JP2015203471A - Vehicle hydraulic control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the lowering of pump durability caused by valve wear, oil pump noise and an impact load of an oil pump.SOLUTION: In the case where the circulation of a working fluid progressing toward a first discharge oil passage 58 from a second discharge oil passage 60 is hindered by a check valve 64, when a flow-out rate of the working fluid flowing out of the first discharge oil passage 58 is increased and decreased, a small flow rate of the working fluid smaller than a flow rate of the working fluid, which is made to circulate to the first discharge oil passage 58 from the second discharge oil passage 60 when the circulation of the working fluid progressing toward the first discharge oil passage 58 from the second discharge oil passage 60 is permitted by the check valve 64, is made to circulate to the second discharge oil passage 60 from the first discharge oil passage 58 through a valve clearance 55 which functions as a throttle oil passage, thereby a width of an increase and decrease of the working hydraulic pressure of the second discharge oil passage 60 is reduced, an abrupt change of second discharge pressure is thus suppressed, and the lowering of pump durability caused by valve wear, oil pump noise, and an impact load of an oil pump can be reduced.

Description

  The present invention relates to a vehicular hydraulic control apparatus including an oil pump having two discharge ports, and more particularly, to suppress a sudden change in the hydraulic pressure of a discharge oil passage connected to one discharge port caused by fluctuations in engine speed, etc. The present invention relates to a technology for suppressing deterioration of pump durability due to wear, oil pump noise, and impact load of an oil pump.

  In order to reduce the waste work of the oil pump, in addition to the first discharge port connected to the first discharge oil passage, when the oil pressure of the first discharge oil passage is less than a predetermined oil pressure regulated by the pressure regulating valve, When the hydraulic oil is circulated to the first discharge oil passage and the hydraulic pressure of the first discharge oil passage is the predetermined hydraulic pressure, the hydraulic oil flows out through the pressure regulating valve, and the second pressure is lower than that of the first discharge oil passage. There has been proposed a hydraulic control device including an oil pump having a second discharge port connected to a discharge oil passage. For example, this is the vehicle hydraulic control device described in Patent Document 1.

  FIG. 8 is a schematic diagram illustrating an example of a conventional vehicle hydraulic control device such as that disclosed in Patent Document 1. The vehicle hydraulic control device 210 has a first discharge port 212 and an oil pump 214 driven by an engine and an oil having a second discharge port 215 driven in the same rotation by the same drive source as the oil pump 214. A pump 216, a first discharge oil passage 220 that supplies hydraulic oil from the first discharge port 212 to the control target 218, and a second discharge oil passage 222 that outputs hydraulic oil from the second discharge port 215. I have. Further, the vehicle hydraulic control device 210 includes a pressure regulating valve 224 that varies the amount of hydraulic oil flowing out from the first discharge oil passage 220 to regulate the hydraulic pressure in the first discharge oil passage 220 to a predetermined pressure P1. . In addition, the vehicle hydraulic control device 210 allows the hydraulic oil to flow from the second discharge oil passage 222 to the first discharge oil passage 220 between the first discharge oil passage 220 and the second discharge oil passage 222. And a check valve 226 that prevents the flow of hydraulic oil from the first discharge oil passage 220 toward the second discharge oil passage 222.

Figure 9 is a diagram showing a relationship between the hydraulic pressure P _L of the engine speed N and the discharge passage in the vehicle hydraulic control unit 210 in FIG. 8. When the engine speed N for driving the oil pump 214 and the oil pump 216 is low, the hydraulic oil is circulated from the second discharge oil passage 222 to the first discharge oil passage 220 via the check valve 226, and the first The rise of pressure regulation by the pressure regulation valve 224 in the discharge oil passage 220 is promoted. When the engine speed N reaches N1, the hydraulic fluid that flows out from the first discharge oil passage 220 of the pressure regulating valve 224 is adjusted so that the hydraulic pressure in the first discharge oil passage 220 is regulated to the predetermined pressure P1 by the pressure regulation valve 224. The amount of is adjusted. When the engine speed N reaches a predetermined speed N2, the flow of hydraulic oil from the second discharge oil path 222 to the first discharge oil path 220 is blocked by the check valve 226, and the second discharge through the pressure regulating valve 224 is performed. The amount of hydraulic oil flowing out from the oil passage 222 is increased, and the hydraulic pressure in the second discharge oil passage 222 is reduced. As described above, when the flow of the hydraulic oil from the second discharge oil passage 222 to the first discharge oil passage 220 for promoting the pressure adjustment by the pressure adjusting valve 224 of the hydraulic pressure of the first discharge pressure oil passage 220 becomes unnecessary, the second Since the hydraulic pressure of the discharge oil passage 222 is reduced to a low pressure, the waste work of the oil pump 216 is reduced.

JP 2007-107698 A

  However, in such a vehicular hydraulic control apparatus 210, when the engine speed N changes in the vicinity of the predetermined speed N2 and fluctuates as shown by the arrow in FIG. Due to the displacement in the axial direction of the spool valve element for adjusting the hydraulic pressure to the predetermined pressure P1, the second discharge pressure is changed with a large amplitude, as shown in FIG. A sudden change in hydraulic pressure occurs. This may cause problems such as valve wear, oil pump noise, and deterioration of pump durability due to the impact load of the oil pump.

  The present invention has been made in the background of the above circumstances, and the object of the present invention is valve wear, oil pump noise, oil pump noise caused by a sudden change in the second discharge pressure caused by fluctuations in the engine speed N. An object of the present invention is to provide a vehicle hydraulic control device that suppresses a decrease in pump durability due to an impact load.

  That is, the gist of the present invention is an oil pump having a first discharge port connected to the first discharge oil passage and a second discharge port connected to the second discharge oil passage, and the first discharge oil passage. A first port for flowing hydraulic oil from the first discharge oil passage, and a second port connected to the second discharge oil passage and for flowing hydraulic oil from the second discharge oil passage, The first port and the second port are opened synchronously, the pressure regulating valve for regulating the hydraulic pressure of the first discharge oil passage by increasing or decreasing the flow rate of the hydraulic oil flowing out from the first discharge oil passage; Provided between one discharge oil passage and the second discharge oil passage, allowing the flow of hydraulic oil from the second discharge oil passage to the first discharge oil passage, and from the first discharge oil passage to the first discharge oil passage. A hydraulic control device for a vehicle, comprising: a check valve that prevents flow of hydraulic oil toward the discharge oil passage; When the flow of hydraulic oil from the second discharge oil passage to the first discharge oil passage is blocked by the check valve, the flow of hydraulic oil from the second discharge oil passage to the first discharge oil passage is prevented. The hydraulic fluid having a flow rate smaller than the flow rate of the hydraulic fluid flowing from the second discharge oil passage to the first discharge oil passage when allowed by the check valve is supplied from the first discharge oil passage to the second. A vehicular hydraulic control device includes a throttle oil passage that circulates to a discharge oil passage.

  According to the hydraulic control device of the present invention, when the flow of the hydraulic oil from the second discharge oil passage to the first discharge oil passage is blocked by the check valve, the hydraulic oil is discharged from the first discharge oil passage. When the flow rate of the hydraulic oil is increased or decreased, the flow of hydraulic oil from the second discharge oil passage to the first discharge oil passage is allowed by the check valve from the second discharge oil passage. Since the hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil flowing to the discharge oil passage is caused to flow out from the first discharge oil passage to the second discharge oil passage through the throttle oil passage, the inside of the second discharge oil passage Since the increase / decrease width of the hydraulic oil pressure is reduced, the rapid decrease and increase of the hydraulic pressure of the second discharge oil passage, that is, the rapid change of the hydraulic pressure is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Here, preferably, the throttle oil passage is configured such that when the check valve prevents the hydraulic oil from flowing from the second discharge oil passage to the first discharge oil passage, A valve clearance is formed between a port to which one discharge oil passage is connected and a port to which the second discharge oil passage is connected. For this reason, when the flow of the hydraulic oil from the second discharge oil passage to the first discharge oil passage is blocked by the check valve, the working oil pressure in the first discharge oil passage is increased or decreased. From the flow rate of hydraulic fluid flowing from the second discharge oil passage to the first discharge oil passage when the check valve allows the flow of hydraulic oil from the two discharge oil passages to the first discharge oil passage A small amount of hydraulic fluid flows from the first discharge oil passage through the valve clearance between the port to which the first discharge oil passage is connected and the port to which the second discharge oil passage is connected. Since it is caused to flow out to the road, the increase / decrease width of the hydraulic pressure in the second discharge oil passage is reduced, and a sudden change in the oil pressure in the second discharge oil passage is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Preferably, the throttle oil passage extends from the second discharge oil passage to the first discharge oil passage between an outer peripheral surface of a spool valve element and an inner peripheral surface of a cylinder bore into which the spool valve element is fitted. It is constituted by a valve clearance of a check valve that permits the flow of the hydraulic oil toward the flow direction and prevents the flow of the hydraulic oil from the first discharge oil path to the second discharge oil path. For this reason, the flow of the hydraulic oil from the second discharge oil passage to the first discharge oil passage is blocked by the check valve, and the flow rate of the hydraulic oil flowing out from the first discharge oil passage is increased or decreased. When the flow of the hydraulic oil from the second discharge oil passage to the first discharge oil passage is permitted by the check valve, the operation is made to flow from the second discharge oil passage to the first discharge oil passage. Since the hydraulic oil having a flow rate smaller than the flow rate of the oil flows from the first discharge oil passage to the second discharge oil passage through the valve clearance of the check valve, the hydraulic oil from the second discharge oil passage The increase / decrease width of the outflow amount is reduced, and a sudden change in the oil pressure in the second discharge oil passage is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Preferably, the throttle oil passage is configured by an orifice that is provided between the first discharge oil passage and the second discharge oil passage and through which hydraulic oil flows. For this reason, when the flow of hydraulic oil from the second discharge oil passage to the first discharge oil passage is blocked by the check valve, the flow rate of the hydraulic oil flowing out from the first discharge oil passage is increased or decreased. The hydraulic oil flowing from the second discharge oil passage to the first discharge oil passage is allowed to flow from the second discharge oil passage to the first discharge oil passage when allowed by the check valve. Since the hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil flows from the first discharge oil passage on the high pressure side to the second discharge oil passage on the low pressure side through the orifice, the hydraulic oil flows out from the second discharge oil passage. The amount of increase / decrease is reduced, and a sudden change in the oil pressure in the second discharge oil passage is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

It is the schematic explaining the structure of the hydraulic control apparatus of this invention. It is the schematic explaining the structure of the hydraulic control apparatus in the other Example of this invention. It is the schematic explaining the structure of the hydraulic control apparatus in the other Example of this invention. FIG. 4 is a front view for explaining in detail a check valve of the hydraulic control device of FIG. 3. It is the top view which looked at the spool of the non-return valve of FIG. 4 from the axial upper side. It is a front view explaining in detail the check valve with which the hydraulic control device in other examples of the present invention was equipped. It is the schematic explaining the structure of the hydraulic control apparatus in the other Example of this invention. It is the schematic explaining the conventional structure of a hydraulic control apparatus. It is a figure which shows the relationship between the engine speed of the hydraulic control apparatus of FIG. 8, and the hydraulic pressure of each discharge oil path.

  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 apparatus 10 includes an oil pump 14 and an oil pump 15 that supply hydraulic oil to a control target 12 that consumes hydraulic oil such as a hydraulic cylinder of A / T or CVT, and the oil pump 14 and the oil pump 15 to the control target 12. And a pressure regulating valve 16 for controlling the hydraulic pressure of the discharged hydraulic oil, that is, the line pressure.

  The oil pump 14 and the oil pump 15 are driven by a common drive shaft by the engine, and a first suction port 22 and a second suction port 24 that suck the working oil stored in the oil pan 18 through the oil strainer 20. Each has a first discharge port 26 and a second discharge port 28 for discharging the sucked hydraulic oil.

  The pressure regulating valve 16 includes a valve body 30, a spool valve element 32 slidably fitted in a bore formed in the valve body 30, and the spool valve element 32 in the valve closing direction, that is, in the upward direction in FIG. 1. The spring 34 is configured to be biased. The valve body 30 has a first input port 36, a second input port 38, a third input port 40 and a feedback port 42 on its outer peripheral surface, and similarly has a first output port 44 and a second output port 46. doing. The spool valve element 32 is formed on the inner peripheral surface of the valve body 30 in the form of a cylindrical land portion slidable in the axial direction on the outer peripheral surface, that is, in order from the upper side in the axial direction of the spool valve element 32 in FIG. Part 48, second land part 50, third land part 52, and fourth land part 54. Further, the spool valve element 32 is on a plane orthogonal to the axial direction of the spool valve element 32 so as to be biased in the valve closing direction, that is, the downward direction in FIG. 1 by the hydraulic pressure of the hydraulic oil input to the feedback port 42. The first land portion 48 and the second land portion 50 are configured to be smaller than the third land portion 52 and the fourth land portion 54. In the pressure regulating valve 16 configured in this way, the urging force in the valve closing direction corresponding to the hydraulic pressure of the hydraulic oil input to the feedback port 42 is larger than the urging force in the valve closing direction of the spring 34, so that the spool When the valve element 32 is slid in the downward direction of FIG. 1 with respect to the valve body 30, between the first input port 36 and the first output port 44 and between the second input port 38 and the second output port 46. Are opened synchronously. The shape of each land portion is such that the opening sectional area between the second input port 38 and the second output port 46 is larger than the opening sectional area between the first input port 36 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 30 and each land portion of the spool valve element 32 are set. . A valve clearance 55 that functions as a throttle oil passage is provided between the feedback port 42 and the third input port 40. As the hydraulic oil is circulated from the high pressure side to the low pressure side and the displacement of the spool valve element 32 in the downward direction in FIG. The outer surface of the third land portion 52 facing the inner peripheral surface between the second input port 40 and the third input port 40 is reduced, that is, the axial length of the valve clearance 55 is reduced. The positional relationship is adjusted. The first input port 36 and the first output port 44 communicated with each other are connected to the first port of the present invention, and the connected second input port 38 and the second output port 46 are connected to the first port of the present invention. The feedback port 42 corresponds to a port to which the first discharge oil passage of the present invention is connected, and the third input port 40 corresponds to a port to which the second discharge oil passage of the present invention is connected. .

  The first oil path 56 connects the first suction port 22 of the oil pump 14, the second suction port 24 of the oil pump 15, and the oil pan 18. The first discharge oil path 58 connects the first discharge port 26 of the oil pump 14 to the first input port 36 and the feedback port 42 of the pressure regulating valve 16, and serves as a hydraulic oil supply path to the control target 12. . The second discharge oil passage 60 is connected to the second discharge port 28 of the oil pump 15 and the second input port 38 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. The third input port 40 is connected. The second oil passage 62 allows the hydraulic oil to flow from the second discharge oil passage 60 side to the first discharge oil passage 58 side, 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 check valve 64 that blocks the flow. The check valve 64 is circulated from the second discharge oil passage 60 to the first discharge oil passage 58 when the hydraulic oil is allowed to flow from the second discharge oil passage 60 to the first discharge oil passage 58. From the high pressure side through the valve clearance 55 between the feedback port 42 and the third input port 40 when the oil flow rate is different between the hydraulic pressure of the first discharge oil passage 58 and the hydraulic pressure of the second discharge oil passage 60. The hydraulic oil is configured to be sufficiently larger than the amount of hydraulic oil circulated to the low pressure side. When the first input port 36 and the first output port 44 of the pressure regulating valve 16 are in communication with each other, the third oil passage 66 supplies the hydraulic oil in the first discharge oil passage 58 to, for example, a second pressure regulating valve (not shown). . The fourth oil passage 68 causes the hydraulic oil in the second discharge oil passage 60 to return to the oil pan 18 when the second input port 38 and the second output port 46 of the pressure regulating valve 16 are in communication.

  Next, the control of the hydraulic pressure of the first discharge oil passage 58 in the hydraulic control device 10 will be described. Due to the rotation of the rotation shafts of the oil pump 14 and the oil pump 15 according to the driving of a drive source such as an engine, the hydraulic oil stored in the oil pan 18 passes through the first oil passage 56 and the first suction port 22 and the second suction port. 24 is sucked into the oil pump 14 and the oil pump 15 and discharged from the first discharge port 26 to the first discharge oil passage 58 and from the second discharge port 28 to the second discharge oil passage 60, respectively. When the engine speed N synchronized with the rotation of the rotary shafts of the oil pump 14 and the oil pump 15 is low, the first discharge pressure is less than the predetermined pressure P1 required for the controlled object 12, and therefore the spring 34 of the pressure regulating valve 16 The energizing force in the valve closing direction is larger than the energizing force in the valve opening direction corresponding to the hydraulic pressure input to the feedback port 42, and between the first input port 36 and the first output port 44, and the second input port 38. The connection with the second output port 46 is closed. At this time, the flow of the hydraulic oil through the second oil passage from the second discharge oil passage 60 to the first discharge oil passage 58 is permitted by the check valve 64, and the pressure regulation by the pressure regulating valve 16 of the first discharge oil passage 58 is performed. The rise of is promoted. When the engine speed N becomes a predetermined speed N1 and the first discharge pressure is sufficient for the supply pressure to the control target 12, the urging force in the valve opening direction corresponding to the hydraulic pressure input to the feedback port 42 is obtained. The first input port 36 and the first output port 44 are opened and closed simultaneously so that the biasing force of the spring 34 in the valve closing direction is balanced and the first discharge pressure becomes a constant pressure P1. The two input ports 38 and the second output port 46 are opened and closed in synchronization. At this time, the opening sectional area between the communicated first input port 36 and the first output port 44 is larger than the opening sectional area between the communicated second input port 38 and the second output port 46. Since the first discharge pressure and the second discharge pressure are the same pressure, the first discharge oil path 58 is connected to the first discharge port 58 through the first input port 36 and the first output port 44 that are communicated with each other as the engine speed is increased. The amount of hydraulic oil that flows out from the second discharge oil passage 60 to the fourth oil passage 68 through the connected second input port 38 and second output port 46 is greater than the amount of hydraulic oil that flows out to the third oil passage 66. Therefore, the flow of hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is blocked by the check valve 64 and discharged from the second discharge port 28 to the second discharge oil passage 60. The hydraulic fluid is communicated with the second input port 38 and the second output port. It is returned to the oil pan 18 through 46 and the fourth oil passage 68.

  When the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is blocked by the check valve and the engine speed N is increased, the pressure of the first discharge oil passage 58 is adjusted. The displacement of the spool valve element 32 in the downward direction in FIG. 1 is increased, and the hydraulic oil from the first discharge oil passage 58 to the third oil passage 66 passing between the first input port 36 and the first output port 44 is increased. As the outflow amount increases, the outflow amount of hydraulic oil from the second discharge oil passage 60 to the fourth oil passage 68 through the second input port 38 and the second output port 46 communicated with each other increases. Therefore, the second discharge pressure is reduced. Further, when the engine speed N is reduced when the second discharge pressure is reduced, the spool valve element 32 is displaced downward in FIG. 1 due to pressure regulation of the first discharge oil passage 58. When the amount of hydraulic fluid flowing out from the first discharge oil passage 58 to the third oil passage 66 between the first input port 36 and the first output port 44 is reduced, the second input port 38 Since the amount of hydraulic oil flowing out from the second discharge oil passage 60 to the fourth oil passage 68 through the second output port 46 is also reduced, the second discharge pressure is increased and the second discharge oil passage 60 The flow of the hydraulic oil to the first discharge oil passage 58 is allowed by the check valve 64.

  When the check valve 64 is opened and closed, it is provided between the feedback port 42 to which the first discharge oil passage 58 of the pressure regulating valve 16 is connected and the third input port 40 to which the second discharge oil passage 60 is connected. When the check valve 64 allows the flow of hydraulic oil from the second discharge oil path 60 to the first discharge oil path 58 through the valve clearance 55 that functions as a throttle oil path, the operation is allowed through the check valve 64. The hydraulic oil having a flow rate smaller than the oil flow rate is circulated from the first discharge oil passage 58 having a pressure higher than the second discharge pressure to the second discharge oil passage 60 in accordance with the differential pressure. For this reason, the increase / decrease width of the hydraulic pressure flowing out from the second discharge oil passage 60 to the fourth oil passage 68 through the second input port 38 and the second output port 46 communicated with each other is reduced. Further, as the engine speed N increases, the differential pressure between the second discharge pressure and the first discharge pressure increases, and the axial length of the valve clearance 55 decreases, so that the first discharge through the valve clearance 55 is reduced. Since the distribution of the hydraulic oil from the oil passage 58 to the second discharge oil passage 60 is increased, the increase / decrease width of the hydraulic pressure in the second discharge oil passage 60 is further reduced.

  As described above, according to the hydraulic control apparatus 10 of the present embodiment, when the flow of hydraulic oil from the second discharge oil passage 60 toward the first discharge oil passage 58 is blocked by the check valve 64, the second discharge When the flow of the hydraulic oil from the oil path 60 to the first discharge oil path 58 is allowed by the check valve 64, the flow rate of the hydraulic oil circulated from the second discharge oil path 60 to the first discharge oil path 58 is larger. A small flow rate of the hydraulic oil flows from the first discharge oil passage 58 to the second discharge oil passage 60 through the valve clearance 55 functioning as a throttle oil passage, so that the increase / decrease width of the hydraulic pressure from the second discharge oil passage 60 is increased. Since the second discharge pressure is reduced, a rapid decrease and increase in the second discharge pressure, that is, a sudden change in hydraulic pressure is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Further, according to the hydraulic control device 10 of the present embodiment, the throttle oil passage is adjusted when the check valve 64 prevents the flow of hydraulic oil from the second discharge oil passage 60 toward the first discharge oil passage 58. The pressure valve 16 includes a valve clearance 55 between the feedback port 42 to which the first discharge oil passage 58 is connected and the third input port 40 to which the second discharge oil passage 60 is connected. For this reason, when the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is blocked by the check valve 64, the outflow amount of the hydraulic oil flowing out from the first discharge oil passage 58 increases or decreases. In this case, when the check valve 64 permits the flow of the working oil from the second discharge oil passage 60 to the first discharge oil passage 58, the second discharge oil passage 60 is supplied from the second discharge oil passage 60 to the first discharge oil passage 58. The valve clearance 55 between the feedback port 42 to which the first discharge oil passage 58 is connected and the third input port 40 to which the second discharge oil passage 60 is connected is smaller than the flow rate of the working oil. Therefore, the increase / decrease width of the hydraulic pressure in the second discharge oil passage 60 is reduced, and a sudden change in the second discharge pressure is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Next, another embodiment of the present invention will be described. In the following embodiments, portions that are substantially common in function to the above embodiments are assigned the same reference numerals, and detailed descriptions thereof are omitted.

  FIG. 2 is a schematic diagram illustrating the configuration of a hydraulic control device 70 according to another embodiment of the present invention. The hydraulic control device 70 is substantially the same in function as the hydraulic control device 10 described above except that the configuration of the pressure regulating valve 72 is different. Therefore, the different configuration will be described in detail with reference to FIG.

  The pressure regulating valve 72 is connected to the high pressure side through a valve clearance 96 between the feedback port 82 and the second input port 80 and a valve clearance 97 (throttle oil passage) between the first input port 78 and the third input port 81. The first input port 78 and the third input port 81 are allowed to flow slightly from the first discharge oil passage 58 to the second discharge oil passage 60 on the low pressure side and within the slidable range of the spool valve element 76. The relative positional relationship between the feedback port 82 and the second input port 80 and the first input port 78 and the third input port 81 is set so that the axial length of the valve clearance 97 between the first input port 78 and the third input port 81 is not changed. Has been. In the right half of the pressure regulating valve 72 in FIG. 2, the spool valve element 76 is not displaced downward, and the left half is the urging force in the valve opening direction corresponding to the hydraulic pressure input to the feedback port 82. The pressure adjustment state in which the biasing force in the valve closing direction of the spring 34 is balanced and the first input port 78 and the first output port 84 and the second input port 80 and the second output port 86 are opened and closed. Is shown.

  A 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 of the hydraulic control device 70. When the check valve 64 allows the hydraulic oil to flow from the second discharge oil path 60 to the first discharge oil path 58, the check valve 64 allows the hydraulic oil to flow from the second discharge oil path 60 to the first discharge oil path 58. The valve clearance 96 functions as a throttle oil path between the feedback port 82 and the second input port 80 and the valve clearance 96 functions as a throttle oil path between the first input port 78 and the third input port 81. 97, the flow rate of the hydraulic oil flowing from the high pressure side to the low pressure side is increased according to the differential pressure between the hydraulic pressure of the first discharge oil passage 58 and the hydraulic pressure of the second discharge oil passage 60. Yes.

  When the check valve 64 is opened and closed, the restriction provided between the feedback port 82 connected to the first discharge oil path 58 of the pressure regulating valve 72 and the second input port 80 connected to the second discharge oil path 60. A valve clearance 96 that functions as an oil passage, and a throttle oil provided between a first input port 78 to which the first discharge oil passage 58 is connected and a third input port 81 to which the second discharge oil passage 60 is connected. When the flow of hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is permitted by the check valve 64 through the valve clearance 97 functioning as a passage, the first discharge from the second discharge oil passage 60 The hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil flowing to the oil passage 58 is circulated from the first discharge oil passage 58 having a pressure higher than the second discharge pressure to the second discharge oil passage 60 according to the differential pressure. The For this reason, the increase / decrease width of the hydraulic pressure of the second discharge oil passage 60 is reduced. Even if the engine speed N is made larger than the predetermined speed, the axial length of the valve clearance 97 between the first input port 78 and the third input port 81 is not changed. The increase in the flow rate of hydraulic fluid from the first discharge oil passage 58 to the second discharge oil passage 60 through 97 is only an increase according to the differential pressure between the first discharge pressure and the second discharge pressure. The controllability of the first discharge pressure of the pressure valve 72 is good.

  As described above, according to the hydraulic control device 70 of the present embodiment, when the flow of hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is blocked by the check valve 64, the first discharge When the flow amount of the hydraulic oil flowing out from the oil passage 58 is increased or decreased, the second time when the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is permitted by the check valve 64. The hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil flowing from the discharge oil passage 60 to the first discharge oil passage 58 is discharged from the first discharge oil passage 58 through the valve clearances 96 and 97 that function as throttle oil passages. Since the oil pressure is distributed to the oil passage 60, the increase / decrease width of the hydraulic pressure in the second discharge oil passage 60 is reduced, so that a rapid decrease and increase in the second discharge pressure, that is, a sudden change in the oil pressure is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Further, according to the hydraulic control device 70 of the present embodiment, the throttle oil passage is the second input to which the feedback port 82 to which the first discharge oil passage 58 of the pressure regulating valve 72 is connected and the second discharge oil passage 60 is connected. A valve clearance 96 provided between the port 80 and a first input port 78 connected to the first discharge oil passage 58 and a third input port 81 connected to the second discharge oil passage 60 are provided. The valve clearance 97 is provided. For this reason, when the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is blocked by the check valve 64, the outflow amount of the hydraulic oil flowing out from the first discharge oil passage 58 increases or decreases. In this case, when the check valve 64 permits the flow of the working oil from the second discharge oil passage 60 to the first discharge oil passage 58, the second discharge oil passage 60 is supplied from the second discharge oil passage 60 to the first discharge oil passage 58. The valve clearance 96 between the feedback port 82 to which the first discharge oil passage 58 is connected and the second input port 80 to which the second discharge oil passage 60 is connected is smaller than the flow rate of the working oil. , And a second clearance from the first discharge oil passage 58 through a valve clearance 97 between the first input port 78 to which the first discharge oil passage 58 is connected and the third input port 81 to which the second discharge oil passage 60 is connected. Since the oil is distributed to the discharge oil passage 60, the second discharge Varying width of the working oil pressure of the road 60 is reduced, abrupt change of the second discharge pressure is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Next, another embodiment of the present invention will be described. FIG. 3 is a schematic diagram illustrating the configuration of a hydraulic control device 98 according to another embodiment of the present invention. When the pressure regulating valve 100 is compared with the pressure regulating valve 16 of the hydraulic control device 10 described above, the other configuration is common to the pressure regulating valve 16 except that a port corresponding to the third input port 40 is not formed. Therefore, the second discharge oil passage 60 of the hydraulic control device 98 is the second discharge oil passage of the hydraulic control device 10 except for the configuration other than the presence or absence of an oil passage connected from the second discharge port 28 to the third input port 40. There is substantially no difference from the 60 configuration.

  4 is a front view illustrating the configuration of the check valve 102 of the hydraulic control device 98, and FIG. 5 is a plan view of the spool valve element 104 of the check valve 102 as viewed from the upper side in the axial direction. The check valve 102 includes a cylindrical valve body 106 with a bottom at one end surface, a long spool valve element 104 that is slidably fitted into the valve body 106, and an inner end of the valve body 106 on the one end surface side. The spring 108 is interposed between the bottom and the spool valve element 104 and urges the spool valve element 104 in one axial direction, that is, upward in FIG. 4, and the shaft of the spool valve element 104 urged by the spring 108. And a plate 110 fastened to the valve body 106 so as to seal the opening of the valve body 106 while being in contact with one end surface in the direction, and is provided in the second oil passage 62. The valve body 106 is formed with a first input port 112 and an output port 114 connected to the first discharge oil passage 58 via the second oil passage 62. The plate 110 is formed with a second input port 115 which is an opening facing the one end surface of the spool valve element 104 and is connected to the second discharge oil passage 60 through the second oil passage 62. As shown in FIG. 5, the one end face of the land portion 116 of the spool valve element 104 is provided with a recess 118 that is recessed in the axial direction. Further, when the check valve 102 prevents the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58, the land portion 116 as shown in the right spool valve element 104 of FIG. Even when one end surface of the valve is in contact with the plate 110, a throttle oil passage between the inner peripheral surface of the cylinder bore between the output port 114 of the check valve 102 and the plate 110 and the outer peripheral surface of the land portion 116 is used. When allowing the hydraulic oil to flow from the second discharge oil passage 60 to the first discharge oil passage 58 through the functioning valve clearance 119 and the depression 118 of the spool valve element 104, the first discharge oil passage 60 makes the first discharge. According to the differential pressure between the first discharge pressure and the second discharge pressure, the hydraulic oil having a flow rate smaller than the amount of the hydraulic oil flowing through the oil path 58 is transferred from the first discharge oil path 58 to the second discharge oil path 60. Configured to circulate To have.

  When the check valve 102 is opened and closed, the valve clearance 119 and the second input port 115 provided between the output port 114 connected to the first discharge oil passage 58 of the check valve 102 and the plate 110 are opposed to each other. When the check valve 102 allows the flow of hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 through the recess 118 of the spool valve element 104, the first discharge oil from the second discharge oil passage 60 is allowed. The hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil flowing to the passage 58 is circulated from the first discharge oil passage 58 having a pressure higher than the second discharge pressure to the second discharge oil passage 60 according to the differential pressure. . For this reason, the increase / decrease width of the hydraulic pressure of the second discharge oil passage 60 is reduced.

  As described above, according to the hydraulic control device 98 of the present embodiment, when the check valve 102 prevents the hydraulic oil from flowing from the second discharge oil passage 60 to the first discharge oil passage 58, the first discharge is performed. When the flow amount of the hydraulic oil flowing out from the oil passage 58 is increased or decreased, the second time when the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is allowed by the check valve 102. The hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil flowing from the discharge oil passage 60 to the first discharge oil passage 58 passes through the valve clearance 119 functioning as a throttle oil passage from the first discharge oil passage 58 to the second discharge oil passage. Therefore, since the increase / decrease range of the operating hydraulic pressure in the second discharge oil passage 60 is reduced, a rapid decrease and increase in the second discharge pressure, that is, a sudden change in the hydraulic pressure is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Further, according to the hydraulic control device 98 of the present embodiment, the throttle oil passage is formed between the outer peripheral surface of the spool valve element 104 and the inner peripheral surface of the cylinder bore in which the spool valve element 104 is fitted. The valve clearance 119 of the check valve 102 that permits the flow of hydraulic oil from the first discharge oil passage 58 to the first discharge oil passage 58 and prevents the flow of hydraulic oil from the first discharge oil passage 58 to the second discharge oil passage 60. Has been. For this reason, when the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is blocked by the check valve 102, the outflow amount of the hydraulic oil flowing out from the first discharge oil passage 58 increases or decreases. In this case, when the check valve 102 permits the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58, the second discharge oil passage 60 passes through the first discharge oil passage 58. Since the hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil is circulated from the first discharge oil passage 58 to the second discharge oil passage 60 through the valve clearance 119 and the depression 118 of the check valve 102, the second discharge oil. The increase / decrease width of the hydraulic pressure in the path 60 is reduced, and a sudden change in the second discharge pressure is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Next, another embodiment of the present invention will be described. The hydraulic control device 120 according to another embodiment of the present invention is different from the above-described hydraulic control device 98 only in the configuration of the check valve, and the configuration of the oil pump, the pressure regulating valve, each oil passage, etc. 98 substantially in common. Therefore, the configuration of the check valve 122 of the hydraulic control device 120 will be described in detail with reference to FIG.

  FIG. 6 is a diagram illustrating the check valve 122 of the hydraulic control device 120 in detail. The check valve 122 includes a bottomed cylindrical valve body 124, a longitudinal spool valve 126 that is slidably fitted in the valve body 124 in the longitudinal direction thereof, an inner bottom of the valve body 124, and a spool valve The spring 126 is interposed between the spring 126 and urges the spool valve element 126 in one axial direction, that is, upward in FIG. 6, and is provided in the second oil passage 62. The valve body 124 includes a first input port 130, a second input port 132, a third input port 134, and an output port 136. The first input port 130 and the second input port 132 are connected to the second oil passage 62. The third input port 134 and the output port 136 are connected to the first discharge oil path 58 via the second oil path 62. The spool valve element 126 has a first land part 138 and a second land part 140. The hydraulic pressure input to the second input port 132 urges the spool valve element 126 upward in FIG. The hydraulic pressure input to the three input port 134 urges the spool valve element 126 downward in FIG. The check valve 122 is configured such that the spool valve element 126 is slid in the axial direction in accordance with the hydraulic pressure input to the second input port 132 and the hydraulic pressure input to the third input port 134. 130 and the output port 136 communicate with each other, permitting the flow of hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58, and the first input port 130 and the output port 136 are shut off, so that the first discharge The hydraulic fluid is configured to be prevented from flowing from the oil passage 58 toward the second discharge oil passage 60. In addition, the check valve 122 is configured such that the cylinder bore between the output port 136 of the valve body 124 and the first input port 130 when the flow of hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is blocked. When allowing hydraulic fluid to flow from the second discharge oil passage 60 to the first discharge oil passage 58 through the valve clearance 141 that functions as a throttle oil passage between the inner peripheral surface and the outer peripheral surface of the first land portion 138. In addition, the hydraulic oil having a flow rate smaller than the amount of hydraulic oil circulated from the second discharge oil passage 60 to the first discharge oil passage 58 is changed according to the differential pressure between the first discharge pressure and the second discharge pressure. It is configured to flow from the discharge oil passage 58 to the second discharge oil passage 60.

  When the check valve 122 is opened and closed, it is provided between the output port 136 to which the first discharge oil passage 58 of the check valve 122 is connected and the first input port 130 to which the second discharge oil passage 60 is connected. When the check valve 122 allows the hydraulic oil to flow from the second discharge oil passage 60 to the first discharge oil passage 58 through the valve clearance 141, which is the throttle oil passage, the second discharge oil passage 60 connects the second discharge oil passage 60 to the first discharge oil passage 58. The hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil flowing through the first discharge oil passage 58 is transferred from the first discharge oil passage 58 having a pressure higher than the second discharge pressure to the second discharge oil passage 60 according to the differential pressure. Distributed. For this reason, the increase / decrease width of the hydraulic pressure of the second discharge oil passage 60 is reduced.

  As described above, according to the hydraulic control device 120 of the present embodiment, when the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is blocked by the check valve 122, the first discharge When the amount of hydraulic oil flowing out from the oil passage 58 is increased or decreased, the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is permitted by the check valve 122. The hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil flowing from the two discharge oil passages 60 to the first discharge oil passage 58 passes from the first discharge oil passage 58 to the second discharge oil through the valve clearance 141 that functions as a throttle oil passage. Since it is distributed to the passage 60, the increase / decrease width of the working oil pressure in the second discharge oil passage 60 is reduced, so that a rapid decrease and increase in the second discharge pressure, that is, a sudden change in the oil pressure is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Further, according to the hydraulic control apparatus 120 of the present embodiment, the throttle oil passage is formed between the outer peripheral surface of the spool valve element 126 and the inner peripheral surface of the cylinder bore in which the spool valve element 126 is fitted. The valve clearance 141 of the check valve 122 that allows the hydraulic oil to flow from the path 60 to the first discharge oil path 58 and prevents the hydraulic oil from flowing from the first discharge oil path 58 to the second discharge oil path 60. It is configured. For this reason, when the flow of hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is blocked by the check valve 122, the outflow amount of the hydraulic oil flowing out from the first discharge oil passage 58 increases or decreases. In this case, when the check valve 122 allows the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58, it is circulated from the second discharge oil passage 60 to the first discharge oil passage 58. Since the hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil is circulated from the first discharge oil passage 58 to the second discharge oil passage 60 through the valve clearance 141 of the check valve 122, The increase / decrease range of the hydraulic pressure is reduced, and a sudden change in the second discharge pressure is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Next, another embodiment of the present invention will be described. FIG. 7 is a schematic diagram illustrating the configuration of the hydraulic control device 142 according to another embodiment of the present invention. The hydraulic control device 142 includes a fifth oil passage 146 that connects the first discharge oil passage 58 and the second discharge oil passage 60 and has an orifice 144 formed in the middle thereof. The oil passages of the hydraulic control device 98 and the hydraulic control device 120 are common in configuration and function. The hydraulic control device 142 replaces the check valve 102 of the hydraulic control device 98 and the check valve 122 of the hydraulic control device 120 with a check valve 64 provided in the hydraulic control device 10 and the hydraulic control device 70 described above. Two oil passages 62 are provided. The orifice 144 functioning as a throttle oil passage is connected to the first discharge oil passage 60 through the first discharge oil passage 60 when the check valve 64 permits the flow of hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58. The hydraulic oil having a flow rate smaller than the amount of hydraulic oil circulated to the oil passage 58 is configured to circulate from the high pressure side to the low pressure side.

  When the check valve 64 is opened and closed, when the check valve 64 allows the flow of hydraulic oil from the second discharge oil path 60 to the first discharge oil path 58, the first discharge oil path 60 causes the first discharge The hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil flowing into the oil passage 58 passes through the orifice 144 provided in the fifth oil passage 146 from the first discharge oil passage 58 having a pressure higher than the second discharge pressure to the second. The oil is distributed to the discharge oil passage 60 according to the differential pressure. For this reason, the increase / decrease width of the hydraulic pressure of the second discharge oil passage 60 is reduced.

  As described above, according to the hydraulic control device 142 of the present embodiment, when the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is blocked by the check valve 64, the first discharge When the flow of hydraulic oil flowing out from the oil passage 58 is increased or decreased, the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is permitted by the check valve 64. The hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil flowing from the two discharge oil passages 60 to the first discharge oil passage 58 passes through the orifice 144 functioning as a throttle oil passage from the first discharge oil passage 58 to the second discharge oil passage. Therefore, since the increase / decrease range of the operating hydraulic pressure in the second discharge oil passage 60 is reduced, a rapid decrease and increase in the second discharge pressure, that is, a sudden change in the hydraulic pressure is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  Further, according to the hydraulic control device 142 of the present embodiment, the orifice 144 through which the hydraulic oil flows is provided between the first discharge oil passage 58 and the second discharge oil passage 60. For this reason, when the flow of the hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is blocked by the check valve 64, the outflow amount of the hydraulic oil flowing out from the first discharge oil passage 58 increases or decreases. When the flow of hydraulic oil from the second discharge oil passage 60 to the first discharge oil passage 58 is permitted by the check valve 64, the second discharge oil passage 60 flows to the first discharge oil passage 58. Since the hydraulic oil having a flow rate smaller than the flow rate of the hydraulic oil to be supplied is circulated from the first discharge oil passage 58 on the high-pressure side to the second discharge oil passage 60 on the low-pressure side through the orifice 144, the second discharge oil passage 60 The increase / decrease range of the hydraulic pressure is reduced, and a sudden change in the second discharge pressure is suppressed. Thereby, deterioration of pump durability due to valve wear, oil pump noise, and impact load of the oil pump can be reduced.

  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 each of the hydraulic control devices of the first to fifth embodiments described above, the oil pump 14 and the oil pump 15 having one discharge port and one suction port are driven by the same drive shaft of the engine. However, the present invention is not limited to this. For example, one oil pump having two discharge ports may be driven by the engine and the other oil pump may be driven separately by the motor. .

10, 70, 98, 120, 142, 210: Hydraulic control devices 16, 72, 100, 224: Pressure regulating valves 55, 96, 97, 119, 141: Valve clearance (throttle oil passage)
58: First discharge oil passage 60: Second discharge oil passage 64, 102, 122, 226: Check valve 144: Orifice (throttle oil passage)

Claims (1)

An oil pump having a first discharge port connected to the first discharge oil passage and a second discharge port connected to the second discharge oil passage;
A first port connected to the first discharge oil passage and allowing hydraulic oil to flow out from the first discharge oil passage; and a first port connected to the second discharge oil passage and allowing hydraulic oil to flow out from the second discharge oil passage. There are two ports, and the first port and the second port are opened synchronously, and the hydraulic pressure of the first discharge oil passage is adjusted by increasing or decreasing the flow rate of the hydraulic oil flowing out from the first discharge oil passage. A pressure regulating valve;
It is provided between the first discharge oil passage and the second discharge oil passage, allows the hydraulic oil to flow from the second discharge oil passage to the first discharge oil passage, and from the first discharge oil passage. A vehicular hydraulic control device comprising: a check valve that prevents the flow of hydraulic fluid toward the second discharge oil passage;
When the flow of hydraulic oil from the second discharge oil passage to the first discharge oil passage is blocked by the check valve, the flow of hydraulic oil from the second discharge oil passage to the first discharge oil passage is prevented. The hydraulic fluid having a flow rate smaller than the flow rate of the hydraulic fluid flowing from the second discharge oil passage to the first discharge oil passage when allowed by the check valve is supplied from the first discharge oil passage to the second. A vehicular hydraulic control device including a throttle oil passage that circulates to a discharge oil passage.

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