

[0008] In the hydraulic system of Patent Document 1, a cylinder-type hydraulic parking lock actuator is used, in which a piston reciprocates within the cylinder. Therefore, the volume required to ensure the pressure area and stroke length is increased.

[0009] The purpose of this disclosure is to provide an integrated pump device that miniaturizes a hydraulic actuator that is integrated with a motor and an electric oil pump.

[0010] The integrated pump device disclosed herein forms a module that integrates a motor, an oil pump, and a hydraulic actuator. Here, in an integrated pump device mounted, for example, in an automobile, the "integrated module" is not necessarily delivered to the automobile manufacturer as a single component. The case where it is delivered as a component and forms an integrated structure after installation in the automobile should also be interpreted as being included within the "integrated module."

[0011] The oil pump rotates using the driving force of a motor, discharging oil drawn in from the oil pan. The hydraulic actuator operates using hydraulic pressure supplied from the oil pump to switch between forward and return states. In one aspect of this disclosure, the hydraulic actuator is a parking lock actuator that actuates the vehicle's parking lock mechanism.

[0012] The hydraulic actuator comprises: a housing having one or more blade chambers; and a blade rotor housed in the housing and provided with one or more blades corresponding to the blade chambers.

[0013] The blades are capable of rotating circumferentially within their respective blade chambers. A forward hydraulic chamber is formed on one side of the blade's circumferential direction, and a return hydraulic chamber is formed on the other side. When oil is supplied to the forward hydraulic chamber, the blade rotor rotates in one direction to enter the forward state; when oil is supplied to the return hydraulic chamber, the blade rotor rotates in the other direction to enter the return state.

[0014] The actuating force of a hydraulic actuator is determined by the product of the pressure-bearing area and the hydraulic pressure. In this disclosure, by using a rotary hydraulic actuator, the pressure-bearing area can be ensured using more than one blade, thus miniaturizing the hydraulic actuator. Therefore, it can be used particularly effectively as a hydraulic actuator for applications such as parking lock actuators where mounting space is limited. Attached Figure Description

[0015] The above-mentioned objects, other objects, features, and advantages of this disclosure will become more apparent from the following detailed description with reference to the accompanying drawings. The accompanying drawings are:

[0016] Figure 1 This is a basic structural diagram of the integrated pump device in this embodiment;

[0017] Figure 2 These are structural diagrams of the integrated pump device and parking lock mechanism according to the first to sixth embodiments;

[0018] Figure 3 This is a diagram showing the appearance of the rotary hydraulic actuator and the flow of oil in the first, third, and fifth embodiments;

[0019] Figure 4 This refers to the unlocking (return state) and locking (forward state) states in the first, third, and fifth embodiments. Figure 3 Sectional view along line IV-IV;

[0020] Figure 5 This is a hydraulic path diagram of the first embodiment when the lock is released (return state);

[0021] Figure 6 This is a hydraulic path diagram of the first embodiment when locked (forward state);

[0022] Figure 7 This is a diagram showing the appearance of the rotary hydraulic actuator and the flow of oil in the second, fourth, and sixth embodiments;

[0023] Figure 8 This refers to the unlocking (return state) and locking (forward state) states in the second, fourth, and sixth embodiments. Figure 7 Sectional view along line VIII-VIII;

[0024] Figure 9This is a hydraulic path diagram for the second embodiment when the lock is released (return state);

[0025] Figure 10 This is a hydraulic path diagram of the second embodiment when locked (forward state);

[0026] Figure 11 This is a hydraulic path diagram for the third embodiment when the lock is released (return state);

[0027] Figure 12 This is the hydraulic path diagram of the third embodiment when locked (forward state);

[0028] Figure 13 This is a hydraulic path diagram for the fourth embodiment when the lock is released (return state);

[0029] Figure 14 This is the hydraulic path diagram for the fourth embodiment when locked (forward state);

[0030] Figure 15 This is a hydraulic path diagram for the fifth embodiment when the lock is released (return state);

[0031] Figure 16 This is the hydraulic path diagram for the fifth embodiment when locked (forward state);

[0032] Figure 17 This is a hydraulic path diagram for the sixth embodiment when the lock is released (return state);

[0033] Figure 18 This is the hydraulic path diagram for the sixth embodiment when locked (forward state);

[0034] Figure 19 This is a structural diagram of an integrated pump unit and parking lock mechanism using a cylinder hydraulic actuator, based on the reference method. Detailed Implementation

[0035] Hereinafter, several embodiments of the integrated pump device of this disclosure will be described based on the accompanying drawings. In the various embodiments, substantially the same structures are labeled with the same reference numerals and descriptions are omitted. The first to sixth embodiments are collectively referred to as "this embodiment". The integrated pump device of this embodiment is formed as a module that integrates a motor, an electric oil pump, and a hydraulic actuator into one unit.

[0036] exist Figure 1 The figure shows the basic structure common to the integrated pump device 90 of this embodiment. The integrated pump device 90 integrates the motor 10, the oil pump 30, and the hydraulic actuator 60 into one unit. In the figure, the motor is labeled "M" and the electric oil pump is labeled "EOP".

[0037] Oil pump 30 is an electric oil pump that is driven by motor 10 to rotate and discharge oil drawn from oil pan.

[0038] The hydraulic actuator 60 is actuated by hydraulic pressure supplied from the oil pump 30 to switch between forward and return states. Here, "forward state" and "return state" are merely convenient terms to distinguish between two opposing states, and either state can be defined as either forward or return.

[0039] The hydraulic actuator 60 in this embodiment is a parking lock actuator that actuates the parking lock mechanism 80 of the vehicle. The hydraulic actuator 60 provides actuation force by locking the parking lock mechanism 80 in the forward state and unlocking it in the return state. Activating the gear to P (Park) is equivalent to locking, and activating the gear to a non-P (Unlocked) position is equivalent to unlocking. Here, non-P is a single gear in a two-position configuration. Furthermore, in configurations including multi-speed transmissions, all gears other than P can be uniformly interpreted as non-P.

[0040] <First Implementation Method>

[0041] Hereinafter, the reference numerals for the integrated pump device in each embodiment will be designated as "901" to "906" corresponding to the embodiment numbers. First, refer to... Figures 2-6 The first embodiment will be described. Figure 2 The image shows an integrated pump device 901 and a parking lock mechanism 80 according to the first embodiment. The integrated pump device 901 uses a cylindrical rotary hydraulic actuator 60, and the motor 10, oil pump 30, and hydraulic actuator 60 are integrated into one unit. Figure 2 In the example, the three are arranged coaxially and in series to form a whole, but they can also be arranged in series with the axis off-axis to form a whole, or they can be arranged side by side to form a whole.

[0042] The parking lock mechanism 80 includes a stop shaft 81, a stop plate 82, a stop spring 83, a switching lever 84, a parking lever 85, a cone 86, a parking lock pawl 87, and a parking gear 88. The stop shaft 81 is the output shaft of the hydraulic actuator 60, which rotates in two directions within a specified angle range through the action of the hydraulic actuator 60. The stop plate 82 is fixed to the stop shaft 81 and rotates together with the stop shaft 81.

[0043] Multiple recesses 823 are formed on the side of the stop plate 82 near the stop spring 83. If a specified or greater rotational force is applied to the stop plate 82, the stop spring 83 elastically deforms, and the stop roller 833 at its front end engages with any one of the recesses 823, thereby restricting the rotation of the stop plate 82. A pin 824 protruding from the surface of the stop plate 82 engages with a slot formed at the front end of the switching rod 84. Furthermore, the pin 824 and the switching rod 84... Figure 19 The reference method shown is used, but may not be present in the first embodiment.

[0044] The parking lever 85 is roughly L-shaped, with one end 851 fixed to the stop plate 82. At the other end 852 of the parking lever 85, a cone 86 is provided, its diameter decreasing as it approaches the other end 852. If the stop plate 82 rotates in a direction that causes the stop roller 833 to be inserted into the recess corresponding to the P position, the cone 86 moves in the direction of arrow P.

[0045] The parking lock pawl 87 abuts against the conical surface of the cone 86 and can swing about the shaft 877. A protrusion 878 is provided on the parking lock pawl 87 that can mesh with the parking gear 88. If the cone 86 moves in the direction of arrow P, the parking lock pawl 87 is pushed up, and the protrusion 878 meshes with the parking gear 88, locking the vehicle. If the cone 86 moves in a direction other than arrow P, the protrusion 878 disengages from the parking gear 88, and the locking state is released.

[0046] Next, refer to Figure 3 , Figure 4 An example of the structure of the rotary hydraulic actuator 60 will be described. Figure 3 , Figure 4 The structure is also applicable in the third and fifth embodiments described later. Figure 4 The upper side shows the completed action status when shifting gears from P to unlocking / locking in non-P gear. Figure 4 The lower side shows the completed action state when shifting gears from non-P gear to P gear locking.

[0047] The hydraulic actuator 60 has a cylindrical housing 61 centered on a rotation axis O and a bladed rotor 63 coaxially housed within the housing 61. The housing 61 has, for example, four bladed chambers 621-624 in the circumferential direction. The inner walls of the bladed chambers 621-624 are formed in an arcuate fan shape on their radially outer sides. In the figure, the reference numerals for the bladed chambers 621-624 extend from the radially outer inner walls.

[0048] The vane rotor 63 has four vanes 641-644 on its outer periphery, corresponding to vane chambers 621-624. One of the vanes 641 has stop portions 645 and 646 at both circumferential ends to limit rotation; these stop portions are larger than the other three vanes 642, 643, and 644. To ensure the volume of the hydraulic chamber, the other three vanes 642, 643, and 644 are smaller. Sealing material is provided on the sliding portion of the radial outer wall of each vane 641-644.

[0049] Each blade 641-644 is capable of circumferential rotation within its corresponding blade chamber 621-624. A forward-side hydraulic chamber 651-654 is formed on one side of the circumferential direction of the blades 641-644 within the blade chambers 621-624. A return-side hydraulic chamber 661-664 is formed on the other side of the circumferential direction of the blades 641-644. Although not shown, the forward-side hydraulic chambers 651-654 are connected to a common forward-side port via distribution oil passages. Similarly, the return-side hydraulic chambers 661-664 are connected to a common return-side port via distribution oil passages.

[0050] exist Figure 4 When the upper side of the vehicle is released from lock, hydraulic pressure is supplied to the return-side hydraulic chambers 661-664, which are marked with dashed lines. This causes the blade rotor 63 to rotate counter-clockwise as shown in the figure, returning to the return state, and the parking lock mechanism 80 is released. Oil is discharged from the forward-side hydraulic chambers 651-654. Figure 3 The double-dotted arrow schematically represents the flow of oil at this time.

[0051] exist Figure 4 When locked as shown on the lower side, hydraulic pressure is supplied to the forward hydraulic chambers 651-654, which are marked with dashed lines. This causes the blade rotor 63 to rotate clockwise as shown in the figure, entering the forward position, and the parking lock mechanism 80 is locked. Oil is discharged from the return hydraulic chambers 661-664. Figure 3 The single-dot dashed arrow schematically represents the oil flow at this time.

[0052] Next, refer to Figure 5 , Figure 6 The oil pump 30 is connected to the electric generator 39 via direct oil supply lines 35 and 38, which branch off from the oil line supplying hydraulic pressure to the hydraulic actuator 60. In the figures and the following description, the electric generator is designated "MG". MG39 is equivalent to an "oil consumer" that supplies oil from the oil pump 30. Specifically, oil is sprayed into the open space to cool the coils in the stator of MG39 that heat up due to energization.

[0053] The following first to sixth embodiments combine three structural modes related to the switching of the operating direction of the hydraulic actuator 60 and two structural modes related to the oil supply path to the MG39. Regarding the switching of the operating direction of the hydraulic actuator 60, in the first and second embodiments, the rotation direction of the oil pump 30 is fixed, and the oil drawn from the oil pan 31 via the suction oil passage 32 flows only in one direction from the suction port 342 to the discharge port 343.

[0054] Between the oil pump 30 and the hydraulic actuator 60, a direction switching valve 56 is provided to switch the flow of oil from the oil pump 30 to the forward hydraulic chambers 651-654 and the return hydraulic chambers 661-664. The port shown in the center of the three IN ports of the direction switching valve 56 is connected to the discharge port 343 of the oil pump 30 via the actuator oil passage 360. The two ports shown on either side of the three IN ports are connected to the suction oil passage 32 via the actuator oil passages 365 and 366, respectively.

[0055] Furthermore, regarding the oil supply path to MG39, in the first, third, and fifth embodiments, a supply switching valve 50 is provided midway through the direct supply oil passages 35 and 38 to switch the connection or disconnection of the direct supply oil passages 35 and 38. The portion of the direct supply oil passages 35 and 38 closer to the oil pump 30 (i.e., upstream side) than the supply switching valve 50 is designated as the "discharge oil passage 35," and the portion closer to MG39 (i.e., downstream side) than the supply switching valve 50 is designated as the "arrival oil passage 38." In addition, the circulation oil passage 37, illustrated with dashed lines between the supply switching valve 50 and the suction oil passage 32, is essentially not considered for use in the first, third, and fifth embodiments. That is, the lowest of the three switching modes constituting the supply switching valve 50 is not used. The discharge oil passage 35 and the arrival oil passage 38 are connected or disconnected. The supply switching valve 50 can also be integrally configured as a module of the integrated pump device 901.

[0056] exist Figure 5 When the lock is released, the supply switching valve 50 is operated to connect the direct supply oil passages 35 and 38. The direction switching valve 56 is operated to connect the actuator oil passage 360 ​​to the return side hydraulic chambers 661-664 and the actuator oil passage 365 to the forward side hydraulic chambers 651-654. Oil discharged from the outlet 343 of the oil pump 30 is supplied to the MG39 via the direct supply oil passages 35 and 38, and to the return side hydraulic chambers 661-664 of the hydraulic actuator 60 via the actuator oil passage 360. In addition, oil returns from the forward side hydraulic chambers 651-654 of the hydraulic actuator 60 to the suction oil passage 32 via the actuator oil passage 365. Thus, the hydraulic actuator 60 is in the return state, and the parking lock mechanism 80 is released.

[0057] exist Figure 6When locked, the supply switching valve 50 is operated to cut off the direct supply oil passages 35 and 38. The direction switching valve 56 is operated to connect the actuator oil passage 360 ​​to the forward hydraulic chambers 651-654 and the actuator oil passage 366 to the return hydraulic chambers 661-664. Oil discharged from the outlet 343 of the oil pump 30 is supplied to the forward hydraulic chambers 651-654 of the hydraulic actuator 60 via the actuator oil passage 360. Additionally, oil from the return hydraulic chambers 661-664 of the hydraulic actuator 60 returns to the suction oil passage 32 via the actuator oil passage 366. Thus, the hydraulic actuator 60 is in the forward state, and the parking lock mechanism 80 is locked.

[0058] The actuating force of a hydraulic actuator is determined by the product of the pressure-bearing area and the hydraulic pressure. By using a rotary hydraulic actuator 60, the pressure-bearing area can be ensured by utilizing multiple blades 641-644, thus miniaturizing the hydraulic actuator 60. Therefore, it can be used particularly effectively as a hydraulic actuator for applications such as parking lock actuators where mounting space is limited. This effect is common to the first through sixth embodiments.

[0059] In the first embodiment, the switching of the operating direction of the hydraulic actuator 60 can be reliably performed by using the direction switching valve 56. Furthermore, in the first embodiment, regarding the oil supply path to the MG39, the supply switching valve 50 provided in the direct oil supply passages 35 and 38 allows the supply of cooling oil to the MG39 to be switched independently of the operation of the hydraulic actuator 60 at any given time.

[0060] <Second Implementation Method>

[0061] Reference Figures 7-10 The second embodiment will be described. Compared to the first embodiment, the integrated pump device 902 in the second embodiment has a different oil supply path to the MG39, which acts as an "oil consumer." In the second embodiment, there is no direct oil supply path 35, 38 between the oil pump 30 and the MG39 as in the first embodiment. Furthermore, in the second embodiment, a supply switching valve 50 is not provided.

[0062] Reference Figure 7 , Figure 8 Here, a structural example of the rotary hydraulic actuator 60 of the second embodiment will be described. Figure 7 , Figure 8 The structure is also applicable in the fourth and sixth embodiments described later. Figure 7 , Figure 8 Corresponding to the first embodiment Figure 3 , Figure 4 .like Figure 8As shown, for example, the blade chamber 621 that powers the blade 641 has a connecting port 67 formed at the midpoint of the rotational direction between the forward hydraulic chamber 651 and the return hydraulic chamber 661. The connecting port 67 is not limited to being formed in one blade chamber 621, but may also be formed in multiple blade chambers.

[0063] like Figure 9 , Figure 10 As shown, the connection port 67 is connected to MG39 via an indirect oil supply line 68. Midway through the indirect oil supply line 68, a consumption-side anti-backflow valve 69 is installed to prevent oil from flowing back from MG39 to the hydraulic actuator 60. The consumption-side anti-backflow valve 69 is not limited to one; multiple valves may be installed.

[0064] Here, Figure 8 The "unlocked" state shown on the upper side is the initial rotational state of the blade rotor 63 when it is locked. Figure 8 The "locked" state shown on the lower side is the initial rotational state of the blade rotor 63 when it is unlocked. Figure 7 A double-dotted arrow schematically represents the oil flow during the transition from the locked state to the unlocked state. A single-dotted arrow schematically represents the oil flow during the transition from the unlocked state to the locked state.

[0065] exist Figure 9 When the lock is released, during the initial rotation of the vane rotor 63, the vane 641 closes the connection port 67 in the return side hydraulic chamber 661, which is the hydraulic chamber supplied with hydraulic pressure from the oil pump 30. After the vane rotor 63 begins to rotate, at a certain rotational position, the connection port 67 opens in the return side hydraulic chamber 661. At least a portion of the oil supplied from the oil pump 30 to the return side hydraulic chamber 661 then flows out from the connection port 67 and is supplied to the MG39 via the indirect supply oil passage 68.

[0066] exist Figure 10 When locked as shown, during the initial rotation of the vane rotor 63, vane 641 closes the connection port 67 in the hydraulic chamber 651 on the forward side, which is the side from which hydraulic pressure is supplied by oil pump 30. After the vane rotor 63 begins to rotate, at a certain rotational position, the connection port 67 opens in the forward side hydraulic chamber 651. At least a portion of the oil supplied from oil pump 30 to the forward side hydraulic chamber 651 then flows out from the connection port 67 and is supplied to MG39 via the indirect supply oil passage 68.

[0067] In the first embodiment, the oil passage from the oil pump 30 to the MG39 and the oil passage from the oil pump 30 to the hydraulic actuator 60 are configured in parallel. In contrast, in the second embodiment, the oil passages are configured in series, connecting the oil pump 30 to the MG39 via the hydraulic actuator 60. By consolidating them into a single path, the structure of the oil passages can be simplified. Furthermore, by using the rotation of the vane rotor 63 to switch the oil supply to the MG39, the supply switching valve 50 can be reduced. Therefore, the system including the integrated pump unit can be further miniaturized.

[0068] <Third Implementation Method>

[0069] Reference Figure 11 , Figure 12 The third embodiment will be described. Compared to the first embodiment, the integrated pump device 903 of the third embodiment has a different hydraulic circuit structure for switching the direction of operation of the hydraulic actuator 60. The oil pump 30 can rotate forward and reverse together with the motor 10, and the suction port and discharge port alternate during forward and reverse rotation. That is, the suction port 342 is the discharge port during reverse rotation, and the suction port 343 is the discharge port during forward rotation.

[0070] exist Figure 11 , Figure 12 For ease of explanation, the rotation direction of the first embodiment, i.e., the rotation direction of the oil pump 30 that supplies oil to MG39 from the discharge port 343 via the direct supply oil passages 35 and 38 when rotating forward, is set to forward rotation. The supply switching valve 50 switches the connection or disconnection of the direct supply oil passages 35 and 38 in the same way as in the first embodiment.

[0071] During forward rotation, the suction port 342 is connected to the forward hydraulic chambers 651-654 of the hydraulic actuator 60 via the actuator oil passage 367. A suction-side anti-backflow valve 57 is provided on the forward rotation suction oil passage 32 connected to the forward rotation suction port 342 to prevent backflow from the oil pump 30 side to the oil pan 31 side.

[0072] During reverse rotation, the suction port 343 is connected to the return-side hydraulic chambers 661-664 of the hydraulic actuator 60 via the actuator oil passage 368. A suction-side anti-backflow valve 58 is provided on the reverse rotation suction oil passage 33 connected to the reverse rotation suction port 343 to prevent backflow from the oil pump 30 side to the oil pan 31 side. In the illustrated example, both the forward rotation suction oil passage 32 and the reverse rotation suction oil passage 33 are connected to the oil pan 31 at one end. However, this is not a limitation; the forward rotation suction oil passage 32 and the reverse rotation suction oil passage 33 may also originate from a common suction oil passage branch connected to the oil pan 31.

[0073] exist Figure 11When the lock is released, the supply switching valve 50 is operated to connect the direct supply oil passages 35 and 38. If the oil pump 30 rotates forward, oil is drawn from the oil pan 31 into the forward suction port 342 via the forward suction oil passage 32. Oil discharged from the forward discharge port 343 is supplied to the MG39 via the direct supply oil passages 35 and 38, and is also supplied to the return side hydraulic chambers 661 to 664 of the hydraulic actuator 60 via the actuator oil passage 368.

[0074] At this time, as indicated by the "×" mark, the suction-side anti-backflow valve 58 prevents oil from flowing back towards the oil pan 31 through the reverse-flow suction oil passage 33. Additionally, oil returns from the forward-side hydraulic chambers 651-654 of the hydraulic actuator 60 to the forward-flow suction oil passage 32 via the actuator oil passage 367. Thus, the hydraulic actuator 60 enters the return state, and the parking lock mechanism 80 is released.

[0075] exist Figure 12 When locked as shown, the supply switching valve 50 is operated to the position of cutting off the direct supply oil passages 35 and 38. If the oil pump 30 reverses, oil is drawn from the oil pan 31 into the reverse suction port 343 via the reverse suction oil passage 33. Oil discharged from the reverse discharge port 342 is supplied to the forward hydraulic chambers 651 to 654 of the hydraulic actuator 60 via the actuator oil passage 367.

[0076] At this time, as indicated by the "×" mark, the suction-side anti-backflow valve 57 prevents oil from flowing back through the forward-rotating suction oil passage 32 to the oil pan 31 side. Additionally, oil returns from the return-side hydraulic chambers 661-664 of the hydraulic actuator 60 to the reverse-rotating suction port 343 via the actuator oil passage 368. Thus, the hydraulic actuator 60 enters the forward state, and the parking lock mechanism 80 is locked.

[0077] <Fourth Implementation Method>

[0078] Reference Figure 13 , Figure 14 The fourth embodiment will be described. The integrated pump device 904 of the fourth embodiment combines the operating direction switching structure of the hydraulic actuator 60 of the third embodiment and the oil supply structure to the MG39 of the second embodiment. Specifically, the operating direction of the hydraulic actuator 60 is switched by switching the forward or reverse rotation of the oil pump 30 and by utilizing the functions of the suction-side anti-backflow valves 57 and 58. Furthermore, oil is supplied to the MG39 from the connection port 67 formed in the hydraulic actuator 60 via the indirect supply oil passage 68. A consumption-side anti-backflow valve 69 is provided on the indirect supply oil passage 68.

[0079] exist Figure 13When the lock is released, if the oil pump 30 rotates forward, the oil discharged from the discharge port 343 during forward rotation is supplied to the return side hydraulic chambers 661-664 of the hydraulic actuator 60 via the actuator oil passage 368. In the initial stage of rotation of the vane rotor 63, the connection port 67 is closed, cutting off the connection between the oil pump 30 and MG39. After the vane rotor 63 begins to rotate, the connection port 67 opens, connecting the oil pump 30 and MG39.

[0080] exist Figure 14 When locked as shown, if the oil pump 30 reverses, the oil discharged from the reverse discharge port 342 is supplied to the forward hydraulic chambers 651-654 of the hydraulic actuator 60 via the actuator oil passage 367. In the initial stage of rotation of the vane rotor 63, the connection port 67 is closed, cutting off the connection between the oil pump 30 and MG39. After the vane rotor 63 begins to rotate, the connection port 67 opens, connecting the oil pump 30 and MG39.

[0081] In the third and fourth embodiments, the direction of operation of the hydraulic actuator 60 is switched by changing the forward or reverse rotation of the oil pump 30, thus reducing the need for the direction switching valve 56. Furthermore, by using the suction-side anti-backflow valves 57 and 58 to prevent backflow of oil to the suction side, the hydraulic pressure supplied to the hydraulic actuator 60 can be ensured. Moreover, the suction-side anti-backflow valves 57 and 58 are not limited to one on each suction oil passage 32 and 33; multiple valves can also be provided.

[0082] <Fifth Implementation Method>

[0083] Reference Figure 15 , Figure 16 The fifth embodiment will be described. Compared to the first and third embodiments, the integrated pump device 905 of the fifth embodiment differs in the structure of the hydraulic circuit that switches the operating direction of the hydraulic actuator 60. Similar to the third embodiment, the oil pump 30 can rotate forward and reverse together with the motor 10, with the suction port and discharge port alternating during forward and reverse rotation. Furthermore, the connection structure between the suction port 342 during forward rotation and the suction port 343 during reverse rotation of the oil pump 30 and the hydraulic actuator 60 is also the same as in the third embodiment.

[0084] Instead of the anti-backflow valves 57 and 58 on the suction side of the third embodiment, a selective shut-off valve 59 is provided on the suction oil passage 32 during forward rotation and the suction oil passage 33 during reverse rotation. The selective shut-off valve 59 opens the suction oil passage 32 during forward rotation and shuts off the suction oil passage 33 during reverse rotation when the oil pump 30 is rotating in reverse; conversely, it opens the suction oil passage 33 during reverse rotation and shuts off the suction oil passage 32 during forward rotation. The selective shut-off valve 59 can also be integrally configured as a module of the integrated pump device 905. Furthermore, the selective shut-off valve 59 is not limited to a solenoid valve and can also be configured as a hydraulic switching valve that switches the valve stem by operating pressure.

[0085] exist Figure 15 When the lock-up is released, the supply switching valve 50 is operated to connect the direct supply oil passages 35 and 38. The selection shut-off valve 59 opens the forward-rotation suction oil passage 32. If the oil pump 30 rotates forward, oil is drawn from the oil pan 31 into the forward-rotation suction port 342 via the forward-rotation suction oil passage 32. Oil discharged from the forward-rotation discharge port 343 is supplied to MG39 via the direct supply oil passages 35 and 38, and...

[0086] The hydraulic fluid is supplied to the return side hydraulic chambers 661-664 of the hydraulic actuator 60 via the actuator oil circuit 368.

[0087] At this time, as indicated by the "×" mark, the shut-off valve 59 cuts off the reverse-flow intake oil passage 33. Additionally, oil returns from the forward-side hydraulic chambers 651-654 of the hydraulic actuator 60 via the actuator oil passage 367 to the forward-flow intake oil passage 32. Thus, the hydraulic actuator 60 enters the return state, and the parking lock mechanism 80 is released.

[0088] exist Figure 16 When locked as shown, the supply switching valve 50 is operated to the position of cutting off the direct supply oil passages 35 and 38. The selection shut-off valve 59 opens the reverse suction oil passage 33. If the oil pump 30 reverses, oil is drawn from the oil pan 31 into the reverse suction port 343 via the reverse suction oil passage 33. Oil discharged from the reverse discharge port 342 is supplied to the forward hydraulic chambers 651 to 654 of the hydraulic actuator 60 via the actuator oil passage 367.

[0089] At this time, as indicated by the "×" mark, the shut-off valve 59 cuts off the forward-rotation intake oil passage 32. Additionally, oil returns from the return-side hydraulic chambers 661-664 of the hydraulic actuator 60 via the actuator oil passage 368 to the reverse-rotation intake oil passage 33. Thus, the hydraulic actuator 60 enters the forward state, and the parking lock mechanism 80 is locked.

[0090] <Sixth Implementation Method>

[0091] Reference Figure 17 , Figure 18 The sixth embodiment will be described. The integrated pump device 906 of the sixth embodiment combines the operating direction switching structure of the hydraulic actuator 60 of the fifth embodiment and the oil supply structure to the MG39 of the second embodiment. Specifically, the operating direction of the hydraulic actuator 60 is switched by switching the forward or reverse rotation of the oil pump 30 and the accompanying switching of the selection shut-off valve 59. Furthermore, oil is supplied to the MG39 from the connection port 67 formed in the hydraulic actuator 60 via the indirect supply oil passage 68. A consumption-side anti-backflow valve 69 is provided on the indirect supply oil passage 68.

[0092] exist Figure 17When the lock is released, if the oil pump 30 rotates forward, the oil discharged from the discharge port 343 during forward rotation is supplied to the return side hydraulic chambers 661-664 of the hydraulic actuator 60 via the actuator oil passage 368. In the initial stage of rotation of the vane rotor 63, the connection port 67 is closed, cutting off the connection between the oil pump 30 and MG39. After the vane rotor 63 begins to rotate, the connection port 67 opens, connecting the oil pump 30 and MG39.

[0093] exist Figure 18 When locked as shown, if the oil pump 30 reverses, the oil discharged from the reverse discharge port 342 is supplied to the forward hydraulic chambers 651-654 of the hydraulic actuator 60 via the actuator oil passage 367. In the initial stage of rotation of the vane rotor 63, the connection port 67 is closed, and the connection between the oil pump 30 and MG39 is cut off.

[0094] After the blade rotor 63 starts to rotate, the connecting port 67 opens, and the oil pump 30 and MG39 are connected.

[0095] In the fifth and sixth embodiments, the direction of operation of the hydraulic actuator 60 is switched by switching the oil pump 30 to either forward or reverse rotation and by switching the selection shut-off valve 59 thereafter, thus reducing the need for the direction switching valve 56. Furthermore, by using the selection shut-off valve 59 to prevent backflow of oil to the suction side, the hydraulic pressure supplied to the hydraulic actuator 60 can be ensured.

[0096] <Reference Method>

[0097] Reference Figure 19 An integrated pump device 907 with a reference configuration of a cylinder-type hydraulic actuator 70 will be described. The cylinder-type hydraulic actuator 70 has a cylinder 71 and a piston 73 that reciprocates within the cylinder 71. A forward hydraulic chamber 75 is formed on one side of the piston 73 in the cylinder 71, and a return hydraulic chamber 76 is formed on the other side of the piston 73 in the axial direction.

[0098] As indicated by the thick arrow, piston 73 is connected to the switching lever 84 of parking lock mechanism 80. The front end of switching lever 84 engages with pin 824 located on stop plate 82. If switching lever 84 reciprocates with the reciprocating movement of piston 73, stop plate 82 is rotated via pin 824, causing parking lever 85 to move, thereby switching between P and non-P gears.

[0099] Oil pump 30 can supply oil to the forward hydraulic chamber 75 and the return hydraulic chamber 76 via ports 721 and 722. The flow of oil to each hydraulic chamber 75 and 76 is switched according to the first or second embodiment of the rotary hydraulic actuator 60. Oil from the discharge side hydraulic chamber returns to the suction side of oil pump 30. Figure 19 The diagram showing the switching path of oil flow is omitted.

[0100] When the lock is released, hydraulic pressure is supplied from oil pump 30 to the return side hydraulic chamber 76, and piston 73 moves towards... Figure 19 The parking lever 85 moves to the left and returns to the original position. Therefore, as the switching lever 84 moves, the parking lever 85 moves in the non-P direction, and the parking lock mechanism 80 is released. When locked, hydraulic pressure is supplied from the oil pump 30 to the forward hydraulic chamber 75, and the piston 71 moves... Figure 19 The lever moves to the right and enters the forward position. Therefore, as the switching lever 84 moves, the parking lever 85 moves in the P direction, and the parking lock mechanism 80 is locked.

[0101] In the reference embodiment, the same hydraulic actuator operation as in the first to sixth embodiments can be achieved. However, it differs from the first to sixth embodiments in that it does not aim at miniaturizing the integrated pump device.

[0102] <Other Implementation Methods>

[0103] (1) The hydraulic actuator 60 is not limited to actuators other than parking lock actuators, but can also be used for any purpose such as shift drums for transmissions. In addition, depending on the actuator used, it is appropriate to set which state to forward state and return state.

[0104] (2) The number of blades in the blade rotor of the hydraulic actuator 60 is not limited to Figure 4 The four examples shown can be replaced by one or more, provided the pressure-bearing area is sufficient. The blade chamber of the outer casing is set according to the number of blades. Alternatively, the stop that limits the rotation may not be located on the blades, but rather between the blade rotor body and the outer casing.

[0105] (3) The "oil consumer" that supplies oil from the oil pump 30 is not limited to MG39, but can be any device that consumes oil. In addition, in the second, fourth and sixth embodiments, if the oil consumer has an anti-backflow function inside, the consumption-side anti-backflow valve 69 may not be provided on the indirect oil supply line 68.

[0106] The present disclosure is not limited to the above-described embodiments and can be implemented in various ways without departing from its spirit.

[0107] This disclosure has been described in accordance with embodiments. However, this disclosure is not limited to these embodiments and structures. This disclosure also includes various modifications and equivalent variations. In addition, various combinations and methods, as well as other combinations and methods that include only one element, more elements, or fewer elements, are also within the scope and spirit of this disclosure.

Claims

1. An integrated pump device, characterized in that, This forms a module that integrates the motor, oil pump, and hydraulic actuator. The oil pump is rotated by the driving force of the motor to discharge the oil drawn in from the oil pan. The hydraulic actuator is a parking lock actuator that actuates the vehicle's parking lock mechanism. It operates using hydraulic pressure supplied from the oil pump to switch between forward and return states. The hydraulic actuator includes: The outer casing has one or more blade chambers; as well as A blade rotor, which is housed in the outer casing, is provided with one or more blades corresponding to the blade chamber; A forward hydraulic chamber is formed on one side of the blade in the blade chamber along its circumference, and a return hydraulic chamber is formed on the other side of the blade in the blade chamber along its circumference. When hydraulic pressure is supplied to the forward-side hydraulic chamber, the blade rotor rotates in one direction to enter the forward state; when hydraulic pressure is supplied to the return-side hydraulic chamber, the blade rotor rotates in the other direction to enter the return state. The parking lock mechanism is locked in the forward position, and the parking lock mechanism is released in the return position. The integrated pump device is equipped with a directional switching valve, which switches the flow of oil from the oil pump to the forward hydraulic chamber and the return hydraulic chamber. The hydraulic actuator is connected to the oil consumer via an indirect oil supply line. At least one of the blade chambers has a communication port formed at the midpoint of the rotation direction of the forward-side hydraulic chamber and the return-side hydraulic chamber, which communicates with the indirect oil supply circuit. In the initial stage of rotation of the blade rotor, within the hydraulic chamber supplied with hydraulic pressure from the oil pump, the blades close the communication port. After the blade rotor begins to rotate, if the communication port is opened in the hydraulic chamber on the side supplied with hydraulic pressure from the oil pump, the oil supplied from the oil pump to the hydraulic actuator is supplied to the oil consumer via the indirect supply oil passage.

2. The integrated pump device according to claim 1, characterized in that, The oil pump is capable of both forward and reverse rotation. During forward and reverse rotation, the suction port and discharge port alternate. The suction port during forward rotation, which serves as the discharge port during reverse rotation, is connected to the forward-side hydraulic chamber. The suction port during reverse rotation, which serves as the discharge port during forward rotation, is connected to the return-side hydraulic chamber. Both the forward-rotation suction oil circuit connected to the forward-rotation suction port and the reverse-rotation suction oil circuit connected to the reverse-rotation suction port are respectively equipped with suction-side anti-backflow valves to prevent backflow from the oil pump side to the oil pan side. By switching the oil pump to either forward or reverse rotation, the flow of oil from the oil pump to the forward hydraulic chamber or the return hydraulic chamber is switched.

3. The integrated pump device according to claim 1, characterized in that, The oil pump is capable of both forward and reverse rotation. During forward and reverse rotation, the suction port and discharge port alternate. The suction port during forward rotation, which serves as the discharge port during reverse rotation, is connected to the forward-side hydraulic chamber. The suction port during reverse rotation, which serves as the discharge port during forward rotation, is connected to the return-side hydraulic chamber. A selective shut-off valve is provided for the forward-rotation suction oil circuit connecting the oil pan and the forward-rotation suction port, and for the reverse-rotation suction oil circuit connecting the oil pan and the reverse-rotation suction port. This selective shut-off valve opens the forward-rotation suction oil circuit and shuts off the reverse-rotation suction oil circuit when the oil pump rotates forward, and opens the reverse-rotation suction oil circuit and shuts off the forward-rotation suction oil circuit when the oil pump rotates in reverse. The flow of oil from the oil pump to the forward-side hydraulic chamber or the return-side hydraulic chamber is switched by switching the oil pump to either forward or reverse rotation and by switching the selector shut-off valve accordingly.

4. The integrated pump device according to any one of claims 1 to 3, characterized in that, The oil pump is connected to the oil consumer via a direct supply line from a branch of the oil line that supplies hydraulic pressure to the hydraulic actuator. A supply switching valve is installed midway through the direct oil supply circuit to switch the connection or disconnection of the direct oil supply circuit.

5. The integrated pump device according to any one of claims 1 to 3, characterized in that, A backflow prevention valve is provided on the consumption side to prevent oil from flowing back from the oil consumer to the hydraulic actuator in the middle of the indirect oil supply circuit.

6. An integrated pump device, characterized in that, This forms a module that integrates the motor, oil pump, and hydraulic actuator. The oil pump is rotated by the driving force of the motor to discharge the oil drawn in from the oil pan. The hydraulic actuator operates using hydraulic pressure supplied from the oil pump to switch between forward and return states. The hydraulic actuator includes: The outer casing has one or more blade chambers; as well as A blade rotor, which is housed in the outer casing, is provided with one or more blades corresponding to the blade chamber; A forward hydraulic chamber is formed on one side of the blade in the blade chamber along its circumference, and a return hydraulic chamber is formed on the other side of the blade in the blade chamber along its circumference. When hydraulic pressure is supplied to the forward-side hydraulic chamber, the blade rotor rotates in one direction to enter the forward state; when hydraulic pressure is supplied to the return-side hydraulic chamber, the blade rotor rotates in the other direction to enter the return state. The oil pump is capable of both forward and reverse rotation. During forward and reverse rotation, the suction port and discharge port alternate. The suction port during forward rotation, which serves as the discharge port during reverse rotation, is connected to the forward-side hydraulic chamber. The suction port during reverse rotation, which serves as the discharge port during forward rotation, is connected to the return-side hydraulic chamber. Both the forward-rotation suction oil circuit connected to the forward-rotation suction port and the reverse-rotation suction oil circuit connected to the reverse-rotation suction port are respectively equipped with suction-side anti-backflow valves to prevent backflow from the oil pump side to the oil pan side. By switching the oil pump to either the forward or reverse direction, the flow of oil from the oil pump to the forward hydraulic chamber or the return hydraulic chamber is switched. The hydraulic actuator is connected to the oil consumer via an indirect oil supply line. At least one of the blade chambers has a communication port formed at the midpoint of the rotation direction of the forward-side hydraulic chamber and the return-side hydraulic chamber, which communicates with the indirect oil supply circuit. In the initial stage of rotation of the blade rotor, within the hydraulic chamber supplied with hydraulic pressure from the oil pump, the blades close the communication port. After the blade rotor begins to rotate, if the communication port is opened in the hydraulic chamber on the side supplied with hydraulic pressure from the oil pump, the oil supplied from the oil pump to the hydraulic actuator is supplied to the oil consumer via the indirect supply oil passage.

7. An integrated pump device, characterized in that, This forms a module that integrates the motor, oil pump, and hydraulic actuator. The oil pump is rotated by the driving force of the motor to discharge the oil drawn in from the oil pan. The hydraulic actuator operates using hydraulic pressure supplied from the oil pump to switch between forward and return states. The hydraulic actuator includes: The outer casing has one or more blade chambers; as well as A blade rotor, which is housed in the outer casing, is provided with one or more blades corresponding to the blade chamber; A forward hydraulic chamber is formed on one side of the blade in the blade chamber along its circumference, and a return hydraulic chamber is formed on the other side of the blade in the blade chamber along its circumference. When hydraulic pressure is supplied to the forward-side hydraulic chamber, the blade rotor rotates in one direction to enter the forward state; when hydraulic pressure is supplied to the return-side hydraulic chamber, the blade rotor rotates in the other direction to enter the return state. The oil pump is capable of both forward and reverse rotation. During forward and reverse rotation, the suction port and discharge port alternate. The suction port during forward rotation, which serves as the discharge port during reverse rotation, is connected to the forward-side hydraulic chamber. The suction port during reverse rotation, which serves as the discharge port during forward rotation, is connected to the return-side hydraulic chamber. A selective shut-off valve is provided for the forward-rotation suction oil circuit connecting the oil pan and the forward-rotation suction port, and for the reverse-rotation suction oil circuit connecting the oil pan and the reverse-rotation suction port. This selective shut-off valve opens the forward-rotation suction oil circuit and shuts off the reverse-rotation suction oil circuit when the oil pump rotates forward, and opens the reverse-rotation suction oil circuit and shuts off the forward-rotation suction oil circuit when the oil pump rotates in reverse. By switching the oil pump to either forward or reverse rotation and correspondingly switching the selector valve, the flow of oil from the oil pump to the forward hydraulic chamber or the return hydraulic chamber is switched. The hydraulic actuator is connected to the oil consumer via an indirect oil supply line. At least one of the blade chambers has a communication port formed at the midpoint of the rotation direction of the forward-side hydraulic chamber and the return-side hydraulic chamber, which communicates with the indirect oil supply circuit. In the initial stage of rotation of the blade rotor, within the hydraulic chamber supplied with hydraulic pressure from the oil pump, the blades close the communication port. After the blade rotor begins to rotate, if the communication port is opened in the hydraulic chamber on the side supplied with hydraulic pressure from the oil pump, the oil supplied from the oil pump to the hydraulic actuator is supplied to the oil consumer via the indirect supply oil passage.

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