JP2015203385A - Hydraulic control device for vehicle - Google Patents

Abstract

Provided is a hydraulic control device that improves the fuel efficiency of a vehicle by suppressing loss torque due to sliding resistance between a vane and a cam ring, and increases wear resistance of the vane pump by suppressing wear caused by sliding between the vane and the cam surface. To do.
In a hydraulic control device, a hydraulic pressure of a second discharge port connected to a second discharge oil passage 60 that is lower than a hydraulic pressure of a first discharge oil passage connected to the first discharge port. Is supplied to the vane through the second back pressure groove 32 as a back pressure that presses the outer end of the vane in the radial direction of the rotor against the inner circumferential cam surface. Therefore, when the vane pump 14 is operated at a high speed, the second suction port 24 is operated. And the pressing force with respect to the internal peripheral cam surface of the vane which divides each pump chamber P between the 2nd discharge ports 28 is reduced.
[Selection] Figure 1

Description

  The present invention relates to a hydraulic control apparatus for a vehicle having a vane pump as a hydraulic source, and more particularly, to improve the fuel efficiency of the vehicle by suppressing the loss torque due to the sliding resistance between the vane and the cam ring, and to improve the sliding surface of the vane and the cam ring. The present invention relates to a technique for suppressing wear and improving its durability.

  At the time of starting the vane pump of the vehicle hydraulic control device, the hydraulic pressure from the discharge port is applied to the vane as the back pressure in order to press the tips of the plurality of vanes provided on the rotor of the vane pump against the inner circumferential cam surface of the cam ring. . For example, this is the vehicle hydraulic control apparatus described in Patent Documents 1 to 3.

  The vane pump of the hydraulic control device for a vehicle described in Patent Documents 1 to 3 is rotatable to the housing such that the housing has an inner peripheral cam surface having a flat cross section and the outer peripheral surface faces the inner peripheral cam surface, for example. And a rotor having a plurality of slits radially formed on the outer peripheral surface in a direction perpendicular to the rotation axis, and a radially outer end, that is, a distal end, fitted into the slit so as to be slidable in the radial direction of the rotor A plurality of vanes slidably contactable with the inner peripheral cam surface, a first suction port and a second suction port for sucking hydraulic oil, and a first discharge port and a second discharge for discharging hydraulic fluid sucked from them And a back pressure groove that communicates with a radially inner end portion of the rotor of the slit and supplies a back pressure that presses the vane against the inner circumferential cam surface. If the discharge pressure at the higher hydraulic pressure, for example, the discharge pressure of the first discharge port is supplied to the back pressure groove as a back pressure for pressing the tip of the vane against the inner circumferential cam surface, the generation of the hydraulic pressure at the time of starting the vane pump is promoted. Responsiveness is enhanced.

JP 2011-196302 A JP 2010-144529 A JP 2013-87751 A

  However, in the vehicle hydraulic control apparatus configured as described above, when the vane pump is operated at a high speed, the hydraulic pressure at the first discharge port becomes higher, so that the back pressure applied to the vane from the back pressure groove also becomes high. As a result, the pressing force of the vane on the inner cam surface increases, the loss due to the sliding resistance between the vane and the inner cam surface increases, and the wear on the sliding surface between the vane tip and the inner cam surface increases. The durability of the vane pump could be reduced.

  The present invention has been made against the background of the above circumstances, and the object of the present invention is to reduce the pressing force of the vane against the inner circumferential cam surface when the vane pump is operated at high speed. An object of the present invention is to increase the durability of the vane pump by suppressing loss due to sliding resistance with the inner peripheral cam surface and improving the fuel efficiency of the vehicle, and suppressing wear caused by sliding between the vane and the inner peripheral cam surface.

  That is, the gist of the present invention is that the housing having an inner circumferential cam surface having an elliptical cross section, and a rotor provided rotatably in the housing such that the outer circumferential surface faces the inner circumferential cam surface; A plurality of vanes provided so as to be slidable in the radial direction of the rotor; a back pressure groove for supplying back pressure to press the outer peripheral side ends of the plurality of vanes against the inner peripheral cam surface; In the vehicle hydraulic control apparatus having a vane pump having a first discharge port and a second discharge port for discharging the first discharge port, the first discharge oil passage connected to the first discharge port and the second discharge port The hydraulic oil is allowed to flow from the second discharge oil passage to the first discharge oil passage between the second discharge oil passage and the hydraulic oil from the first discharge oil passage to the second discharge oil passage. A first check oil passage having a check valve for preventing circulation; In the hydraulic control apparatus for a vehicle, wherein the second discharge fluid passage which is in hydraulic or less is communicated with the back pressure groove.

  According to the vehicle hydraulic control apparatus of the present invention, the first discharge oil passage from the second discharge oil passage is caused by a check valve provided between the first discharge oil passage and the second discharge oil passage. The hydraulic oil is allowed to flow toward the second discharge oil passage and is prevented from flowing from the first discharge oil passage to the second discharge oil passage. The hydraulic pressure of the hydraulic oil in the discharge oil passage is supplied as a back pressure that presses the outer peripheral side ends of the plurality of vanes against the inner peripheral cam surface through the back pressure groove. For this reason, since the pressing force of the vane against the inner peripheral cam surface is reduced even during high-speed operation of the vane pump, the loss due to the sliding resistance between the vane and the inner peripheral cam surface is suppressed, and the fuel efficiency of the vehicle is improved. The durability of the vane pump can be enhanced by suppressing wear caused by sliding between the vane and the inner peripheral cam surface.

  Here, preferably, the first discharge oil passage is a hydraulic oil supply oil passage to a control target that consumes hydraulic pressure, and opens and closes between the first discharge oil passage and the third oil passage. When the hydraulic pressure of the first valve section, the second valve section that opens and closes between the second discharge oil path and the fourth oil path, and the hydraulic pressure of the first discharge oil path becomes a predetermined hydraulic pressure, the first valve section and the And a valve element operable to open the second valve portion synchronously, and the amount of hydraulic oil flowing out from the second discharge oil passage to the fourth oil passage when the second valve portion is opened. Is configured to be larger in accordance with the operation amount of the first valve element than the amount of hydraulic oil flowing out from the first discharge oil passage to the third oil passage when the first valve portion is opened. It is comprised so that a pressure regulation valve may be provided. For this reason, when the hydraulic pressure of the first discharge oil passage for supplying hydraulic oil to the controlled object is smaller than the predetermined hydraulic pressure, the first valve portion and the second valve portion of the pressure regulating valve are not opened, and the first discharge oil passage and The flow of hydraulic oil from the second discharge oil passage to the first discharge oil passage through a check valve provided between the second discharge oil passage and the first discharge oil passage is permitted. The hydraulic pressure is approximately the same. As a result, when the vane pump is started, the hydraulic pressure of the second discharge oil passage having substantially the same pressure as the first discharge oil passage is supplied as a back pressure that presses the vane against the inner circumferential cam surface through the back pressure groove. The pressing force against the inner peripheral cam surface of the vane, that is, the hydraulic response is ensured. Further, when the hydraulic pressure of the first discharge oil passage becomes a predetermined hydraulic pressure, the first valve portion and the second valve portion of the pressure regulating valve are opened synchronously and are discharged from the second discharge oil passage to the fourth oil passage. The amount of hydraulic oil is increased according to the amount of operation of the first valve element rather than the amount of hydraulic oil flowing out from the first discharge oil passage to the third oil passage, so the hydraulic pressure in the second discharge oil passage decreases. And the check valve is closed. For this reason, when the vane pump rotates at high speed, the hydraulic pressure of the hydraulic oil in the second discharge oil passage that is lower than the hydraulic pressure in the first discharge oil passage is supplied as a back pressure that presses the vane against the inner circumferential cam surface through the back pressure groove. Therefore, the pressing force of the vane against the inner peripheral cam surface is reduced, the loss due to the sliding resistance between the vane and the inner peripheral cam surface is suppressed, the vehicle fuel efficiency is improved, and the vane and the inner peripheral cam surface The durability of the vane pump can be improved by suppressing wear due to sliding.

  Preferably, the check valve is a spool valve, allows hydraulic oil to flow from the second discharge oil passage to the first discharge oil passage, and passes through the second discharge oil passage from the second discharge oil passage. The hydraulic oil is configured to be prevented from flowing to the discharge oil passage. For this reason, since the pressing force of the vane against the inner peripheral cam surface is reduced even during high-speed operation of the vane pump, the loss due to the sliding resistance between the vane and the inner peripheral cam surface is suppressed, and the fuel efficiency of the vehicle is improved. The durability of the vane pump can be enhanced by suppressing wear caused by sliding between the vane and the inner peripheral cam surface.

It is the schematic explaining the structure of the principal part of the hydraulic control apparatus for vehicles of one Example of this invention. FIG. 2 is a front view of a state in which a pump cover of a vane pump provided in the vehicle hydraulic control device of FIG. 1 is removed. FIG. 2 is a diagram showing a relationship between an engine speed and hydraulic pressures of first and second discharge oil passages in the vehicle hydraulic control device of FIG. 1. It is a front view of the state where the pump cover of the vane pump with which the hydraulic control device for vehicles in other examples of the present invention was equipped was removed. It is a figure explaining in detail the check valve with which the hydraulic control device for vehicles in other examples of the present invention was equipped.

  Hereinafter, an embodiment of a hydraulic control device of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a schematic diagram illustrating the configuration of a hydraulic control device according to the present invention. The hydraulic control device 10 includes a vane pump 14 that supplies hydraulic fluid to a control target 12 that consumes hydraulic fluid such as a hydraulic cylinder of A / T or CVT, and hydraulic pressure of hydraulic fluid supplied from the vane pump 14 to the control target 12, for example, A pressure regulating valve 16 for controlling the line pressure and a check valve 64 are provided.

  The vane pump 14 is driven by the rotation of an engine (not shown), and the first suction port 22 and the second suction port 24 that suck the working oil stored in the oil pan 18 through the oil strainer 20 and the sucked working oil. A first discharge port 26 and a second discharge port 28 for discharging the gas to the outside of the pump. Further, a first back pressure groove 30 for supplying a back pressure for forming a pump chamber around the first suction port 22 and the first discharge port 26, and a pump chamber around the second suction port 24 and the second discharge port 28 are provided. And a second back pressure groove 32 for supplying a back pressure for forming the.

  The pressure regulating valve 16 includes a valve body 34, a spool valve element 36 that is slidably fitted in a bore formed inside the valve body 34, and one of the spool valve elements 36 in the valve closing direction, that is, in FIG. And a spring 37 that urges the spool valve element 36 upward. The valve body 34 has a first input port 38, a feedback port 40, and a second input port 42 in order from the upper side in the longitudinal direction of FIG. 1, and similarly has a first output port 44 and a second output port 46. doing. The spool valve element 36 has a cylindrical land portion slidable in the axial direction on the inner peripheral surface of the valve body 34, that is, in order from the upper side in the axial direction of FIG. The land portion 50, the third land portion 52, and the fourth land portion 54 are provided. Further, the spool valve element 36 is configured so that the spool valve element 36 is urged by the hydraulic pressure applied to the feedback port 40 in the valve opening direction opposite to the urging force of the spring 37, that is, in the lower side of FIG. The first land portion 48 and the second land portion 50 are configured to be smaller in cross-sectional area on the plane orthogonal to the axial direction of the valve element 36 than the third land portion 52 and the fourth land portion 54. Further, when the second land portion 50 and the fourth land portion 54 are slid downward in FIG. 1 by the hydraulic pressure input to the feedback port 40, the pressure regulating valve 16 has a first input port 38 and a first output port. 44 and the second input port 42 and the second output port 46 are opened synchronously. The shape of each land portion such that the opening cross-sectional area between the second input port 42 and the second output port 46 is larger than the opening cross-sectional area between the first input port 38 and the first output port 44; For example, a chamfer (not shown) formed at the upper end portion in the axial direction of the fourth land portion 54 and a relative positional relationship between each port of the valve body 34 and each land portion are set. The spool valve element 36 is provided in the valve element of the present invention, between the first input port 38 and the first output port 44, in the first valve part of the present invention, and between the second input port 42 and the second output port 46. Corresponds to the second valve portion of the present invention.

  The first oil passage 56 is connected to the first suction port of the vane pump 14 via the oil strainer 20 so that the hydraulic oil stored in the oil pan 18 is sucked into the first suction port 22 and the second suction port 24. 22 and the second suction port 24 and the oil pan 18 are connected. The first discharge oil passage 58 is supplied to the first discharge port 26 of the vane pump 14 and the first input of the pressure regulating valve 16 so that the hydraulic oil discharged from the first discharge port 26 is pressure-fed to the controlled object 12 and the pressure regulating valve 16. The port 38 and the feedback port 40 are connected and a hydraulic oil supply path to the controlled object 12 is provided. The second discharge oil passage 60 connects the second discharge port 28 of the vane pump 14 and the second input port 42 of the pressure regulating valve 16 so that the hydraulic oil discharged from the second discharge port 28 is discharged from the pressure regulating valve 16. Connecting. The second oil passage 62 allows the hydraulic oil to flow from the second discharge oil passage 60 to the first discharge oil passage 58 and allows the hydraulic oil to flow from the first discharge oil passage 58 to the second discharge oil passage 60. The first discharge oil passage 58 and the second discharge oil passage 60 are connected via a ball valve type check valve 64 that blocks. When the space between the first input port 38 and the first output port 44 of the pressure regulating valve 16 is opened, the third oil passage 66 supplies, for example, a second pressure regulating valve (not shown) to the hydraulic oil in the first discharge oil passage 58. To supply. The fourth oil passage 67 recirculates the hydraulic oil in the second discharge oil passage 60 when the space between the second input port 42 and the second output port 46 of the pressure regulating valve 16 is open.

  FIG. 2 is a front view showing a state in which the pump cover of the vane pump 14 provided in the hydraulic control device 10 is removed. The vane pump 14 has a housing 69 in which a substantially cylindrical recess 68 is formed, a substantially cylindrical shape, a cam ring 70 fitted in the recess 68 so that the housing 69 cannot rotate together, and a disc shape. And one plane is interposed between the bottom wall surface of the recess 68 and the cam ring 70 such that the other plane abuts against the substantially circular one end surface of the cam ring 70. The side plate 72 has a cylindrical shape, the outer peripheral surface thereof faces the inner peripheral cam surface 78 of the cam ring 70 with a slight space therebetween, and one end surface in the rotational axis direction of the side plate 72 A rotor 74 slidably received on the other plane, fixed to the rotor 74 coaxially with the rotation axis of the rotor 74, and rotatably supported by the housing 69, such as an engine The pump shaft 76 that rotates the rotor 74 in the direction of the arrow shown in FIG. 2 according to the driving of the moving source, that is, the other end surface in the axial direction of the rotor 74, is in contact with the substantially circular other end surface of the cam ring 70. And a pump cover (not shown) that is fastened to the housing 69 so as to cover the opening of the recess 68 so as to be slidable to the housing.

  The cam ring 70 has an inner peripheral cam surface 78 that is an inner peripheral surface having a substantially elliptical cross section. The rotor 74 has a plurality of slits 80 formed radially from the central portion in the radial direction to the outer peripheral surface and at equal intervals in the circumferential direction over the entire axial length of the outer peripheral surface, and a rectangular flat plate fitted into the slit 80. A plurality of vanes 81 having a shape are provided. The vane 81 has a circumferential side surface of the rotor 74 slidable in the radial direction of the rotor 74 with respect to the inner wall facing the slit 80, and an axial side surface of the other end surface of the side plate 72 and the pump cover. A radially outer end surface is slidably inserted into the slit 80 on the inner peripheral cam surface 78 of the cam ring 70 so as to be in sliding contact with each of the inner wall surfaces.

  When the rotor 74 is driven to rotate, the vane 81 is pushed out of the inner wall of the slit 80 radially outside the rotor 74 by the back pressure from the first back pressure groove 30 and the second back pressure groove 32, and the radial direction The outer end surface is pressed against the inner peripheral cam surface 78 of the cam ring 70 and is slid with respect to the inner peripheral cam surface 78 in the rotational direction of the rotor 74 in this state. For this reason, a plurality of pump chambers P are formed by the circumferentially opposed side surfaces of the adjacent vanes 81, the inner peripheral cam surface 78, the outer peripheral surface of the rotor 74, the other end surface of the side plate 72, and the inner wall surface of the pump cover. Partitioned. Since the inner circumferential cam surface 78 of the pump chamber P has a substantially elliptical shape, the vane 81 is reciprocated twice in the radial direction of the rotor 74 in the slit 80 when the rotor 74 is rotated once. Increased or decreased twice.

  The side plate 72 is formed with a pair of first suction port 22 and second suction port 24 that communicate with the pump chamber P whose volume increases with the rotation of the rotor 74 with the pump shaft 76 interposed therebetween. In addition, a pair of first discharge port 26 and second discharge port 28 are formed in the side plate 72 and communicated with the pump chamber P whose volume decreases according to the rotation direction of the rotor 74 with the pump shaft 76 interposed therebetween. ing. The first discharge port 26 is positioned on the rotation direction side of the rotor 74 with respect to the first suction port 22, and the second discharge port 28 is positioned on the rotation direction side of the rotor 74 with respect to the second suction port 24. Yes.

  The side plate 72 communicates with the inner peripheral side end portion of the slit 80 in which the vanes 81 defining the pump chambers P are fitted between the first suction port 22 and the first discharge port 26. A first back pressure groove 30 that supplies back pressure that presses 81 against the inner circumferential cam surface 78 is formed in a semi-annular shape in the circumferential direction of the rotor 74. Further, the side plate 72 communicates with the inner peripheral side end portion of the slit 80 into which the vanes 81 defining the pump chambers P are fitted between the second suction port 24 and the second discharge port 28. A second back pressure groove 32 that supplies back pressure that presses each vane 81 against the inner circumferential cam surface 78 is formed in a semi-annular shape in the circumferential direction of the rotor 74.

  Further, the hydraulic pressure of the first discharge oil passage 58 acts on the vanes 81 that partition the pump chambers P between the first suction port 22 and the first discharge port 26 through the first back pressure groove 30. As described above, a first communication path 82 that communicates the first discharge port 26 and the first back pressure groove 30 is formed, and the first discharge oil path 58 and the first back pressure groove 30 communicate with each other. The second discharge oil passage 60 is operated so that the oil pressure of the second discharge oil passage 60 is applied to each vane 81 that partitions each pump chamber P between the second suction port 24 and the second discharge port 28 through the second back pressure groove 32. A second communication passage 83 that communicates the two discharge ports 28 and the second back pressure groove 32 is formed, and the second discharge oil passage 60 and the second back pressure groove 32 communicate with each other.

  When the vane pump 14 is started in accordance with the drive of the engine and the rotor 74 is rotated clockwise in FIG. 2, the hydraulic oil of the oil pan 18 passes through the first oil passage 56 to the first suction port 22 and the second suction port 24. The air is sucked and transferred to each pump chamber P of the vane pump 14 whose volume is gradually increased by the rotation of the rotor 74. The hydraulic oil sucked into each pump chamber P decreases from the first discharge port 26 and the second discharge port 28 to the first discharge oil passage by reducing the volume of each pump chamber P as the rotor 74 rotates. 58 and the second discharge oil passage 60. The oil pressures of the first discharge oil passage 58 and the second discharge oil passage 60 communicated with the first back pressure groove 30 and the second back pressure groove 32 by the first communication passage 82 and the second communication passage 83 are the first The radially outer end face of each vane 81 that defines each pump chamber P between the suction port 22 and the first discharge port 26 and between the second suction port 24 and the second discharge port 28 is the inner periphery of the cam ring 70. It is supplied as a back pressure that presses against the cam surface 78.

Figure 3 is a diagram showing a relationship between the hydraulic pressure P _L of the engine speed N and the discharge oil passage in the hydraulic control device 10. The engine speed N is smaller than N1, the rotor 74 is at a low speed, and the hydraulic pressure of the hydraulic oil discharged from the first discharge port 26 to the first discharge oil passage 58, that is, the first discharge pressure is required for the controlled object 12. When the predetermined pressure P1 is not satisfied, the valve closing direction of the spring 37 is larger than the biasing force in the valve opening direction corresponding to the first discharge pressure input to the feedback port 40 with respect to the spool valve element 36 of the pressure regulating valve 16. The energizing force of the first input port 38 and the first output port 44 and between the second input port 42 and the second output port 46 are closed. At this time, the working oil is circulated from the second discharge oil passage 60 to the first discharge oil passage 58 through the check valve 64 in which the gap between the second input port 96 and the output port 94 is opened. The rise of the pressure regulation by the 58 pressure regulating valve 16 is promoted, and the second discharge pressure of the second discharge oil passage 60 is the same as the first discharge pressure. When the vane pump 14 is started, the first discharge pressure and the second discharge pressure, which are set to the same pressure, are supplied as back pressure to the vanes 81 through the first back pressure groove 30 and the second back pressure groove 32. Therefore, the outer peripheral end surface of each vane 81 sufficient to partition each pump chamber P between the first suction port 22 and the first discharge port 26 and between the second suction port 24 and the second discharge port 28. The pressing force to the inner peripheral cam surface 78, that is, the hydraulic response is ensured.

  When the engine speed N is N1 or more and less than N2, the biasing force in the valve opening direction of the spool valve element 36 corresponding to the first discharge pressure input to the feedback port 40 and the biasing force in the valve closing direction of the spring 37 are balanced. In addition, the first input port 38 and the first output port 44 are opened and closed so that the first discharge pressure becomes a constant pressure P1, and at the same time, between the second input port 42 and the second output port 46. Are opened and closed synchronously. Further, the hydraulic oil in the second discharge oil passage 60 is recirculated through the fourth oil passage 67 via the second input port 42 and the second output port 46 communicated with each other. In addition, since the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 through the second oil passage 62 is continued by being allowed by the check valve 64, the second discharge pressure is also reduced. P1 is maintained at the same pressure as the first discharge pressure.

  When the engine speed N is equal to or higher than N2, the first discharge oil passage 58 has an oil amount sufficient to regulate the first discharge pressure to the predetermined oil pressure P1, and therefore the first increase increased in proportion to the high rotation of the rotor 74. Corresponding to the flow rate of the hydraulic oil in the first discharge oil passage 58, the displacement of the spool valve element 36 in the downward direction in FIG. 1 further increases, and the operation flows out from the first discharge oil passage 58 to the third oil passage 66. Both the oil amount and the amount of hydraulic oil flowing out from the second discharge oil passage 60 to the fourth oil passage 67 are increased. Here, the first input port 38 and the first output port 44 and the second input port 42 and the second output port 46 communicate with each other in synchronization, and the second input port 42 and the second output port 46 communicated with each other. Since the cross-sectional area is larger than the opening cross-sectional area of the first input port 38 and the first output port 44 communicated with each other, the hydraulic pressure in the second discharge oil passage 60 is reduced and the check valve 64 is closed. Thus, when the engine speed N is N2 or more, that is, when the rotor 74 of the vane pump 14 is rotating at high speed, the reduced second discharge pressure is supplied as back pressure to each vane 81 through the second back pressure groove 32. The pressing force of the outer peripheral side end face of the vane 81 that divides each pump chamber P between the two suction port 24 and the second discharge port 28 to the inner peripheral cam surface 78 is reduced.

  As described above, according to the hydraulic control device 10 of the present embodiment, the check valve 64 is closed and the first discharge connected to the first discharge port 26 in the high rotation state where the engine speed N is higher than N2. The second back pressure in which the hydraulic pressure of the second discharge port 28 connected to the second discharge oil path 60 that is lower than the hydraulic pressure of the oil path 58 is communicated to the second discharge oil path 60 by the second communication path 83. Through the groove 32, the vane 81 acts on the vane 81 as a back pressure that presses the outer end of the rotor 74 in the radial direction of the rotor 74 against the inner circumferential cam surface 78. For this reason, when the vane pump 14 is operated at high speed, the pressing force against the inner peripheral cam surface 78 of the vane 81 that partitions each pump chamber P between the second suction port 24 and the second discharge port 28 is reduced. Therefore, the loss torque due to the sliding resistance between the vane 81 and the cam ring 70 is suppressed to improve the fuel efficiency of the vehicle, and the wear due to the sliding between the vane 81 and the inner peripheral cam surface 78 is suppressed, so that the durability of the vane pump 14 is improved. Enhanced. In addition, as a countermeasure against wear, it is not necessary to use a material that is resistant to wear or to process with severe surface properties, so that an increase in the product cost of the hydraulic control device 10 is suppressed.

  Further, according to the hydraulic control device 10 of the present embodiment, when the hydraulic pressure of the first discharge oil passage 58 that supplies hydraulic oil to the hydraulic control target 12 is lower than the predetermined hydraulic pressure P1, the first input of the pressure regulating valve 16 is used. Between the port 38 and the first output port 44 and between the second input port 42 and the second output port 46 are closed, and a second oil passage connecting the first discharge oil passage 58 and the second discharge oil passage 60. By opening the check valve 64 provided at 62, the flow of the hydraulic oil to the first discharge oil passage 58 is permitted, and the hydraulic pressures of the first discharge oil passage 58 and the second discharge oil passage are substantially the same pressure. It is said. As a result, the hydraulic pressure in the first discharge oil passage 58 and the second discharge oil passage 60 passes through the first back pressure groove 30 and the second back pressure groove 32 and between the first suction port 22 and the first discharge port 26 and Since each vane 81 is supplied as a back pressure to press each vane 81 against the inner peripheral cam surface 78 with respect to each vane 81 partitioning each pump chamber P between the two suction ports 24 and the second discharge port 28, the vane pump 14 The pressing force of the vane 81 on the inner peripheral cam surface 78 at the time of starting, that is, the hydraulic response is ensured. When the hydraulic pressure in the first discharge oil passage 58 is regulated to a predetermined hydraulic pressure P1, the second input port is synchronized with the communication between the first input port 38 and the first output port 44 of the pressure regulating valve 16. 42 and the 2nd output port 46 are connected, and the pressure of the 2nd discharge oil path 60 falls. For this reason, the check valve 64 prevents the hydraulic oil from flowing into the first discharge oil passage 58, and the second discharge pressure with the reduced hydraulic pressure is supplied as a back pressure that presses each vane 81 against the inner peripheral cam surface 78. Therefore, when the vane pump 14 rotates at high speed, the pressing force against the inner peripheral cam surface 78 of each vane 81 defining each pump chamber P between the second suction port 24 and the second discharge port 28 is reduced. Further, the loss torque due to the sliding resistance between the vane 81 and the cam ring 70 is suppressed to improve the fuel efficiency of the vehicle, and the wear due to the sliding between the vane 81 and the inner peripheral cam surface 78 is suppressed to increase the durability of the vane pump 14. It is done.

  Next, another embodiment of the present invention will be described. In the following embodiments, parts that are substantially the same as those in the above embodiments are denoted by the same reference numerals, and detailed description thereof is omitted.

  The hydraulic control apparatus according to the present embodiment is substantially the same as the hydraulic control apparatus 10 described above except that the configuration of the vane pump 100 and the configuration of the connection between the vane pump 100 and the oil passage are different. Therefore, only the different configuration will be described in detail with reference to FIG.

  FIG. 4 is a front view of a vane pump 100 according to another embodiment of the present invention with a pump cover removed. The rotor 102 communicates with the radially inner end portion of the slit 80 in which the vanes 81 that divide the pump chambers P are radially inserted, and a back pressure that presses the vanes 81 against the inner peripheral cam surface 78 is supplied. Back pressure grooves 104a and 104b are formed annularly in the circumferential direction on both end surfaces of the rotor 102 in the axial direction. Further, the side plate 106 has a first suction port 108 a, a second suction port 110 a, a first discharge port 112 a, and a second discharge port 114 a, with each suction port and each discharge port facing each other across the pump shaft 76. Thus, the first discharge port 112a and the second discharge port 114a are formed so as to be positioned in the rotational direction of the rotor 102 with respect to the first suction port 108a and the second suction port 110a, respectively. Further, the side plate 106 is formed with a communication path 116a that communicates the second discharge port 114a and the back pressure groove 104a. Similarly to the side plate 106, the pump cover (not shown) includes the first suction port 108b, the second suction port 110b, the first discharge port 112b, the second discharge port 114b, the second discharge port 114b, and the rotor 102. A communication path 116b is formed to communicate with the back pressure groove 104b provided on the other end surface in the axial direction. The first suction port 108 a and the second suction port 110 a of the side plate 106 and the first suction port 108 b and the second suction port 110 b of the pump cover are connected to the first oil passage 56, and the first discharge port 112 a of the side plate 106. The first discharge port 112b of the pump cover is connected to the first discharge oil passage 58, and the second discharge port 114a of the side plate 106 and the second discharge port 114b of the pump cover are connected to the second discharge oil passage 60. Yes. In short, the second discharge pressure is applied to the vanes 81 that partition the pump chambers P through the back pressure grooves 104a and 104b formed on both end surfaces of the rotor 102 in the axial direction.

  When the engine speed N is low and the rotor 102 of the vane pump 100 is rotating at a low speed, the second discharge oil passage 60 permitted by the check valve 64 is used to promote the pressure adjustment by the pressure adjustment valve 16 of the first discharge pressure. The second discharge pressure, which is the same pressure as the first discharge pressure, is supplied as the back pressure to the vanes 81 through the back pressure grooves 104a and 104b by the circulation of the working oil to the first discharge oil passage 58. Further, when the rotor 102 of the vane pump 100 is rotated at a high speed in accordance with the engine speed N and the regulation of the first discharge pressure by the pressure regulating valve 16 is started, the first input port 38 and the first output port 44 communicated with each other. By increasing the outflow of hydraulic fluid from the second discharge oil passage 60 to the fourth oil passage 67 through the second input port 42 and the second output port 46 communicated in synchronization with each other, the check valve 64 causes the first The second discharge pressure in which the flow to the one discharge oil passage 58 is blocked and the hydraulic pressure is reduced is supplied as the back pressure to the vanes 81 through the back pressure grooves 104a and 104b.

  As described above, according to the hydraulic control device of the present embodiment, the hydraulic pressure of the first discharge oil passage 58 connected to the first discharge ports 112a and 112b is set to a lower pressure and connected to the second discharge ports 114a and 114b. The oil pressure of the second discharge oil passage 60 is passed through the back pressure grooves 104a and 104b connected to the second discharge oil passage 60 by the communication passages 116a and 116b, and the outer end of the vane 81 in the radial direction of the rotor 102 is Since the back pressure to be pressed against the cam surface 78 is supplied to the vane 81, even when the vane pump 100 is operated at high speed, the inner peripheral cam surface 78 of the vane 81 that defines each pump chamber P over the entire circumference in the circumferential direction of the rotor 102. The pressing force against is reduced. Accordingly, the loss torque due to the sliding resistance between the vane 81 and the cam ring 70 is suppressed to improve the fuel efficiency of the vehicle, and the wear due to the sliding between the vane 81 and the inner peripheral cam surface 78 is suppressed, so that the durability of the vane pump 100 is improved. Sexuality is enhanced.

  Further, according to the hydraulic control apparatus of the present embodiment, when the hydraulic pressure of the first discharge oil passage 58 that supplies hydraulic oil to the hydraulic control target 12 is lower than the predetermined hydraulic pressure P1, the first input port of the pressure regulating valve 16 38 and the first output port 44 and between the second input port 42 and the second output port 46 are both closed, and the second oil that connects the first discharge oil path 58 and the second discharge oil path 60. When the check valve 64 provided in the passage 62 is opened, the flow of the hydraulic oil to the first discharge oil passage 58 is permitted, and the second discharge pressure that is substantially the same as the first discharge pressure is Through the pressure grooves 104a and 104b, each vane 81 is supplied as a back pressure that presses each vane 81 against the inner circumferential cam surface 78 with respect to each vane 81 that divides each pump chamber over the entire circumference in the circumferential direction of the rotor 102. Inner cam of vane 81 at start-up Pressing force or hydraulic responsiveness to 78 is ensured. When the hydraulic pressure in the first discharge oil passage 58 is regulated to a predetermined hydraulic pressure P1, the second input port is synchronized with the communication between the first input port 38 and the first output port 44 of the pressure regulating valve 16. 42 and the 2nd output port 46 are connected, and the pressure of the 2nd discharge oil path 60 falls. For this reason, the check valve 64 prevents the hydraulic oil from flowing to the first discharge oil passage 58, and the second discharge pressure with reduced hydraulic pressure is supplied as a back pressure that presses each vane 81 against the inner peripheral cam surface 78. Therefore, when the vane pump 100 rotates at high speed, the pressing force against the inner circumferential cam surface 78 of each vane 81 that defines each pump chamber P over the entire circumference in the circumferential direction of the rotor 102 is reduced. The loss torque due to the sliding resistance with respect to 70 is suppressed to improve the fuel efficiency of the vehicle, and the wear due to the sliding between the vane 81 and the inner peripheral cam surface 78 can be suppressed to increase the durability of the vane pump 100.

  As mentioned above, although this invention was demonstrated in detail with reference to the table | surface and drawing, this invention can be implemented in another aspect, and can be variously changed in the range which does not deviate from the main point.

  For example, in the vane pump 14 of the first embodiment and the vane pump 100 of the second embodiment, the cam ring 70 having the inner peripheral cam surface 78 is fitted in the recess 68 of the housing 69. However, the present invention is not limited to this. For example, the inner peripheral cam surface 78 that faces the outer peripheral surfaces of the rotors 74 and 102 may be formed directly on the inner peripheral surface of the recess 68 of the housing 69, and may be configured without a cam ring.

  Further, the vane pump 14 of the first embodiment has the pair of discharge ports 26 and 28 and the pair of suction ports 22 and 24. However, the present invention is not limited to this. For example, the first suction port 22 and a first vane pump having a first discharge port 26 and a second vane pump having a second suction port 24 and a second discharge port 28.

  In the hydraulic control apparatus 10 according to the first embodiment, a ball valve type check valve 64 is provided in the second oil passage 62 that connects the first discharge oil passage 58 and the second discharge oil passage 60. However, the present invention is not limited to this, and when the engine speed N is small, the flow of hydraulic oil from the second discharge oil path 60 to the first discharge oil path 58 is permitted, and the engine speed N is large. In some cases, the check valve may be a spool valve type check valve that prevents the flow of hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58. FIG. 5 shows an example check valve 84. In the check valve 84, the valve closing direction corresponding to the biasing force of the spring 88 and the hydraulic pressure input to the first input port 92, that is, the upward biasing force in FIG. 5 is input to the second input port 96. 4 is large with respect to the valve opening direction, that is, the downward biasing force in FIG. 4, the one end surface of the land portion 98 is brought into contact with the plate 90, and the second end surface and the outer peripheral surface of the land portion 98 The input port 96 and the output port 94 are closed, and the urging force corresponding to the hydraulic pressure input to the second input port 96 corresponds to the urging force of the spring 88 and the hydraulic pressure input to the first input port 92. When the force is larger than the biasing force, the spool valve element 86 is displaced downward in FIG. 5 and the space between the second input port 96 and the output port 94 is opened. For this reason, even when the vane pump provided with the check valve 84 is operated at high speed, the pressing force of the vane 81 against the inner peripheral cam surface 78 is reduced. Therefore, due to the sliding resistance between the vane 81 and the inner peripheral cam surface 78. It is possible to increase the durability of the vane pump by suppressing the loss and improving the fuel efficiency of the vehicle and suppressing the wear caused by the sliding between the vane 81 and the inner peripheral cam surface 78.

  In the hydraulic control apparatus 10 according to the first embodiment, the first suction port 22, the second suction port 24, the first discharge port 26, the second discharge port 28, and the first back pressure groove 30 are provided on the side plate 72. The second back pressure groove 32, the first communication path 82, and the second communication path 83 are provided, but the present invention is not limited to this. For example, instead of the side plate, The suction and discharge ports, the back pressure grooves and the communication paths may be formed, and the first discharge port and the second discharge port may be connected to the first discharge oil path and the second discharge oil path. Further, the suction port, the back pressure groove and the communication passage are formed in both the side plate and the pump cover, and the first discharge port and the second discharge port are the first discharge oil passage and the second discharge port. It may be connected to the oil passage.

  In the hydraulic control apparatus of the second embodiment described above, the first suction ports 108a and 108b, the second suction ports 110a and 110b, the first discharge ports 112a and 112b, and the first discharge ports are formed on the side plates 106 and the inner wall surfaces of the pump cover. The two discharge ports 114a and 114b and the communication passages 116a and 116b are formed, and the back pressure grooves 104a and 104b are formed on both end surfaces in the axial direction of the rotor 102. However, the present invention is not limited to this. The suction / discharge ports may be formed on any one of the side plate and the pump cover, and a back pressure groove may be formed on one end surface in the axial direction of the rotor. Moreover, it replaces with the back pressure groove formed in the rotor, and the back pressure groove may be formed in the side plate and the pump cover.

  Moreover, in the hydraulic control apparatus 10 of the above-described first embodiment, the single pressure regulating valve 16 is used. However, the pressure regulating valve 16 is not limited to this. For example, the hydraulic pressure of the first discharge oil path is increased by the first pressure regulating valve. May be regulated to a predetermined hydraulic pressure, and the hydraulic pressure of the second discharge oil passage may be regulated to the predetermined hydraulic pressure by the second pressure regulating valve.

10: Hydraulic control device 14, 100: Vane pump 16: Pressure regulating valve 30: First back pressure groove 32: Second back pressure groove 58: First discharge oil passage 60: Second discharge oil passage 64, 84: Check valve 70 : Cam ring 74, 102: Rotor 78: Inner peripheral cam surface 81: Vane 104a, 104b: Back pressure groove

Claims (1)

A housing having an elliptical inner circumferential cam surface, a rotor rotatably provided in the housing so that the outer circumferential surface faces the inner circumferential cam surface, and a slidable radial direction of the rotor A plurality of vanes formed, a back pressure groove for supplying a back pressure that presses the outer peripheral end of the plurality of vanes against the inner circumferential cam surface, a first discharge port and a second discharge for discharging the sucked hydraulic oil In a vehicle hydraulic control device having a vane pump with a port,
Operation from the second discharge oil passage to the first discharge oil passage between the first discharge oil passage connected to the first discharge port and the second discharge oil passage connected to the second discharge port A second check valve configured to allow a flow of oil and to prevent a flow of hydraulic oil from the first discharge oil passage toward the second discharge oil passage, and to be equal to or lower than a hydraulic pressure of the first discharge oil passage; A vehicle hydraulic control apparatus, wherein a discharge oil passage is communicated with the back pressure groove.

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