JPH08158839A - Oil pump device - Google Patents

Abstract

PURPOSE: To enable press-feeding of a required amount of oil to an engine in a medium speed rotation area of the engine without using a preset pressure variable device, nor a controller for commanding variation to the preset pressure variable device. CONSTITUTION: A relief valve 5 is movably arranged inside a cylinder 52 having an input port 51 communicated with an input passage, and an opening 521 and a valve seat 522 opened toward the input port at one end, opposedly to first and second output ports formed on the cylinder 52 so as to communicate with an output passage. When discharge pressure of an oil pump 3 reaches a first preset value, the input port is communicated only with the first output port 53. When the discharge pressure reaches a second preset value higher than the first preset value, the input port is communicated at least with the second output port by means of a valve body 55 which is engageable/ disengageable with a valve seat. The valve body is energized in the direction of seating the valve seat by means of a spring 56.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil pump device capable of pumping an optimum amount of oil to an engine in each rotation range such as a low rotation range, an intermediate rotation range and a high rotation range of an engine.

[0002]

2. Description of the Related Art In the low engine speed range where the oil pressure tends to be low, all the oil discharged from the oil pump is pumped to the engine, and in the high engine speed range where the oil pressure tends to be high, the oil discharged from the oil pump is increased. An oil pump device that allows a part of the oil to escape is generally known. Specifically, this is because the oil pump that rotates in conjunction with the engine pumps oil to the engine and when the discharge pressure of the oil pump reaches the set pressure (that is, the engine speed reaches the set speed). And a relief valve for releasing a part of the oil discharged from the oil pump.

However, in this engine, in the engine middle speed range where the discharge pressure of the oil pump is less than the set pressure, more oil than necessary is pumped to the engine, resulting in large sliding loss of the engine and fuel consumption. There is a problem that it gets worse.

Therefore, conventionally, as a technique for solving this problem, the technique disclosed in Japanese Utility Model Laid-Open No. 63-73510 is known. This type has a valve body that opens a relief passage that connects the oil pump downstream side and the oil pan when the discharge pressure exceeds a set pressure, and a valve body that allows a part of the discharged oil to escape to the oil pan, and a valve body that is attached in the closing direction. It has a biasing spring and a set pressure varying device for varying the set pressure by the spring by moving the set position of the spring. Here, the set pressure varying device includes a rotatable pin having an axis perpendicular to the direction of expansion and contraction of the spring, a cam fixed integrally rotatably to the pin, and varying the set position (position of one end) of the spring, And a pin rotation mechanism that is connected to the pin via a link and rotates the pin.

In this engine, since the relief valve closes the relief passage in the low engine speed region, the entire discharge amount is pumped to the engine. Further, in the engine middle speed range, since the set pressure varying device can set a relatively low first set pressure, a part of the relief passage is opened by the relief valve, and the first predetermined amount of the discharged oil is the oil. Bread escapes. Further, in the high engine speed region, the second preset pressure higher than the first preset pressure can be set by the preset pressure varying device, so that the relief valve fully opens the relief passage, so that the first predetermined amount of the discharged oil is lower than the first predetermined amount. A large second predetermined amount is released to the oil pan.

[0006]

However, in this device, the set load of the spring of the relief valve is changed by the set pressure changing device according to the rotation region of the engine, so that not only the set pressure changing device but also the variable command is changed. A controller for taking out is required, which is disadvantageous in cost.

Further, since the set pressure varying device is composed of a pin, a cam, a link and a pin rotating mechanism, it has many components and is complicated, and it is disadvantageous from the viewpoint of cost.

Therefore, the present invention provides an oil pump device capable of pumping a required amount of oil to the engine in the engine middle speed range without using a set pressure varying device and a controller for issuing a variable command to the set pressure varying device. Providing is a technical issue.

[0009]

The technical means (to be referred to as the first technical means hereinafter) taken in the invention of claim 1 to solve the above technical problems are an oil supply source and an oil supply source. A main passage that connects the engine and the engine, an oil pump that is arranged in the middle of the main passage, rotates in conjunction with the engine, and pumps oil to the engine, and a main passage downstream of the oil pump, an oil supply source, and an oil pump. At least one of the upstream main passage and the suction port of the oil pump
An oil pump device having a relief passage connecting the two and a relief valve arranged in the middle of the relief passage for opening and closing the relief passage according to the discharge pressure of the oil pump; Aisle,
The relief valve comprises an output passage downstream of the relief valve; the relief valve communicates with the output passage and a cylinder having an input port communicating with the input passage, an opening at one end opening toward the input port, and a valve seat. First formed on the cylinder
And a second output port, which is movably arranged in the cylinder so as to face the input port, and allows the input port to communicate with only the first output port when the discharge pressure of the oil pump reaches the first set pressure, A valve body that is attachable to and detachable from a valve seat that allows the input port to communicate with at least the second output port when the discharge pressure reaches a second set pressure that is higher than the first set pressure, and a direction in which the valve body is seated on the valve seat. That is, it is provided with a biasing spring.

As the above first technical means, the following three modes can be considered.

The first form is that the first output port is formed closer to the input port than the second output port, and a single valve body and a single spring are used.

In the second embodiment, the first output port is formed at a position closer to the input port than the second output port; the valve body is attachable to and detachable from the valve seat and between the input port and the first output port. A first valve body that communicates with or shuts off, and a second valve body that is disposed to face the first valve body so as to be in contact with the first valve body and that communicates with or shuts off between the input port and the second output port; A first spring that urges the valve body in the direction to be seated on the valve seat, and a second valve body that urges in the same direction as the urging direction of the first spring, and the set load thereof is greater than the set load of the first spring. The second spring is made larger.

In a third form, the first output port is formed at a position farther from the input port than the second output port; the valve body has a through hole communicating with the input port and a second valve seat,
A main valve element that can be attached to and detached from the valve seat and that connects or disconnects the input port and the second output port, and a through hole that opens and closes by attaching to and detached from the second valve seat to connect the input port and the first output port. Or a sub-valve for shutting off; a spring,
The main spring, which urges the main valve body to seat on the valve seat, and the sub-valve, which urges in the same direction as the main spring, make sure that the set load is smaller than the set load of the main spring. It consists of a sub spring.

In order to solve the above technical problem, a fifth aspect is provided.
The technical means taken in the invention (hereinafter referred to as the second technical means) comprises a relief passage, which comprises an input passage on the upstream side of the relief valve and an output passage on the downstream side of the relief valve; An input port communicating with the input passage,
A cylinder having an opening at one end that opens toward the input port and a valve seat, an output port formed on the cylinder and communicating with the output passage, and a cylinder formed so as to be closer to the input port than the output port An output groove communicating with the port, a valve body that is attachable to and detachable from a valve seat that is movably arranged in the cylinder so as to face the input port, and a spring that urges the valve body in a direction to seat the valve seat. Be prepared.

A sixth aspect of the present invention is provided to solve the above technical problems.
The technical means taken in the invention (hereinafter referred to as the third technical means) comprises a relief passage including an input passage on the upstream side of the relief valve and an output passage on the downstream side of the relief valve; A first input port opening to the input passage, and a second input port communicating with at least one of the main passage and the input passage on the upstream side of the oil pump,
A cylinder having an opening at one end that opens toward the first input port and a valve seat; an output port formed in the cylinder and communicating with the output passage; and a cylinder movably in the cylinder so as to face the first input port. When the discharge pressure of the oil pump reaches the first set pressure, only the second input port communicates with the output port, and when the discharge pressure reaches the second set pressure higher than the first set pressure. At least the second input port is provided with a valve body that is attachable to and detachable from a valve seat that communicates with the output port, and a spring that urges the valve body in a direction to seat the valve seat on the valve seat.

[0016]

The operation of the first technical means will be described below.

Although the discharge pressure (discharge amount) of the oil pump rises as the engine speed increases, the valve body is seated on the valve seat in the low engine speed range, that is, when the discharge pressure is less than the first set pressure. And the relief passage is closed. As a result, all of the discharged oil is pumped to the engine. Further, when the engine middle speed range, that is, when the discharge pressure is equal to or higher than the first set pressure, the valve body separates from the valve seat and the input port communicates with the first output port. As a result, the first predetermined amount of the discharged oil is released to, for example, the oil supply source. Further, in the high engine speed range, that is, when the discharge pressure is equal to or higher than the first set pressure, the input port is changed to the first and second output ports (however, the diameter of the second output port is smaller than the diameter of the first output port) by the valve body. If the diameter is large, only the second output port is acceptable). As a result, the second predetermined amount larger than the first predetermined amount of the discharged oil is released to, for example, the oil supply source.

As described above, according to the above technical means, a part of the discharged oil is released when it reaches the engine middle speed range, so that excessive discharge oil is prevented from being pumped to the engine middle speed range. This makes it possible to pump the required amount of oil to the engine. Therefore, it is possible to avoid an increase in the sliding loss of the engine in the middle rotation range of the engine, and the fuel consumption is improved accordingly.

Further, since two output ports are provided and the valve body allows the input port to communicate with one of the output ports in the engine middle speed range and the input port to communicate with at least the other output port in the high engine speed range, A setting pressure varying device having a complicated structure like the technology and a controller for issuing a variable command to the setting pressure varying device are not required, which is advantageous in terms of cost and the occupied space can be shortened.

Here, the operations of the above-mentioned three modes in the above-mentioned first technical means will be described.

First mode: In the low engine speed region, the valve body is seated on the valve seat, and the relief passage is closed. As a result, all of the discharged oil is pumped to the engine.
Further, in the middle rotation range of the engine, the valve element separates from the valve seat and moves in the direction against the spring, and the input port communicates only with the first output port. As a result, the first predetermined amount of the discharged oil is released to, for example, the oil supply source. Here, the contraction amount from the natural length of the spring increases with the movement of the valve element, and the set load of the spring also increases,
The valve body stops at a position where the force due to the discharge pressure balances the set load, and is maintained at that position. Furthermore, in the high engine speed region, the valve body further moves in the direction against the biasing force of the spring, and the input port communicates with the first and second output ports. As a result, the second of the discharged oil, which is larger than the first predetermined amount,
A predetermined amount is released to the oil supply source, for example.

As described above, according to the first embodiment, the discharge pressure is controlled by the single valve body and the single spring by utilizing the fact that the set load increases due to the contraction of the spring. Therefore, the structure of the relief valve is simplified, which is cost effective.

Second mode: In the low engine speed region, the first valve body is seated on the valve seat, and the relief passage is closed. As a result, all of the discharged oil is pumped to the engine. Further, in the middle rotation speed range of the engine, the first valve body separates from the valve seat and moves against the urging force of the first spring, and the input port communicates with the first output port. As a result, the first predetermined amount of the discharged oil is released to, for example, the oil supply source. At this time, since the second valve body does not move, the first valve body stops at the position where it abuts against the second valve body. Furthermore, in the high engine speed range,
The second valve body moves together with the first valve body against the biasing force of the second spring, and the input port communicates with the first and second output ports. As a result, the second predetermined amount larger than the first predetermined amount of the discharged oil is released to, for example, the oil supply source.

As described above, according to the second embodiment, since the discharge pressure is controlled as described above by the two valve bodies having different operating states and the two springs having different set loads for urging them, the relief valve of the relief valve is controlled. The operation becomes more reliable.

Third mode: In the low engine speed region, the main valve body is seated on the valve seat and the auxiliary valve body is also seated on the second valve seat of the main valve body, so that the relief passage is closed. as a result,
All of the discharged oil is pumped to the engine. Further, in the middle rotation speed range of the engine, the auxiliary valve element separates from the second valve seat and moves against the urging force of the auxiliary spring, and the input port communicates with the first output port through the through hole. As a result, the first predetermined amount of the discharged oil is released to, for example, the oil supply source. At this time, since the main valve body does not move, the input port and the second output port are cut off. Further, in the high engine speed region, the main valve body moves against the biasing force of the main spring, and the input port also communicates with the second output port. As a result, the second predetermined amount larger than the first predetermined amount of the discharged oil is released to, for example, the oil supply source.

As described above, according to the third embodiment, the discharge pressure is controlled as described above by the two valve bodies having different operating states and the two springs having different set loads for biasing the valve bodies. As with the form, the operation of the relief valve becomes more reliable.

Since the operation of the second technical means is substantially the same as the operation of the first technical means of the first mode, the description thereof will be omitted.

The operation of the third technical means will be described below.

In the low engine speed region, the relief valve is closed because the valve element is seated on the valve seat. As a result, all of the discharged oil is pumped to the engine. Further, in the middle rotation speed range of the engine, the valve element separates from the valve seat and moves against the biasing force of the spring, and only the first input port communicates with the output port. As a result, the first predetermined amount of the discharged oil is released to, for example, the oil supply source. Furthermore, in the high engine speed region, the valve body further moves against the biasing force of the spring, and the second input port also communicates with the output port. As a result, the second predetermined amount larger than the first predetermined amount of the discharged oil is released to, for example, the oil supply source.

As described above, according to the third technical means, as in the first and second technical means, part of the discharged oil is released when the engine reaches the middle rotation speed range. It is possible to prevent excessive discharge of oil from being pumped to the engine in the middle rotation range, and it is possible to pump a required amount of oil to the engine. Therefore, it is possible to avoid an increase in the sliding loss of the engine in the middle rotation range of the engine, and the fuel consumption is improved accordingly.

Further, since two input ports are provided and one input port is made to communicate with the output port in the engine middle speed range by the valve body, and at least the other input port is made to communicate with the output port in the engine high speed range, A setting pressure varying device having a complicated structure like the technology and a controller for issuing a variable command to the setting pressure varying device are not required, which is advantageous in terms of cost and the occupied space can be shortened.

[0032]

Embodiments of the present invention will be described below with reference to the accompanying drawings.

FIG. 1 is an overall configuration diagram of the oil pump device according to the first to fourth embodiments.

As shown in FIG. 1, an oil pump device 10 according to the first to fourth embodiments has an oil pan (oil supply source) 1 in which oil is stored, and a main connecting the oil pan 1 and the engine 0. A passage 2 and an oil pump 3 which is arranged in the middle of the main passage 2 and rotates in conjunction with the engine 0 to pump oil to the engine 0, and a main passage downstream of the oil pump 3 (hereinafter referred to as a second main passage). (Referred to) 22 and a relief passage 4 that connects the oil pan 1, and a relief passage 4 that is disposed in the middle of the relief passage 4 and that corresponds to the discharge pressure of the oil pump 3.
And a relief valve 5 for opening and closing.

The relief passage 4 has an input passage 41 upstream of the relief valve 5 and an output passage 42 downstream of the relief valve 5. The output passage 42 is the first output passage 421.
And a second output passage 422 located farther than the first output passage 421. The relief passage 4 (that is, the output passage 42) may be joined to a main passage 21 on the upstream side of the oil pump 3 (hereinafter referred to as a first main passage) 21 or an intake port of the oil pump 3 described later.

As shown in FIG. 2, the oil pump 3 is a trochoidal type oil pump, and has a body 31 having a cylindrical space 311 and a rotary shaft 32 pivotally supported by the body 31.
An inner rotor 33 supported around the rotary shaft 32 in the cylindrical space 311, and an outer rotor 35 arranged around the inner rotor 33 so as to form a plurality of pump chambers 34 between the inner rotor 33 and the inner rotor 33. A suction port 36 for sucking oil into the pump chamber 34, a discharge port 37 for discharging oil compressed from the pump chamber 34 toward the engine, and a cover 38 for covering the inner rotor 33 and the outer rotor 35 are provided. .

The body 31 is fixed to a cylinder block (not shown) of the engine 0. The rotating shaft 32 is directly connected to a crankshaft (not shown) of the engine 0.

The rotary shaft 32 may be connected to the crankshaft via a V-belt or the like.

The rotary shaft 32 may be directly connected to the crankshaft. The inner rotor 33 has a plurality of outer teeth 33.
One. The outer rotor 35 is the inner rotor 3
3 has a plurality of inner teeth 351 that engage with the outer teeth 331 of the inner rotor 33, and the center of rotation is eccentric to the center of rotation of the inner rotor 33.

The pump chamber 34 communicates with the suction port 36, and its volume gradually increases as the inner rotor 33 rotates in the rotational direction.
7, a discharge pump chamber group (not shown) whose volume gradually decreases in the rotational direction of the inner rotor 33.
And a maximum volume pump chamber that is formed between the suction pump chamber group 341 and the discharge pump chamber group (that is, between the suction port 36 and the discharge port 37) and is not in communication with the suction and discharge ports 36, 37 (see FIG. (Not shown). Therefore, as the inner rotor 33 rotates, the suction pump chamber group 34
When 1 is expanded, oil is sucked from the suction port 36, and the discharge pump chamber group is compressed, so that high-pressure oil is discharged to the discharge port 37.

The intake port 36 communicates with the first main passage 21 and is formed in an arc shape at the bottom of the first pump chamber group 341. The discharge port 37 is the second main passage 2
2 and is formed in an arc shape at the bottom of the second pump chamber group.

The operation of the trochoidal type oil pump 3 constructed as described above will be described. The inner rotor 33 rotates in accordance with the rotation of the rotary shaft 32, and the outer rotor 35 also engages with the outer teeth 331 of the inner rotor 33 in the same direction ( 2). Then, the well-known pump action is performed due to the volume change of the pump chamber 34.

Although a trochoidal type oil pump has been described as an example here, the present invention is not limited to this, and for example, a vane pump, an external gear pump,
An oil pump such as a plunger pump may be adopted.

The relief valve 5 is arranged in the body 31 of the oil pump 3. The relief valve 5 does not have to be arranged in the body 31.

Hereinafter, the relief valve 5 according to the first to fourth embodiments, which is the main part of the present invention, will be described with reference to FIGS. 3 to 6, members having the same function are designated by the same reference numerals.

The relief valve 5 of the first embodiment shown in FIG.
An input port 51 formed in the body 31 so as to communicate with the input passage 41, an opening 521 formed in the body 31 and opening at one end toward the input port 51, and a valve seat 52.
And a first output port 53 formed in the body 31 so as to communicate with the first output passage 421.
A second output port 54 formed in the body 31 so as to communicate with the second output passage 422; and a second output port 54 movably arranged in the cylinder 52 so as to face the input port 51. When the first set pressure is reached, the input port 51 is communicated with only the first output port 53, and when the discharge pressure reaches the second set pressure higher than the first set pressure, the input port 51 is set to the first and second A valve body 55 that is attachable to and detachable from a valve seat 522 that communicates with the output ports 53 and 54, and a spring 56 that urges the valve body 55 in a direction to seat the valve body 55 on the valve seat 522 are provided.

The cylinder 52 extends in the axial direction of the input port 51 and has a cylindrical shape.

The first and second output ports 53, 54 extend inward in the radial direction of the cylinder 52 and are open. The first output port 53 is formed at a position closer to the input port 51 than the second output port 54, and its diameter is the second
It is smaller than the diameter of the output port 54. The first
The diameter of the output port 53 may be equal to the diameter of the second output port 54.

The valve body 55 has a bottomed cylindrical shape, and has a recess 551 on the surface opposite to the surface on which the valve seat 521 is seated. The spring 56 is arranged between the bottom surface of the recess 551 and the cylinder 52, and its set load increases as the amount of contraction from the natural length increases.
The room 57 that houses the spring 56 is
It communicates with the atmosphere through a passage 523 formed in the.

The operation of the oil pump device 10 according to the first embodiment configured as described above will be described with reference to FIGS. 3 and 9.

In the low engine speed region (A in FIG. 9, for example, the engine speed is less than 1500 rpm), the valve body 55 is seated on the valve seat 522, and between the input port 51 and the first and second output ports 53, 54. Communication is blocked. As a result, all the oil discharged from the oil pump 3 is pumped to the engine 0. Therefore, in this area, the oil supply amount to the engine 0 increases in proportion to the engine speed.

Next, in the engine middle speed range (B in FIG. 9, for example, engine speed 1500 to 4000 rpm), the force acting on the valve body 55 by the discharge pressure of the oil pump 3 becomes larger than the set load of the spring 56. So valve body 5
5 disengages from the valve seat 522 and moves to the right in FIG. 3 against the urging force of the spring 56, and the input port 51 communicates only with the first output port 53. As a result, the first predetermined amount of the discharged oil is released to the oil pan 1. Here, the valve body 55
The amount of contraction of the spring 56 from its natural length increases with the movement of the spring 56, and the set load of the spring 56 also increases. Therefore, the valve body 55 stops at a position where the force due to the discharge pressure balances the set load, Maintained in that position. Therefore, in this area, it is possible to prevent the excessive discharge oil shown by the diagonal lines in FIG. 9 from being pumped to the engine 0.

Finally, in the high engine speed region (C in FIG. 9, for example, engine speed of 4000 rpm or more), the discharge pressure of the oil pump 3 further increases, so that the valve body 55 further resists the biasing force of the spring 56. 3 to the right in FIG. 3, the input port 51 is connected to the first and second output ports 53,
Communicating with 54. As a result, the second predetermined amount larger than the first predetermined amount of the discharged oil is released to the oil pan 1. Therefore, even in this area, it is possible to prevent excessive discharge oil from being pumped to the engine 0.

As described above, in the first embodiment, part of the discharged oil is released when reaching the engine middle speed range.
It is possible to prevent excessive discharge of oil from being pumped to the engine in the engine middle speed range, and it is possible to pump a required amount of oil to the engine. Therefore, it is possible to avoid an increase in the sliding loss of the engine in the middle rotation range of the engine, and the fuel consumption is improved accordingly.

Further, two output ports 53 and 54 are provided,
Since the valve body 55 allows the input port 51 to communicate with one of the output ports 53 in the engine middle speed range, and allows the input port to communicate with both output ports 53, 54 in the engine high speed range,
The set pressure varying device and the controller for issuing a variable command to the set pressure varying device as in the prior art are not required, which is advantageous in terms of cost and the occupied space can be shortened.

Further, since the discharge pressure is controlled by the single valve body 55 and the single spring 56 as described above by utilizing the fact that the set load increases due to the contraction of the spring 56, the structure of the relief valve 5 is described. Is simpler and more cost effective.

Since the diameter of the first output port 53 is smaller than the diameter of the second output port 54, the relief amount can be gradually increased.

The relief valve 5 of the second embodiment shown in FIG.
Similar to the first embodiment, the input port 51 and the cylinder 52
And a first output port 53, a second output port 54, a valve body 55, and a spring 56. Below, the first
Only the points different from the configuration of the embodiment will be described.

In FIG. 4, the cylinder 52 has a stepped columnar shape, and the small diameter portion 5 continuous with the input port 51.
2a and the large diameter part 52b larger in diameter than the diameter of the small diameter part 52a continuous with the small diameter part 52a.

The valve body 55 has a diameter smaller than that of the first valve body 55a slidably arranged in the small diameter portion 52a and the diameter of the first valve body 55a slidably arranged in the large diameter portion 52b. Also has a large diameter second valve body 55b. The first valve body 55a is attachable to and detachable from the first valve seat 522, and makes the input port 51 communicate with only the first output port 53 when the discharge pressure of the oil pump 3 reaches the first set pressure. . In addition, the first valve body 55a is provided with a recess 55 so as to face the second valve body 55b.
1a is formed. The second valve body 55b is the cylinder 5
The second valve seat 524 formed on the second stepped portion is detachable, and when the discharge pressure reaches a second set pressure higher than the first set pressure, the input port 51 is connected to the first and second output ports. 53,
54 is communicated with. Further, the second valve body 55b is formed with a recess 552a facing the first valve body 55a. The recess 552a accommodates a part of the first valve body 55a, and the bottom surface of the recess 552a can come into contact with the right end surface of the first valve body 55a in the figure.

The spring 56 connects the first valve body 55a to the first
The first spring 56a that urges the valve seat 522 in the direction to be seated and the second valve body 55b that is urged in the direction to seat on the second valve seat 524, and the set load thereof is the first spring 56a.
Second spring 56 that is larger than the set load of
b and. The first spring 56a is housed in the first spring chamber 57a and is disposed between the bottom surface of the recess 551a of the first valve body 55a and the bottom surface of the recess 551b of the second valve body 55b. The second spring 56b is the second
It is housed in the spring chamber 57b and is arranged between the second valve body 55b and the cylinder 52.

The second valve body 55b has a through hole 55 for communicating between the first and second spring chambers 57a and 57b.
2b are formed, and as a result, the first spring chamber 5 is formed.
7a communicates with the atmosphere through the through hole 552b, the second spring chamber 57b, and the passage 523.

The operation of the oil pump device 10 according to the second embodiment configured as described above will be described with reference to FIGS. 4 and 9.

In the low engine speed region (A in FIG. 9, for example, the engine speed is less than 1500 rpm), the first valve body 55a.
Is seated on the first valve seat 522, and the input port 5
The communication between the first and first and second output ports 53 and 54 is cut off. As a result, all the oil discharged from the oil pump 3 is pumped to the engine 0. Therefore, in this area, the oil supply amount to the engine 0 increases in proportion to the engine speed.

Next, in the engine middle speed range (B in FIG. 9, for example, engine speed 1500 to 4000 rpm), the force acting on the first valve body 55a by the discharge pressure of the oil pump 3 is the set load of the first spring 56a. Therefore, the first valve body 55a is disengaged from the first valve seat 522 to resist the urging force of the first spring 56a, and the second valve body 55a moves to the right in FIG.
It moves until it comes into contact with the valve body 55b, and the input port 51 communicates with the first output port 53. As a result, the first predetermined amount of the discharged oil is released to the oil pan 1. Here, the force acting on the first valve body 55a by the discharge pressure of the oil pump 3 is the set load of the first spring 56a and the second spring 56a.
Since it is smaller than the sum of the set load of b, the first valve body 55a
The second valve body 55b does not move even when the second valve body 55b contacts the second valve body 55b. As a result, the first valve body 55a is maintained at the position in contact with the second valve body 55b. Therefore, in this area, it is possible to prevent the excessive discharge oil shown by the diagonal lines in FIG. 9 from being pumped to the engine 0.

Finally, in the high engine speed region (C in FIG. 9, for example, the engine speed is 4000 rpm or more), the discharge pressure of the oil pump 3 further increases, and the force is the set load of the first spring 56a and the second spring. Since it becomes larger than the sum of the set load of 56b, the second valve body 55b moves rightward in FIG. 4 together with the first valve body 55a against the biasing force of the second spring 56b, and the input port 51 moves to the first position. And the second output ports 53 and 54. As a result, as a result,
A second predetermined amount larger than the first predetermined amount of the discharged oil is released to the oil pan 1. Therefore, even in this area, it is possible to prevent excessive discharge oil from being pumped to the engine 0.

As described above, in the second embodiment, the two valve bodies 55a and 55b having different operating states and the two springs 56a and 56 having different set loads for biasing them are provided.
Since the discharge pressure is controlled by b as described above, the operation of the relief valve 5 becomes more reliable and the reliability is improved.

The relief valve 5 of the third embodiment shown in FIG.
Similar to the first embodiment, the input port 51 and the cylinder 52
The first output port 53, the second output port 54 having a diameter larger than the diameter of the first output port 53, the valve body 55, and the spring 56. Only the points different from the configuration of the first embodiment will be described below.

In FIG. 5, the first output port 53 is formed at a position farther from the input port 51 than the second output port 54. The first output port 53 communicates with the second output passage 422, and the second output port 54 communicates with the first output passage 421.

The valve element 55 comprises a first valve element (sub valve element) 55a which is a ball valve element, and a cylindrical second valve element (main valve element) 55b which can be attached to and detached from the valve seat 522. There is. Second
The valve body 55b connects the input port 51 to the first and second output ports 53 and 54 when the discharge pressure of the oil pump 3 reaches a second set pressure higher than the first set pressure. Further, the second valve body 55b is provided with a recess 551b, a through hole 553b communicating with the input port 51, and a valve seat 554b located near the right end of the through hole 553b.

The first valve body 55a is housed in the recess 551b of the second valve body 55b so as to be attached to and detached from the valve seat 554b formed on the second valve body 55b, and the discharge pressure is lower than the second set pressure. The input port 51 communicates with the first output port 53 when the set pressure reaches 1. A retainer 58 is provided in the recess 551b of the second valve body 55b so as to accommodate the first valve body 55a, and the first valve body 55 is provided in the center thereof.
A guide hole 581 for guiding the oil that has entered from the input port 51 to the first output port 53 when a is opened is formed.

The spring 56 urges the first spring (sub spring) 56a for urging the first valve body 55a to seat on the valve seat 554 and the second valve body 55b for seating on the valve seat 522. However, the second spring (main spring) 56b whose set load is set to be larger than the set load of the first spring 56a.

The first spring 56a is the first valve body 55a.
At the same time, the first valve element 55a and the retainer 58 are housed in a first spring chamber 57a formed in the retainer 58.
It is arranged in between. The second spring 56b is housed in the second spring chamber 57b and is arranged between the retainer 58 and the cylinder 52.

The operation of the oil pump device 10 according to the third embodiment configured as described above will be described with reference to FIGS. 5 and 9.

In the low engine speed region (A in FIG. 9, for example, the engine speed is less than 1500 rpm), the first valve body 55a.
Is seated on the valve seat 554b and the second valve body 55b is seated on the valve seat 52.
The seat 2 is in the seated state, and the communication between the input port 51 and the first and second output ports 53 and 54 is cut off. As a result, all the oil discharged from the oil pump 3 is pumped to the engine 0. Therefore, in this area, the oil supply amount to the engine 0 increases in proportion to the engine speed.

Next, in the engine middle speed range (B in FIG. 9, for example, engine speed 1500 to 4000 rpm), the force acting on the first valve body 55a by the discharge pressure of the oil pump 3 is the set load of the first spring 56a. Therefore, the first valve body 55a disengages from the first valve seat 522 and moves to the right in FIG. 5 against the urging force of the first spring 56a, and the input port 51 moves through the through hole 553b and the first port. It communicates with the first output port 53 via the spring chamber 57a, the guide hole 581 and the second spring chamber 57b. As a result, the first predetermined amount of the discharged oil is released to the oil pan 1. Since the force acting on the second valve body 56a by the discharge pressure of the oil pump 3 is smaller than the set load of the second spring 56a, the second valve body 55b does not move. Therefore, in this area, it is possible to prevent the excessive discharge oil shown by the diagonal lines in FIG. 9 from being pumped to the engine 0.

Finally, in the high engine speed region (C in FIG. 9, for example, engine speed 4000 rpm or more), the discharge pressure of the oil pump 3 further increases and its force becomes larger than the set load of the second spring 56b. Therefore, the second valve body 5
5b moves to the right in FIG. 5 against the biasing force of the second spring 56b together with the first valve body 55a, and the input port 51 communicates with the first and second output ports 53, 54. As a result, as a result, the second amount of the discharged oil that is larger than the first predetermined amount is increased.
A predetermined amount is released to the oil pan 1. Therefore, even in this area, it is possible to prevent excessive discharge oil from being pumped to the engine 0.

As described above, in the third embodiment, the two valve bodies 55a and 55b having different operating states and the two springs 56a and 56 having different set loads for biasing them are provided.
Since the discharge pressure is controlled by b as described above, the operation of the relief valve 5 becomes more reliable and the reliability is improved.

Further, since the retainer 58 supporting one end of the first spring 56a by the second spring 56b is pressed against the bottom surface of the recess 551b of the second valve body 55b, the retainer 5
There is no need to fix or fix 8 to the second valve body, which is cost effective.

Further, since the ball valve body 55a is slidably guided in the first spring chamber 57a formed in the retainer 58, the ball valve body 55a does not rattle.

Furthermore, since the first valve body 55a is a ball valve body, it is inexpensive.

The relief valve 5 of the fourth embodiment shown in FIG.
Instead of the first output port 53 adopted in the first embodiment,
It differs from that of the first embodiment only in that an output groove 59 communicating with the second output port 54 is adopted. This output groove 59 is
It is formed on the body 32, is located closer to the input port 51 than the second output port 54, and has an opening area smaller than that of the second output port 54.

Since the operation of the oil pump device 10 according to the fourth embodiment is substantially the same as that of the first embodiment, its explanation is omitted.

In the fourth embodiment, it is possible to control the discharge pressure in the engine medium speed rotation range only by providing the output groove 59 on the input port 51 side with respect to the second output port 54. Therefore, similar to the first embodiment. Since only the single valve body 55 and the single spring 56 are required, the structure of the relief valve 5 is simple.

FIG. 7 is an overall configuration diagram of an oil pump device according to the fifth embodiment.

As shown in FIG. 7, the oil pump device 10 according to the fifth embodiment has an oil pan (oil supply source) 1, a main passage 2, and an oil pump 3 as in the first to fourth embodiments. And a relief passage 4 and a relief valve 5.

The relief passage 4 has an input passage 41 on the upstream side of the relief valve 5 and an output passage 42 on the downstream side of the relief valve 5. The input passage 41 is the first input passage 411.
And a second input passage 412 branched from the main passage 2 on the downstream side of the first input passage 411. The second input passage 412 may be branched from the first input passage 411.

Since the structure of the oil pump 3 is the same as that of the first to fourth embodiments, its explanation is omitted.

A relief valve 5 according to the fifth embodiment will be described with reference to FIG.

The relief valve 5 has a first input port 51 communicating with the first input passage 411, a second input port 60 communicating with the second input passage 412, and a first input port 5 at one end.
1, a cylinder 52 having an opening 521 opening toward 1 and a valve seat 522, an output port 54 formed in the cylinder 52 and communicating with the output passage 42, and a first input port 51.
Is movably arranged in the cylinder 52 so as to face the
When the discharge pressure of the oil pump 3 reaches the first set pressure, only the second input port 60 communicates with the output port 54, and at least when the discharge pressure reaches the second set pressure higher than the first set pressure. A valve body 55 that connects the first input port 51 to the output port 54 and a spring 56 that urges the valve body 55 in the direction in which the valve body 55 is seated on the valve seat 522 are provided.

The second input port 60 is opened toward the inner side in the radial direction of the cylinder 52 so as to face the output port 54, and the diameter thereof is smaller than the diameter of the first input port 51. The single output port 54 corresponds to the second output port according to the first embodiment.

The valve body 55 has a recess 551 and an annular groove 5.
52 is formed. Bottom of recess 551 and cylinder 5
A spring 56 similar to that of the first embodiment is arranged between the two. The annular groove 552 connects or disconnects the second input port 60 and the output port 54, and the opening width to the output port 54 is substantially equal to the diameter of the output port 54.

The rest of the configuration is the same as that of the first embodiment, so its explanation is omitted.

The operation of the oil pump device 10 according to the fifth embodiment configured as described above will be described with reference to FIGS. 8 and 9.

In the low engine speed range (A in FIG. 9, for example, the engine speed is less than 1500 rpm), the valve body 55 is seated on the valve seat 522, and the first and second input ports 51, 60 and the output port 54 are not connected. Communication is blocked. As a result, all the oil discharged from the oil pump 3 is pumped to the engine 0. Therefore, in this area, the oil supply amount to the engine 0 increases in proportion to the engine speed.

Next, in the engine middle speed range (B in FIG. 9, for example, engine speed 1500 to 4000 rpm), the force acting on the valve element 55 by the discharge pressure of the oil pump 3 becomes larger than the set load of the spring 56. So valve body 5
8 disengages from the valve seat 522 and moves to the right in FIG. 8 against the biasing force of the spring 56, and the second input port 60 communicates only with the output port 54 via the annular groove 552. As a result, the first predetermined amount of the discharged oil is released to the oil pan 1. Here, the amount of contraction of the spring 56 from the natural length increases with the movement of the valve body 55, and the set load of the spring 56 also increases. Therefore, the valve is placed at a position where the force due to the discharge pressure balances with the set load. Body 55 is stopped and maintained in that position. Therefore, in this area, FIG.
It is possible to prevent the excessive discharge oil indicated by the slanted line from being pumped to the engine 0.

Finally, in the high engine speed region (C in FIG. 9, for example, engine speed 4000 rpm or more), the discharge pressure of the oil pump 3 further increases, so the valve body 55 further resists the biasing force of the spring 56. 8 to the right in FIG. 8, the first and second input ports 51 and 60 communicate with the output port 54. As a result, the second predetermined amount larger than the first predetermined amount of the discharged oil is released to the oil pan 1. Therefore, even in this area, it is possible to prevent excessive discharge oil from being pumped to the engine 0.

As described above, in the first embodiment, two input ports 51 and 60 are provided, and one input port 60 is formed on the valve body 55 by the valve body 55 in the middle rotation range of the engine. To communicate with the output port 54 via
Since at least the other input port 51 is made to communicate with the output port 54 in the high engine speed region, a set pressure varying device and a controller for issuing a variable command to the set pressure varying device as in the prior art are not required, which is cost effective. It is advantageous to the machine and the occupied space can be shortened.

Further, since the discharge pressure is controlled by the single valve body 55 and the single spring 56 by utilizing the fact that the set load increases due to the contraction of the spring 56, the discharge pressure is controlled as in the first embodiment. Similarly, the structure of the relief valve 5 is simplified, which is advantageous in terms of cost.

Since the diameter of the second input port 60 is smaller than the diameter of the first input port 51, the relief amount can be gradually increased.

(Comparative Example) With reference to FIG. 10, an oil pump device according to a comparative example will be described.

The oil pump device according to the comparative example includes
Similar to the fifth embodiment, an oil pan (oil supply source) 1, a main passage 2, an oil pump 3, a relief passage 4, and a relief valve 5 are provided. The relief passage 4 has an input passage 41 on the upstream side of the relief valve 5 and an output passage 42 on the downstream side of the relief valve 5.

The oil pump 3 has two divided intake ports 36a and 36b. One suction port (hereinafter referred to as the first suction port) 36a is connected to the oil pan 1 via the first main passage 21, and the other suction port (hereinafter referred to as the second suction port) 36b is connected to the negative pressure passage 7.
Is connected to a spring chamber 57 of the relief valve 5 which will be described later.

The relief valve 5 is arranged in the middle of the relief passage 4 and opens and closes the relief passage 4 according to the discharge pressure of the oil pump 3. The relief valve 5 includes a cylinder 52 having one end opened to the input passage, and a valve body 55 slidably disposed in the cylinder 52 and detachable from the valve seat 522.
And a spring 56 for urging the valve body 56 in a direction to seat it on the valve seat 522. Here, as described above, since the spring chamber 57 that houses the spring 56 communicates with the second suction port 36b via the negative pressure passage 7, the negative pressure is always introduced into the spring chamber 57.

The operation of the oil pump device of the comparative example will be described with reference to FIGS. 9 and 10.

In the low engine speed region (A in FIG. 9, for example, the engine speed is less than 1500 rpm), the valve body 55 is seated on the valve seat 522, and the relief passage 4 is closed. As a result, all the oil discharged from the oil pump 3 is pumped to the engine 0. Therefore, in this area, the oil supply amount to the engine 0 increases in proportion to the engine speed.

Next, in the engine middle speed range (B in FIG. 9, for example, engine speed 1500 to 4000 rpm), the force acting on the valve element 55 by the discharge pressure of the oil pump 3 is still smaller than the set load of the spring 56. Therefore, as shown in FIG. 9, all the oil discharged from the oil pump 3 is discharged from the engine 0.
Pumped to.

Finally, in the high engine speed region (C in FIG. 9, for example, an engine speed of 4000 rpm or more), the negative pressure introduced into the spring chamber 57 increases, so that the force due to the negative pressure and the force due to the discharge pressure are increased. Since the sum becomes larger than the set weight of the spring 56, the valve body 55 moves in a direction against the biasing force of the spring 56, and the relief passage 4 opens. As a result, a predetermined amount of the discharged oil is released to the oil pan 1. Therefore, in this area, as shown in FIG. 9, it is possible to prevent excessive discharge oil from being pumped to the engine 0.

As is apparent from FIG. 9, in the first to fifth embodiments, a larger amount of discharged oil can be relieved in the engine middle speed range (B in FIG. 9) than in the comparative example.

[0110]

The invention of claim 1 has the following effects.

When the engine reaches the middle speed range, a part of the discharged oil is released, so that it is possible to prevent the excessive discharge oil from being pumped to the middle speed range of the engine, and to pump the necessary amount of oil to the engine. Will be possible. Therefore, in the engine middle speed range, it is possible to avoid an increase in sliding loss of the engine,
The fuel efficiency is improved accordingly.

Further, since two output ports are provided and the valve body allows the input port to communicate with one output port in the engine middle speed range, and allows the input port to communicate with at least the other output port in the engine high speed range, A setting pressure varying device having a complicated structure like the technology and a controller for issuing a variable command to the setting pressure varying device are not required, which is advantageous in terms of cost and the occupied space can be shortened.

The invention of claim 2 has the following effect in addition to the effect of the invention of claim 1.

Since the discharge pressure is controlled by the single valve body and the single spring by utilizing the fact that the set load increases due to the contraction of the spring, the structure of the relief valve is simplified, It is advantageous in terms of cost.

The invention of claim 3 has the following effect in addition to the effect of the invention of claim 1.

Since the discharge pressure is controlled as described above by the two valve bodies having different operating states and the two springs having different set loads for biasing them, the operation of the relief valve becomes more reliable.

The invention of claim 4 has the following effect in addition to the effect of the invention of claim 1.

Since the discharge pressure is controlled as described above by the two valve bodies having different operating states and the two springs having different set loads for urging them, the same as in the invention of claim 3.
The relief valve operates more reliably.

The invention of claim 5 has the following effects.

When the engine reaches the middle speed range, a part of the discharged oil is released, so that it is possible to avoid sending the excessive discharge oil to the engine in the middle speed range of the engine, and to pump a necessary amount of oil to the engine. Will be possible. Therefore, in the engine middle speed range, it is possible to avoid an increase in sliding loss of the engine,
The fuel efficiency is improved accordingly.

Further, an output port and an output groove communicating with the output port are provided so as to be located closer to the input port than the output port, and the valve body allows the input port to communicate with the output groove in the engine middle speed range, thereby increasing the engine rotation speed. Since the input port is communicated with at least the output port in the area, a set pressure varying device and a controller for issuing a variable command to the set pressure varying device, which has a complicated structure as in the prior art, are not required, which is advantageous in cost. At the same time, the occupied space can be shortened.

The invention of claim 6 has the following effects.

When the engine reaches the middle speed range, a part of the discharged oil is released, so that it is possible to prevent the excessive discharge oil from being pumped to the middle speed range of the engine, and to pump a necessary amount of oil to the engine. Will be possible. Therefore, in the engine middle speed range, it is possible to avoid an increase in sliding loss of the engine,
The fuel efficiency is improved accordingly.

Further, since two input ports are provided and one input port is made to communicate with the output port in the engine middle speed range by the valve body, and at least the other input port is made to communicate with the output port in the engine high speed range, A setting pressure varying device having a complicated structure like the technology and a controller for issuing a variable command to the setting pressure varying device are not required, which is advantageous in terms of cost and the occupied space can be shortened.

[Brief description of drawings]

FIG. 1 is an overall configuration diagram of an oil pump device according to first to fourth embodiments of the present invention.

FIG. 2 is a plan view of an oil pump according to this embodiment.

FIG. 3 is a sectional view of a relief valve according to the first embodiment.

FIG. 4 is a sectional view of a relief valve according to a second embodiment.

FIG. 5 is a sectional view of a relief valve according to a third embodiment.

FIG. 6 is a sectional view of a relief valve according to a fourth embodiment.

FIG. 7 is an overall configuration diagram of an oil pump device according to a fifth embodiment of the present invention.

FIG. 8 is a sectional view of a relief valve according to a fifth embodiment.

FIG. 9 is a graph showing the relationship between the engine speed and the amount of oil supplied to the engine in the devices of this example and the comparative example.

FIG. 10 is an overall configuration diagram of an oil pump device according to a comparative example of the present invention.

[Explanation of symbols]

 0 engine 1 oil pan (oil supply source) 2 main passage 3 oil pump 4 relief passage 41 input passage 42 output passage 5 relief valve 51 input port, first input port 52 cylinder 521 opening 522, 524 valve seat 53 first output Port 54 Second output port 55 Valve body 55a First valve body (sub valve body) 55b Second valve body (main valve body) 553b Through hole 554b Valve seat (second valve seat) 56 Spring 56a First spring (auxiliary spring) ) 56b Second spring (main spring) 59 Output groove 60 Second input port

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Naohiro Hara 2-1-1 Asahi-machi, Kariya city, Aichi Prefecture Aisin Seiki Co., Ltd. (72) Kingo Aoki 2-1-1 Asahi-cho, Kariya city, Aichi prefecture Aisin Seiki Co., Ltd. (72) Inventor Takayuki Kurumi 2-1, Asahi-cho, Kariya City, Aichi Prefecture Aisin Seiki Co., Ltd. (72) Ichiro Kimura 2-chome, Asahi-cho, Kariya City, Aichi Aisi Within Seiki Co., Ltd.

Claims (6)

[Claims] 1. An oil supply source, a main passage connecting the oil supply source and an engine, an oil pump disposed in the middle of the main passage, rotating in conjunction with the engine, and pumping oil to the engine. A relief passage connecting the main passage on the downstream side of the oil pump and at least one of the oil supply source, the main passage on the upstream side of the oil pump, and the suction port of the oil pump, and a relief passage in the middle of the relief passage. An oil pump device provided with a relief valve that opens and closes the relief passage according to a discharge pressure of the oil pump, wherein the relief passage includes an input passage on an upstream side of the relief valve and a downstream side of the relief valve. The relief valve comprises an input port communicating with the input passage, and an opening at one end opening toward the input port. A cylinder having a valve seat, a first and second output ports formed in the cylinder so that communicates with the output passage,
Displaceable in the cylinder so as to face the input port, the input port communicates only with the first output port when the discharge pressure of the oil pump reaches a first set pressure, Reaches the second set pressure higher than the first set pressure, the input port is at least moved to the second set pressure.
A valve element that is attachable to and detachable from the valve seat that communicates with the output port;
An oil pump device, comprising: a spring for urging the valve element in a direction to be seated on the valve seat. 2. The oil pump device according to claim 1, wherein the first output port is formed at a position closer to the input port than the second output port. 3. The first valve body according to claim 2, wherein the valve body is attachable to and detachable from the valve seat and connects or disconnects the input port and the first output port. The input port and the second port are arranged to face each other so that they can come into contact with each other.
A second valve body that communicates or cuts off between the output ports, and the spring urges the first valve body to urge the first valve body on the valve seat and the second valve body. An oil pump device, comprising: a second spring that is biased in the same direction as the biasing direction of the first spring and has a set load larger than the set load of the first spring. 4. The first output port according to claim 1, wherein the first output port is formed farther from the input port than the second output port, and the valve body has a through hole and a second hole communicating with the input port.
A main valve body having a valve seat, which is attachable to and detachable from the valve seat formed on the cylinder and which connects or disconnects between the input port and the second output port, and a main valve body which is attached to and detached from the second valve seat to penetrate. A sub-valve body that opens and closes a hole and connects or disconnects between the input port and the first output port, and the spring urges the main valve body in a direction in which the main valve body is seated on the valve seat. And a sub-spring that urges the sub-valve in the same direction as the urging direction of the main spring, and the set load thereof is smaller than the set load of the main spring. Oil pump device. 5. An oil supply source, a main passage connecting the oil supply source and the engine, an oil pump disposed in the middle of the main passage, rotating in conjunction with the engine, and pumping the oil to the engine. A relief passage connecting the main passage on the downstream side of the oil pump and at least one of the oil supply source, the main passage on the upstream side of the oil pump and the suction port of the oil pump, and a relief passage in the middle of the relief passage. An oil pump device provided with a relief valve that opens and closes the relief passage according to a discharge pressure of the oil pump, wherein the relief passage includes an input passage on the upstream side of the relief valve and a downstream side of the relief valve. The relief valve comprises an input port communicating with the input passage, and an opening at one end opening toward the input port. A cylinder having a valve seat, an output port formed in the cylinder and communicating with the output passage, and an output groove formed in the cylinder so as to be closer to the input port than the output port and communicating with the output port And a valve element that is detachably attached to the valve seat that is movably disposed in the cylinder so as to face the input port, and a spring that urges the valve element in a direction to be seated on the valve seat. An oil pump device characterized in that 6. An oil supply source, a main passage connecting the oil supply source and the engine, an oil pump arranged in the middle of the main passage, rotating in conjunction with the engine, and pumping the oil to the engine. A relief passage connecting the main passage on the downstream side of the oil pump and at least one of the oil supply source, the main passage on the upstream side of the oil pump, and the suction port of the oil pump, and a relief passage in the middle of the relief passage. An oil pump device provided with a relief valve that opens and closes the relief passage according to a discharge pressure of the oil pump, wherein the relief passage includes an input passage on an upstream side of the relief valve and a downstream side of the relief valve. The relief valve includes a first input port opening to the input passage, a main passage upstream of the oil pump, and A second input port communicating with at least one of the input passages; a cylinder having an opening at one end toward the first input port; and a valve seat; An output port communicating with the passage and a first input port are movably disposed in the cylinder so as to face the first input port, and only the second input port is provided when the discharge pressure of the oil pump reaches a first set pressure. A valve element that is detachable from the valve seat and that causes at least the second input port to communicate with the output port when the discharge pressure reaches a second set pressure higher than the first set pressure. An oil pump device, comprising: a spring for urging the valve element in a direction to be seated on the valve seat.