JP2013068313A - Drive device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a drive device for a vehicle, in which elimination of a check valve is enabled in an oil path structure with oil paths of two oil pumps merged and connected to an oil pressure regulating part.SOLUTION: A drive device for the vehicle includes a mechanical type oil pump 7 which is drive-connected to a driving motor 3, an electric oil pump 10 which is drive-connected to an independently driven electric motor 11, and has an oil path structure 13 in which oil paths a1, a2 communicated therewith are merged. On the basis of hydraulic pressure acting from another oil pump which is driven after one oil pump of the two pumps has stopped, the driving motor 3 or the electric motor 11 is driven again so that a leak amount ratio varying depending on a rotation directional position of the oil pump which has stopped falls in a permissible range or below, and position adjustment of a stop position of the oil pump which has stopped is performed. Since an oil leak amount in the oil pump which has stopped is significantly reduced, it becomes unnecessary to provide check vales in the oil paths a1, a2.

Description

  The present invention relates to a vehicle drive device mounted on a vehicle or the like, and more particularly to a vehicle drive device that drives a second oil pump while one oil pump is stopped to ensure a hydraulic pressure supply to a hydraulic pressure adjusting unit. .

  2. Description of the Related Art In recent years, vehicle drive devices such as hybrid drive devices mounted on vehicles and the like have been mainly used to stop the vehicle drive system by idling the engine when the vehicle is stopped, for the purpose of improving fuel efficiency. . Such a vehicle drive device requires hydraulic pressure to perform hydraulic control and lubrication of the automatic transmission, cooling of the motor generator, etc., and is connected to a drive system (engine or motor generator), for example. If there is only a mechanical oil pump, the mechanical oil pump stops when the vehicle drive system is stopped, and the required oil pressure cannot be secured. Therefore, the electric oil pump that is separately driven by the electric motor Must be provided (see Patent Document 1).

  In the vehicle drive device as described above, the mechanical oil pump and the electric oil pump are connected in parallel to one hydraulic control device, that is, the oil passage connected to the discharge ports of the two oil pumps is In such a structure, it is communicated with a hydraulic pressure adjusting unit such as a regulator valve in a merged form. The mechanical oil pump and the electric oil pump are driven so that one of them is driven while the other is stopped, so that the hydraulic pressure is always secured. In order to prevent reverse flow and loss of hydraulic pressure, check valves are respectively provided in the oil passages connected to the discharge ports of the oil pumps.

JP 2007-139060 A

  However, since the check valve is disposed in the oil passage connected to the discharge port of the oil pump, the check valve acts as a throttle and causes a hydraulic pressure loss. There is a problem of causing a decrease in On the other hand, if the check valve is increased in diameter to avoid hydraulic loss, the check valve will be enlarged, so that there is a problem that the mountability to the vehicle drive device is not good.

  In particular, in a hybrid drive device (so-called series hybrid system) in which a motor generator is assembled in an automatic transmission, an automatic transmission for an internal combustion engine having only a mechanical oil pump and a hybrid drive device are used. By sharing the automatic transmission with the automatic transmission, it is possible to divert the automatic transmission for the internal combustion engine as an automatic transmission for the hybrid drive device, and to reduce the cost of the hybrid drive device, Secure a space for arranging the enlarged check valve as described above in an automatic transmission for an internal combustion engine (or design with an unnecessary space for the check valve in advance). In the end, the automatic transmission for the hybrid drive system has been redesigned.

  Therefore, the present invention has an oil passage structure in which the oil passages of two oil pumps are joined and connected to a hydraulic pressure regulating unit, and it is possible to eliminate the check valve. An object of the present invention is to provide a vehicle drive device that can be shared.

The present invention (see, for example, FIGS. 1 to 7) includes a first oil pump (7) that is drivingly connected to a drive shaft (3A) of a first rotating electrical machine (3);
A second oil pump (10) drivingly connected to a drive shaft (11A) of a second rotating electrical machine (11) that can be driven independently of the first rotating electrical machine (3);
Two oil passages (a1, a2) communicating with each of the first oil pump (7) and the second oil pump (10) are joined and connected to a hydraulic pressure adjusting unit, and oil is supplied to each other oil passage. A flowing oil passage structure (13);
A control unit (21) for driving and controlling the other oil pump (10 or 7) while one oil pump (7 or 10) of the first oil pump (7) and the second oil pump (10) is stopped; With
When the one oil pump (7 or 10) is stopped or stopped, the control unit (21) depends on the stop position (ωp) in the rotation direction of the one oil pump (7 or 10). The rotating electrical machine (3 or 3) that drives the one oil pump of the first rotating electrical machine and the second rotating electrical machine so that the ratio (Qr) of the variable oil leakage amount is equal to or less than the allowable range (Qrp). 11) is driven to adjust the stop position of the one oil pump (7 or 10).

In the present invention (see, for example, FIG. 3), the first oil pump (7) and the second oil pump have a drive gear (16) formed with external teeth (16a) and an internal tooth (17a). A geared oil pump having a formed driven gear (17), a suction port (7a) for sucking oil, and a discharge port (7b) for discharging oil;
The control unit (21) adjusts the stop position of one of the stopped oil pumps (for example, 7) between the suction port (7a) and the discharge port (7b) (for example, A). The target position is a position where the apex of the external teeth (16a) of the drive gear (16) and the apex of the internal teeth (17a) of the driven gear (17) face each other.

Furthermore, the present invention (see, for example, FIG. 1, FIG. 6, FIG. 7) includes an output shaft (2A) of the internal combustion engine (2) and a drive shaft (3A) of the first rotating electrical machine (3) capable of driving wheels. A first clutch (6) capable of interrupting transmission of driving force between
An automatic transmission (4) that is drivingly connected to the drive shaft (3A) of the first rotating electrical machine (3) and that can change the rotation of the drive shaft (3A) and output it to the wheels (90);
A second clutch (4C) capable of connecting and disconnecting drive transmission between the drive shaft (3A) of the first rotating electrical machine (3) and the wheel (90);
The controller (21) performs the position adjustment on the first oil pump (7) after releasing the first clutch (6) and the second clutch (4C). And

Further, the present invention (see, for example, FIGS. 1 to 3), a rotation angle sensor (8) for detecting a rotation position of the drive shaft (3A) of the first rotating electrical machine (3),
Positioning means (16c) for positioning relative angular positions of the drive shaft (3A) of the first rotating electrical machine (3) and the first oil pump (7) when the first oil pump (7) is assembled. 16d, 4Aa, 4Ab), and
The control unit (21) performs the position adjustment on the first oil pump (7) based on the rotational position detected by the rotation angle sensor (8).

  In addition, although the code | symbol in the said parenthesis is for contrast with drawing, this is for convenience for making an understanding of invention easy, and has no influence on the structure of a claim. It is not a thing.

  According to the first aspect of the present invention, when the one oil pump is stopped, or after the oil pump is stopped, the ratio of the oil leakage amount that varies according to the stop position in the rotation direction of the one oil pump is within an allowable range. Since the rotary electric machine that drives one oil pump of the first rotary electric machine and the second rotary electric machine is driven and controlled to adjust the position of the stop position of one of the oil pumps, In one of the oil pumps, the amount of leakage due to hydraulic backflow can be greatly reduced, and it is not necessary to provide a check valve in the oil passage connected to the discharge ports of the first and second oil pumps. As a result, the vehicle drive device can be made compact, and the automatic transmission can be shared.

  According to the second aspect of the present invention, when adjusting the stop position of one of the oil pumps that are stopped, the apex of the external teeth of the drive gear and the apex of the internal teeth of the driven gear are between the suction port and the discharge port. Therefore, the position control can be performed with the position where the leakage amount of one of the stopped oil pumps is the smallest as a target.

  According to the third aspect of the present invention, there is provided a so-called series-type hybrid drive device in which the first rotating electric machine capable of driving the wheel by releasing the first clutch and the second clutch is used for the internal combustion engine and the wheel. After the transmission of the driving force is interrupted, it is possible to adjust the position of the first oil pump that is drivingly connected to the first rotating electrical machine.

  According to the fourth aspect of the present invention, when the drive shaft of the first rotating electrical machine and the first oil pump are assembled, positioning means for positioning the relative angular positions of each other is provided. The rotational angle position between the angle sensor and the first oil pump can be uniquely determined, and thereby the position adjustment is performed on the first oil pump based on the rotational position detected by the rotational angle sensor. Can be possible.

The block diagram which shows the vehicle carrying the vehicle drive device which concerns on this invention. The schematic diagram which shows the drive system and oil path structure in this vehicle drive device. It is sectional drawing which shows a mechanical oil pump, (a) is a figure which shows the rotational direction position with the smallest leakage amount, (b) is a figure which shows the rotational direction position with the largest leakage amount. The figure which shows the relationship between the leak amount in an oil pump, and the hydraulic pressure which acts. The figure which shows the relationship between the leakage amount ratio in an oil pump, and a drive gear rotation direction position. The flowchart which shows the position adjustment control which concerns on this invention. The time chart which shows the position adjustment control which concerns on this invention.

  Embodiments according to the present invention will be described below with reference to FIGS. First, a schematic configuration of a hybrid drive device (vehicle drive device) to which the present invention can be applied and a vehicle equipped with the hybrid drive device will be described with reference to FIG.

  As shown in FIG. 1, an FF (front engine / front drive) type vehicle 100 has an internal combustion engine (E / G) 2 such that an output shaft (crankshaft) 2A is transverse to the vehicle traveling direction. The hybrid drive device 1 according to the present invention is drivably coupled to the output shaft 2A of the internal combustion engine 2. The hybrid drive device 1 is drivingly connected to a front wheel axle 91, and left and right front wheels 90 are connected to the front wheel axle 91. In addition, the left and right rear wheels 90 are connected to the rear side of the vehicle 100 via the rear wheel axle 92.

  The vehicle drive system of the vehicle 100 refers to a device disposed in the power transmission path from the internal combustion engine 2 to the wheels 90, 90. The hybrid drive device 1 is a part of the vehicle drive system. It is composed. The hybrid drive device 1 is roughly configured to include a first clutch 6 for disconnecting the engine, a drive motor generator (M / G) (first rotating electrical machine) 3, and an automatic transmission 4. That is, the drive motor generator 3 is a rotating electric machine for a vehicle drive system, and the automatic transmission 4 is a transmission for a vehicle drive system.

  The hybrid drive device 1 includes an automatic transmission control unit (A / T ECU) 20 that performs connection / disconnection control of the first clutch 6 and shift control of the automatic transmission 4 (connection / disconnection control of the second clutch 4C). A hybrid control unit (H / T ECU) 21 that cooperates with the automatic transmission control unit 20 and performs power running control and regenerative control of the drive motor 3 via an inverter circuit 30 connected to the battery 31. Is provided.

  Specifically, automatic transmission control is performed between the output shaft 2A of the internal combustion engine 2 and the drive motor generator 3 (hereinafter simply referred to as “drive motor 3”) on the power transmission path of the hybrid drive device 1. A first clutch 6 that is engaged / released by a hydraulic servo (not shown) is provided based on a command from the unit 20, and when the first clutch 6 is engaged, the driving force of the internal combustion engine 2 is increased. When it is transmitted to the automatic transmission 4 via the drive shaft 3A of the drive motor 3 and the first clutch 6 is released, the internal combustion engine 2, the drive motor 3 and the automatic transmission 4 are disconnected, and the internal combustion engine 2 is disconnected. Is transmitted to the drive motor 3 and the automatic transmission 4.

  The drive motor 3 is a motor that can drive the wheels 90, 90, and has a drive shaft (rotor shaft) 3A that is drivingly connected to the first clutch 6 and the automatic transmission 4. When the first clutch 6 is engaged, the driving force of the driving motor 3 is assisted by the driving force of the internal combustion engine 2, and when the first clutch 6 is released, EV traveling (powering / regeneration) by the driving force of the driving motor 3 is enabled. Note that a resolver (rotation angle sensor) 8 that can detect the rotation angle of the drive shaft 3A is disposed in the automatic transmission 4 described in detail later. Based on the detection result of the resolver 8, the inverter circuit 30 By performing PWM control (pulse width modulation control) on the drive motor 3, the drive motor 3 is subjected to power running / regeneration control.

  The automatic transmission 4 has substantially the same configuration as a multistage automatic transmission for a vehicle that uses only a general internal combustion engine as a drive source, and is input coupled to the drive shaft 3A of the drive motor 3. A damper device (not shown) that has a shaft 4A and absorbs rotational vibration of the input shaft 4A, and an automatic transmission mechanism (not shown) that transmits the rotation of the input shaft 4A to the front-wheel axle 91 by multi-stage shifting. (Shown). The automatic transmission mechanism is provided with a second clutch 4C, which is a plurality of shift clutches for changing the transmission path in accordance with the shift speed. By releasing all of the second clutch 4C, The drive transmission between the drive shaft 3A of the drive motor 3 and the wheels 90 (that is, the front wheel axle 91) is cut off. The automatic transmission 4 is provided with the above-described resolver 8 on the input shaft 4A, and a mechanical oil pump (first oil) connected to the drive shaft 3A via the input shaft 4A. Pump) 7 is provided.

  Next, a drive system and an oil passage structure for the oil pump in the hybrid drive device 1 will be described with reference to FIG. As shown in FIG. 2, the hybrid drive device 1 includes a mechanical oil pump (O / P) 7 described above and an electric oil pump (second oil pump) arranged in parallel with the mechanical oil pump 7. ) (EO / P) 10.

  As described above, in the mechanical oil pump 7, since the input shaft 4 </ b> A of the automatic transmission 4 and the drive shaft 3 </ b> A of the drive motor 3 are drivingly connected, the output of the internal combustion engine 2 via the first clutch 6. The shaft 2A and the drive shaft 3A of the drive motor 3 are drivingly connected, that is, they are configured to be driven in conjunction with the drive source of the vehicle drive system. As described above, the resolver (rotation angle sensor) 8 for detecting the rotation position (rotation angle) of the drive shaft 3A of the drive motor 3 is disposed on the input shaft 4A of the automatic transmission 4. The resolver 8 can detect the rotational angle position of the drive gear 16 of the mechanical oil pump 7 described later.

  On the other hand, the electric oil pump 10 is drivingly connected to an electric motor (second rotating electrical machine) 11 that can be driven independently of the vehicle drive system (particularly the drive motor 3), that is, while the vehicle drive system is stopped. Even if it exists, it is comprised so that the electric oil pump 10 can be driven independently. The electric motor 11 has a drive shaft 11A that is drivingly connected to a drive gear (not shown) of the electric oil pump 10, and a resolver 12 is disposed on the drive shaft 11A. Can detect the rotational angle position of the drive gear of the electric oil pump 10.

  The mechanical oil pump 7 and the electric oil pump 10 are communicated with oil passages a1 and a2 that communicate with the respective discharge ports. When the mechanical oil pump 7 and the electric oil pump 10 are driven, they are not shown. The oil sucked into the suction port from the oil pan is compressed and generated as a hydraulic pressure from the discharge port, and the hydraulic pressure is supplied to the oil passages a1 and a2. In the hybrid drive device 1, these two oil passages a <b> 1 and a <b> 2 are joined to the oil passage a <b> 3 and connected to a hydraulic pressure adjusting unit (regulator valve or the like) (not shown) of the hydraulic control device (V / B) 14. The road structure 13 is provided, and the hydraulic pressure regulated by the hydraulic control device (V / B) 14 is supplied to the automatic transmission (AT) 4 as the engagement pressure of the hydraulic servo of each second clutch 4C and the lubricating hydraulic pressure. At the same time, it is supplied as the engagement pressure of the hydraulic servo of the first clutch 6.

  The mechanical oil pump 7 and the electric oil pump 10 described above are controlled so that when one oil pump is stopped, the other oil pump is driven by the control of the hybrid control unit 21 (see FIG. 1). The That is, while the vehicle is running, while the internal combustion engine 2 and the drive motor 3 are driven and the input shaft 4A of the automatic transmission 4 is driven and controlled, the mechanical oil pump 7 is driven to rotate and the hydraulic pressure is increased. When the vehicle is stopped, the internal combustion engine 2 is disconnected by the first clutch 6, and the rotational drive of the drive motor 3 is stopped, the mechanical oil pump 7 is stopped. Therefore, the electric motor 11 is driven and the electric oil pump 10 is driven and controlled.

  While the mechanical oil pump 7 is being driven and the electric oil pump 10 is stopped, hydraulic pressure is supplied from the mechanical oil pump 7 to the hydraulic control device 14 via the oil passages a1 and a3. The oil pressure acts on the electric oil pump 10 through the oil passage a2 in a reverse flow. On the contrary, when the electric oil pump 10 is being driven and the mechanical oil pump 7 is stopped, hydraulic pressure is supplied from the electric oil pump 10 to the hydraulic control device 14 via the oil passages a2 and a3. At the same time, the hydraulic pressure acts on the mechanical oil pump 7 through the oil passage a1 in a reverse manner.

  Next, while explaining the structure of the mechanical oil pump 7, the relationship between the stop position of the drive gear in the rotational direction and the amount of oil leakage from the mechanical oil pump 7 will be described with reference to FIGS. FIG. 3 shows the structure of the mechanical oil pump 7. The leakage amounts in FIGS. 4 and 5 show the leakage amount and the leakage rate ratio when the mechanical oil pump 7 is stopped. Since the same applies to the pump 10, the description about the electric oil pump 10 is omitted with the description about the mechanical oil pump 7. The “oil leakage amount” is the amount of oil that flows into the suction port from the discharge port in an oil pump structure that will be described in detail later.

  As shown in FIG. 3, the mechanical oil pump 7 has a pump body 7Bo in which a gear housing hole 7H is formed. The mechanical oil pump 7 is housed in the gear housing hole 7H so as to be input to the automatic transmission 4. A so-called gear-type oil pump having a drive gear 16 connected and fixed in the rotational direction with respect to the shaft 4A, and a driven gear 17 meshed with the drive gear 16 and driven and rotated at an eccentric position. Consists of.

  The pump body 7Bo is formed with an oil hole 7A communicating with an oil pan (not shown). The oil hole 7A opens toward the side surfaces of the drive gear 16 and the driven gear 17 to suck in oil. A suction port 7a is configured. Further, the pump body 7Bo is formed with an oil hole 7B communicating with the oil passage a1, and the oil hole 7B opens toward the side surfaces of the drive gear 16 and the driven gear 17 to discharge oil. 7b is configured. Accordingly, in the mechanical oil pump 7, the suction port 7a that communicates with an oil pan (not shown) and the discharge port 7b that discharges compressed oil to the oil passage a1 do not communicate with each other over substantially half a circumference. So that they are arranged at such a distance.

  A pump cover (not shown) is attached to the pump body 7Bo to seal the gear housing hole 7H. The suction port 7a and the discharge port 7b are also preferably formed on the pump cover side so that oil can be sucked from both sides of the drive gear 16 and the driven gear 17 and compressed and discharged.

  The drive gear 16 has keys (positioning means) 16c and 16d formed so as to protrude at two locations on the inner peripheral side, and a key groove (positioning means) 4Aa formed on the outer periphery of the input shaft 4A. By being inserted into 4Ab, the rotational position of the drive gear 16 with respect to the input shaft 4A is positioned and fixed. That is, when the mechanical oil pump 7 and the drive motor 3 are assembled, the drive shaft 3A of the drive motor 3 The relative angular position with respect to the drive gear 16 is positioned. Thus, the rotational angle position of the drive shaft 3A of the drive motor 3 and the rotational angle position of the drive gear 16 are uniquely positioned, and the drive motor 3 is driven and controlled based on the detection result of the resolver 8, thereby driving the drive motor 3. The rotational angle position of the gear 16 can be adjusted.

  In addition, the rotation direction position of the key 16c and the apex position of one external tooth 16a of the drive gear 16 are configured to coincide with each other, so that the rotation angle of the resolver 8 is based on the visual recognition of the key position at the time of assembly. Adjustment and rotation angle position adjustment of the drive motor 3 can be facilitated. Further, the key 16c is formed wider than the key 16d and is not erroneously assembled to 4Ab formed narrower than the key groove 4Aa.

  On the outer peripheral surface of the drive gear 16, external teeth 16a projecting toward the outer periphery and trough portions 16b are formed between the external teeth 16a so as to have a smooth curved shape. The inner teeth 17a are formed on the inner peripheral surface 17 so as to protrude in a convex shape toward the inner periphery, and the valleys 17b are formed between the inner teeth 17a so as to have a smooth curved shape. The outer teeth 16a and the valleys 17b of the driven gear 17 mesh with each other, and the valleys 16b of the drive gear 16 and the inner teeth 17a of the driven gear 17 mesh with each other. As a result, when the drive gear 16 is rotationally driven in the rotational direction ω, the outer peripheral surface of the driven gear 17 is slidably rotatable along the inner surface of the cylindrical hole of the case (not shown). It is rotationally driven by ω.

  In the mechanical oil pump 7 configured as described above, when the meshing portion of the drive gear 16 and the driven gear 17 rotates in the rotational direction ω, the outer peripheral surface of the drive gear 16 and the driven gear 17 at the portion corresponding to the suction port 7a. By gradually expanding the space between the inner peripheral surface, oil is sucked into the space between them, and the oil is confined in the space in the section A partitioning the suction port 7a and the discharge port 7b. In the portion corresponding to the discharge port 7b, the space between the outer peripheral surface of the drive gear 16 and the inner peripheral surface of the driven gear 17 is gradually reduced, so that oil is compressed into the space between them, and the discharge port Hydraulic pressure is generated from 7b.

  By the way, when the drive gear 16 and the driven gear 17 are rotationally driven, in consideration of prevention of burn-in, etc., there is a slight clearance between the vertices of the outer teeth 16a of the drive gear 16 and the inner teeth 17a of the driven gear 17. In addition, a slight clearance is also required between the drive gear 16 and the driven gear 17 and a case (not shown) that slidably supports them, that is, driving between the suction port 7a and the discharge port 7b. It is difficult to completely seal with the gear 16 and the driven gear 17, and an oil leakage amount is generated based on the hydraulic pressure acting from the electric oil pump 10 that is being driven while the mechanical oil pump 7 is stopped.

  However, depending on the rotational direction position ωp of the drive gear 16 (note that the rotational direction position of the driven gear 17 is determined by the rotational direction position of the drive gear 16), the leakage amount fluctuates, that is, the position where the leakage amount becomes maximum, There is a position where the amount of leakage is minimized. That is, as shown in FIG. 3A, the apex of the external teeth 16a of the drive gear 16 and the apex of the internal teeth 17a of the driven gear 17 are opposed to each other in the section A that partitions the suction port 7a and the discharge port 7b. At the rotational angle position ωp1, the clearance between the vertices of the external teeth 16a of the drive gear 16 and the internal teeth 17a of the driven gear 17 is minimized, and is between the suction port 7a and the discharge port 7b. Since the teeth 17a form a partition, the leakage amount Q varies depending on the hydraulic pressure P applied from the electric oil pump 10 as shown in FIG. 4, but the minimum leakage amount Qmin. It becomes.

  On the contrary, as shown in FIG. 3B, at the rotation angle position ωp2 where the vertex of the external tooth 16a of the drive gear 16 and the vertex of the internal tooth 17a of the driven gear 17 are moved by a half pitch, the suction port 7a and the exhaust port 7a are exhausted. In the section A partitioning the outlet 7b, the clearance between the outer teeth 16a and the inner teeth 17a is shifted and the clearance is increased, and the space between the valley section 16b and the valley section 17b in the section A is increased. Since the suction port 7a and the discharge port 7b are bridged and communicated with each other, the leakage amount Q is a maximum that varies depending on the hydraulic pressure P applied from the electric oil pump 10 being driven, as shown in FIG. Leakage amount Qmax.

  Assuming that the hydraulic pressure P acting on the mechanical oil pump 7 being stopped from the electric oil pump 10 being driven is constant, the relationship between the rotational direction position ωp of the drive gear 16 and the leakage amount ratio (variation ratio) Qr is shown in FIG. A sine wave shape as shown in FIG. That is, at the rotational direction position ωp1 of the drive gear 16 shown in FIG. 3A, the leakage amount ratio Qr becomes the minimum value Qrmin, and at the rotational direction position ωp2 of the drive gear 16 shown in FIG. It becomes. If the leak rate ratio Qr is less than or equal to the allowable range Qrp, the hydraulic pressure is not significantly lost and it can be said that it is within the allowable range. Accordingly, the rotational direction position ωp of the drive gear 16 when the mechanical oil pump 7 is stopped is adjusted within the range of the section Z shown in FIG. 5 with the rotational direction position ωp1 shown in FIG. It is preferable.

  In the above description, the relationship of the leakage amount at the stop position of the mechanical oil pump 7 while the electric oil pump 10 is driven has been described. However, the stop position of the electric oil pump 10 while the mechanical oil pump 7 is driven. The same applies to the leakage amount relationship. Further, the positional relationship between the drive gear of the electric oil pump 10 and the drive shaft 11A of the electric motor 11 is also detected by the resolver 12 in the same manner by inserting a key into the key groove as in FIG. The position adjustment control based on is enabled.

  Next, the position adjustment control of the drive gear 16 will be described with reference to FIGS. The hybrid control unit 21 starts the position adjustment control while the vehicle 100 is traveling (S1), and at time t1, for example, the driver requests to decelerate the vehicle 100 by depressing the foot brake. When the operation is performed, the internal combustion engine 2 is stopped (S2), the first clutch 6 is released, the internal combustion engine 2 is disconnected from the vehicle drive system, and regenerative control by the drive motor 3 is executed (S3). As a result, the vehicle speed of the vehicle 100 is gradually reduced, and the rotational speed of the drive motor 3 also decreases. At time t2, when the stop of the vehicle 100 is determined based on the detection result of a vehicle speed sensor (not shown) (S4), the second clutch 4C built in the automatic transmission 4 is released (S5), that is, The automatic transmission 4 is set to the neutral state.

  When the vehicle 100 is thus stopped, the rotation of the vehicle drive system (particularly, the input shaft 4A of the automatic transmission 4) is stopped, so that the rotational drive of the mechanical oil pump 7 is stopped. Then, the hybrid control unit 21 starts driving the electric motor 11 and starts supplying hydraulic pressure by the electric oil pump 10 in order to secure the hydraulic pressure supply to the hydraulic control device 14 (hydraulic pressure adjusting unit) (see FIG. 2). .

  Subsequently, when the vehicle 100 is stopped as described above and the first clutch 6 and the second clutch 4C are released, the drive motor 3 and its drive shaft 3A, the input shaft 4A of the automatic transmission 4, the resolver 8, Since the mechanical oil pump 7 is in a freely rotatable state, the control shifts to the position adjustment control of the stop position in the rotational direction of the mechanical oil pump 7 (drive gear 16).

  That is, first, the hybrid control unit 21 detects the angular position in the rotational direction of the drive shaft 3A stopped by the resolver 8, that is, the rotational direction position ωp of the drive gear 16 (S6). Subsequently, the hybrid control unit 21 determines whether or not the rotational direction position ωp of the drive gear 16 is within the range of the section Z (see FIG. 5) described above (S7).

  Here, when the rotational direction position ωp of the drive gear 16 is not within the range of the section Z (No in S7), the rotational direction position ωp1 (that is, the apex of the external teeth 16a of the drive gear 16) shown in FIG. By driving the drive motor 3 with the target of the position facing the apex of the internal teeth 17a of the driven gear 17 (S8), the stopped drive gear 16 is driven to rotate again, and the resolver 8 drives the drive gear 16 Is detected (S6), and the position of the drive gear 16 is adjusted until the rotational direction position ωp of the drive gear 16 is within the range of the section Z. At time t3, when the rotational direction position ωp of the drive gear 16 is within the range Z (Yes in S7), the drive motor 3 is stopped and the position adjustment control is terminated (S10).

  As described above, the rotational direction position ωp of the drive gear 16 of the mechanical oil pump 7 is adjusted within the range of the section Z, so that the oil based on the hydraulic pressure acting from the driving electric oil pump 10 as described above can be obtained. The leakage amount ratio Qr is suppressed to the allowable range Qrp or less. Thereby, since the hydraulic pressure loss due to the oil leakage of the mechanical oil pump 7 that is stopped is significantly reduced, it is possible to eliminate the need to provide a check valve or the like in the oil passage a1, for example.

  Thereafter, at time t4, for example, when the driver performs a driving operation requesting the start of the vehicle 100 by releasing the foot brake pressure and depressing the accelerator pedal, the second clutch 4C of the automatic transmission 4 is engaged. At the same time, power running control by the drive motor 3 is started, and the vehicle 100 is started in a so-called EV traveling state. At time t5, when the vehicle speed becomes equal to or higher than the predetermined vehicle speed, the hybrid control unit 21 determines that the internal combustion engine 2 is started, ignites and starts the internal combustion engine 2, and engages the first clutch 6. By t6, the vehicle shifts to an assist travel state in which both the internal combustion engine 2 and the drive motor 3 are used as drive sources, and thereafter, the internal combustion engine 2 and the drive motor 3 are based on the accelerator opening, the remaining amount of the battery 31, and the like. It will be in a running state that is properly used.

  By the way, at the timing when the vehicle is started and the mechanical oil pump 7 is driven (after time t4), the hydraulic oil supply from the electric oil pump 10 becomes unnecessary based on the increase in hydraulic pressure from the mechanical oil pump 7. The drive of the electric motor 11 is stopped and the electric oil pump 10 is stopped. In this case, the amount of leakage in the stopped electric oil pump 10 can be made to be within the allowable range Qrp by driving the electric motor 11 and adjusting the position in the same manner as in steps S6 to S9. Thereby, since the hydraulic pressure loss due to the oil leakage of the stopped electric oil pump 10 is significantly reduced, it is unnecessary to provide a check valve or the like in the oil passage a2, for example.

  As described above, according to the hybrid drive device 1, after one of the mechanical oil pump 7 and the electric oil pump 10 is stopped, the other oil pump that is operating acts on the stopped oil pump. After stopping the drive motor 3 or the electric motor 11 again, the ratio of the amount of oil leakage that fluctuates according to the stop position in the rotation direction of the oil pump that is stopped based on the hydraulic pressure to be stopped is less than the allowable range. Since the position of the stop position of the oil pump to be stopped is controlled by drive control, the amount of leakage due to hydraulic backflow in the stopped oil pump can be greatly reduced, and the mechanical oil pump 7 and the electric oil pump 10 are reduced. It is unnecessary to provide a check valve in the oil passages a1 and a2 connected to the discharge port. As a result, the hybrid drive device can be made compact, and the automatic transmission 4 can be shared with an automatic transmission that uses only the internal combustion engine as a drive source.

  Further, when adjusting the stop position of the stopped oil pump, for example, taking the mechanical oil pump 7 as an example, in the section A between the suction port 7a and the discharge port 7b, the external teeth of the drive gear 16 are provided. Since the position where the apex of 16a and the apex of the internal teeth 17a of the driven gear 17 face each other is targeted, that is, the position where the amount of leakage of the stopped oil pump is the smallest can be targeted.

  Furthermore, in the series-type hybrid drive device 1 as described in the present embodiment, the first clutch 6 and the second clutch 4C are disengaged, so that the drive motor 3 for the vehicle drive system is replaced with the internal combustion engine 2 and It is possible to adjust the position of the mechanical oil pump 7 that is drivingly connected to the driving motor 3 after cutting the drive transmission to the wheel 90.

  In particular, since the second clutch 4C is a shift clutch built in the automatic transmission 4, there is no need to provide a new clutch between the automatic transmission 4 and the drive motor 3, and the automatic shift by the shift clutch. By setting the machine 4 to the neutral state, the drive transmission between the drive motor 3 and the wheels 90 can be disconnected.

  Further, when the drive shaft 3A of the drive motor 3 and the mechanical oil pump 7 are assembled, the key groove 4Aa is provided as a positioning means for positioning the relative angular positions of each other, so that the drive motor 3 and the resolver 8 The rotational angle position of the mechanical oil pump 7 with respect to the drive gear 16 can be uniquely determined, thereby making it possible to adjust the position of the mechanical oil pump 7 based on the detection of the resolver 8. can do.

  In the above-described embodiment, the hybrid drive device 1 has been described as an example of the vehicle drive device. However, in the idle stop vehicle drive device, the electric vehicle drive device, and the like, two oil pumps are provided. The present invention can be applied to any drive device provided in parallel. Moreover, although the hybrid drive device 1 has been described as a series type, two oil pumps are arranged in parallel in the same manner even if the type is a so-called parallel type, split type, or series / parallel type. The present invention can be applied to any drive device.

  Moreover, in this Embodiment demonstrated above, after stopping the vehicle 100, although the case where the drive motor 3 was driven and the rotational position of the mechanical oil pump 7 was adjusted was demonstrated, the case where the vehicle 100 is stopped In accordance with the above, the rotational position of the mechanical oil pump 7 may be adjusted. In this case, when the vehicle 100 is in an inertial running state, the first clutch 6 is released and the internal combustion engine 2 is stopped, and then the motor changes according to the operation of the accelerator or the foot brake in accordance with the stop of the vehicle 100. The second clutch 4 </ b> C is slipped so that the change in output torque is not transmitted to the vehicle 100. At this time, when the drive motor 3 is stopped while controlling the slip state of the second clutch 4C, the drive motor 3 is stopped in consideration of the rotational position of the mechanical oil pump 7.

  In the present embodiment, the mechanical oil pump 7 and the electric oil pump 10 are so-called inscribed gear type oil pumps. However, the present invention is not limited to this, and a vane type oil pump, a crescent type oil pump is used. Even if it is a gear type oil pump, a circumscribed type gear type oil pump, etc., the present invention can be applied as long as it is an oil pump whose oil leakage amount varies depending on the stop position. Of course, as an inscribed gear type oil pump, the tooth surface may be formed in a trochoid shape.

  In the present embodiment, the automatic transmission 4 has been described as an example of a multi-stage automatic transmission having a plurality of shift clutches (second clutches) 4C. However, the present invention is not limited to this, and the belt-type continuously variable transmission is not limited thereto. Or an automatic transmission having a clutch capable of cutting power transmission in a neutral state. In particular, if the automatic transmission does not have a built-in clutch that can cut power transmission, a separate clutch that can cut power transmission between the drive motor and the wheels may be provided. Furthermore, when the automatic transmission has a starting clutch or the like, this may be used as the second clutch.

1 Vehicle drive device (hybrid drive device)
2 Internal combustion engine 2A Output shaft 3 First rotating electrical machine (drive motor)
3A Drive shaft 4Aa Positioning means (keyway)
4Ab positioning means (keyway)
4 Automatic transmission 4C Second clutch (shifting clutch)
6 First clutch 7 First oil pump (mechanical oil pump)
7a Intake port 7b Outlet port 8 Rotation angle sensor (resolver)
10 Second oil pump (electric oil pump)
11 Second rotating electrical machine (electric motor)
11A Drive shaft 13 Oil passage structure 16 Drive gear 16a External tooth 16c Positioning means (key)
16d Positioning means (key)
17 Driven gear 17a Internal tooth 21 Control part (hybrid control part)
90 Wheel a1, a2 Oil passage Qr Leakage ratio Qrp Allowable range ωp Stop position in the rotation direction

Claims (4)

A first oil pump drivingly connected to the drive shaft of the first rotating electrical machine;
A second oil pump drive-coupled to a drive shaft of a second rotating electrical machine that can be driven independently of the first rotating electrical machine;
An oil passage structure in which two oil passages communicating with each of the first oil pump and the second oil pump are joined and connected to a hydraulic pressure adjusting unit, and oil flows through each oil passage;
A control unit that drives and controls the other oil pump while one oil pump of the first oil pump and the second oil pump is stopped,
The control unit is configured so that the ratio of the amount of oil leakage that fluctuates according to the stop position in the rotation direction of the one oil pump is equal to or less than an allowable range when the one oil pump is stopped or after the one oil pump is stopped. Driving and controlling the rotary electric machine that drives the one oil pump of the first rotary electric machine and the second rotary electric machine, and adjusting the position of the stop position of the one oil pump;
The vehicle drive device characterized by the above-mentioned. The first oil pump and the second oil pump each have a drive gear with external teeth formed, a driven gear with internal teeth formed, an intake port for sucking oil, and a discharge port for discharging oil. It consists of a gear type oil pump,
When the position of the stop position of the one oil pump being stopped is adjusted, the control unit is located between the suction port and the discharge port, and the vertex of the external teeth of the drive gear and the vertex of the internal teeth of the driven gear Target the position where and
The vehicle drive device according to claim 1. A first clutch capable of interrupting transmission of driving force between the output shaft of the internal combustion engine and the drive shaft of the first rotating electrical machine capable of driving the wheels;
An automatic transmission that is drivingly connected to the drive shaft of the first rotating electrical machine and that can change the rotation of the drive shaft and output it to the wheels;
A second clutch capable of connecting / disconnecting drive transmission between the drive shaft of the first rotating electrical machine and the wheel,
The controller is configured to perform the position adjustment on the first oil pump after releasing the first clutch and the second clutch.
The vehicle drive device according to claim 1, wherein the vehicle drive device is a vehicle drive device. A rotation angle sensor for detecting a rotation position of a drive shaft of the first rotating electrical machine;
Positioning means for positioning relative angular positions of the drive shaft of the first rotating electrical machine and the first oil pump when the first oil pump is assembled;
The control unit performs the position adjustment with respect to the first oil pump based on a rotation position detected by the rotation angle sensor.
The vehicle drive device according to claim 1, wherein the vehicle drive device is a vehicle drive device.

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