CN213870242U - Oil pump device - Google Patents

Abstract

The utility model provides an oil pump device that can reduce the work load of pump through restraining the surplus oil pressure of oil from oil pump discharge. The oil pump device 5 includes an oil pump 3 and a valve 4 provided on the discharge side of the oil pump 3. The valve 4 includes a housing 4a in which an inlet 42b and an outlet 43a are formed, and a valve body 4 c. The valve body 4c or the housing 4a has an oil outflow space 4e through which oil flows out toward the outlet port 43a in the initial opening state of the outlet port 43 a.

Description

Oil pump device

Technical Field

The present invention relates to an oil pump device, and more particularly to an oil pump device including an oil pump for discharging oil.

Background

Conventionally, an oil pump device including an oil pump for discharging oil is known (for example, see patent document 1).

Patent document 1 discloses a hydraulic oil supply device (oil pump device) including an oil pump for discharging oil. The hydraulic oil supply device is provided with a flow rate control valve. The oil discharged from the oil pump is supplied to a plurality of oil supply points, and the flow rate adjustment valve is configured to change a distribution ratio of the flow rate of the oil supplied to the plurality of oil supply points.

The flow rate control valve of patent document 1 includes a housing and a valve body. The housing is formed with a 1 st inflow hole, a 1 st outflow hole, a 2 nd inflow hole, and a 2 nd outflow hole. The 1 st inflow hole and the 2 nd inflow hole are connected to an oil pump. The 1 st outflow hole communicates with the 1 st inflow hole and with the oil supply portion. The 2 nd outflow hole communicates with the 2 nd inflow hole and with the oil supply portion. The valve body is disposed in the housing so as to be slidable. The valve body is configured to slide by oil flowing from the oil pump into the 1 st inlet hole.

In the flow rate control valve of patent document 1, both the 1 st inlet port and the 1 st outlet port are fully opened by the valve body in the initial state of the valve body. In the flow rate control valve, the oil flowing from the 1 st inflow hole flows out from the 1 st outflow hole and is supplied to the oil supply portion. In the flow rate control valve, in the initial state of the valve body, a part of the 2 nd inflow port is opened by the valve body, and a part of the 2 nd outflow port is opened. In the flow rate control valve, the oil flowing from the 2 nd inflow hole flows out from the 2 nd outflow hole and is supplied to the oil supply portion.

Patent document

Patent document 1: japanese patent No. 6007746

SUMMERY OF THE UTILITY MODEL

Here, in the hydraulic oil supply device of patent document 1, in the initial state of the valve body (initial opening state of the 2 nd outflow port), it is necessary to maintain the opening area of the 2 nd outflow port by opening a part of the 2 nd inflow port and opening a part of the 2 nd outflow port by the valve body disposed in the housing. However, the opening area of the 2 nd outlet port in the initial opening state is likely to vary due to a tolerance of the initial position of the valve body, a tolerance of the shape of the 2 nd outlet port, a tolerance of the arrangement position of the 2 nd outlet port, and the like.

In the hydraulic oil supply device of patent document 1, if the opening area of the 2 nd outlet port in the initial opening state is deviated in the increasing direction, the flow rate of the oil flowing out from the 2 nd outlet port is increased, and therefore, a large oil pressure exceeding the necessity is secured in the oil supply portion. In this way, in the hydraulic oil supply device of patent document 1, a surplus hydraulic pressure is generated in the oil discharged from the oil pump due to the variation in the opening area in the initial opening state of the 2 nd outflow hole. Therefore, in the hydraulic oil supply device of patent document 1, it is desired to reduce the work load (amount of work) of the pump by suppressing the residual oil pressure of the oil discharged from the oil pump.

The present invention has been made to solve the above problems, and an object of the present invention is to provide an oil pump device capable of reducing the work load of a pump by suppressing the residual oil pressure of oil discharged from an oil pump.

In order to achieve the above object, an oil pump device according to an aspect of the present invention includes an oil pump for discharging oil, a valve provided on a discharge side of the oil pump, and an outflow passage provided downstream of the valve, wherein the valve includes a case in which an inflow port through which oil from the oil pump flows and an outflow port connected to the outflow passage and through which the oil flows out are formed, and a valve body movably provided in the case and moving forward and backward by the oil flowing in from the inflow port, and the valve body or the case has an oil outflow space for allowing the oil to flow out toward the outflow port in an initial opening state of the outflow port.

In the oil pump apparatus according to an aspect of the present invention, as described above, a valve provided on the discharge side of the oil pump is provided. The valve is provided with a housing and a valve body in which an inlet and an outlet are formed. The valve body or the housing is provided with an oil outflow space for allowing oil to flow out toward the outlet port in an initial open state of the outlet port. Thus, when the valve is a pressure regulating valve, when oil is caused to flow out from the outlet port, the oil outflow space is provided in the valve body or the housing, whereby variation in the oil pressure of the oil flowing out from the outlet port can be suppressed. That is, in the case where the oil outflow space is provided in the valve body, although a deviation occurs due to a tolerance of the initial position of the valve body, since the oil pressure flowing out from the outflow port is set by the flow path cross-sectional area of the oil outflow space, it is possible to suppress a deviation in the flow rate of the oil flowing out from the outflow port in the initial opening state by securing the accuracy of the flow path cross-sectional area of the oil outflow space regardless of the shape of the valve body and the deviation of the initial opening area of the outflow port. Here, even when the oil outflow space is provided in the casing, although variations occur due to tolerances in the installation state of the casing, variations in the flow rate of the oil flowing out from the outlet in the initial opening state can be suppressed by ensuring the accuracy of the flow path cross-sectional area of the oil outflow space regardless of variations in the shape of the casing and the initial opening area of the outlet. Further, in order to smoothly flow the oil from the oil outflow space toward the outflow port, the initial opening state of the outflow port may be set to have an opening area larger than the flow path cross-sectional area of the oil outflow space, and therefore, the accuracy required for the opening area of the initial opening state of the outflow port can be controlled. This can suppress variations due to tolerances in the shape of the outlet port. Therefore, in the initial opening state of the outlet port, the residual oil pressure of the oil discharged from the oil pump can be suppressed by suppressing the variation in the oil pressure of the oil flowing out from the outlet port, and thus the work load of the pump can be reduced. In addition, in the case where the valve is a relief valve, by providing an oil outflow space for allowing oil to flow out toward the outlet port in the initial opening state of the outlet port in the valve body or the housing, it is possible to allow oil to flow out not only from the outlet port opened by the movement of the valve body but also from the outlet port via the oil outflow space before the outlet port is opened by the movement of the valve body. Therefore, by discharging the oil from the outlet port opened by the movement of the valve body, the oil pressure discharged from the oil pump can be adjusted to the oil pressure of the oil supply portion where the required oil pressure is the maximum. Further, the oil can be discharged from the oil pump to the oil pressure of another oil supply portion by flowing out the oil from the outlet port through the oil outflow space. Therefore, the excess oil pressure of the oil discharged from the oil pump can be suppressed, and thus the work amount of the pump can be reduced.

In the oil pump device according to the above aspect, the oil outflow space is preferably provided on an outer peripheral surface of the valve body.

With this configuration, since the oil discharge space can be easily formed even when the valve is either a pressure regulator valve or a relief valve, it is possible to reduce the work load of the pump while suppressing a significant change in the valve structure.

In the oil pump device according to the above-described one aspect, it is preferable that, in the initial opening state, an opening area of the outflow port opened by the spool is larger than a flow path sectional area of the oil outflow space.

With this configuration, in the case where the valve is either a pressure regulating valve or a relief valve, the flow rate of the oil flowing out from the outlet port can be made larger than the flow rate of the oil flowing out from the oil outflow space, and therefore the oil can smoothly flow from the oil outflow space to the outlet port. Therefore, the work load of the pump can be further reduced.

In the oil pump device according to the above-described one aspect, it is preferable that the flow path sectional area of the oil outflow space is smaller than the flow path sectional area of the outflow flow path.

With this configuration, in the case where the valve is either a pressure regulating valve or a relief valve, the flow of oil from the oil outflow space to the outflow passage is not hindered by the flow passage cross-sectional area of the oil outflow space being larger than the flow passage cross-sectional area of the outflow passage. Therefore, the oil can be smoothly flowed from the oil outflow space to the outflow port, and thus the work load of the pump can be further reduced.

In the oil pump device according to the above-described one aspect, it is preferable that the oil outflow space has a groove shape.

With this configuration, since the oil outflow space can be formed with a simple structure in the case where the valve is either a pressure regulating valve or a relief valve, it is possible to reduce the work load of the pump while suppressing a significant change in the structure of the valve.

In the oil pump device according to the above aspect, it is preferable that the valve includes a pressure regulating valve which is disposed between the oil pump and a supply portion to which oil from the oil pump is supplied and which regulates an oil pressure of the oil supplied from the oil pump, the outflow path includes a 1 st flow path and a 2 nd flow path provided downstream of the pressure regulating valve, the outflow port of the case has a 1 st outflow port and a 2 nd outflow port, the 1 st outflow port is connected to the 1 st flow path and is supplied with the oil and flows out, the 2 nd outflow port is connected to the 2 nd flow path and is supplied with the oil and flows out, the valve body has a 1 st valve portion which opens or closes the 1 st outflow port, a 2 nd valve portion which opens or closes the 2 nd outflow port, and a 3 rd valve portion disposed between the 1 st valve portion and the 2 nd valve portion, and the oil outflow space is formed by the 3 rd valve portion and the case.

With this configuration, the 3 rd valve part of the pressure regulating valve and the housing form the oil outflow space, so that the variation in the oil pressure of the oil flowing out from the 1 st outlet port can be suppressed to the variation due to the tolerance of the initial position of the 3 rd valve part, the flow path cross-sectional area of the oil outflow space, and the tolerance of the arrangement position of the 1 st outlet port. Here, in order to prevent oil from leaking to the outside through a gap between a space in the housing in which the valve element is housed and the valve element, the dimensional accuracy of the space is formed with high accuracy, and therefore, the tolerance between the housing and the 3 rd valve portion is suppressed. Therefore, the residual oil pressure of the oil discharged from the oil pump can be suppressed. Further, the pressure regulating valve can distribute the oil pressure discharged from the oil pump so as to correspond to oil supply locations requiring different oil pressures, and therefore, the excess oil pressure of the oil discharged from the oil pump can be suppressed. Therefore, the remaining oil pressure of the oil can be suppressed not only in the initial open state when the oil is caused to flow out from the outlet port but also in a state other than the initial open state, and the work load of the pump can be further reduced.

In the oil pump device according to the above aspect, the valve preferably includes a relief valve that releases oil, and the relief valve is configured to release oil from the oil outflow space to the flow passage until the outflow port is in an open valve state.

With this configuration, in the relief valve, the oil can be released from the outlet port that is opened by the movement of the valve body, and the oil can be made to flow out from the outlet port via the oil outflow space before the outlet port is opened. Therefore, unlike the case where the outlet port is opened by the movement of the valve body to allow the oil to flow out, the oil pressure discharged from the oil pump can be adjusted so as to correspond to not only the oil pressure of the oil supply portion where the required oil pressure is the maximum but also the oil pressure of another oil supply portion. Therefore, the excess oil pressure of the oil discharged from the oil pump can be suppressed, and thus the work amount of the pump can be reduced.

In the oil pump device according to the above aspect, the following configuration may be considered.

(additional item 1)

That is, in the oil pump device including the relief valve, the oil outflow space of the relief valve is inclined with respect to the advancing direction of the valve body, and is formed by the valve body and the housing.

With this configuration, the oil outflow space is formed by the valve element and the housing while being inclined with respect to the advancing direction of the valve element, and the length of the oil outflow space can be changed by merely adjusting the inclination angle of the oil outflow space. Therefore, by changing the length of the oil outflow space, the resistance to the oil flowing in the oil outflow space can be changed, and thus the amount of oil released from the relief valve can be changed. As a result, the oil pressure discharged from the oil pump can be easily adjusted. Further, since the oil outflow space is inclined with respect to the direction in which the outer peripheral surface of the valve body is polished, the polishing tool is less likely to be caught in the oil outflow space when the outer peripheral surface of the valve body is polished in the circumferential direction.

(additional item 2)

In the oil pump device according to the above aspect, the oil outflow space is provided in the housing along the advancing/retreating direction of the valve body, and the oil is made to flow out toward the outlet port in the initial opening state of the outlet port.

With this configuration, when the valve is a pressure regulating valve, the oil outflow space is provided in the case instead of the valve body, whereby the structure of the valve body can be prevented from being complicated and enlarged.

(additional item 3)

In the oil pump device having the pressure regulating valve provided with the 1 st valve part, the 2 nd valve part, and the 3 rd valve part, the length of the 3 rd valve part is smaller than the length of the 1 st valve part and the length of the 2 nd valve part in the advancing and retreating direction of the valve element.

With this configuration, the length of the 3 rd valve portion having the function of partitioning the 1 st valve portion side space and the 2 nd valve portion side space can be reduced as much as possible, thereby suppressing an increase in size of the pressure regulating valve in the advancing/retreating direction of the valve element.

(additional item 4)

In the oil pump device including the pressure regulating valve, the valve body of the pressure regulating valve has a reduced portion having a smaller diameter than other portions, and the oil outflow space includes a 1 st oil outflow space extending from an end portion of a portion of the valve body on the inlet side of the flow than the reduced portion to the reduced portion, and a 2 nd oil outflow space passing through the reduced portion in a direction orthogonal to the advancing and retreating direction of the valve body from the 1 st oil outflow space, and the inlet and the outlet communicate with a space between the reduced portion and the inner peripheral surface of the housing via the 1 st oil outflow space and the 2 nd oil outflow space.

With this configuration, the length of the oil passage from the inlet port to the outlet port can be increased as compared with the case where the oil outlet space is provided in the traveling direction of the valve body on the outer peripheral surface of the valve body by allowing the inlet port and the outlet port to communicate with the space between the reduction portion and the inner peripheral surface of the housing via the 1 st oil outlet space and the 2 nd oil outlet space. Therefore, by increasing the length of the oil outflow space, the amount of oil released from the pressure regulating valve can be reduced, and thus the amount of oil flowing out of the pressure regulating valve can be more precisely adjusted.

Drawings

Fig. 1 is a schematic diagram showing a pressure regulating valve and a circulation of oil dispensed from the pressure regulating valve according to a first embodiment.

Fig. 2 is a graph showing the relationship between the change in the engine speed and the main-gallery-side oil pressure and the VVT-side oil pressure in the oil pump device according to the first embodiment.

Fig. 3 is a sectional view of a pressure regulating valve of an oil pump device according to a first embodiment.

Fig. 4 is a perspective view of a spool of a pressure regulating valve of an oil pump device according to a first embodiment.

Fig. 5 is a side view of the 3 rd valve portion of the valve spool in the pressure regulating valve of the oil pump apparatus according to the first embodiment as viewed from the X2 direction side.

Fig. 6 is a graph showing a relationship between a change in oil pressure of the oil pump device according to the first embodiment and a change in the opening area of the 1 st outlet port and a change in the opening area of the 2 nd outlet port.

Fig. 7 is a sectional view showing an initial state of a pressure regulating valve of the oil pump device according to the first embodiment.

Fig. 8 is a sectional view showing an intermediate state of a pressure regulating valve of the oil pump device according to the first embodiment.

Fig. 9 is a sectional view showing a final state of a pressure regulating valve of the oil pump device according to the first embodiment.

Fig. 10 is a schematic diagram showing an oil pump device according to a second embodiment and circulation of oil discharged from the oil pump device.

Fig. 11 is a sectional view of a relief valve of an oil pump device according to a second embodiment.

Fig. 12 is a perspective view of a relief valve spool in a relief valve of an oil pump device according to a second embodiment.

Fig. 13 is a side view of a relief valve body in a relief valve of an oil pump device according to a second embodiment as viewed from the side of the direction X2.

Fig. 14 is a graph showing the relationship between the engine speed and the oil pressure of the oil pump device according to the second embodiment.

Fig. 15 is a sectional view showing an initial state of a relief valve of the oil pump device according to the second embodiment.

Fig. 16 is a sectional view showing a final state of a relief valve of the oil pump device according to the second embodiment.

Fig. 17 is a graph showing the relationship between the oil pressure and the oil discharge amount of the oil pump device according to the second embodiment.

Fig. 18 is a sectional view showing an initial state of a pressure regulating valve of an oil pump device according to a third embodiment.

Fig. 19 is a sectional view showing a final state of a pressure regulating valve of the oil pump device according to the third embodiment.

Fig. 20 is a graph showing the relationship between the engine speed and the oil pressure of the oil pump device according to the third embodiment.

Fig. 21 is a sectional view showing an initial state of a pressure regulating valve of an oil pump device according to a fourth embodiment.

Fig. 22 is a sectional view showing a final state of a pressure regulating valve of the oil pump device according to the fourth embodiment.

Fig. 23 is a side view of a valve body in a pressure regulating valve of an oil pump device according to a fourth embodiment as viewed from the side of the direction X2.

Fig. 24 is a sectional view showing an initial state of a pressure regulating valve of an oil pump device according to a fifth embodiment.

Fig. 25 is a sectional view showing a final state of a pressure regulating valve of the oil pump device according to the fifth embodiment.

Fig. 26(a) is a side view of the 3 rd valve portion of the valve body in the pressure regulating valve of the oil pump device according to the modification of the first embodiment as viewed from the X2 direction side, and fig. 26(B) is a side view of the 3 rd valve portion of the valve body in the pressure regulating valve of the oil pump device according to the modification of the first embodiment as viewed from the X2 direction side.

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[ first embodiment ]

The structure of the oil pump device 5 provided in the engine 100 will be described with reference to fig. 1 to 9.

As shown in fig. 1, an engine 100 for a vehicle (automobile) is configured to circulate oil (engine oil) therein and supply the oil to a plurality of oil supply sites 2a, which are respective parts of the engine 100. Specifically, the engine 100 includes an oil pan 1, an engine main body 2 including a plurality of oil supply sites 2a, and an oil pump device 5 including an oil pump 3 and a pressure regulating valve 4 (an example of a "valve" in the present embodiment).

The oil pan 1 stores oil that circulates in the engine 100. The oil pump 3 is configured to suck oil in the oil pan 1 and discharge the oil in a state where a predetermined oil pressure is generated (compressed state). The oil pump 3 is configured to generate a predetermined oil pressure from oil sucked up from the oil pan 1 by a driving force of a crankshaft (not shown). Therefore, in the oil pump 3, as the engine speed increases, the specified oil pressure of the oil discharged from the oil pump 3 also increases.

The pressure regulating valve 4 is configured to distribute oil of a predetermined oil pressure discharged from the oil pump 3 to the oil supply sites 2a of the respective portions of the engine 100. The pressure regulating valve 4 is provided on the discharge side of the oil pump 3. The pressure control valve 4 will be described in detail later.

The oil distributed from the pressure regulating valve 4 is used for hydraulic driving, lubrication, cooling, and the like according to the functions of the plurality of oil supply portions 2 a. Here, the plurality of fueling portions 2a are devices constituting the engine 100 disposed in the engine main body 2.

As shown in fig. 1 and 2, the plurality of oil supply portions 2a include a 1 st oil supply portion 21 and a 2 nd oil supply portion 22.

Fig. 2 shows a relationship between a change in the engine speed and a change in the hydraulic pressure. In fig. 2, the oil pressure of the oil supplied from the oil pump 3 to the main gallery 21a as the 1 st oil supply portion 21 via the regulator valve 4 (main gallery side oil pressure (indicated by a solid line in fig. 2)) is shown. Fig. 2 shows an oil pressure (VVT side oil pressure (indicated by a two-dot chain line in fig. 2)) of oil supplied from the oil pump 3 to a Variable Valve Timing (VVT) 22a as a 2 nd oil supply portion 22 through a regulator Valve 4.

The 1 st fueling position 21 is a device that requires a smaller hydraulic pressure than the 2 nd fueling position 22 in a state where the engine speed is equal to or less than the specified speed R (low speed). Further, the 1 st fueling site 21 is a device that increases the required oil pressure if the engine speed exceeds the specified speed R.

Specifically, the 1 st oil supply portion 21 has the above-described main oil gallery 21 a. The main oil gallery 21a is a basic flow passage for supplying oil to sliding members such as pistons (not shown), cylinders (not shown), and bearings (not shown) of a crankshaft. The main oil gallery 21a is a device that requires a large amount of oil for cooling and lubrication as the engine speed increases.

The 2 nd fueling position 22 is a device that requires a larger hydraulic pressure than the 1 st fueling position 21 in a state where the engine speed is equal to or less than the specified speed R (low speed). The 2 nd fueling site 22 is a device that suppresses the required oil pressure (saturation) if the engine speed exceeds the specified speed R.

Specifically, the 2 nd fueling position 22 has a variable valve timing mechanism (the VVT 22a described above). The VVT 22a has a function of controlling a phase of a camshaft (not shown) by a hydraulic pressure of oil according to an operation state.

Therefore, in the main gallery 21a, when the specified rotation speed R or more is reached, the oil pressure of the oil supplied to the main gallery 21a is increased by distributing the remaining oil pressure generated in the VVT 22a to the main gallery 21 a.

The oil pump device 5 includes a 1 st flow path 6 (an example of the "outflow flow path" in the present invention) and a 2 nd flow path 7 (an example of the "outflow flow path" in the present invention). The 1 st flow path 6 and the 2 nd flow path 7 are provided downstream of the pressure regulating valve 4. The 1 st flow path 6 connects the pressure regulating valve 4 and the main oil gallery 21 a. The 2 nd flow path 7 connects the regulator valve 4 and the VVT 22 a.

As described above, in the engine 100, the oil supplied to the main oil gallery 21a via the 1 st flow passage 6 and the oil supplied to the VVT 22a via the 2 nd flow passage 7 are returned to the oil pan 1 by the oil pump device 5.

(pressure regulating valve)

The pressure regulating valve 4 is disposed between the oil pump 3 and the oil supply portion 2a to which oil from the oil pump 3 is supplied, and regulates the oil pressure of the oil supplied from the oil pump 3. In detail, the pressure regulating valve 4 is configured to reduce the residual oil pressure generated in the main oil gallery 21a and the VVT 22a by appropriately distributing oil to the main oil gallery 21a and the VVT 22 a. Such a pressure regulating valve 4 is attached to the engine body 2.

Specifically, as shown in fig. 3, the pressure regulating valve 4 includes a case 4a, a lid 4b, a valve body 4c, an urging member 4d, and an oil outflow space 4 e. The pressure regulating valve 4 is configured to distribute oil of a predetermined oil pressure discharged from the oil pump 3 by moving the valve body 4c against the biasing force of the biasing member 4d in the valve body housing space 41 in the case 4a closed by the lid portion 4 b.

Here, in the pressure regulating valve 4, the moving direction of the valve body 4c in the case 4a is defined as the X direction, the 1 st flow path 6 side in the X direction is defined as the X1 direction, and the 2 nd flow path 7 side in the X direction is defined as the X2 direction. In the pressure regulating valve 4, the direction in which the case 4a is adjacent to the engine body 2 is the Y direction, the side of the engine body 2 in the Y direction is the Y1 direction, and the side of the case 4a in the Y direction is the Y2 direction. In the pressure regulating valve 4, a direction orthogonal to the X direction and the Y direction is a Z direction, one side of the Z direction is a Z1 direction, and the other side of the Z direction is a Z2 direction.

The housing 4a is configured to house the valve body 4 c. Specifically, the case 4a is formed with a concave valve body accommodating space 41 depressed in the X2 direction. Here, the spool housing space 41 includes a slide space 41a and a hydraulic pressure supply space 41 b.

The valve body 4c is housed in the sliding space 41a in a state of being slidable in the X direction. Specifically, the slide space 41a has substantially the same size as the valve body 4c in the direction orthogonal to the X direction. The slide space 41a is formed in a substantially circular shape substantially identical to a cross-sectional shape of a 1 st valve portion 142 (a 2 nd valve portion 143) of the valve body 4c, which will be described later, in a cross-section orthogonal to the X direction.

The hydraulic pressure supply space 41b is configured to generate a hydraulic pressure for sliding the valve body 4c accommodated in the slide space 41a in the X1 direction by storing oil. Specifically, the hydraulic pressure supply space 41b communicates with the 2 nd flow path 7 via the branch flow path 8, and the branch flow path 8 extends from the 2 nd flow path 7 connected to the VVT 22 a. That is, the oil supplied to the VVT 22a flows into the hydraulic pressure supply space 41b, thereby generating a hydraulic pressure corresponding to the hydraulic pressure flowing through the 2 nd passage 7.

The casing 4a is formed with a plurality of inflow ports 42 and a plurality of outflow ports 43. The plurality of inlets 42 are configured to allow oil from the oil pump 3 to flow therein. That is, the plurality of inflow ports 42 are connected to the downstream side of the oil pump 3. The plurality of inflow ports 42 penetrate from the outer surface of the housing 4a to the sliding space 41 a. Here, among the plurality of inlets 42, the X1 direction side is referred to as the 1 st inlet 42a, and the X2 direction side is referred to as the 2 nd inlet 42b (an example of "inlet" in the present invention).

The plurality of outlet ports 43 are configured to supply oil to the main gallery 21a and the VVT 22a, respectively. The plurality of outflow ports 43 penetrate from the outer surface of the housing 4a to the sliding space 41 a. Here, among the plurality of outflow ports 43, the X1 direction side is referred to as a 1 st outflow port 43a (an example of "outflow port" in the present invention), and the X2 direction side is referred to as a 2 nd outflow port 43 b.

The portion on the X1 direction side of the 1 st outflow port 43a faces the portion on the X2 direction side of the 1 st inflow port 42 a. That is, the center position C1 in the X direction of the 1 st outlet 43a is located at a position shifted by the interval M from the center position D1 in the X direction of the 1 st inlet 42 a.

The 1 st outlet 43a is connected to the 1 st flow path 6 and configured to discharge oil. That is, the 1 st outflow port 43a causes the oil that has flowed in from the 1 st inflow port 42a to flow out to the main oil gallery 21 a. The 2 nd outlet 43b is connected to the 2 nd flow path 7 and configured to discharge oil. That is, the 2 nd outlet 43b allows the oil flowing in from the 2 nd inlet 42b to flow out to the VVT 22 a.

The 1 st inflow port 42a, the 2 nd inflow port 42b, the 1 st outflow port 43a, and the 2 nd outflow port 43b have substantially the same opening area.

As shown in fig. 3 and 4, the valve body 4c is movably provided in the housing 4a, and moves forward and backward by the oil flowing in from the 2 nd inlet 42 b. That is, the valve body 4c adjusts the open/close states of the 1 st inlet 42a, the 2 nd inlet 42b, the 1 st outlet 43a, and the 2 nd outlet 43 b. Specifically, the valve body 4c moves to a position where the biasing force from the biasing member 4d in the X2 direction and the pressing force from the hydraulic pressure supply space 41b in the X1 direction are balanced, thereby adjusting the open/closed state of the 1 st inlet 42a, the 2 nd inlet 42b, the 1 st outlet 43a, and the 2 nd outlet 43 b.

Here, in the state before the engine start, the valve body 4c is disposed at the position closest to the X2 direction side in the sliding space 41a due to the biasing force from the biasing member 4d toward the X2 direction side. After the engine is started, the valve body 4c is disposed at the position closest to the X1 direction side in the sliding space 41a due to the pressing force of the VVT side hydraulic pressure in the suppressed state.

Specifically, the valve body 4c includes a shaft portion 141, a 1 st valve portion 142, a 2 nd valve portion 143, and a 3 rd valve portion 144.

The shaft portion 141 has a substantially cylindrical shape. The shaft portion 141 extends in the X direction. The shaft 141 is disposed at the center of the sliding space 41a in the direction perpendicular to the X direction. In the shaft portion 141, the 1 st valve portion 142, the 3 rd valve portion 144, and the 2 nd valve portion 143 are arranged in this order from the X1 direction side.

The 1 st valve part 142 is configured to open or close the 1 st outflow port 43a and the 1 st inflow port 42 a. The 1 st valve portion 142 has a substantially cylindrical shape. The 1 st valve portion 142 is configured to increase the opening area of the 1 st inlet 42a and the opening area of the 1 st outlet 43a with movement in the X1 direction. The size of the cross section of the 1 st valve portion 142 in the direction orthogonal to the X direction is substantially the same as the size of the sliding space 41a in the direction orthogonal to the X direction. The length of the 1 st valve portion 142 in the X direction is greater than the length of the 1 st inlet port 42a in the X direction.

The 2 nd valve part 143 is configured to open or close the 2 nd inlet 42b and the 2 nd outlet 43 b. The 2 nd valve portion 143 has a substantially cylindrical shape. The 2 nd valve part 143 is configured to reduce the opening area of the 2 nd inlet 42b and the opening area of the 2 nd outlet 43b with the movement in the X1 direction. The size of the cross section of the 2 nd valve portion 143 in the direction orthogonal to the X direction is substantially the same as the size of the sliding space 41a in the direction orthogonal to the X direction. The length of the 2 nd valve portion 143 in the X direction is substantially the same as the length of the 2 nd inlet 42b in the X direction.

The 3 rd valve portion 144 is configured to separate a space on the 1 st valve portion 142 side in the slide space 41a from a space on the 2 nd valve portion 143 side in the slide space 41 a. That is, the 3 rd valve part 144 is disposed between the 1 st valve part 142 and the 2 nd valve part 143. The 3 rd valve portion 144 has a substantially cylindrical shape. The 3 rd valve portion 144 reciprocates across the 1 st outflow port 43a and the 2 nd outflow port 43b in the X direction. The size of the cross section of the 3 rd valve part 144 in the direction orthogonal to the X direction is substantially the same as the size of the sliding space 41a in the direction orthogonal to the X direction. The length of the 3 rd valve portion 144 is smaller than the length of the 1 st valve portion 142 and the length of the 2 nd valve portion 143 in the traveling direction (X direction) of the valve body 4 c.

When the valve body 4c is positioned on the side closest to the X2 direction in the slide space 41a, the 1 st inflow port 42a is completely closed by the 1 st valve portion 142, and the portion on the X1 direction side of the 1 st outflow port 43a is closed. When the valve body 4c is positioned on the side closest to the X2 direction in the slide space 41a, all of the 2 nd inlet ports 42b are opened by the 2 nd valve portion 143, and all of the 2 nd outlet ports 43b are opened. At this time, the oil having passed through the oil outflow space 4e flows out from the 1 st outflow port 43 a. In this way, the state in which only the oil having passed through the oil outflow space 4e flows out from the 1 st outflow port 43a is set as the initial state.

When the valve body 4c is positioned on the side closest to the direction X1 in the slide space 41a, all of the 1 st inlet ports 42a are opened by the 1 st valve part 142, and all of the 1 st outlet ports 43a are opened. When the valve body 4c is positioned on the side closest to the X1 direction in the slide space 41a, the 2 nd inlet port 42b is substantially completely closed by the 2 nd valve portion 143, and the 2 nd outlet port 43b is substantially completely closed. At this time, not only the oil passing through the oil outflow space 4e but also the oil passing through the 1 st inflow port 42a flows out from the 1 st outflow port 43 a. In this way, the state in which the valve body 4c is positioned on the side closest to the X1 direction in the sliding space 41a and the oil having passed through the portion other than the oil outflow space 4e flows out from at least the 1 st outflow port 43a is set as the final state.

The state in which the valve body 4c is positioned between the arrangement position in the initial state and the arrangement position in the final state and the oil having passed through both the oil outflow space 4e and the portion other than the oil outflow space 4e flows out from the 1 st outflow port 43a is set as the intermediate state.

Here, the area of the opening through which oil flows out from the 1 st outlet port 43a in the initial state is referred to as an initial opening area 110 (an example of "opening area of outlet port" in the present embodiment). The state in which the opening area of the 1 st outlet 43a is the initial opening area 110 is referred to as an initial opening state.

The urging member 4d has a compression coil spring. In the urging member 4d, the end on the X1 direction side abuts on the lid portion 4b, and the end on the X2 direction side abuts on the 1 st valve portion 142.

Here, in the pressure regulating valve 4, the oil flows into the sliding space 41a except for the shaft portion 141 surrounded by the surface of the 1 st valve portion 142 on the X2 direction side, the surface of the 3 rd valve portion 144 on the X1 direction side, and the inner peripheral surface of the case 4 a. The oil flows into the sliding space 41a except for the shaft portion 141 surrounded by the surface of the 2 nd valve portion 143 on the X1 direction side, the surface of the 3 rd valve portion 144 on the X2 direction side, and the inner peripheral surface of the housing 4 a.

< oil outflow space >

The oil outflow space 4e of the first embodiment is provided in the valve body 4c, and allows oil to flow out to the 1 st outlet port 43a in the initial opening state of the outlet port 43. Specifically, the oil outflow space 4e always flows the oil to the 1 st outflow port 43a, not only in the initial opening state of the outflow port 43. That is, the oil outflow space 4e causes the oil to flow out to the 1 st outlet port 43a regardless of the position of the valve body 4 c.

Specifically, as shown in fig. 4 and 5, the oil outflow space 4e has a groove shape. The oil outflow space 4e is provided on the outer peripheral surface of the valve element 4c along the advancing/retreating direction (X direction) of the valve element 4 c. That is, the oil outflow space 4e is formed by recessing the 3 rd valve portion 144 from the outer peripheral surface toward the center of the 3 rd valve portion 144 as viewed from the X2 direction side. The oil outflow space 4e has a substantially rectangular shape as viewed from the X2 direction side. The oil outflow space 4e extends in the X direction. The oil outflow space 4e is formed by the 3 rd valve portion 144 and the housing 4 a. Specifically, the oil outflow space 4e is formed by being surrounded by the outer peripheral surface of the 3 rd valve portion 144 and the inner peripheral surface of the housing 4 a.

The oil outflow space 4e is configured to be able to flow oil to the 1 st outflow port 43a in order to satisfy the required hydraulic pressure of the main gallery 21a in a state where the 1 st inflow port 42 is completely closed in the initial state. That is, the flow passage cross-sectional area 111 of the oil outflow space 4e is set to a size corresponding to the required oil pressure of the main oil gallery 21a in the initial state. The required oil pressure indicates the oil pressure required at the oil supply portion 2 a.

The oil outflow space 4e is configured to allow oil to smoothly flow out to the 1 st outflow port 43 a. That is, the 1 st outlet 43a is formed not to throttle the oil flowing out from the oil outflow space 4 e. Specifically, in the initial opening state, the initial opening area 110 of the 1 st outlet port 43a opened by the valve body 4c is larger than the flow path cross-sectional area 111 of the oil outflow space 4 e. The oil outflow space 4e has a flow passage cross-sectional area 111 smaller than a flow passage cross-sectional area 112 of the 1 st flow passage 6. In addition, in the oil flow direction, the flow path sectional area of the space on the upstream side of the oil outflow space 4e is larger than the flow path sectional area 111 of the oil outflow space 4e, and the flow path sectional area of the space on the downstream side of the oil outflow space 4e is larger than the flow path sectional area 111 of the oil outflow space 4 e.

(opening area characteristics)

The relationship (opening area characteristics) between the change in the hydraulic pressure and the change in the opening area of the 1 st outlet port 43a and the change in the opening area of the 2 nd outlet port 43b will be described with reference to fig. 6 to 9. Here, the change in the hydraulic pressure indicates a change in the hydraulic pressure in the oil supply portion 2 a. That is, the change in the oil pressure of the oil supplied to the main gallery 21a is indicated by a solid line in fig. 6 as the change in the oil pressure. In fig. 6, the change in the oil pressure of the oil supplied to the VVT 22a is indicated by a two-dot chain line as a change in the oil pressure.

As shown in fig. 6 and 7, in the initial state, the 1 st inlet 42a is closed by the 1 st valve part 142 and the 1 st outlet 43a is opened initially in the pressure regulating valve 4. In the initial state, in the pressure regulating valve 4, since the movement of the valve body 4c toward the X1 direction side is not started, the opening area of the 1 st inlet 42a and the initial opening area 110 of the 1 st outlet 43a are maintained. At this time, the oil that has flowed in from the 2 nd inflow port 42b and passed through the oil outflow space 4e flows out from the 1 st outflow port 43a and is supplied to the main gallery 21 a.

In the initial state, the 2 nd inlet 42b and the 2 nd outlet 43b are opened by the 2 nd valve portion 143 and the pressure regulating valve 4, respectively. In the initial state, since the valve element 4c does not start moving toward the X1 direction side in the pressure regulating valve 4, the opening area of the 2 nd inlet 42b and the opening area of the 2 nd outlet 43b are maintained. At this time, the oil flowing in from the 2 nd inlet 42b and flowing out from the 2 nd outlet 43b is supplied to the VVT 22 a.

As shown in fig. 6 and 8, when the hydraulic pressure (control pressure) rises to the hydraulic pressure P1, the valve element 4c starts moving in the X1 direction in the regulator valve 4. This state corresponds to the intermediate state described above.

In the intermediate state, in the pressure regulating valve 4, the 1 st inlet port 42a is gradually opened by the 1 st valve part 142, and the 1 st outlet port 43a is also gradually opened. In the intermediate state, in the pressure regulating valve 4, the valve body 4c starts moving toward the X1 direction side, and therefore the opening area of the 1 st inlet 42a and the opening area of the 1 st outlet 43a gradually increase. At this time, the oil flowing in from the 1 st inlet port 42a and the oil flowing in from the 2 nd inlet port 42b and passing through the oil outflow space 4e flow out from the 1 st outlet port 43a and are supplied to the main oil gallery 21 a.

In the intermediate state, in the pressure regulating valve 4, the 2 nd inlet 42b is gradually closed by the 2 nd valve part 143, and the 2 nd outlet 43b is also gradually closed. In the intermediate state, in the pressure regulating valve 4, the valve body 4c starts moving toward the X1 direction side, and therefore the opening area of the 2 nd inlet 42b and the opening area of the 2 nd outlet 43b gradually decrease. At this time, the oil flowing in from the 2 nd inlet 42b flows out from the 2 nd outlet 43b and is supplied to the VVT 22 a.

As shown in fig. 6 and 9, when the hydraulic pressure (control pressure) rises to the hydraulic pressure P2, the movement of the valve element 4c in the X1 direction is restricted in the regulator valve 4. This state corresponds to the above-described final state.

In the final state, in the pressure regulating valve 4, the 1 st inlet 42a is opened by the 1 st valve part 142, and the 1 st outlet 43a is opened. In the final state, in the pressure regulating valve 4, since the movement of the valve body 4c toward the X1 direction side is completed and restricted, the opening area of the 1 st inlet 42a and the opening area of the 1 st outlet 43a are maintained. At this time, the oil flowing in from the 1 st inlet port 42a and the oil flowing in from the 2 nd inlet port 42b and passing through the oil outflow space 4e flow out from the 1 st outlet port 43a and are supplied to the main oil gallery 21 a.

In the final state, in the pressure regulating valve 4, the 2 nd inlet 42b is substantially closed by the 2 nd valve part 143, and the 2 nd outlet 43b is also substantially closed. In the final state, in the pressure regulating valve 4, the movement of the valve body 4c toward the X1 direction side is completed and restricted, and therefore the opening area of the 2 nd inlet 42b and the opening area of the 2 nd outlet 43b are maintained. At this time, the oil flowing in from the 2 nd inlet 42b flows out from the 2 nd outlet 43b and is supplied to the VVT 22 a.

(Effect of the first embodiment)

In the first embodiment, the following effects can be obtained.

In the first embodiment, as described above, the oil pump device 5 is provided with the pressure regulating valve 4 provided on the discharge side of the oil pump 3. The pressure regulating valve 4 is provided with a case 4a in which a 2 nd inlet 42b and a 1 st outlet 43a are formed, and a valve body 4 c. The valve body 4c is provided with an oil outflow space 4e through which oil flows out toward the 1 st outlet port 43a in the initial opening state of the 1 st outlet port 43 a. Thus, when the oil is discharged from the 1 st outlet port 43a, the oil discharge space 4e is provided in the valve body 4c, so that variation in the oil pressure of the oil discharged from the 1 st outlet port 43a can be suppressed. That is, in the case where the oil outflow space 4e is provided in the valve body 4c, although there is a variation due to a tolerance of the initial position of the valve body 4c, since the flow rate of the oil flowing out from the 1 st outlet 43a is set according to the flow path cross-sectional area of the oil outflow space 4e, it is possible to suppress a variation in the flow rate of the oil flowing out from the 1 st outlet 43a in the initial opening state, regardless of the shape of the valve body 4c and the variation in the initial opening area of the 1 st outlet 43a, as long as the accuracy of the flow path cross-sectional area of the oil outflow space 4e is ensured. Further, in order to smoothly flow the oil from the oil outflow space 4e toward the 1 st outflow port 43a, the initial opening state of the 1 st outflow port 43a may be set to an opening area larger than the flow passage cross-sectional area of the oil outflow space 4e, and therefore, the accuracy required for the opening area of the 1 st outflow port 43a in the initial opening state can be suppressed. This can suppress variations due to tolerances in the shape of the 1 st outflow port 43 a. As a result, in the initial opening state of the 1 st outlet port 43a, by suppressing the variation in the oil pressure of the oil flowing out from the 1 st outlet port 43a, the excess oil pressure of the oil discharged from the oil pump 3 can be suppressed, and therefore the amount of work of the pump can be reduced.

In the first embodiment, as described above, the oil outflow space 4e is provided on the outer peripheral surface of the valve body 4 c. This makes it possible to easily form the oil discharge space 4e, and thus to reduce the amount of work of the pump while suppressing a significant change in the structure of the pressure regulating valve 4.

In the first embodiment, as described above, in the initial opening state, the opening area of the 1 st outlet port 43a opened by the valve body 4c is made larger than the flow passage cross-sectional area 111 of the oil outflow space 4 e. Accordingly, the flow rate of the oil flowing out of the 1 st outlet port 43a can be made larger than the flow rate of the oil flowing out of the oil outflow space 4e, and therefore the oil can smoothly flow from the oil outflow space 4e to the 1 st outlet port 43 a. Therefore, the work load of the pump can be further reduced.

In the first embodiment, as described above, the flow passage cross-sectional area 111 of the oil outflow space 4e is made smaller than the flow passage cross-sectional area 112 of the 1 st flow passage 6. Thus, the flow of the oil from the oil outflow space 4e to the 1 st flow path 6 is not hindered by the cross-sectional area of the flow path of the oil outflow space 4e being larger than that of the 1 st flow path 6. Therefore, the oil can smoothly flow from the oil outflow space 4e to the 1 st outflow port 43a, and the work load of the pump can be further reduced.

In addition, in the first embodiment, as described above, the oil outflow space 4e is provided in a groove shape. Thus, the oil outflow space 4e can be formed with a simple structure, and thus, the amount of work of the pump can be reduced while suppressing a large change in the structure of the pressure regulating valve 4.

In the first embodiment, as described above, the 1 st valve part 142 for opening or closing the 1 st outflow port 43a, the 2 nd valve part 143 for opening or closing the 2 nd outflow port 43b, and the 3 rd valve part 144 disposed between the 1 st valve part 142 and the 2 nd valve part 143 are provided in the valve body 4 c. The oil outflow space 4e is formed by the 3 rd valve portion 144 and the housing 4 a. Thus, by forming the oil outflow space 4e by using the 3 rd valve portion 144 of the pressure regulating valve 4 and the casing 4a, the variation in the oil pressure of the oil flowing out from the 1 st outlet 43a can be suppressed to the variation caused by the tolerance of the initial position of the 3 rd valve portion 144, the flow path cross-sectional area of the oil outflow space 4e, and the tolerance of the arrangement position of the 1 st outlet 43 a. Here, in order to prevent oil from leaking to the outside through the gap between the valve element housing space 41 and the valve element 4c in the housing 4a housing the valve element 4c, the dimensional accuracy of the valve element housing space 41 is made high, and therefore, the tolerance between the housing 4a and the 3 rd valve portion 144 is suppressed. Therefore, the residual oil pressure of the oil discharged from the oil pump 3 can be suppressed. Further, the pressure regulating valve 4 can distribute the hydraulic pressure discharged from the oil pump 3 corresponding to the oil supply portion 2a different from the required hydraulic pressure, and thus can suppress the excess hydraulic pressure of the oil discharged from the oil pump 3. Therefore, the remaining oil pressure of the oil can be suppressed not only in the initial open state when the oil is discharged from the 1 st discharge port 43a but also in a state other than the initial open state, and therefore the work load of the pump can be further reduced.

[ second embodiment ]

Next, the structure of an oil pump device 205 according to a second embodiment of the present invention will be described with reference to fig. 10 to 17. In the second embodiment, an example of the oil pump device 205 is described, and unlike the oil pump device 5 of the first embodiment which includes the pressure regulating valve 4 for regulating the distribution of the oil supplied to the plurality of oil supply sites 2a, the oil pump device 205 includes a relief valve 204 for reducing the oil pressure by discharging a part of the oil supplied to the oil supply sites 2a through the relief valve 204. In embodiment 2, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.

As shown in fig. 10 to 17, the oil pump device 205 of the second embodiment is configured to circulate oil (engine oil) therein and supply the oil to a plurality of oil supply sites 2a that are respective portions of the engine 100. Specifically, the engine 100 includes an oil pan 1, an engine main body 2 including a plurality of oil supply sites 2a, and an oil pump device 205 including an oil pump 203 and a relief valve 204 (an example of a "valve" in the present embodiment). The oil pump device 205 includes a discharge passage 206 (an example of an "outflow passage" in the present embodiment) connected to the relief valve 204.

The oil pump 203 includes a suction port 231, a discharge port 232, an inner rotor 233, and an outer rotor 234.

As shown in fig. 10, the suction port 231 is configured to introduce oil into a pump chamber formed by the inner rotor 233 and the outer rotor 234. The discharge port 232 is configured to introduce oil to the outside of the pump chamber.

The inner rotor 233 and the outer rotor 234 have a pump function by expanding or contracting the pump chambers by rotating the pump chambers. Therefore, as the volume of the pump chamber expands, oil flows into the pump chamber from the suction port 231. Further, as the volume of the pump chamber decreases, oil flows out from the pump chamber to the discharge port 232. The inner rotor 233 is configured to rotate the outer rotor 234 by rotating about a rotation center axis eccentric to the rotation center axis of the outer rotor 234.

(Overflow valve)

As shown in fig. 10 and 11, the relief valve 204 is configured to discharge oil. Specifically, the relief valve 204 is configured to open when the oil pressure of the oil discharged from the discharge port 232 is higher than a predetermined oil pressure (when the oil pressure is high).

Specifically, the relief valve 204 includes a housing 204a, a relief valve element 204c (an example of a "valve element" in the present invention), an urging member 204d, an oil overflow inlet 242 (an example of an "inlet" in the present invention), an oil overflow outlet 243 (an example of an "outlet" in the present invention), and an oil outflow space 204 e.

Here, in the relief valve 204, the moving direction (advancing direction) of the relief valve element 204c in the housing 204a is defined as the X direction, the discharge port 232 side in the X direction is defined as the X1 direction, and the opposite direction is defined as the X2 direction.

A portion of the housing 204a is inserted into the discharge port 232. The spill valve body 204c is disposed in the housing 204a so as to be slidable in the X1 direction (opening direction) and the X2 direction (closing direction). The biasing member 204d biases the relief valve element 204c toward the X2 direction. The oil spill inflow port 242 is configured to allow high-pressure oil to flow into the casing 204a from the discharge port 232. The oil overflow inlet 242 is a through hole formed in the casing 204 a. The oil overflow outlet 243 is configured to discharge the high-pressure oil that has flowed into the casing 204a to the suction port 231 via the discharge flow path 206. The oil overflow outlet 243 is a through hole formed in the casing 204 a. The oil overflow outlet 243 communicates with the discharge passage 206. Here, the relief valve 204 and the suction port 231 are connected to the discharge passage 206.

In the oil pump device 205, oil flowing out from the oil pump 203 is supplied to the main oil gallery 21a, the piston nozzle 223a, and the like. In the oil pump device 205, oil flowing out from the oil pump 203 to the relief valve 204 flows back to the suction port 231.

In this manner, the relief valve 204 is opened by the hydraulic pressure of the oil in the drain port 232, and the oil larger than the predetermined hydraulic pressure flows out to the discharge passage 206. That is, in the relief valve 204, the relief valve body 204c is moved in the X1 direction by the oil flowing from the inside of the discharge port 232, whereby the oil relief outlet 243 is opened and the oil is released to the discharge flow path 206. In the relief valve 204, the relief valve body 204c is moved in the X2 direction by the biasing member 204d, so that the oil relief inlet 242 is closed and release of oil is restricted.

Here, a state in which only the oil having passed through the oil outflow space 204e flows out from the oil overflow outlet 243 is set as an initial state. The state in which the spill valve body 204c is positioned closest to the side in the X1 direction and the oil that has passed through the portion other than the oil outflow space 204e flows out at least from the oil spill outlet 243 is set as the final state.

[ oil outflow space ]

The relief valve 204 of the second embodiment is configured to release oil from the oil outflow space 204e to the discharge flow path 206 until the oil overflow outlet 243 is opened (opened valve state). The relief valve 204 is configured to release oil to the discharge flow path 206 without passing through the oil outflow space 204e in the open state. That is, the relief valve 204 can change the discharge amount of oil to the discharge flow path 206 in two stages.

Specifically, as shown in fig. 12 and 13, the relief valve 204 includes an oil outflow space 204 e. The oil outflow space 204e is inclined with respect to the X direction, and is formed by the relief valve element 204c and the housing 204 a. That is, the oil outflow space 204e is provided on the outer peripheral surface of the spill valve body 204c so as to be inclined with respect to the X direction. The oil outflow space 204e has a groove shape recessed toward the center of the spill valve body 204c when viewed from the X2 direction side. The oil outflow space 204e is a space surrounded by the outer peripheral surface of the relief valve element 204c and the inner peripheral surface of the housing 204 a. Here, the flow path cross-sectional area 211 of the oil outflow space 204e is smaller than the opening area of the oil overflow inlet 242. The opening area of the oil overflow outlet 243 is larger than the flow path cross-sectional area 211 of the oil outflow space 204 e.

In this manner, the relief valve 204 is configured to be able to switch the amount of oil released from the release passage 206 so as to correspond to the plurality of oil supply locations 2a that require different oil pressures. Further, the oil discharge amount is changed by changing the length of the oil outflow space 204 e. That is, by increasing the length of the oil outflow space 204e, the oil is less likely to flow from the oil outflow space 204e to the discharge flow path 206, and the amount of oil discharged is reduced. Further, by reducing the length of the oil outflow space 204e, the oil easily flows from the oil outflow space 204e to the discharge flow path 206, and therefore the oil discharge amount increases.

(oil pressure characteristics)

A relationship between a change in the engine speed and a change in the hydraulic pressure (hydraulic pressure characteristic (indicated by a solid line in fig. 14)) will be described with reference to fig. 14 to 16. The hydraulic pressure indicates the hydraulic pressure of the oil discharged from the oil pump 203.

As shown in fig. 14, during the period from when the engine speed is increased to when the oil pressure is increased to the oil pressure Q1, the relief valve 204 is closed by the relief valve body 204c because the relief valve body 204c does not start moving in the X1 direction. At this time, the oil pressure increases in proportion to the engine speed.

As shown in fig. 14 and 15, if the oil pressure reaches the oil pressure Q1 by increasing the engine speed, the relief valve element 204c starts moving in the X1 direction. Thus, the relief valve 204 is in an initial state in which the oil is released to the release flow path 206 only through the oil outflow space 204 e. Therefore, the oil pressure of the oil discharged from the oil pump 203 is lower than that in the case of the oil pump apparatus 205 (indicated by a chain line in fig. 14) using the relief valve 204 in which the oil outflow space 204e is not provided. That is, the oil pressure is gradually increased while the oil pressure is increased from the oil pressure Q1 to the oil pressure Q2 by increasing the engine speed.

As shown in fig. 14 and 16, if the oil pressure reaches the oil pressure Q2 by increasing the engine speed, the spill valve spool 204c opens all of the oil spill outlet 243. Thus, the relief valve 204 is in a final state in which the oil is released to the discharge flow path 206 without passing through the oil outflow space 204 e. Therefore, the oil pressure of the oil discharged from the oil pump 203 increases in the same manner as in the case of the oil pump apparatus 205 (indicated by a chain line in fig. 14) using a relief valve not provided with the oil outflow space 204 e.

(discharge characteristics)

The relationship (discharge characteristic) between the change in the hydraulic pressure and the discharge amount of the oil discharged from the oil pump 203 will be described with reference to fig. 15 to 17. The discharge characteristic when the engine speed is the 1 st designated speed is indicated by a chain line. Further, the discharge characteristic when the engine speed is the 2 nd specified speed is indicated by a two-dot chain line. The 2 nd specified rotation speed is greater than the 1 st specified rotation speed.

As shown in fig. 17, during the period until the oil pressure increases to the oil pressure T1, the spill valve 204c does not start moving in the X1 direction, and therefore the spill valve 204 is closed by the spill valve 204 c. At this time, the discharge amount gradually decreases as the oil pressure increases.

As shown in fig. 15 and 17, if the hydraulic pressure reaches the hydraulic pressure T1, the relief valve element 204c starts moving in the X1 direction. Thus, the relief valve 204 is in an initial state in which the oil is released to the discharge flow path 206 through the oil outflow space 204 e. Therefore, the oil pressure of the oil discharged from the oil pump 203 is reduced as compared with the case of the oil pump apparatus 205 (shown by a broken line in fig. 17) using the relief valve 204 in which the oil outflow space 204e is not provided.

As shown in fig. 16 and 17, if the hydraulic pressure reaches the hydraulic pressure T2, the spill valve spool 204c opens all of the oil spill outlet ports 243. Thus, the relief valve 204 is in a final state in which the oil is released to the discharge flow path 206 without passing through the oil outflow space 204 e. Therefore, the oil pressure of the oil discharged from the oil pump 203 is reduced in the same manner as in the case of the oil pump apparatus 205 (shown by a broken line in fig. 17) using the relief valve 204 in which the oil outflow space 204e is not provided.

(Effect of the second embodiment)

The effect of the second embodiment will be explained.

In the second embodiment, as described above, the relief valve 204 provided on the discharge side of the oil pump 203 is provided. The relief valve 204 includes a case 204a having an oil relief inlet 242 and an oil relief outlet 243 formed therein, and a relief valve body 204 c. The relief valve element 204c is provided with an oil outflow space 204e through which oil flows out toward the oil overflow outlet 243 in an initial open state of the oil overflow outlet 243. Thus, not only the oil can be caused to flow out from the oil overflow outlet 243 that is opened by the movement of the overflow valve body 204c, but also the oil can be caused to flow out from the oil overflow outlet 243 via the oil outflow space 204e before the oil overflow outlet 243 is opened by the movement of the overflow valve body 204 c. Therefore, the oil is discharged from the oil spill valve outlet 243 opened by the movement of the spill valve body 204c, whereby the oil pressure discharged from the oil pump 203 can be adjusted to the oil pressure of the oil supply portion where the required oil pressure is the maximum. Further, the oil is discharged from the oil overflow outlet 243 through the oil discharge space 204e, whereby the oil pressure discharged from the oil pump 203 can be adjusted to the oil pressure of another oil supply portion. Therefore, the excess oil pressure of the oil discharged from the oil pump 203 can be suppressed, and thus the work amount of the pump can be reduced.

In the second embodiment, as described above, the oil outflow space 204e of the relief valve 204 is inclined with respect to the X direction, and is formed by the relief valve core 204c and the housing 204 a. Thus, by forming the oil outflow space 204e by the relief valve element 204c and the case 204a while being inclined with respect to the X direction, the length of the oil outflow space 204e can be changed by merely adjusting the inclination angle of the oil outflow space 204 e. Therefore, by changing the length of the oil outflow space 204e, the resistance to the oil flowing in the oil outflow space 204e can be changed, and thus the amount of oil released from the relief valve 204 can be changed. As a result, the oil pressure discharged from the oil pump 203 can be easily adjusted. Further, since the oil outflow space 204e is inclined with respect to the direction in which the outer peripheral surface of the relief valve core 204c is polished, when the outer peripheral surface of the relief valve core 204c is polished in the circumferential direction, it is possible to make it difficult for a polishing tool to be hooked in the oil outflow space 204 e. Other effects of the second embodiment are the same as those of the first embodiment.

[ third embodiment ]

Next, the structure of an oil pump device 305 according to a third embodiment of the present invention will be described with reference to fig. 18 to 20. In the third embodiment, an example of the oil pump device 305 is described, and unlike the oil pump device 5 including the pressure regulating valve 4 in which the oil outflow space 4e is provided in the valve body 4c, the oil pump device 305 includes the pressure regulating valve 304 in which the oil outflow space 304e is provided in the housing 304 a. In the third embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.

As shown in fig. 18 and 19, a pressure regulating valve 304 (an example of a "valve" according to the present invention) according to a third embodiment includes a case 304a, a lid portion 4b, a valve body 304c, an urging member 4d, and an oil outflow space 304 e.

The housing 304a has a concave valve body accommodating space 41 recessed in the X2 direction. Here, the spool housing space 41 includes a slide space 41a and a hydraulic pressure supply space 41 b.

The slide space 41a is configured to house the valve body 304c in a state in which it can be slid in the X direction. The hydraulic pressure supply space 41b is a space into which oil flows in the 2 nd flow path 7 (an example of the "outflow flow path" in the present embodiment) connected to the VVT 22 a. The hydraulic pressure supply space 41b communicates the 2 nd flow path 7 with the 1 st flow path 6 (an example of the "outflow flow path" in the present embodiment). In this manner, the oil supplied to the VVT 22a flows into the hydraulic pressure supply space 41b, thereby generating a hydraulic pressure corresponding to the hydraulic pressure flowing through the 2 nd passage 7.

An inlet 342 into which oil discharged from the oil pump 3 flows and an outlet 343 are formed in the housing 304 a. The inlet 342 is configured to allow oil from the oil pump 3 to flow therein. The inlet port 342 extends from the outer surface of the housing 304a to the hydraulic pressure supply space 41 b. The outlet 343 is configured to supply oil to the main gallery 21 a. The outflow port 343 penetrates from the outer surface of the housing 304a to the slide space 41 a.

The valve body 304c is movably disposed in the housing 304a, and advances and retreats by the oil flowing in from the inflow port 342. That is, the valve body 304c is configured to adjust the open/close state of the outflow port 343. Specifically, the valve body 304c adjusts the open/closed state of the outlet 343 by moving to a position where the biasing force from the biasing member 4d in the X2 direction is balanced with the pressing force from the hydraulic pressure supply space 41b in the X1 direction.

Here, the valve body 304c is disposed at the position closest to the X2 direction side in the sliding space 41a by the biasing force toward the X2 direction from the biasing member 4d in the state before the engine is started. The valve body 304c is disposed at a position closest to the X1 direction side in the sliding space 41a by the pressing force of the hydraulic pressure in the hydraulic pressure supply space 41b after the engine is started.

When the valve body 304c is located at the position closest to the X2 direction side in the slide space 41a, the outflow port 343 is completely closed by the valve body 304 c. When the valve body 304c is located at the position closest to the X2 direction side in the slide space 41a, the outflow port 343 is fully opened by the valve body 304 c.

Here, a state in which only the oil having passed through the oil outflow space 304e flows out from the outflow port 343 is set as an initial state. The state in which the valve body 304c is positioned on the side of the direction X1 and the oil that has passed through the portion other than the oil outflow space 304e flows out at least from the outflow port 343 is set to the final state.

Further, the valve body 304c sets the area of the opening through which oil flows out of the outflow port 343 in the initial state as the initial opening area 310 (an example of "the opening area of the outflow port" in the present embodiment). The state in which the opening area of the outlet 343 is the initial opening area 310 is referred to as an initial opening state.

< oil outflow space >

The oil outflow space 304e of the third embodiment is provided in the housing 304a along the X direction, and allows oil to flow out toward the outflow port 343 in the initial open state of the outflow port 343. Specifically, the oil outflow space 304e causes oil to flow out to the outflow port 343 regardless of the position of the valve body 304 c.

Specifically, the oil outflow space 304e has a groove shape. The oil outflow space 304e is provided on the surface of the case 304a on the engine body 2 side in the X direction. The oil outflow space 304e is formed by being surrounded by the outer surface of the housing 304a and the surface of the engine main body 2.

(oil pressure characteristics)

The relationship between the change in the engine speed and the change in the hydraulic pressure will be described with reference to fig. 18 to 20. Fig. 20 shows the oil pressure of the oil supplied from the oil pump 3 to the main gallery 21a via the pressure regulating valve 304 (main gallery side oil pressure (indicated by a solid line in fig. 20)). Fig. 20 shows the oil pressure of the oil supplied from the oil pump 3 to the VVT 22a via the regulator valve 304 (VVT-side oil pressure (indicated by a two-dot chain line in fig. 20)).

As shown in fig. 18 and 20, the time for increasing the engine speed to increase the VVT side oil pressure to the oil pressure P1 is the initial state. At this time, in the pressure regulating valve 304, oil is supplied to the main gallery 21a via the oil outflow space 304 e.

As shown in fig. 19 and 20, the final state is achieved when the VVT side hydraulic pressure reaches the hydraulic pressure P2 by increasing the engine speed. At this time, since the outflow port 343 is completely opened by the valve body 304c, the main-gallery-side oil pressure and the VVT-side oil pressure similarly increase.

(Effect of the third embodiment)

The effect of the third embodiment will be described.

In the third embodiment, as described above, the housing 304a is provided with the oil outflow space 304e, and the oil outflow space 304e flows out the oil toward the outflow port 343 in the initial opening state of the outflow port 343. Accordingly, in the initial open state when the oil is caused to flow out from the outflow port 343, the deviation of the oil pressure of the oil flowing out from the outflow port 343 is suppressed, whereby the remaining oil pressure of the oil discharged from the oil pump 3 can be suppressed, and therefore the amount of work of the pump can be reduced.

In the third embodiment, as described above, the oil outflow space 304e is provided in the X direction in the housing 304 a. The oil outflow space 304e is configured to allow oil to flow out toward the outflow port 343 in an initial opening state of the outflow port 343. Thus, by providing the oil outflow space 304e not in the valve body 304c but in the housing 304a, the structure of the valve body 304c can be prevented from being complicated and enlarged. Other effects of the third embodiment are the same as those of the first embodiment.

[ fourth embodiment ]

Next, a structure of an oil pump device 405 according to a fourth embodiment of the present invention will be described with reference to fig. 21 to 23. In the fourth embodiment, an example of the oil pump device 405 is explained, and unlike the oil pump device 5 of the first embodiment which includes the pressure regulating valve 4 provided with the 1 st valve part 142, the 2 nd valve part 143, and the 3 rd valve part 144, the oil pump device 405 includes the pressure regulating valve 404 provided with a single valve body 404 c. In the fourth embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.

As shown in fig. 21 and 22, a pressure regulating valve 404 (an example of a "valve" according to the present invention) according to a fourth embodiment includes a case 404a, a lid portion 4b, a valve body 404c, an urging member 4d, and an oil outflow space 404 e.

The housing 404a has a concave valve body accommodating space 41 recessed in the X2 direction. Here, the spool housing space 41 includes a slide space 41a and a hydraulic pressure supply space 41 b.

The slide space 41a is configured to house the valve body 404c in a state in which it can be slid in the X direction. The hydraulic pressure supply space 41b is a space into which oil in the 2 nd flow path 7 connected to the VVT 22a flows. The hydraulic pressure supply space 41b communicates the 2 nd flow path 7 (an example of the "outflow flow path" in the present embodiment) with the 1 st flow path 6 (an example of the "outflow flow path" in the present embodiment). In this manner, the oil supplied to the VVT 22a flows into the hydraulic pressure supply space 41b, thereby generating a hydraulic pressure corresponding to the hydraulic pressure flowing through the 2 nd passage 7.

An inlet 442 and an outlet 443 into which oil discharged from the oil pump 3 flows are formed in the housing 404 a. The inlet port 442 is configured to allow oil from the oil pump 3 to flow therein. The inlet port 442 penetrates from the outer surface of the housing 404a to the hydraulic pressure supply space 41 b. The outlet 443 is configured to supply oil to the main gallery 21 a. The outflow port 443 penetrates from the outer surface of the housing 404a to the sliding space 41 a.

The valve body 404c is movably provided in the housing 404a, and advances and retreats by the oil flowing in from the inflow port 442. That is, the valve body 404c adjusts the open/close state of the throttle outlet 443. Specifically, the valve body 404c is configured to adjust the open/closed state of the outlet 443 by moving to a position where the biasing force from the biasing member 4d in the X2 direction and the pressing force from the hydraulic pressure supply space 41b in the X1 direction are balanced.

In the state before the engine start, the valve body 404c is disposed at the position closest to the X2 direction side in the sliding space 41a by the biasing force from the biasing member 4d toward the X2 direction side. The valve body 404c is disposed at a position closest to the X1 direction side in the sliding space 41a by the pressing force of the hydraulic pressure in the hydraulic pressure supply space 41b after the engine is started.

When the spool 404c is located at the position closest to the X2 direction side in the slide space 41a, the outflow port 443 is completely closed by the spool 404 c. When the spool 404c is located at the position closest to the X2 direction side in the slide space 41a, the outflow port 443 is fully opened by the spool 404 c.

Here, the state in which only the oil having passed through the oil outflow space 404e flows out from the outflow opening 443 is set as the initial state. The state in which the valve body 404c is positioned closest to the side in the X1 direction and the oil that has passed through the oil outflow space 404e flows out at least from the outflow opening 443 is set to the final state.

In addition, the area of the opening through which oil flows out of the outlet 443 in the initial state is set as the initial opening area 410 (the "opening area of the outlet" in the present embodiment). The state in which the opening area of the outlet 443 is the initial opening area 410 is referred to as an initial opening state.

< oil outflow space >

As shown in fig. 22 and 23, the oil discharge space 404e of the fourth embodiment is provided in the valve body 404c in the X direction, and discharges oil to the discharge port 443 in an initial open state of the discharge port 443.

Specifically, the oil outflow space 404e has a groove shape. That is, the oil outflow space 404e has a substantially rectangular shape as viewed from the X2 direction side. The oil discharge space 404e is provided on the outer peripheral surface of the valve body 404c in the X direction. The oil outflow space 404e extends in the X direction. The oil outflow space 404e is formed by being surrounded by the outer surface of the spool 404c and the inner surface of the housing 404 a.

(Effect of the fourth embodiment)

The effect of the fourth embodiment will be described.

In the fourth embodiment, as described above, the valve body 404c is provided with the oil outflow space 404e that allows oil to flow out toward the outflow port 443 in the initial opening state of the outflow port 443. Accordingly, in the initial open state when the oil is caused to flow out from the outlet 443, the deviation of the oil pressure of the oil flowing out from the outlet 443 is suppressed, whereby the remaining oil pressure of the oil discharged from the oil pump 3 can be suppressed, and therefore the amount of work of the pump can be reduced. Other effects of the fourth embodiment are the same as those of the first embodiment.

[ fifth embodiment ]

Next, a structure of an oil pump device 505 according to a fifth embodiment of the present invention will be described with reference to fig. 24 and 25. In the fifth embodiment, an example of the oil pump device 505 is described, and unlike the oil pump device 405 of the fourth embodiment which includes the pressure regulating valve 404 having the oil outflow space 404e formed in the outer peripheral surface of the valve body 404c, the oil pump device 505 includes the pressure regulating valve 504 having the oil outflow space 504e formed inside the valve body 504 c. In the fifth embodiment, the same components as those in the fourth embodiment are denoted by the same reference numerals, and description thereof is omitted.

As shown in fig. 24 and 25, a pressure regulating valve 504 (an example of a "valve" according to the present invention) according to a fifth embodiment includes a case 404a, a lid 4b, a valve body 504c, an urging member 4d, and an oil outflow space 504 e.

The housing 404a has a concave valve body accommodating space 41 recessed in the X2 direction. Here, the spool housing space 41 includes a slide space 41a and a hydraulic pressure supply space 41 b.

The valve body 504c is movably provided in the housing 404a, and moves forward and backward by the oil flowing in from the inflow port 442. The valve body 504c has a reduced portion 514 having a smaller diameter than the other portions. Specifically, the length of the reduced portion 514 in the direction orthogonal to the X direction is smaller than that of the other portions.

Here, a state in which only the oil having passed through the oil outflow space 504e flows out from the outflow opening 443 is set as an initial state. The state in which the valve body 504c is positioned closest to the side in the X1 direction and the oil that has passed through the portion other than the oil outflow space 504e flows out at least from the outflow opening 443 is set to the final state.

In addition, the area of the opening through which oil flows out of the outlet 443 in the initial state is set as the initial opening area 510 (an example of "opening area of the outlet" in the present embodiment). The state in which the opening area of the outlet 443 is the initial opening area 510 is referred to as an initial opening state.

< oil outflow space >

The oil outflow space 504e of the fifth embodiment has a 1 st oil outflow space 541 and a 2 nd oil outflow space 542. That is, the oil outflow space 504e is formed in a substantially T-shape in a cross section along the X direction. Specifically, the 1 st oil outflow space 541 extends from an end of the valve body 504c on the inlet 442 side of the reduced portion 514 to the reduced portion 514. The 2 nd oil outflow space 542 penetrates the constricted portion 514 from the 1 st oil outflow space 541 in a direction orthogonal to the X direction.

In this way, the inlet port 442 and the outlet port 443 communicate with the space between the reduced portion 514 and the inner circumferential surface of the casing 404a via the 1 st oil outflow space 541 and the 2 nd oil outflow space 542.

(Effect of the fifth embodiment)

The effect of the fifth embodiment will be described.

In the fifth embodiment, as described above, the valve body 504c is provided with the oil outflow space 504e that allows oil to flow out toward the outlet 443 in the initial open state of the outlet 43. Accordingly, in the initial open state when the oil is caused to flow out from the outlet 443, the deviation of the oil pressure of the oil flowing out from the outlet 443 is suppressed, whereby the excess oil pressure of the oil discharged from the oil pump 3 can be suppressed, and therefore the amount of work of the pump can be reduced.

In the fifth embodiment, as described above, the inlet port 442 and the outlet port 443 are communicated with the space between the reduced portion 514 and the inner circumferential surface of the housing 404a via the 1 st oil outlet space 541 and the 2 nd oil outlet space 542. Thus, the length of the oil flow path from the inlet port 442 to the outlet port 443 can be increased as compared to a case where an oil outlet space is provided in the outer peripheral surface of the valve body 504c in the traveling direction of the valve body 504 c. Therefore, the amount of oil discharged from the pressure regulating valve 504 can be reduced by increasing the length of the oil outflow space 504e, and thus the amount of oil flowing out of the pressure regulating valve 504 can be more precisely adjusted. Other effects of the fifth embodiment are the same as those of the fourth embodiment.

[ modified examples ]

The embodiments disclosed herein are illustrative in all respects and should not be considered restrictive. The scope of the present invention is defined by the claims, not by the description of the above embodiments, and includes meanings equivalent to the claims and all modifications (variations) within the scope of the claims.

For example, in the first embodiment, the example in which the oil outflow space 4e has a substantially rectangular shape as viewed from the X2 direction side is shown, but the present invention is not limited thereto. In the present invention, the oil outflow space 604e may be formed by cutting a part of the valve body 604c as in the modification shown in fig. 26(a), or the oil outflow space 704e may have a substantially circular shape as viewed from the X2 direction side as in the modification shown in fig. 26 (B).

In the first embodiment, the 3 rd valve part 144 is smaller than the 1 st valve part 142 and the 2 nd valve part 143 in the X direction, but the present invention is not limited to this. In the present invention, the length of the 3 rd valve part may be substantially the same as the length of the 1 st valve part and the length of the 2 nd valve part in the X direction.

In the second embodiment, the oil outflow space 204e of the relief valve 204 is inclined with respect to the X direction, but the present invention is not limited thereto. In the present invention, the oil outflow space of the overflow valve may be formed in a straight line along the X direction.

In the third embodiment, the oil outflow space 304e is provided in the housing 304a in the X direction, but the present invention is not limited thereto. The oil outflow space may be provided in the housing obliquely with respect to the X direction.

In addition, in the second embodiment, the example in which the oil flowing out from the oil pump 203 to the relief valve 204 flows back to the suction port 231 is shown, but the present invention is not limited thereto. In the present invention, the oil flowing out from the oil pump to the overflow valve may also flow back to the oil pan.

Description of the symbols

3. 203 oil pump

4. 304, 404, 504 pressure regulating valve (valve)

4a, 204a, 304a, 404a housing

4c, 304c, 404c, 504c spools

4e, 204e, 304e, 404e, 504e, 604e, 704e oil flows out of the space

5. 205, 305, 405, 505 oil pump device

6 1 st flow path (outflow flow path)

7 flow path 2 (outflow flow path)

42b second inlet (inflow port)

43a 1 st outflow opening (outflow opening)

43b 2 nd outflow opening

110 initial opening area (opening area of outflow port)

Cross-sectional area of flow path of 111 oil outflow space

112 flow passage cross-sectional area of the 1 st flow passage

142 1 st valve part

143 nd 2 nd valve part

144 3 rd valve part

204 overflow valve (valve)

204c overflow valve core (valve core)

206 discharge flow path (outflow flow path)

242 oil overflow inlet (inflow port)

243 oil overflow outlet (outflow outlet)

342. 442 flow inlet

343. 443 an outflow port.

Claims (7)

1. An oil pump device is characterized by comprising:

an oil pump that discharges oil;

a valve provided on a discharge side of the oil pump; and

an outflow flow path provided downstream of the valve,

the valve comprises:

a casing in which an inlet into which oil from the oil pump flows and an outlet which is connected to the outlet flow path and from which the oil flows out are formed; and

a valve body movably disposed in the housing and advanced and retracted by the oil flowing in from the inflow port,

the valve body or the housing has an oil outflow space that, in an initial open state of the outlet port, causes oil to flow out toward the outlet port.

2. The oil pump apparatus as set forth in claim 1,

the oil outflow space is provided on an outer peripheral surface of the valve element.

3. The oil pump apparatus as claimed in claim 1 or 2,

in the initial opening state, an opening area of the outlet port opened by the valve body is larger than a flow path sectional area of the oil outflow space.

4. The oil pump apparatus as set forth in claim 1,

the oil outflow space has a flow path cross-sectional area smaller than that of the outflow flow path.

5. The oil pump apparatus as set forth in claim 1,

the oil outflow space has a groove shape.

6. The oil pump apparatus as set forth in claim 1,

the valve includes a pressure regulating valve that is disposed between the oil pump and an oil supply portion to which oil from the oil pump is supplied, and that regulates a pressure of the oil supplied from the oil pump,

the outflow channel includes a 1 st channel and a 2 nd channel disposed downstream of the pressure regulating valve,

the outflow port of the housing has:

a 1 st outflow port connected to the 1 st flow path and through which oil flows out; and

a 2 nd outlet port connected to the 2 nd flow path and supplied with oil to be discharged,

the valve core is provided with:

a 1 st valve portion that opens or closes the 1 st outflow port;

a 2 nd valve part which opens or closes the 2 nd outflow port; and

a 3 rd valve part, the 3 rd valve part being disposed between the 1 st valve part and the 2 nd valve part,

the oil outflow space is formed by the 3 rd valve portion and the housing.

7. The oil pump apparatus as set forth in claim 1,

the valve includes an overflow valve that releases oil,

the relief valve is configured to release oil from the oil outflow space to the outflow passage until the outflow port is opened.

Images