WO2015046578A1 - 車両用油圧供給装置 - Google Patents
車両用油圧供給装置 Download PDFInfo
- Publication number
- WO2015046578A1 WO2015046578A1 PCT/JP2014/076135 JP2014076135W WO2015046578A1 WO 2015046578 A1 WO2015046578 A1 WO 2015046578A1 JP 2014076135 W JP2014076135 W JP 2014076135W WO 2015046578 A1 WO2015046578 A1 WO 2015046578A1
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- WO
- WIPO (PCT)
- Prior art keywords
- oil passage
- oil
- pump
- discharge
- joint portion
- Prior art date
Links
- 230000005540 biological transmission Effects 0.000 claims description 37
- 238000003860 storage Methods 0.000 claims description 20
- 238000005304 joining Methods 0.000 abstract description 7
- 239000000470 constituent Substances 0.000 description 27
- 230000002093 peripheral effect Effects 0.000 description 14
- 230000015572 biosynthetic process Effects 0.000 description 13
- 238000002485 combustion reaction Methods 0.000 description 13
- 238000003780 insertion Methods 0.000 description 8
- 230000037431 insertion Effects 0.000 description 8
- 230000004323 axial length Effects 0.000 description 6
- 238000005452 bending Methods 0.000 description 6
- 238000003825 pressing Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 238000004891 communication Methods 0.000 description 3
- 230000001276 controlling effect Effects 0.000 description 3
- 239000000446 fuel Substances 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000005192 partition Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K25/00—Auxiliary drives
- B60K25/02—Auxiliary drives directly from an engine shaft
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
- B60W30/1819—Propulsion control with control means using analogue circuits, relays or mechanical links
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
- F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K25/00—Auxiliary drives
- B60K25/02—Auxiliary drives directly from an engine shaft
- B60K2025/026—Auxiliary drives directly from an engine shaft by a hydraulic transmission
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/20—Fluid liquid, i.e. incompressible
- F04C2210/206—Oil
Definitions
- a mechanical oil pump driven by a wheel driving force source an oil passage component forming an oil passage connected to the mechanical oil pump, and supplied from the mechanical oil pump through the oil passage component
- the present invention relates to a vehicle hydraulic pressure supply device including a hydraulic pressure control device that controls the supplied hydraulic pressure and supplies the hydraulic pressure to a vehicle drive transmission device.
- Patent Document 1 As the above-described vehicle hydraulic pressure supply device, for example, a device described in Patent Document 1 below is already known.
- oil discharged from a mechanical oil pump is supplied to a valve body B via an oil passage formed in a partition wall Ma of a case (transmission housing M) that houses a vehicle drive transmission device. It is comprised so that it may be supplied in.
- a vehicular hydraulic pressure supply device that can reduce the bend of the oil passage that conveys the oil discharged from the mechanical oil pump to the valve body, reduce the oil passage, and reduce pressure loss. Realization is desired.
- a mechanical oil pump driven by a driving force source of a wheel, an oil passage component forming an oil passage connected to the mechanical oil pump, and the oil passage configuration from the mechanical oil pump And a hydraulic control device that controls the hydraulic pressure supplied via the member and supplies the hydraulic pressure to the vehicle drive transmission device.
- the rotating shaft of the mechanical oil pump is disposed on an axis different from an input shaft which is a shaft serving as a connecting portion to the driving force source in the vehicle drive transmission device
- the oil passage component is A storage chamber surface constituting a rotor storage chamber in which a first pump rotor which is a pump rotor of the mechanical oil pump is stored; A first discharge oil passage through which oil discharged by the first pump rotor flows; A first member joint formed with an opening of the first discharge oil passage,
- the hydraulic control device includes a valve body that forms an oil passage for adjusting the hydraulic pressure supplied to each supply target of the vehicle drive transmission device and a storage chamber in which a hydraulic control valve for controlling the hydraulic pressure is stored.
- the valve body includes a first body oil passage, and a first body joint portion in which an opening of the first body oil passage is formed, The first member joint and the first body joint are joined in a state of facing each other, and the first discharge oil passage and the first body oil passage are connected.
- the rotational shaft of the mechanical oil pump is disposed on a different shaft from the input shaft of the vehicle drive transmission device.
- the degree of freedom can be increased, and the oil passage constituent member can be disposed close to the valve body.
- the oil passage component member includes a storage chamber surface that forms a rotor storage chamber of the mechanical oil pump, and also has a role as a housing of the mechanical oil pump. Therefore, the oil path constituent member can receive the oil discharged from the first pump rotor of the mechanical oil pump at the shortest distance and transport it to the valve body.
- the oil passage component member further includes a first surface that is in contact with an axial end surface of the first pump rotor, and the first surface has a shape recessed inside the oil passage component member, A first discharge port is formed through which oil is discharged from the mechanical oil pump;
- the first discharge oil passage extends from the first discharge port to the opening of the first member joint portion toward the outside in the radial direction with reference to the rotational axis of the mechanical oil pump.
- the first discharge port is formed on the first surface where the axial end surface of the first pump rotor is in contact, oil can be supplied from the first pump rotor to the oil path constituent member at the shortest distance. it can. Since the first discharge oil passage extends from the first discharge port to the opening of the first member joint portion toward the outside in the radial direction with respect to the rotational axis of the mechanical oil pump, The bend of the oil passage of the oil passage can be reduced, the oil passage can be shortened, and the pressure loss can be reduced.
- first member joint portion and the first body joint portion are connected in a state of facing each other directly or via a cylindrical tubular member extending linearly.
- the joint portion is equivalent to the tubular member.
- the oil passage extends, since the first member joint portion and the first body joint portion can be joined in a straight line, bending of the oil passage at the joint portion can be reduced.
- an auxiliary hydraulic source is further provided,
- the oil passage component is A second discharge oil passage through which oil discharged from the auxiliary hydraulic power source flows;
- the valve body further includes a second body oil passage, and a second body joint portion in which an opening of the second body oil passage is formed, It is preferable that the second member joint portion and the second body joint portion are joined in a state of facing each other and the second discharge oil passage and the second body oil passage are connected.
- the oil discharged from the auxiliary hydraulic power source can also be conveyed to the second body oil passage provided in the valve body through the second discharge oil passage provided in the oil passage constituent member. And since the second member joint portion of the oil passage component member and the second body joint portion of the valve body are joined to each other, the bending of the oil passage at the joining portion is reduced, and the oil passage is shortened. Can be planned.
- the auxiliary hydraulic pressure source is preferably an electric oil pump driven by an electric motor, an electromagnetic pump driven by an electromagnetic actuator, or an accumulator.
- the auxiliary hydraulic power source is an electric oil pump driven by an electric motor, and oil discharged by a second pump rotor that is a pump rotor of the electric oil pump flows through the second discharge oil passage.
- the oil passage component is A first surface in contact with an axial end surface of the first pump rotor; It is preferable to further include a second surface that faces in a direction opposite to the first surface and that is in contact with the axial end surface of the second pump rotor.
- the axial end surface of the first pump rotor of the mechanical oil pump is disposed in contact with the first surface of the oil path constituent member, and the second surface facing the direction opposite to the first surface is electrically driven.
- the axial end surface of the second pump rotor of the oil pump is disposed in contact. Therefore, the oil path constituent member can also receive the oil discharged from the second pump rotor of the electric oil pump at the shortest distance and transport it to the valve body.
- the oil passage component member includes an oil passage and an electric oil pump connected to the mechanical oil pump by efficiently arranging a mechanical oil pump and an electric oil pump on the first surface and the second surface. Since the oil passage to be connected can be formed efficiently, the vehicle hydraulic pressure supply device can be reduced in size.
- the second surface has a shape that is recessed inside the oil passage component, and a second discharge port is formed through which oil is discharged from the electric oil pump.
- the second discharge oil passage is preferably extended from the second discharge port to the opening of the second member joint portion toward the outside in the radial direction with reference to the rotation axis of the electric oil pump. .
- the second discharge port is formed on the second surface that is in contact with the axial end surface of the second pump rotor, oil can be supplied from the second pump rotor to the oil path constituent member at the shortest distance. it can.
- the second discharge oil passage extends from the second discharge port to the opening of the second member joint portion toward the outside in the radial direction with respect to the rotation axis of the electric oil pump. The bend of the oil passage of the passage can be reduced, the oil passage can be shortened, and the pressure loss can be reduced.
- the oil passage component member is A suction oil passage through which oil sucked by the first pump rotor flows; A return hole for returning the oil discharged by the first pump rotor to the suction oil passage; A third member joint portion in which the opening of the return hole is formed,
- the valve body includes a third body oil passage, and a third body joint portion in which an opening of the third body oil passage is formed, It is preferable that the third member joint portion and the third body joint portion are joined in a state of facing each other and the third body oil passage is connected to the return hole.
- the oil passage component member is A suction oil passage through which oil sucked by the first pump rotor flows; A return hole for returning the oil discharged by the first pump rotor to the suction oil passage; A third member joint portion in which the opening of the return hole is formed,
- the valve body includes a third body oil passage, and a third body joint portion in which an opening of the third body oil passage is formed, The third member joint and the third body joint are joined in an opposing state, and the third body oil passage is connected to the return hole,
- the first member joint, the second member joint, and the third member joint are formed on the same surface or surfaces parallel to each other, and these extend the rotation axis of the first pump rotor. Formed in a plane parallel to the current direction, It is preferable that the second member joint, the first member joint, and the third member joint are arranged in this order from one circumferential side with respect to the rotation axis of the first pump rotor. .
- the first member joint portion, the second member joint portion, and the third member joint portion are formed on the same surface or parallel to each other.
- the joint structure between the body joint portion and the third body joint portion can be simplified, and the joint seal structure can be simplified.
- the processing of the oil passage constituent member and the valve body can be facilitated. Since the first member joint, the second member joint, and the third member joint are formed on surfaces parallel to the extending direction of the rotation axis of the first pump rotor, the first discharge oil passage, It is easy to extend the two discharge oil passages and the return holes outward in the radial direction so as to open at the respective joint portions.
- the 1st member junction part is arrange
- the discharge capacity of the mechanical oil pump is larger than the discharge capacity of the electric oil pump, the effect of reducing the pressure loss can be increased.
- the 2nd member junction part, the 1st member junction part, and the 3rd member junction part are arranged side by side in the circumferential direction, it can suppress that the width
- the axial length of the entire apparatus can be shortened.
- the return hole includes a discharge return oil passage that communicates with the first discharge oil passage and returns the oil in the first discharge oil passage to the suction oil passage.
- the return hole accommodates a return oil passage control valve that controls the opening of the discharge return oil passage,
- the opening of the return hole is an opening for supplying a command oil pressure for operating the return oil passage control valve to the return oil passage control valve,
- the third body oil passage is preferably an oil passage for supplying the command oil pressure.
- the return hole is a body return oil passage for returning the oil in the third body oil passage to the suction oil passage
- the opening of the return hole is an opening for supplying oil to be returned to the suction oil passage
- the third body oil passage is an oil passage through which oil discharged from the hydraulic control valve is circulated.
- oil can be returned from the third body oil passage of the valve body to the suction oil passage through the return hole that is the body return oil passage. Therefore, after discharging excess oil from the valve body to the oil reservoir, the oil discharged from the valve body can be returned to the intake side in a shorter distance than when returning oil from the oil reservoir to the intake oil passage. Loss can be reduced.
- FIG. 1 is a schematic diagram illustrating a schematic configuration of a vehicle hydraulic pressure supply device and a vehicle drive transmission device according to an embodiment of the present invention. It is an axial section of an oil way constituent member, a mechanical oil pump, and an electric oil pump concerning an embodiment of the present invention. It is the figure which looked at the oil-path component member which concerns on embodiment of this invention from the 1st surface side in the axial direction. It is the figure which looked at the oil-path component member which concerns on embodiment of this invention from the 2nd surface side in the axial direction.
- the vehicle hydraulic pressure supply device 1 forms a mechanical oil pump MOP driven by a driving force source of the wheels W and an oil passage connected to the mechanical oil pump MOP.
- An oil path constituent member 2 and a hydraulic control device PC that controls the hydraulic pressure supplied from the mechanical oil pump MOP via the oil path constituent member 2 and supplies the hydraulic pressure to the vehicle drive transmission device 3 are provided.
- the vehicle hydraulic pressure supply device 1 is accommodated in a case CS that accommodates the vehicle drive transmission device 3.
- the vehicle hydraulic pressure supply device 1 further includes an electric oil pump EOP that is driven by an electric motor MG.
- the oil path component 2 further forms an oil path connected to the electric oil pump EOP.
- the hydraulic control device PC is also supplied with hydraulic pressure from the electric oil pump EOP via the oil passage constituting member 2.
- the oil path constituent member 2 was discharged by the first pump rotor R1 and the storage chamber surface 11 constituting the first rotor storage chamber 17 in which the first pump rotor R1, which is the pump rotor of the mechanical oil pump MOP, is stored.
- a first discharge oil passage 50 through which oil flows and a first member joint portion 53 in which an opening of the first discharge oil passage 50 is formed are provided.
- the hydraulic control device PC includes a valve body VB that forms a storage chamber in which an oil passage for adjusting the hydraulic pressure supplied to each supply target of the vehicle drive transmission device 3 and a hydraulic control valve for controlling the hydraulic pressure is stored. I have.
- the valve body VB includes a first body oil passage 60 and a first body joint portion 63 in which an opening of the first body oil passage 60 is formed.
- the first discharge oil passage 50 and the first body oil passage 60 are connected by joining the first member joint portion 53 and the first body joint portion 63 so as to face each other.
- each configuration will be described in detail.
- the vehicle drive transmission device 3 is drivingly connected to an internal combustion engine ENG as a driving force source for driving the vehicle, and converts the rotational driving force of the internal combustion engine ENG into a torque converter TC.
- the speed is changed by the speed change device TM and transmitted to the wheels W.
- the internal combustion engine ENG is a heat engine that is driven by the combustion of fuel.
- various known internal combustion engines such as a gasoline engine and a diesel engine can be used.
- the torque converter TC transmits driving force between the input-side (drive-side) pump impeller TCa and the output-side (driven-side) turbine runner TCb via oil filled therein.
- the torque converter TC includes a lockup clutch LC that connects the pump impeller TCa and the turbine runner TCb so as to rotate together. Oil that has been regulated by the hydraulic control device PC is supplied to the torque converter TC including the lockup clutch LC.
- the speed change device TM is configured to shift the rotation of an input shaft, which is a shaft serving as a connecting portion to the internal combustion engine ENG, at a predetermined speed ratio and transmit it to the output shaft.
- the transmission apparatus TM is a stepped automatic transmission apparatus having a plurality of shift speeds having different gear ratios, and a plurality of engagements such as clutches and brakes are formed in order to form the plurality of shift speeds.
- a gear mechanism such as a device and a planetary gear mechanism is provided.
- the rotation state of the gear mechanism is switched according to the engagement or release of the plurality of engagement apparatuses, and each shift stage is formed.
- the driving force transmitted to the output shaft is distributed and transmitted to the left and right axles via the counter gear mechanism CG and the differential gear unit DF, and is transmitted to the wheels W that are drivingly connected to the respective axles.
- a torque converter TC, a transmission TM, a counter gear mechanism CG, a differential gear device DF, and the like constituting the vehicle drive transmission device 3 are accommodated in a case CS.
- the case CS includes an outer wall formed so as to cover the outside of the vehicle drive transmission device 3. Further, the case CS is a part for supporting or isolating the torque converter TC, the transmission device TM, the counter gear mechanism CG, the differential gear device DF, and the power transmission member that couples them and transmits the power.
- a partition wall covering the entire or entire surface is provided.
- the vehicle hydraulic pressure supply device 1 includes a hydraulic pressure source and a hydraulic pressure control device PC that controls the hydraulic pressure supplied from the hydraulic pressure source and supplies the hydraulic pressure to the vehicle drive transmission device 3.
- the vehicular hydraulic pressure supply device 1 includes a mechanical oil pump MOP driven by a driving force source of the wheels W and an auxiliary hydraulic pressure source as hydraulic pressure sources.
- the auxiliary hydraulic power source is an electric oil pump EOP driven by the electric motor MG.
- the hydraulic control device PC includes a hydraulic circuit including an oil passage and a plurality of hydraulic control valves for adjusting the hydraulic pressure supplied to each supply target of the vehicle drive transmission device 3.
- the hydraulic control valve includes a solenoid valve that generates a signal pressure, a switching valve that switches an oil passage, a pressure regulating valve that regulates hydraulic pressure, and the like.
- the oil adjusted to the required hydraulic pressure by the hydraulic control device PC is supplied to the plurality of engagement devices of the transmission TM, the torque converter TC, the vehicle drive transmission device 3 such as the lockup clutch LC, and the like. Supplied to each supply object to engage or release the engagement device, used as oil for power transmission of the torque converter TC, used for lubrication of gears, bearings, etc., friction plate of the engagement device It is used for cooling.
- Valve body VB The hydraulic control device PC includes a valve body VB that forms a storage chamber in which an oil passage for adjusting the hydraulic pressure supplied to each supply target of the vehicle drive transmission device 3 and a hydraulic control valve for controlling the hydraulic pressure is stored.
- the valve body VB is a plate-like member that is thick in appearance, and a plurality of plate-like members are stacked via a separate plate or the like.
- the valve body VB is formed with a large number of oil passages stretched inside, a cylindrical storage chamber for storing a spool, a spring, and the like that constitute a hydraulic control valve.
- the valve body VB includes a fixing portion that is fixed to the case CS, and is fixed to the case CS by a fastening bolt or the like.
- the valve body VB includes a first body oil passage 60 and a first body joint portion 63 in which an opening of the first body oil passage 60 is formed.
- the first body joint portion 63 is joined to the first member joint portion 53 of the oil passage constituent member 2, and the first body oil passage 60 is connected to the first discharge oil passage 50 of the oil passage constituent member 2.
- the valve body VB further includes a second body oil passage 61 and a second body joint portion 64 in which an opening of the second body oil passage 61 is formed.
- the second body joint portion 64 is joined to the second member joint portion 54 of the oil passage constituting member 2, and the second body oil passage 61 is connected to the second discharge oil passage 51 of the oil passage constituting member 2.
- the valve body VB includes a third body oil passage 62 that supplies command oil pressure to the return oil passage control valve 40 and a third body joint portion 65 in which an opening of the third body oil passage 62 is formed. .
- the third body joint portion 65 is joined to the third member joint portion 55 of the oil passage constituent member 2, and the third body oil passage 62 is connected to the command pressure oil passage 47 of the oil passage constituent member 2.
- the first member 66 and the second member 67 are overlapped via a separate plate 68.
- the first member 66 and the second member 67 are both formed in a plate shape, and the overlapping surface 69 of the first member 66 and the second member 67 is a flat surface.
- the first body joint portion 63, the second body joint portion 64, and the third body joint portion 65 joined to the oil passage constituent member 2 are the oil passage constituent member 2 side in the valve body VB (first plate member 66). It is formed in the edge part.
- the formation surface on which the body joint portions 63, 64, 65 are formed is a plane parallel to the overlapping surface 69 of the valve body VB.
- Each of the body joint portions 63, 64, 65 is provided in a protruding portion that protrudes toward the oil passage component member 2 in the direction perpendicular to the overlapping surface 69.
- the openings formed in the body joint portions 63, 64, and 65 are open to the oil passage constituting member 2 side.
- the first body oil passage 60, the second body oil passage 61, and the third body oil passage 62 are respectively along the direction orthogonal to the overlapping surface 69 from the openings of the corresponding body joint portions 63, 64, 65. It extends to the valve body VB side.
- the oil supplied to the hydraulic control valve is adjusted to a predetermined hydraulic pressure such as a line pressure.
- Oil pressure adjusted by a hydraulic control valve such as a solenoid valve, oil drained from a hydraulic control valve such as a regulator valve, and the like are supplied to the third body oil passage 62 as a command hydraulic pressure.
- Oil pump ⁇ Rotating shaft> the rotational axis A1 of the mechanical oil pump MOP (hereinafter referred to as the first rotational axis A1) and the rotational axis A2 of the electric oil pump EOP (hereinafter referred to as the second rotational axis A1).
- the rotation axis A2) is arranged in parallel. Therefore, the axial direction is a direction common to these two rotation axes A1 and A2.
- the direction from the electric oil pump EOP to the mechanical oil pump MOP in the axial direction (left side in FIG. 3) is defined as the first axial direction X1, and the opposite direction is from the mechanical oil pump MOP to the electric oil pump EOP.
- the direction (the right side in FIG. 3) is defined as the axial second direction X2.
- “parallel” includes a substantially parallel state in which there is a slight inclination due to a manufacturing error or the like.
- the first rotation axis A1 and the second rotation axis A2 are arranged close to each other. Specifically, the first rotation axis A1 is disposed so as to overlap with the second rotation axis S2 of the electric oil pump EOP when viewed in the axial direction.
- the second rotation axis A2 is arranged so as to overlap with the first rotation axis S1 of the mechanical oil pump MOP when viewed in the axial direction.
- the first rotation axis A1 and the second rotation axis A2 are arranged coaxially. Further, the first rotation axis A1 and the second rotation axis A2 are disposed on an axis different from the rotation axis of the driving force source of the wheel W.
- the first rotation axis A1 and the second rotation axis A2 are parallel to the formation surface on which the first member joint 53 is formed.
- the mechanical oil pump MOP is an oil pump that sucks oil from the first suction port PI1 and discharges it to the first discharge port PO1 when the first pump rotor R1 rotates by the driving force of the driving force source of the wheel W. is there.
- a gear pump, a vane pump, etc. can be used for such a mechanical oil pump MOP.
- the mechanical oil pump MOP is a gear pump, and a first outer rotor R1o having a gear on the inner side and a first inner rotor having a gear on the inner side and having a gear on the outer side as the first pump rotor R1.
- R1i, and the center of the first outer rotor R1o and the first inner rotor R1i is eccentric and meshed.
- the trochoid pump is not provided with a crescent.
- the first pump rotor R1 is housed in a cylindrical first rotor housing chamber 17 formed in the first pump housing PH1.
- the outer peripheral surface of the first outer rotor R1o is in contact with the inner peripheral surface of the first rotor accommodating chamber 17 and is rotatably supported.
- the axial length of the first rotor accommodating chamber 17 matches the axial length of the first pump rotor R1.
- an axial through hole 15 is formed at the center of the first inner rotor R1i, and the first rotary shaft S1 passes through the through hole 15 and is connected to rotate integrally. ing.
- the first rotation axis A1 coincides with the rotation axis of the first rotation axis S1.
- the end portion of the first rotating shaft S1 that protrudes toward the second axial direction X2 with respect to the first pump rotor R1 is inserted into the shaft support hole HS formed in the first surface F1 of the oil passage component member 2, It is rotatably supported.
- the first pump housing PH1 that covers the first axial direction X1 side of the first pump rotor R1 is formed with an axial through hole 16, and the first rotation shaft S1 passes through the through hole 16 and rotates. Supported as possible.
- the first pump housing PH1 covers and covers the rotor housing housing member PH1a that forms the outer peripheral surface of the first rotor housing chamber 17, and the end surfaces on the first axial direction X1 side of the first pump rotor R1 and the rotor housing housing member PH1a.
- the rotor housing member PH1a is a member having the same length as the axial length of the first pump rotor R1.
- the first rotating shaft S1 passes through the through hole 16 and protrudes toward the first axial direction X1.
- An input gear Gi is connected to an end of the first rotation shaft S1 on the side in the first axial direction X1 so as to rotate integrally.
- the input gear Gi is connected to a drive gear Go provided in a power transmission path that connects the internal combustion engine ENG and the wheels W via a chain CH.
- the drive gear Go is drivingly connected to rotate integrally with the pump impeller TCa of the torque converter TC, and is configured to rotate integrally with the internal combustion engine ENG.
- the case CS includes an intermediate wall 18 that supports a driving force transmission shaft that transmits a driving force of a driving force source from the torque converter TC to the transmission device TM.
- the cover housing member PH ⁇ b> 1 b is integrally formed with the intermediate wall 18. That is, a part of the first pump housing PH1 (cover housing member PH1b) is integrally formed with the case CS.
- the electric oil pump EOP is an oil pump that sucks oil from the second suction port PI2 and discharges it to the second discharge port PO2 when the second pump rotor R2 rotates by the driving force of the electric motor MG.
- a gear pump, a vane pump, etc. can be used for such an electric oil pump EOP.
- the electric oil pump EOP is a gear pump, and as the second pump rotor R2, a second outer rotor R2o having a gear on the inside, and a second inner rotor R2i having a gear on the inside and having a gear on the outside.
- the center of the second outer rotor R2o and the second inner rotor R2i is eccentric and meshed.
- the trochoid pump is not provided with a crescent.
- the second pump rotor R2 is accommodated in a cylindrical second rotor accommodating chamber 27 formed in the second pump housing PH2.
- the outer peripheral surface of the second outer rotor R2o is in contact with the inner peripheral surface of the second rotor accommodating chamber 27 and is rotatably supported.
- the axial length of the second rotor accommodating chamber 27 matches the axial length of the second pump rotor R2.
- an axial through hole 25 is formed at the center of the second inner rotor R2i, and the second rotary shaft S2 passes through the through hole 25 and is connected to rotate integrally. ing.
- the second rotation axis A2 coincides with the rotation axis of the second rotation axis S2.
- An axial through hole 26 is formed in the second pump housing PH2 that covers the second axial direction X2 side of the second pump rotor R2, and the second rotary shaft S2 passes through the through hole 26 and rotates. Supported as possible.
- the motor rotor of the electric motor MG is connected to the end of the second rotating shaft S2 on the side in the second axial direction X2 so as to rotate integrally.
- the electric motor MG has a function as a motor (electric motor) that receives power supplied from a battery or the like to generate power.
- Oil passage component 2 The oil path constituent member 2 forms an oil path connected to the mechanical oil pump MOP and an oil path connected to the electric oil pump EOP.
- the oil passage constituting member 2 is composed of two members, a member 2a on the first axial direction X1 side and a member 2b on the second axial direction X2 side. 5-1.
- Fixed part The oil passage component 2 includes a case fixing part 10 fixed to the case CS.
- the oil passage component member 2 is a part that is fixed to the case CS instead of a part of the case CS, and a driving force transmission mechanism that transmits the driving force of the driving force source to the wheels W is directly or Not indirectly supported.
- the oil path component 2 is different from that in which the oil path is formed in the case CS.
- the oil passage constituting member 2 is provided with a plurality of bolt insertion holes 19 extending in the axial direction and formed with female threads as the case fixing portion 10.
- the fastening bolt 20 is screwed.
- the cover housing member PH1b and the rotor housing housing member PH1a constituting the first pump housing PH1 are formed with bolt through holes 21b and 21a extending in the axial direction, into which the fastening bolts 20 are respectively inserted.
- a plurality of bolt through holes 21 b and 21 a are provided corresponding to the bolt insertion holes 19 formed in the oil passage constituting member 2.
- the fastening bolt 20 is inserted and screwed into the bolt through hole 21b of the cover housing member PH1b, the bolt through hole 21a of the rotor housing housing member PH1a, and the bolt insertion hole 19 of the oil passage constituting member 2 from the first axial direction X1 side.
- the rotor housing member PH1a and the oil passage constituting member 2 are fixed to the cover housing member PH1b.
- the cover housing member PH1b is integrally formed with the intermediate wall 18 constituting the case CS, and the oil passage constituting member 2 is fixed to the case CS.
- the oil path component 2 is provided with the electric pump fixing
- the bolt insertion hole 19 is used in common with the case fixing portion 10 as the electric pump fixing portion 22.
- the second pump housing PH2 is formed with an axially extending bolt through hole 24 into which the fastening bolt 23 is inserted.
- a plurality of bolt through holes 24 are provided corresponding to the bolt insertion holes 19.
- the fastening bolt 23 is inserted and screwed into the bolt through hole 24 of the second pump housing PH2 and the bolt insertion hole 19 of the oil passage constituting member 2 from the second axial direction X2 side, and the second pump housing PH2 is constituted as an oil passage. It is fixed to the member 2. Therefore, the electric oil pump EOP is fixed to the case CS via the oil passage constituting member 2.
- the oil passage component member 2 includes a first surface F1 that is in contact with an end surface FE1 on the second axial direction X2 side of the first pump rotor R1 of the mechanical oil pump MOP.
- the 1st surface F1 comprises the storage chamber surface 11 which comprises the inner surface at the side of the 2nd axial direction X2 of the 1st rotor storage chamber 17 in which 1st pump rotor R1 is accommodated. That is, the oil path component 2 also serves as a housing for the mechanical oil pump MOP.
- the first surface F1 is a plane orthogonal to the first rotation axis A1. As shown in FIGS.
- the first surface F ⁇ b> 1 has a shape that is recessed on the inner side (in this example, the second surface F ⁇ b> 2 side) of the oil passage component member 2,
- a first suction port PI1 for supplying oil and a first discharge in which oil is discharged from a mechanical oil pump MOP having a shape recessed on the inside (in this example, the second surface F2 side) of the oil passage component 2 Port PO1 is formed.
- the first suction port PI1 is a depression on the suction side of the first surface F1 that supplies oil to the gap formed by the first pump rotor R1.
- the first suction port PI1 is formed by the first pump rotor R1 in a region overlapping with the first rotor housing chamber 17 in the axial direction in the depression portion on the suction side of the first surface F1. This is an arcuate region overlapping with the gap when viewed in the axial direction.
- the first suction port PI1 has a gap between the first outer rotor R1o and the first inner rotor R1i in the depression on the suction side of the first surface F1, and the first pump rotor R1 rotates.
- the rotational direction RD1 of the first pump rotor R1 of the mechanical oil pump MOP (hereinafter referred to as the first rotational direction RD1) is a clockwise direction as viewed in the second axial direction X2, as shown in FIG. Yes.
- the first discharge port PO1 is a depression on the discharge side of the first surface F1 from which oil is discharged from a gap formed by the first pump rotor R1.
- the first discharge port PO1 is formed by the first pump rotor R1 in a region overlapping the first rotor accommodating chamber 17 in the axial direction in the discharge-side depression portion of the first surface F1. And a circular arc-shaped region overlapping when viewed from the axial direction.
- the first discharge port PO1 has a gap between the first outer rotor R1o and the first inner rotor R1i in the recess on the discharge side of the first surface F1, and the first pump rotor R1 rotates.
- a region distributed in this case is an arcuate region that overlaps when viewed in the axial direction.
- the oil path component 2 is a surface facing in the direction opposite to the first surface F1, and the end surface FE2 on the first axial direction X1 side of the second pump rotor R2 of the electric oil pump EOP is A second surface F2 in contact therewith is provided.
- the 2nd surface F2 comprises the storage chamber surface 12 which comprises the inner surface at the side of the 1st axial direction X1 of the 2nd rotor storage chamber 27 in which 2nd pump rotor R2 is accommodated. That is, the oil path component 2 also serves as a housing for the electric oil pump EOP.
- the second surface F2 is a plane orthogonal to the second rotation axis A2, and is parallel to the first surface F1. As shown in FIGS. 3 and 5, the second surface F2 has a shape that is recessed on the inner side of the oil passage component 2 (in this example, the first surface F1 side), and oil is supplied to the electric oil pump EOP.
- the second suction port PI2 to be supplied, and the second discharge port PO2 having a shape recessed on the inner side (in this example, the first surface F1 side) of the oil passage component member 2 and for discharging oil from the electric oil pump EOP. And are formed.
- the second suction port PI2 is a depression on the suction side of the second surface F2 that supplies oil to the gap formed by the second pump rotor R2.
- the second suction port PI2 is formed by the second pump rotor R2 in a region overlapping with the second rotor accommodating chamber 27 in the axial direction in the hollow portion on the suction side of the second surface F2. This is an arcuate region overlapping with the gap when viewed in the axial direction.
- the second suction port PI2 has a gap between the second outer rotor R2o and the second inner rotor R2i in the recess on the suction side of the second surface F2, and the second pump rotor R2 rotates.
- a region distributed in this case is an arcuate region that overlaps when viewed in the axial direction.
- the rotational direction RD2 of the second pump rotor R2 of the electric oil pump EOP (hereinafter referred to as the second rotational direction RD2) is a clockwise direction as viewed in the first axial direction X1, as shown in FIG. .
- the second rotational direction RD2 of the electric oil pump EOP is a counterclockwise direction when viewed in the axial second direction X2. Therefore, the second rotation direction RD2 of the electric oil pump EOP is opposite to the first rotation direction RD1 of the mechanical oil pump MOP.
- the second discharge port PO2 is a depression on the discharge side of the second surface F2 from which oil is discharged from a gap formed by the second pump rotor R2.
- the second discharge port PO2 includes a gap formed by the second pump rotor R2 in a region overlapping with the second rotor accommodating chamber 27 in the discharge direction of the second surface F2, and the shaft It is an arcuate region that overlaps when viewed from the direction.
- the second discharge port PO2 has a gap between the second outer rotor R2o and the second inner rotor R2i in the recess on the discharge side of the second surface F2, and the second pump rotor R2 rotates.
- a region distributed in this case is an arcuate region that overlaps when viewed in the axial direction.
- the oil path component 2 includes a suction oil path 57 through which oil sucked by the first pump rotor R1 flows.
- the suction oil passage 57 is shared with the suction oil passage through which the oil sucked by the second pump rotor R2 flows. That is, the suction oil passage 57 is shared between the first pump rotor R1 and the second pump rotor R2.
- the suction oil passage 57 communicates with both the first suction port PI1 and the second suction port PI2 and supplies oil.
- the oil passage component 2 includes a suction joint portion 58 in which an opening of the suction oil passage 57 is formed.
- the suction joint 58 is formed on the outer peripheral surface F3 surrounding the outer edges of the first surface F1 and the second surface F2.
- a portion of the outer peripheral surface F3 (hereinafter referred to as a forming surface) where the suction joint portion 58 is formed is a plane parallel to the axial direction, and the opening formed in the suction joint portion 58 is directed outward in the radial direction. Open.
- a joint portion of the strainer ST is joined to the suction joint portion 58, and the suction oil passage 57 and the strainer ST are connected.
- the strainer ST is disposed in an oil reservoir such as an oil pan OP, and oil is supplied from the strainer ST to the suction oil passage 57.
- the oil path component 2 includes a strainer fixing portion (not shown) that fixes the strainer ST.
- a bolt insertion hole (not shown) that extends in a direction orthogonal to the formation surface and has an internal thread is formed on the formation surface of the suction joint portion 58.
- the fastening bolt is inserted into and screwed into the bolt through hole formed in the strainer ST and the bolt insertion hole of the oil passage component member 2 to fix the strainer ST to the oil passage component member 2 (not shown). Therefore, the strainer ST is fixed to the case CS via the oil passage constituting member 2.
- the oil passage constituent member 2 includes a first discharge oil passage 50 through which oil discharged by the first pump rotor R1 flows.
- the first discharge oil passage 50 is an oil passage for conveying oil supplied from the first discharge port PO1.
- the first discharge oil passage 50 extends from the first discharge port PO1 to the opening of the first member joint portion 53 toward the radially outer side with respect to the first rotation axis A1.
- the oil path component 2 includes a second discharge oil path 51 through which oil discharged from the auxiliary hydraulic power source flows.
- the oil discharged by the second pump rotor R2 flows through the second discharge oil passage 51.
- the second discharge oil passage 51 is an oil passage for conveying oil supplied from the second discharge port PO2.
- the second discharge oil passage 51 extends from the second discharge port PO2 to the opening of the second member joint 54 toward the radially outer side with respect to the second rotation axis A2.
- the first discharge oil passage 50 and the second discharge oil passage 51 are formed independently of each other.
- “independently” means that the first discharge oil passage 50 and the second discharge port PO2 do not communicate with each other in the oil passage constituting member 2.
- the first discharge oil passage 50 is connected to the first body oil passage 60 of the valve body VB, and the second discharge oil passage 51 is connected to the second body oil passage 61 of the valve body VB.
- the first body oil passage 60 and the second body oil passage 61 merge in the valve body VB.
- a first check valve 70 which is a check valve that prevents backflow to the first pump rotor R1 side, is provided in the first body oil passage 60, and a check that prevents backflow to the second pump rotor R2 side.
- a second check valve 71 which is a valve, is provided in the second body oil passage 61. That is, the first check valve 70 and the second check valve 71 are not provided in the oil passage constituting member 2 but are provided in the valve body VB. Since the first check valve 70 and the second check valve 71 are provided outside the oil path constituent member 2, it is possible to suppress an increase in the width (length in the axial direction) of the oil path constituent member 2.
- the oil passage component member 2 includes a first member joint portion 53 in which an opening of the first discharge oil passage 50 is formed.
- the 1st member junction part 53 is formed in the outer peripheral surface F3 surrounding the outer edge of the 1st surface F1 and the 2nd surface F2.
- the first member joint portion 53 and the first body joint portion 63 are joined in a state of facing each other, and the first discharge oil passage 50 and the first body oil passage 60 are connected.
- the joint portion of the oil passage component 2 and the joint portion of the valve body VB are joined to each other, the two joint portions are joined without the case CS, and the two joint portions are It is connected directly or via a linear tubular member in an opposing state.
- the first member joint portion 53 and the first body joint portion 63 are directly connected to face each other.
- the inner diameter of the opening of the first member joint portion 53 is larger than the inner diameter of the first discharge oil passage 50, and the protruding portion of the first body joint portion 63 is fitted inside the opening of the first member joint portion 53. It is comprised so that it may be united.
- the first member joint portion 53 and the first body joint portion 63 may be joined via the seal member by fitting a seal member such as a gasket inside the opening of the first member joint portion 53.
- the oil passage constituting member 2 includes a second member joint portion 54 in which an opening of the second discharge oil passage 51 is formed.
- the second member joint 54 is formed on the outer peripheral surface F3.
- the 2nd member joint part 54 and the 2nd body joint part 64 are joined in the state which opposes, and the 2nd discharge oil path 51 and the 2nd body oil path 61 are connected.
- the 2nd member junction part 54 and the 2nd body oil path 61 are connected in the state which opposes directly.
- the inner diameter of the opening of the second member joint portion 54 is larger than the inner diameter of the second discharge oil passage 51, and the protruding portion of the second body joint portion 64 is fitted inside the opening of the second member joint portion 54. It is comprised so that it may be united.
- the second member joint portion 54 and the second body joint portion 64 may be joined via the seal member by fitting a seal member such as a gasket inside the opening of the second member joint portion 54.
- the oil path component 2 is formed with a return hole 46 for returning the oil discharged by the first pump rotor R ⁇ b> 1 to the suction oil path 57 and an opening of the return hole 46. And a third member joining portion 55.
- the return hole 46 includes a discharge return oil passage 45 that communicates with the first discharge oil passage 50 and returns the oil in the first discharge oil passage 50 to the suction oil passage 57. Further, the return hole 46 accommodates a return oil passage control valve 40 that controls the opening degree of the discharge return oil passage 45.
- the opening of the return hole 46 is an opening for supplying a command hydraulic pressure for operating the return oil path control valve 40 to the return oil path control valve 40, and the third body oil path 62 is an oil path for supplying the command hydraulic pressure. ing. That is, the opening side portion of the return hole 46 serves as a command pressure oil passage 47 through which a command oil pressure for operating the return oil passage control valve 40 flows.
- the discharge return oil passage 45 is provided with suction oil before supplying excess oil to the hydraulic control device PC (valve body VB). Used to return to path 57.
- surplus oil is supplied to the hydraulic control device PC, surplus oil flows through the oil passage in the valve body VB, drains from the hydraulic control valve, returns to the oil pan OP, and is re-inhaled from the strainer ST. The Therefore, the oil passage through which the surplus oil flows becomes longer and the pipe resistance increases, so that the driving load of the mechanical oil pump MOP increases.
- a part of the return hole 46 that accommodates the spool 41 of the return oil passage control valve 40 constitutes the discharge return oil passage 45 and the command pressure oil passage 47.
- the return hole 46 is formed in a columnar shape and opens to the valve body VB side.
- the return hole 46 communicates with the suction oil passage 57 and also communicates with the first discharge oil passage 50.
- the spool 41 is configured by combining a plurality of columnar members.
- the diameters of the discharge-side end portion 42 and the suction-side end portion 43 in the axial direction of the spool 41 match the diameter of the return hole 46, and between the discharge-side end portion 42 and the suction-side end portion 43.
- the intermediate portion 44 has a diameter smaller than that of the return hole 46.
- a cylindrical gap between the outer peripheral surface of the intermediate portion 44 and the inner peripheral surface of the return hole 46 is a discharge return oil passage 45.
- the command hydraulic pressure acts on the discharge-side end surface 48 (hereinafter referred to as command pressure supply surface 48) of the discharge-side end portion 42 of the spool 41.
- the return hole 46 on the discharge side from the command pressure supply surface 48 is a command pressure oil passage 47.
- a portion where the opening on the discharge side of the return hole 46 is formed is a third member joint portion 55 where the opening of the command pressure oil passage 47 is formed.
- the third member joint portion 55 is formed on the outer peripheral surface F3.
- the spool 41 is pushed to the suction side by the pressing force corresponding to the command oil pressure.
- a spring 49 is provided on the suction side of the end portion 43 on the suction side of the spool 41, and the spool 41 is pushed to the discharge side by the pressing force of the spring 49.
- the command oil pressure is not supplied, as shown in FIG. 6, the spool 41 is moved to the discharge side moving end by the pressing force of the spring 49, and the discharge return oil passage 45 and the first discharge oil passage 50 are moved. Although the communication is established, the discharge return oil passage 45 and the suction oil passage 57 are not communicated with each other.
- the spool 41 moves to the suction side, the discharge return oil passage 45 and the first discharge oil passage 50 communicate with each other, and the discharge return oil passage 45. And the suction oil passage 57 communicate with each other.
- the communication opening degree between the discharge return oil passage 45 and the suction oil passage 57 increases and decreases according to the pressure of the command oil pressure, and the amount of oil returned from the first discharge oil passage 50 to the suction oil passage 57 increases and decreases.
- the third member joint portion 55 and the third body joint portion 65 of the valve body VB are joined to face each other, and the third body oil passage 62 is connected to the return hole 46 (command pressure oil passage 47).
- the 3rd member junction part 55 and the 3rd body junction part 65 are connected in the state which opposes directly.
- the third member joint portion 55 is formed on the outer peripheral surface F3.
- the inner diameter of the opening of the third member joint portion 55 is larger than the inner diameter of the command pressure oil passage 47 (return hole 46),
- the protruding portion of the body joint portion 65 is configured to be fitted.
- the third member joint portion 55 and the third body joint portion 65 may be joined via a seal member by fitting a seal member such as a gasket inside the opening of the third member joint portion 55.
- the first member joint portion 53, the second member joint portion 54, and the third member joint portion 55 are formed on surfaces parallel to each other, and these are extending directions (axial direction) of the first rotation axis A1. ) Is formed on a plane parallel to. And it arrange
- the direction perpendicular to the formation surface on which the first member joint 53 is formed is defined as the joint perpendicular direction.
- a direction (upper side in FIGS. 4 to 6) from the oil passage component 2 to the valve body VB in the joint vertical direction is defined as a joint vertical first direction Y1, and the oil passage from the valve body VB which is the opposite direction.
- the direction (the lower side in FIGS. 4 to 6) toward the component member 2 is defined as a joint vertical second direction Y2.
- the first body joint portion 63, the second body joint portion 64, and the third body joint portion 65 are formed on surfaces parallel to each other.
- the formation surface on which the member joint portions 53, 54, and 55 are formed, and the body joint portions 63, 64, and 65 The formed surface is parallel to the formed surface.
- the formation surface of the first member joint portion 53 is parallel to the overlapping surface 69 of the valve body VB, and the vertical direction of the joint portion is a direction perpendicular to the overlapping surface 69.
- the first suction port PI1 and the second suction port PI2 are formed on the joint vertical second direction Y2 side with respect to the first rotation axis A1.
- the suction oil passage 57 extends from the first suction port PI1 and the second suction port PI2 toward the joint vertical second direction Y2.
- the formation surface on which the suction joint portion 58 of the suction oil passage 57 is formed is a plane parallel to the formation surface of the first member joint portion 53 that faces away from the formation surface of the first member joint portion 53. ing.
- the opening formed in the suction joint 58 opens toward the joint vertical second direction Y2.
- the strainer ST is disposed on the joint vertical second direction Y2 side of the surface on which the suction joint 58 is formed.
- first discharge port PO1 and the second discharge port PO2 are formed on the joint vertical first direction Y1 side with respect to the first rotation axis A1, and the first discharge oil passage 50 and the second discharge oil passage. Reference numerals 51 respectively extend outward in the radial direction from the first discharge port PO1 and the second discharge port PO2.
- the first discharge oil passage 50 and the second discharge oil passage 51 do not overlap when viewed in the axial direction but overlap when viewed in the circumferential direction as shown in FIG. 3. Is formed. Thereby, even if two discharge oil paths are provided, the width (length in the axial direction) of the oil path component 2 can be reduced.
- the first rotational direction RD1 of the first pump rotor R1 and the second rotational direction RD2 of the second pump rotor R2 are opposite to each other.
- connection portion between the first discharge oil passage 50 and the first discharge port PO1 is arranged close to the first rotation direction RD1 side of the first discharge port PO1, and the second discharge oil passage 51 and the second discharge port PO2 are arranged. Is disposed close to the second rotation direction RD2 side of the second discharge port PO2. For this reason, the first discharge oil passage 50 and the second discharge oil passage 51 can be arranged so as not to overlap when viewed in the axial direction.
- the first discharge oil passage 50 extends toward the joint vertical first direction Y1.
- the second discharge oil passage 51 is disposed on the second rotation direction RD2 side with respect to the first discharge oil passage 50.
- the formation surface on which the first member joint portion 53 of the first discharge oil passage 50 and the second member joint portion 54 of the second discharge oil passage 51 are formed is a plane parallel to each other and facing the joint portion vertical first direction Y1. Has been.
- the openings formed in the first member joint portion 53 and the second member joint portion 54 open toward the joint portion vertical first direction Y1.
- the discharge return oil passage 45, the return hole 46, and the command pressure oil passage 47 are on the first rotation direction RD1 side with respect to the first discharge oil passage 50 and on the second rotation direction RD2 side with respect to the suction oil passage 57. And extends in the first vertical direction Y1 of the joint portion.
- the discharge return oil passage 45, the return hole 46, and the command pressure oil passage 47 are the first discharge oil passage 50 and the second discharge oil passage 51 except for the communication portion between the first discharge oil passage 50 and the suction oil passage 57. Further, the suction oil passage 57 is formed so as not to overlap in the axial direction but to overlap in the circumferential direction.
- the formation surface on which the third member joint portion 55 of the command pressure oil passage 47 is formed is a plane parallel to the formation surface of the first member joint portion 53 that faces the joint portion vertical first direction Y1.
- the opening formed in the third member joint portion 55 opens toward the joint portion vertical first direction Y1.
- the oil passage component member 2 includes a second member joint 54 and a first member joint from the second rotational direction RD2 side in the circumferential direction with respect to the first rotational axis A1 toward the first rotational direction RD1 side. 53 and the third member joint portion 55 are arranged in this order.
- the 1st member junction part 53 is arrange
- first discharge oil passage 50 and the second discharge oil passage 51 are not provided with an oil passage formed in the case CS therebetween, and the first body oil passage 60 and the second body oil passage 61 of the valve body VB. Therefore, the oil passage can be shortened and the pressure loss can be reduced.
- the embodiment of the present invention is not limited to this. That is, in addition to the internal combustion engine ENG as a driving force source for the wheels W, an electric motor having functions of an electric motor and a generator may be provided. Alternatively, as a driving force source for the wheels W, an electric motor may be provided instead of the internal combustion engine ENG.
- the oil passage constituting member 2 is an example in which the oil passage constituting member 2 is composed of two members, that is, the member 2a on the first axial direction X1 side and the member 2b on the second axial direction X2 side.
- the embodiment of the present invention is not limited to this. That is, the oil passage constituent member 2 may be constituted by one member or may be constituted by three or more members.
- first rotation axis A1 and the second rotation axis A2 coincide and are parallel to each other has been described as an example.
- the embodiment of the present invention is not limited to this.
- the first rotation axis A1 and the second rotation axis A2 may be arranged in parallel but not aligned.
- the first rotation axis A1 and the second rotation axis A2 may be arranged in a direction (including a three-dimensional intersection) intersecting each other without being arranged in parallel.
- first surface F1 and the second surface F2 may be arranged in directions intersecting each other without being arranged in parallel.
- first discharge oil passage 50 and the second discharge oil passage 51 are formed independently of each other.
- the embodiment of the present invention is not limited to this. That is, the first discharge oil passage 50 and the second discharge oil passage 51 may be formed to communicate with each other via a check valve or the like, or the first discharge oil passage 50 and the second discharge oil passage 51 are integrated.
- the common discharge oil passage may be used.
- the suction oil passage 57 is shared between the first pump rotor R1 and the second pump rotor R2 has been described as an example.
- the embodiment of the present invention is not limited to this. That is, the suction oil passage for supplying oil to the first pump rotor R1 and the suction oil passage for supplying oil to the second pump rotor R2 may be formed independently of each other.
- the strainer ST is directly connected to the suction joint 58 as an example.
- the embodiment of the present invention is not limited to this. That is, the strainer ST may be connected to the suction joint portion 58 via an oil passage formed in another member.
- the vehicle hydraulic pressure supply device 1 is provided with the electric oil pump EOP, and the oil passage component member 2 includes the second discharge oil passage 51, the second member joint portion 54, and the second member.
- the suction port PI2 and the second discharge port PO2 are provided and the valve body VB is provided with the second body oil passage 61 and the second body joint portion 64 has been described as an example.
- the embodiment of the present invention is not limited to this. That is, the vehicle hydraulic pressure supply device 1 is not provided with the electric oil pump EOP, the oil passage constituting member 2 is not provided with the second discharge oil passage 51, and the second body oil passage 61 is provided in the valve body VB. Etc. may not be provided.
- the oil passage constituting member 2 is provided with the discharge return oil passage 45, the return hole 46, the command pressure oil passage 47, and the third member joint portion 55, and the valve body VB has the first
- the three body oil passages 62 and the third body joint portion 65 are provided. That is, the oil return component 2 is not provided with the discharge return oil passage 45, the return hole 46, the command pressure oil passage 47, and the third member joint portion 55, and the valve body VB has the third body oil passage 62 and the second passage.
- the three body joint portion 65 may not be provided.
- first member joint portion 53, the second member joint portion 54, and the third member joint portion 55 are formed on surfaces parallel to each other.
- the embodiment of the present invention is not limited to this. That is, the first member joint portion 53, the second member joint portion 54, and the third member joint portion 55 may be formed on the same surface.
- the first member joint portion 53, the second member joint portion 54, and the third member joint portion 55 may be formed on surfaces that are not parallel to each other.
- first body joint portion 63, the second body joint portion 64, and the third body joint portion 65 are formed on surfaces parallel to each other.
- the embodiment of the present invention is not limited to this. That is, the first body joint 63, the second body joint 64, and the third body joint 65 may be formed on the same surface. Alternatively, the first body joint 63, the second body joint 64, and the third body joint 65 may be formed on surfaces that are not parallel to each other.
- the first discharge oil passage 50, the second discharge oil passage 51, the discharge return oil passage 45, and the like do not overlap each other when viewed in the axial direction but overlap when viewed in the circumferential direction.
- the case where it is formed as described above has been described as an example.
- the embodiment of the present invention is not limited to this. That is, the first discharge oil passage 50, the second discharge oil passage 51, the discharge return oil passage 45, and the like may be formed so as to overlap when viewed in the axial direction or not overlap when viewed in the circumferential direction.
- the second member joint portion 54, the first member joint portion 53, and the third member joint portion 55 are arranged in this order from one side in the circumferential direction with the first rotation axis A1 as a reference.
- the case is described as an example.
- the embodiment of the present invention is not limited to this. That is, these may be arranged in an arbitrary order, or may be arranged in an arbitrary manner such as overlapping in the axial direction.
- first member joint portion 53 and the first body joint portion 63 are directly connected to each other.
- the embodiment of the present invention is not limited to this. That is, as shown in FIG. 7, the first member joint portion 53 and the first body joint portion 63 may be connected to each other via a tubular tubular member 72 that extends linearly. Further, the second member joint portion 54 and the second body joint portion 64 may be connected to each other via a cylindrical tubular member 73 extending linearly. The third member joint portion 55 and the third body joint portion 65 may be connected to each other through a tubular member 74 that extends linearly. In the example shown in FIG. 7, these cylindrical members 72, 73, and 74 are formed in a cylindrical shape.
- the auxiliary hydraulic power source is an electric oil pump driven by the electric motor MG
- the embodiment of the present invention is not limited to this. That is, the auxiliary hydraulic pressure source may be an electromagnetic pump SP driven by an electromagnetic actuator as shown in FIG.
- the electromagnetic pump SP is an oil pump that draws oil from the suction port HI and discharges it to the discharge port HO by the driving force of the electromagnetic actuator.
- a pump that repeatedly sucks and discharges oil by a reciprocating motion of a plunger (piston) by electromagnetic force can be used.
- the suction oil passage 57 communicates with the suction port HI and supplies oil to the suction port HI.
- the second discharge oil passage 51 communicates with the discharge port HO, and the oil discharged from the discharge port HO flows therethrough.
- the auxiliary hydraulic power source may be an accumulator AM as shown in FIG.
- the accumulator AM is a pressure accumulator that stores therein the hydraulic pressure generated by the mechanical oil pump MOP and discharges the stored hydraulic pressure to the valve body VB side as necessary.
- the second discharge oil passage 51 through which the hydraulic pressure discharged from the accumulator AM flows and the supply oil passage 75 that supplies the hydraulic pressure generated by the mechanical oil pump MOP to the accumulator AM are shared. It is considered as a common oil passage.
- the accumulator AM includes a solenoid valve 76 on the common oil passages 51 and 75, and can block or communicate the oil flow in the common oil passages 51 and 75.
- the electromagnetic valve 76 is opened when the hydraulic pressure generated by the mechanical oil pump MOP is supplied to the accumulator AM and accumulated, or when the hydraulic pressure accumulated in the accumulator AM is discharged to the valve body VB side.
- the electromagnetic valve 76 is closed.
- the second discharge oil passage 51 which is a common oil passage, is connected to the second body in the valve body VB via the joint between the second member joint 54 and the second body joint 64, as in the above embodiment. It is connected to the oil passage 61.
- the second body oil passage 61 is connected to the first body oil passage 60 to which the hydraulic pressure generated by the mechanical oil pump MOP is supplied in the valve body VB.
- the second check valve 71 is not provided in the second body oil passage 61, and an electromagnetic valve 76 is provided in the oil passage constituent member 2 instead. Therefore, the hydraulic pressure generated by the mechanical oil pump MOP is stored in the accumulator via the first discharge oil passage 50, the first body oil passage 60, the second body oil passage 61, and the second discharge oil passage 51 (common oil passage). Supplied to AM.
- the return hole 46 includes the discharge return oil passage 45 that returns the oil in the first discharge oil passage 50 to the suction oil passage 57, and the return oil passage control valve 40 is provided in the return hole 46.
- the return hole 46 has an opening for supplying command oil pressure
- the third body oil passage 62 is an oil path for supplying command oil pressure.
- the embodiment of the present invention is not limited to this. That is, as shown in FIG. 10, the return hole 46 is a body return oil passage 77 that returns the oil in the third body oil passage 62 to the suction oil passage 57, and the opening of the return hole 46 returns to the suction oil passage 57.
- the third body oil passage 62 may be an oil passage through which oil discharged from the hydraulic control valve of the valve body VB flows. In this case, the return hole 46 communicates with the suction oil passage 57 but does not communicate with the first discharge oil passage 50.
- the present invention includes a mechanical oil pump that is driven by a driving force source of a wheel, an oil path component that forms an oil path connected to the mechanical oil pump, and the oil path component from the mechanical oil pump. And a hydraulic control device that controls the hydraulic pressure supplied via the hydraulic pressure and supplies the hydraulic pressure to the vehicle drive transmission device.
- Vehicle hydraulic pressure supply device 2 Oil passage component 3: Vehicle drive transmission device 10: Case fixing portion 11: Storage chamber surface 17: First rotor storage chamber (rotor storage chamber) 18: Intermediate wall 22: Electric pump fixing part 27: Second rotor accommodating chamber 40: Return oil passage control valve 45: Discharge return oil passage 46: Return hole 47: Command pressure oil passage 50: First discharge oil passage 51: First Two discharge oil passages 53: first member joint portion 54: second member joint portion 55: third member joint portion 57: suction oil passage 58: suction joint portion 60: first body oil passage 61: second body oil passage 62 : Third body oil passage 63: first body joint portion 64: second body joint portion 65: third body joint portion 69: valve body overlap surface A1: first rotation axis (rotation shaft of the first pump rotor) heart) A2: Second rotation axis (rotation axis of the second pump rotor) CS: Case ENG: Internal combustion engine EOP: Electric oil pump (auxiliary hydraulic power source) F1: First surface F2: Second surface F3
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Abstract
Description
前記機械式オイルポンプの回転軸は、前記車両用駆動伝達装置における前記駆動力源への連結部となる軸である入力軸とは異なる軸上に配置され、
前記油路構成部材は、
前記機械式オイルポンプのポンプロータである第一ポンプロータが収容されるロータ収容室を構成する収容室面と、
前記第一ポンプロータにより吐出された油が流通する第一吐出油路と、
前記第一吐出油路の開口が形成された第一部材接合部と、を備え、
前記油圧制御装置は、前記車両用駆動伝達装置の各供給対象に供給する油圧を調整するための油路及びそのための油圧を制御する油圧制御弁が収容された収容室を形成するバルブボディを備え、
前記バルブボディは、第一ボディ油路と、当該第一ボディ油路の開口が形成された第一ボディ接合部と、を備え、
前記第一部材接合部と前記第一ボディ接合部とが対向する状態で接合されて、前記第一吐出油路と前記第一ボディ油路とが接続されている点にある。
従って、機械式オイルポンプから吐出された油をバルブボディまで搬送する油路の曲がりを少なくできると共に、油路の短縮を図ることができ、圧力損失を低減することができる。よって、機械式オイルポンプの駆動負荷を低減でき、車両の燃費を向上させることができる。
前記第一吐出油路は、前記第一吐出ポートから前記第一部材接合部の開口まで、前記機械式オイルポンプの回転軸心を基準とした径方向の外側に向かって延びている。
前記油路構成部材は、
前記補助油圧源から吐出された油が流通する第二吐出油路と、
前記第二吐出油路の開口が形成された第二部材接合部と、を更に備え、
前記バルブボディは、第二ボディ油路と、当該第二ボディ油路の開口が形成された第二ボディ接合部と、を更に備え、
前記第二部材接合部と前記第二ボディ接合部とが対向する状態で接合されて、前記第二吐出油路と前記第二ボディ油路とが接続されていると好適である。
前記油路構成部材は、
前記第一ポンプロータの軸方向端面が接する第一面と、
前記第一面とは反対方向を向く面であって前記第二ポンプロータの軸方向端面が接する第二面と、を更に備えると好適である。
前記第二吐出油路は、前記第二吐出ポートから前記第二部材接合部の開口まで、前記電動オイルポンプの回転軸心を基準とした径方向の外側に向かって延びていると好適である。
前記第一ポンプロータにより吸入される油が流通する吸入油路と、
前記第一ポンプロータにより吐出された油を前記吸入油路に戻すための戻し孔と、
前記戻し孔の開口が形成された第三部材接合部と、を更に備え、
前記バルブボディは、第三ボディ油路と、当該第三ボディ油路の開口が形成された第三ボディ接合部と、を備え、
前記第三部材接合部と前記第三ボディ接合部とが対向する状態で接合されて、前記戻し孔に前記第三ボディ油路が接続されていると好適である。
また、戻し孔の開口が形成された第三部材接合部とバルブボディの第三ボディ接合部とが対向する状態で接合されるので、接合箇所での、油路の曲がりを少なくし、油路の短縮を図ることができる。
前記第一ポンプロータにより吸入される油が流通する吸入油路と、
前記第一ポンプロータにより吐出された油を前記吸入油路に戻すための戻し孔と、
前記戻し孔の開口が形成された第三部材接合部と、を更に備え、
前記バルブボディは、第三ボディ油路と、当該第三ボディ油路の開口が形成された第三ボディ接合部と、を備え、
前記第三部材接合部と前記第三ボディ接合部とが対向する状態で接合されて、前記戻し孔に前記第三ボディ油路が接続され、
前記第一部材接合部と前記第二部材接合部と前記第三部材接合部とは、同一面又は互いに平行な面に形成されていると共に、これらが前記第一ポンプロータの回転軸心の延在方向に平行な面に形成され、
前記第一ポンプロータの回転軸心を基準とした周方向の一方側から、前記第二部材接合部、前記第一部材接合部、前記第三部材接合部の順に配置されていると好適である。
また、第一部材接合部が、周方向における第二部材接合部と第三部材接合部との間に配置されているので、第一吐出油路を径方向外側に向けて延ばすことができる。よって、第一吐出油路の油路の曲がりを少なくできると共に、第一吐出油路を最短距離で配置することができ、圧力損失を低減することができる。機械式オイルポンプの吐出能力が、電動オイルポンプの吐出能力より大きくされている場合は、圧力損失の低減効果を大きくすることができる。
また、第二部材接合部と第一部材接合部と第三部材接合部とが周方向に並べて配置されているので、油路構成部材の幅(軸方向長さ)が長くなることを抑制でき、装置全体の軸方向の長さの短縮を図ることができる。
前記戻し孔には、前記吐出戻し油路の開度を制御する戻し油路制御弁が収容され、
前記戻し孔の開口は、前記戻し油路制御弁を動作させる指令油圧を当該戻し油路制御弁に供給する開口とされ、
前記第三ボディ油路は、前記指令油圧を供給する油路とされていると好適である。
前記戻し孔の開口は、前記吸入油路に戻す油を供給する開口とされ、
前記第三ボディ油路は、前記油圧制御弁から排出された油を流通させる油路とされていると好適である。
図1及び図2に示すように、車両用油圧供給装置1は、車輪Wの駆動力源により駆動される機械式オイルポンプMOPと、当該機械式オイルポンプMOPに接続される油路を形成する油路構成部材2と、機械式オイルポンプMOPから油路構成部材2を介して供給された油圧を制御して車両用駆動伝達装置3に供給する油圧制御装置PCと、を備えている。
本実施形態では、車両用油圧供給装置1は、車両用駆動伝達装置3を収容するケースCS内に収容されている。車両用油圧供給装置1は、電動モータMGにより駆動される電動オイルポンプEOPを更に備えている。また、油路構成部材2は、電動オイルポンプEOPに接続される油路を更に形成している。油圧制御装置PCには、電動オイルポンプEOPからも油路構成部材2を介して油圧が供給される。
油圧制御装置PCは、車両用駆動伝達装置3の各供給対象に供給する油圧を調整するための油路及びそのための油圧を制御する油圧制御弁が収容された収容室を形成するバルブボディVBを備えている。バルブボディVBは、第一ボディ油路60と、当該第一ボディ油路60の開口が形成された第一ボディ接合部63と、を備えている。
第一部材接合部53と第一ボディ接合部63とが対向する状態で接合されて、第一吐出油路50と第一ボディ油路60とが接続されている。
以下、各構成について詳細に説明する。
車両用駆動伝達装置3は、車両駆動用の駆動力源としての内燃機関ENGに駆動連結され、内燃機関ENGの回転駆動力を、トルクコンバータTCを介して変速装置TMで変速して車輪Wに伝達する構成となっている。
トルクコンバータTCは、内部に充填された油を介して、入力側(駆動側)のポンプインペラTCaと出力側(従動側)のタービンランナTCbとの間の駆動力の伝達を行う。トルクコンバータTCは、ポンプインペラTCaとタービンランナTCbとを一体回転させるように連結するロックアップクラッチLCを備えている。ロックアップクラッチLCを含むトルクコンバータTCには、油圧制御装置PCにより調圧された油が供給される。
変速装置TMは、複数の係合装置の係合又は解放に応じて、歯車機構の回転状態が切り替わり、各変速段が形成される。出力軸に伝達された駆動力は、カウンタギヤ機構CG及び差動歯車装置DFを介して左右二つの車軸に分配されて伝達され、各車軸に駆動連結された車輪Wに伝達される。
車両用駆動伝達装置3を構成するトルクコンバータTC、変速装置TM、カウンタギヤ機構CG、及び差動歯車装置DFなどは、ケースCS内に収容されている。ケースCSは、車両用駆動伝達装置3の外側を覆うように形成された外壁を備えている。また、ケースCSは、トルクコンバータTC、変速装置TM、カウンタギヤ機構CG、及び差動歯車装置DFやこれらを連結し動力を伝達する動力伝達部材を、それぞれ支持するため又は隔離するために、部分的又は全体的に覆った隔壁を備えている。
次に、車両用油圧供給装置1について説明する。車両用油圧供給装置1は、油圧源と、油圧源から供給された油圧を制御して車両用駆動伝達装置3に供給する油圧制御装置PCとを備えている。
車両用油圧供給装置1は、油圧源として、車輪Wの駆動力源により駆動される機械式オイルポンプMOPと、補助油圧源と、を備えている。本実施形態では、補助油圧源は、電動モータMGにより駆動される電動オイルポンプEOPとされている。
油圧制御装置PCは、車両用駆動伝達装置3の各供給対象に供給する油圧を調整するための油路及びそのための油圧を制御する油圧制御弁が収容された収容室を形成するバルブボディVBを備えている。バルブボディVBは、外観は厚い板状の部材であり、複数枚の板状の部材が、セパレートプレートなどを介して積層されている。バルブボディVBには、内部に張り巡らされた多数の油路や、油圧制御弁を構成するスプールやバネなどを収容する円柱状の収容室などが形成されている。バルブボディVBは、ケースCSに固定される固定部を備えており、締結ボルトなどによりケースCSに固定されている。
また、バルブボディVBは、第二ボディ油路61と、当該第二ボディ油路61の開口が形成された第二ボディ接合部64と、を更に備えている。第二ボディ接合部64は、油路構成部材2の第二部材接合部54に接合されて、第二ボディ油路61が、油路構成部材2の第二吐出油路51に接続される。
バルブボディVBは、戻し油路制御弁40に指令油圧を供給する第三ボディ油路62と、当該第三ボディ油路62の開口が形成された第三ボディ接合部65と、を備えている。第三ボディ接合部65は、油路構成部材2の第三部材接合部55に接合されて、第三ボディ油路62が、油路構成部材2の指令圧油路47に接続される。
油路構成部材2に接合される第一ボディ接合部63、第二ボディ接合部64、及び第三ボディ接合部65は、バルブボディVB(第一板状部材66)における油路構成部材2側の端部に形成されている。ボディ接合部63、64、65が形成された形成面は、バルブボディVBの重ね合わせ面69に平行な平面とされている。
第一ボディ油路60と第二ボディ油路61と第三ボディ油路62とは、それぞれ、対応するボディ接合部63、64、65の開口から、重ね合わせ面69に直交する方向に沿ってバルブボディVB側に延びている。
第三ボディ油路62には、ソレノイド弁などの油圧制御弁により調整された油圧や、レギュレータ弁などの油圧制御弁からドレインされた油などが、指令油圧として供給される。
<回転軸心>
本実施形態では、図3に示すように、機械式オイルポンプMOPの回転軸心A1(以下、第一回転軸心A1と称す)と、電動オイルポンプEOPの回転軸心A2(以下、第二回転軸心A2)とは、平行に配置されている。よって、軸方向は、これらの2つの回転軸心A1、A2で共通した方向となる。軸方向において電動オイルポンプEOPから機械式オイルポンプMOPに向かう方向(図3における左側)を、軸第一方向X1と規定し、その反対方向である機械式オイルポンプMOPから電動オイルポンプEOPに向かう方向(図3における右側)を軸第二方向X2と規定している。なお、本実施形態において「平行」とは、製造誤差などによる多少の傾きがある実質的に平行な状態も含む。
本実施形態では、第一回転軸心A1と第二回転軸心A2とは、同軸上に配置されている。また、第一回転軸心A1と第二回転軸心A2とは、車輪Wの駆動力源の回転軸心とは異なる軸心上に配置されている。また、第一回転軸心A1と第二回転軸心A2とは、第一部材接合部53が形成された形成面に平行にされている。
機械式オイルポンプMOPは、車輪Wの駆動力源の駆動力により第一ポンプロータR1が回転することにより、油を第一吸入ポートPI1から吸入し、第一吐出ポートPO1に吐出するオイルポンプである。このような機械式オイルポンプMOPには、歯車ポンプやベーンポンプなどを用いることができる。
本実施形態では、機械式オイルポンプMOPは、歯車ポンプとされ、第一ポンプロータR1として、内側に歯車を有する第一アウターロータR1oと、その内側に収まり、外側に歯車を有する第一インナーロータR1iとを有しており、第一アウターロータR1oと第一インナーロータR1iの中心が偏心されて噛み合わされている。本実施形態では、クレッセンドが設けられていない、トロコイドポンプとされている。
第一ポンプロータR1に対して軸第二方向X2側に突出した第一回転軸S1の端部は、油路構成部材2の第一面F1に形成された軸支持孔HSに挿入されて、回転可能に支持されている。第一ポンプロータR1の軸第一方向X1側を覆う第一ポンプハウジングPH1には、軸方向の貫通孔16が形成されており、第一回転軸S1が当該貫通孔16を貫通して、回転可能に支持されている。
本実施形態では、図2及び図3に示すように、カバーハウジング部材PH1bは、中間壁18と一体形成されている。すなわち、第一ポンプハウジングPH1の一部(カバーハウジング部材PH1b)は、ケースCSと一体形成されている。
電動オイルポンプEOPは、電動モータMGの駆動力により第二ポンプロータR2が回転することにより、油を第二吸入ポートPI2から吸入し、第二吐出ポートPO2に吐出するオイルポンプである。このような電動オイルポンプEOPには、歯車ポンプやベーンポンプなどを用いることができる。
本実施形態では、電動オイルポンプEOPは、歯車ポンプとされ、第二ポンプロータR2として、内側に歯車を有する第二アウターロータR2oと、その内側に収まり、外側に歯車を有する第二インナーロータR2iとを有しており、第二アウターロータR2oと第二インナーロータR2iの中心が偏心されて噛み合わされている。本実施形態では、クレッセンドが設けられていない、トロコイドポンプとされている。
油路構成部材2は、機械式オイルポンプMOPに接続される油路及び電動オイルポンプEOPに接続される油路を形成している。
本実施形態では、油路構成部材2は、軸第一方向X1側の部材2aと、軸第二方向X2側の部材2bとの二つの部材から構成されている。
5-1.固定部
油路構成部材2は、ケースCSに固定されるケース固定部10を備えている。油路構成部材2は、ケースCSの一部ではなくケースCSに固定される部品であり、ケースCSのように、駆動力源の駆動力を車輪Wに伝達する駆動力伝達機構を直接的又は間接的に支持していない。このように、油路構成部材2は、ケースCSに油路が形成されたものとは異なる。
締結ボルト20は、軸第一方向X1側からカバーハウジング部材PH1bのボルト貫通孔21b、ロータ収容ハウジング部材PH1aのボルト貫通孔21a及び油路構成部材2のボルト挿入孔19に挿入され螺合されて、ロータ収容ハウジング部材PH1a及び油路構成部材2をカバーハウジング部材PH1bに固定している。カバーハウジング部材PH1bは、ケースCSを構成する中間壁18と一体形成されており、油路構成部材2は、ケースCSに固定される。
締結ボルト23は、軸第二方向X2側から第二ポンプハウジングPH2のボルト貫通孔24及び油路構成部材2のボルト挿入孔19に挿入され螺合されて、第二ポンプハウジングPH2を油路構成部材2に固定している。よって、電動オイルポンプEOPは、油路構成部材2を介してケースCSに固定される。
<第一面F1>
油路構成部材2は、図3に示すように、機械式オイルポンプMOPの第一ポンプロータR1の軸第二方向X2側の端面FE1が接する第一面F1を備えている。第一面F1は、第一ポンプロータR1が収容される第一ロータ収容室17の軸第二方向X2側の内面を構成する収容室面11を構成する。すなわち、油路構成部材2は、機械式オイルポンプMOPのハウジングとしての役割も有する。
本実施形態では、第一面F1は、第一回転軸心A1と直交する平面とされている。
第一面F1には、図3及び図4に示すように、油路構成部材2の内側(本例では、第二面F2側)に窪んだ形状を有し、機械式オイルポンプMOPに油を供給する第一吸入ポートPI1と、油路構成部材2の内側(本例では、第二面F2側)に窪んだ形状を有し、機械式オイルポンプMOPから油が吐出される第一吐出ポートPO1と、が形成されている。
第一吸入ポートPI1は、第一ポンプロータR1により形成される隙間に油を供給する、第一面F1の吸入側の窪み部である。具体的には、第一吸入ポートPI1は、第一面F1の吸入側の窪み部の内、第一ロータ収容室17と軸方向に見て重なる領域内において第一ポンプロータR1により形成される隙間と、軸方向から見て重複する円弧状の領域である。本実施形態では、第一吸入ポートPI1は、第一面F1の吸入側の窪み部の内、第一アウターロータR1oと第一インナーロータR1iとの間の隙間が、第一ポンプロータR1が回転した場合に分布する領域と、軸方向から見て重複する円弧状の領域となる。
機械式オイルポンプMOPの第一ポンプロータR1の回転方向RD1(以下、第一回転方向RD1と称す)は、図4に示すように、軸第二方向X2に見て時計回りの方向とされている。
第一吐出ポートPO1は、第一ポンプロータR1により形成される隙間から油が吐出される、第一面F1の吐出側の窪み部である。具体的には、第一吐出ポートPO1は、第一面F1の吐出側の窪み部の内、第一ロータ収容室17と軸方向に見て重なる領域内において、第一ポンプロータR1により形成される隙間と、軸方向から見て重複する円弧状の領域である。本実施形態では、第一吐出ポートPO1は、第一面F1の吐出側の窪み部の内、第一アウターロータR1oと第一インナーロータR1iとの間の隙間が、第一ポンプロータR1が回転した場合に分布する領域と、軸方向から見て重複する円弧状の領域となる。
<第二面F2>
油路構成部材2は、図3に示すように、第一面F1とは反対方向を向く面であって、電動オイルポンプEOPの第二ポンプロータR2の軸第一方向X1側の端面FE2が接する第二面F2を備えている。第二面F2は、第二ポンプロータR2が収容される第二ロータ収容室27の軸第一方向X1側の内面を構成する収容室面12を構成する。すなわち、油路構成部材2は、電動オイルポンプEOPのハウジングとしての役割も有する。
本実施形態では、第二面F2は、第二回転軸心A2と直交する平面とされており、第一面F1と平行にされている。
第二面F2には、図3及び図5に示すように、油路構成部材2の内側(本例では、第一面F1側)に窪んだ形状を有し、電動オイルポンプEOPに油を供給する第二吸入ポートPI2と、油路構成部材2の内側(本例では、第一面F1側)に窪んだ形状を有し、電動オイルポンプEOPから油が吐出される第二吐出ポートPO2と、が形成されている。
第二吸入ポートPI2は、第二ポンプロータR2により形成される隙間に油を供給する、第二面F2の吸入側の窪み部である。具体的には、第二吸入ポートPI2は、第二面F2の吸入側の窪み部の内、第二ロータ収容室27と軸方向に見て重なる領域内において第二ポンプロータR2により形成される隙間と、軸方向から見て重複する円弧状の領域である。本実施形態では、第二吸入ポートPI2は、第二面F2の吸入側の窪み部の内、第二アウターロータR2oと第二インナーロータR2iとの間の隙間が、第二ポンプロータR2が回転した場合に分布する領域と、軸方向から見て重複する円弧状の領域となる。
第二吐出ポートPO2は、第二ポンプロータR2により形成される隙間から油が吐出される、第二面F2の吐出側の窪み部である。第二吐出ポートPO2は、第二面F2の吐出側の窪み部の内、第二ロータ収容室27と軸方向に見て重なる領域内において、第二ポンプロータR2により形成される隙間と、軸方向から見て重複する円弧状の領域である。本実施形態では、第二吐出ポートPO2は、第二面F2の吐出側の窪み部の内、第二アウターロータR2oと第二インナーロータR2iとの間の隙間が、第二ポンプロータR2が回転した場合に分布する領域と、軸方向から見て重複する円弧状の領域となる。
油路構成部材2は、第一ポンプロータR1により吸入される油が流通する吸入油路57を備えている。本実施形態では、吸入油路57は、第二ポンプロータR2により吸入される油が流通する吸入油路と共通化されている。すなわち、吸入油路57は、第一ポンプロータR1と第二ポンプロータR2との間で共用されている。吸入油路57は、第一吸入ポートPI1及び第二吸入ポートPI2の双方に連通して油を供給する。
吸入接合部58にストレーナSTの接合部が接合されて、吸入油路57とストレーナSTとが接続されている。ストレーナSTは、オイルパンOPなどの油溜内に配置され、ストレーナSTから吸入油路57に油が供給される。
油路構成部材2は、第一ポンプロータR1により吐出された油が流通する第一吐出油路50を備えている。第一吐出油路50は、第一吐出ポートPO1から供給された油を搬送するための油路である。第一吐出油路50は、第一吐出ポートPO1から第一部材接合部53の開口まで、第一回転軸心A1を基準とした径方向外側に向けて延びている。
図1及び図4に示すように、第一吐出油路50と第二吐出油路51とは、互いに独立して形成されている。ここで、「独立して」とは、油路構成部材2内で、第一吐出油路50と第二吐出ポートPO2とが連通していないことを意味する。
図1及び図6に示すように、油路構成部材2は、第一ポンプロータR1により吐出された油を吸入油路57に戻すための戻し孔46と、戻し孔46の開口が形成された第三部材接合部55と、を備えている。本実施形態では、戻し孔46は、第一吐出油路50に連通し、第一吐出油路50の油を吸入油路57に戻す吐出戻し油路45を備えている。また、戻し孔46には、吐出戻し油路45の開度を制御する戻し油路制御弁40が収容されている。戻し孔46の開口は、戻し油路制御弁40を動作させる指令油圧を当該戻し油路制御弁40に供給する開口とされ、第三ボディ油路62は、指令油圧を供給する油路とされている。すなわち、戻し孔46における開口側の部分が、戻し油路制御弁40を動作させる指令油圧が流通する指令圧油路47とされる。
指令油圧が供給されていない場合は、図6に示すように、バネ49の押圧力により、スプール41が吐出側の移動端まで移動し、吐出戻し油路45と第一吐出油路50とが連通するが、吐出戻し油路45と吸入油路57とが連通しない状態となる。一方、指令油圧の押圧力がバネ49の押圧力を上回ると、スプール41が吸入側に移動して、吐出戻し油路45と第一吐出油路50とが連通すると共に、吐出戻し油路45と吸入油路57とが連通する。指令油圧の押圧力に応じて、吐出戻し油路45と吸入油路57との連通開度が増減し、第一吐出油路50から吸入油路57に戻される油量が増減する。
第一部材接合部53と第二部材接合部54と第三部材接合部55とは、互いに平行な面に形成されていると共に、これらが第一回転軸心A1の延在方向(軸方向)に平行な面に形成されている。
そして、第一回転軸心A1を基準とした周方向の一方側から、第二部材接合部54、第一部材接合部53、第三部材接合部55の順に配置されている。
部材接合部53、54、55とボディ接合部63、64、65とが接合された状態で、部材接合部53、54、55が形成された形成面と、ボディ接合部63、64、65が形成された形成面とは、平行になる。この状態では、第一部材接合部53の形成面は、バルブボディVBの重ね合わせ面69に平行になり、接合部垂直方向は重ね合わせ面69に垂直な方向になる。
そして、吸入油路57の吸入接合部58が形成された形成面は、第一部材接合部53の形成面とは反対側を向く、第一部材接合部53の形成面に平行な平面とされている。吸入接合部58に形成された開口は、接合部垂直第二方向Y2に向けて開口している。そして、ストレーナSTは、吸入接合部58の形成面の接合部垂直第二方向Y2側に配置されている。
図4に示すように、軸第二方向X2に見て、第一ポンプロータR1の第一回転方向RD1と第二ポンプロータR2の第二回転方向RD2とは逆方向にされている。そのため、第一吐出油路50と第一吐出ポートPO1との接続部は、第一吐出ポートPO1の第一回転方向RD1側に寄せて配置され、第二吐出油路51と第二吐出ポートPO2との接続部は、第二吐出ポートPO2の第二回転方向RD2側に寄せて配置されている。このため、第一吐出油路50と第二吐出油路51とが、軸方向に見て重複しないように配置することができている。
第一吐出油路50の第一部材接合部53及び第二吐出油路51の第二部材接合部54が形成された形成面は、接合部垂直第一方向Y1を向く、互いに平行な平面とされている。第一部材接合部53及び第二部材接合部54に形成された開口は、接合部垂直第一方向Y1に向けて開口している。
吐出戻し油路45、戻し孔46、及び指令圧油路47は、第一吐出油路50及び吸入油路57との連通部を除いて、第一吐出油路50及び第二吐出油路51並びに吸入油路57と軸方向に見て重複せず、周方向に見て重複するように形成されている。よって、吐出戻し油路45、戻し孔46、及び指令圧油路47を設けても、油路構成部材2の幅(軸方向の長さ)を薄く維持できている。
指令圧油路47の第三部材接合部55が形成された形成面は、接合部垂直第一方向Y1を向く、第一部材接合部53の形成面に平行な平面とされている。第三部材接合部55に形成された開口は、接合部垂直第一方向Y1に向けて開口している。
最後に、本発明のその他の実施形態について説明する。なお、以下に説明する各実施形態の構成は、それぞれ単独で適用されるものに限られず、矛盾が生じない限り、他の実施形態の構成と組み合わせて適用することも可能である。
2 :油路構成部材
3 :車両用駆動伝達装置
10 :ケース固定部
11 :収容室面
17 :第一ロータ収容室(ロータ収容室)
18 :中間壁
22 :電動ポンプ固定部
27 :第二ロータ収容室
40 :戻し油路制御弁
45 :吐出戻し油路
46 :戻し孔
47 :指令圧油路
50 :第一吐出油路
51 :第二吐出油路
53 :第一部材接合部
54 :第二部材接合部
55 :第三部材接合部
57 :吸入油路
58 :吸入接合部
60 :第一ボディ油路
61 :第二ボディ油路
62 :第三ボディ油路
63 :第一ボディ接合部
64 :第二ボディ接合部
65 :第三ボディ接合部
69 :バルブボディの重ね合わせ面
A1 :第一回転軸心(第一ポンプロータの回転軸心)
A2 :第二回転軸心(第二ポンプロータの回転軸心)
CS :ケース
ENG :内燃機関
EOP :電動オイルポンプ(補助油圧源)
F1 :第一面
F2 :第二面
F3 :外周面
FE1 :第一ポンプロータの軸方向端面
FE2 :第二ポンプロータの軸方向端面
Gi :入力ギヤ
Go :駆動ギヤ
MG :電動モータ
MOP :機械式オイルポンプ
PC :油圧制御装置
PH1 :第一ポンプハウジング
PH2 :第二ポンプハウジング
PI1 :第一吸入ポート
PI2 :第二吸入ポート
PO1 :第一吐出ポート
PO2 :第二吐出ポート
R1 :第一ポンプロータ
R2 :第二ポンプロータ
RD1 :第一回転方向
RD2 :第二回転方向
S1 :第一回転軸
S2 :第二回転軸
ST :ストレーナ
TC :トルクコンバータ
TM :変速装置
VB :バルブボディ
W :車輪
X1 :軸第一方向
X2 :軸第二方向
Y1 :接合部垂直第一方向
Y2 :接合部垂直第二方向
Claims (11)
- 車輪の駆動力源により駆動される機械式オイルポンプと、当該機械式オイルポンプに接続される油路を形成する油路構成部材と、前記機械式オイルポンプから前記油路構成部材を介して供給された油圧を制御して車両用駆動伝達装置に供給する油圧制御装置と、を備えた車両用油圧供給装置であって、
前記機械式オイルポンプの回転軸は、前記車両用駆動伝達装置における前記駆動力源への連結部となる軸である入力軸とは異なる軸上に配置され、
前記油路構成部材は、
前記機械式オイルポンプのポンプロータである第一ポンプロータが収容されるロータ収容室を構成する収容室面と、
前記第一ポンプロータにより吐出された油が流通する第一吐出油路と、
前記第一吐出油路の開口が形成された第一部材接合部と、を備え、
前記油圧制御装置は、前記車両用駆動伝達装置の各供給対象に供給する油圧を調整するための油路及びそのための油圧を制御する油圧制御弁が収容された収容室を形成するバルブボディを備え、
前記バルブボディは、第一ボディ油路と、当該第一ボディ油路の開口が形成された第一ボディ接合部と、を備え、
前記第一部材接合部と前記第一ボディ接合部とが対向する状態で接合されて、前記第一吐出油路と前記第一ボディ油路とが接続されている車両用油圧供給装置。 - 前記油路構成部材は、前記第一ポンプロータの軸方向端面が接する第一面を更に備え、前記第一面には、前記油路構成部材の内側に窪んだ形状を有し、前記機械式オイルポンプから油が吐出される第一吐出ポートが形成され、
前記第一吐出油路は、前記第一吐出ポートから前記第一部材接合部の開口まで、前記機械式オイルポンプの回転軸心を基準とした径方向の外側に向かって延びている請求項1に記載の車両用油圧供給装置。 - 直接、又は、直線状に延びる筒状の筒状部材を介して、前記第一部材接合部と前記第一ボディ接合部とが対向する状態で接続されている請求項1又は2に記載の車両用油圧供給装置。
- 補助油圧源を更に備え、
前記油路構成部材は、
前記補助油圧源から吐出された油が流通する第二吐出油路と、
前記第二吐出油路の開口が形成された第二部材接合部と、を更に備え、
前記バルブボディは、第二ボディ油路と、当該第二ボディ油路の開口が形成された第二ボディ接合部と、を更に備え、
前記第二部材接合部と前記第二ボディ接合部とが対向する状態で接合されて、前記第二吐出油路と前記第二ボディ油路とが接続されている請求項1から3のいずれか一項に記載の車両用油圧供給装置。 - 前記補助油圧源は、電動モータにより駆動される電動オイルポンプ、電磁アクチュエータにより駆動される電磁ポンプ、又はアキュムレータである請求項4に記載の車両用油圧供給装置。
- 前記補助油圧源は、電動モータにより駆動される電動オイルポンプであり、前記第二吐出油路には、前記電動オイルポンプのポンプロータである第二ポンプロータにより吐出された油が流通し、
前記油路構成部材は、
前記第一ポンプロータの軸方向端面が接する第一面と、
前記第一面とは反対方向を向く面であって前記第二ポンプロータの軸方向端面が接する第二面と、を更に備えた請求項4又は5に記載の車両用油圧供給装置。 - 前記第二面には、前記油路構成部材の内側に窪んだ形状を有し、前記電動オイルポンプから油が吐出される第二吐出ポートが形成され、
前記第二吐出油路は、前記第二吐出ポートから前記第二部材接合部の開口まで、前記電動オイルポンプの回転軸心を基準とした径方向の外側に向かって延びている請求項6に記載の車両用油圧供給装置。 - 前記油路構成部材は、
前記第一ポンプロータにより吸入される油が流通する吸入油路と、
前記第一ポンプロータにより吐出された油を前記吸入油路に戻すための戻し孔と、
前記戻し孔の開口が形成された第三部材接合部と、を更に備え、
前記バルブボディは、第三ボディ油路と、当該第三ボディ油路の開口が形成された第三ボディ接合部と、を備え、
前記第三部材接合部と前記第三ボディ接合部とが対向する状態で接合されて、前記戻し孔に前記第三ボディ油路が接続されている請求項1から7のいずれか一項に記載の車両用油圧供給装置。 - 前記油路構成部材は、
前記第一ポンプロータにより吸入される油が流通する吸入油路と、
前記第一ポンプロータにより吐出された油を前記吸入油路に戻すための戻し孔と、
前記戻し孔の開口が形成された第三部材接合部と、を更に備え、
前記バルブボディは、第三ボディ油路と、当該第三ボディ油路の開口が形成された第三ボディ接合部と、を備え、
前記第三部材接合部と前記第三ボディ接合部とが対向する状態で接合されて、前記戻し孔に前記第三ボディ油路が接続され、
前記第一部材接合部と前記第二部材接合部と前記第三部材接合部とは、同一面又は互いに平行な面に形成されていると共に、これらが前記第一ポンプロータの回転軸心の延在方向に平行な面に形成され、
前記第一ポンプロータの回転軸心を基準とした周方向の一方側から、前記第二部材接合部、前記第一部材接合部、前記第三部材接合部の順に配置されている請求項4に記載の車両用油圧供給装置。 - 前記戻し孔は、前記第一吐出油路に連通し、前記第一吐出油路の油を前記吸入油路に戻す吐出戻し油路を備え、
前記戻し孔には、前記吐出戻し油路の開度を制御する戻し油路制御弁が収容され、
前記戻し孔の開口は、前記戻し油路制御弁を動作させる指令油圧を当該戻し油路制御弁に供給する開口とされ、
前記第三ボディ油路は、前記指令油圧を供給する油路とされている請求項8又は9に記載の車両用油圧供給装置。 - 前記戻し孔は、前記第三ボディ油路の油を前記吸入油路に戻すボディ戻し油路とされ、
前記戻し孔の開口は、前記吸入油路に戻す油を供給する開口とされ、
前記第三ボディ油路は、前記油圧制御弁から排出された油を流通させる油路とされている請求項8又は9に記載の車両用油圧供給装置。
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DE112014003656.0T DE112014003656B4 (de) | 2013-09-30 | 2014-09-30 | Fahrzeughydraulikdruckversorgungsvorrichtung |
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US20160207401A1 (en) | 2016-07-21 |
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