JPH03134283A - Oil pump for vehicle - Google Patents

Abstract

PURPOSE:To prevent generation of an engine stop following an increase of a load even in an idling condition by providing a pressure switch main unit in which a driving condition of a pump main unit is detected following a condition where a movable member is attached to and detached from a terminal part in accordance with a differential pressure between high and low pressure sides of the pump main unit. CONSTITUTION:When a flow amount in a pump main unit is increased, a differential pressure between high and low pressure sides of the pump main unit is increased, and by a pressure of oil in a high pressure condition of acting in the second pressure oil chamber 78b of a pressure switch mounting hole 78, a movable member 81 is pressed in a direction of a terminal part 80 and operation-moved against urging force of a spring member 82. In the point of time in which the differential pressure reaches a preset value, the movable member 81 is brought into contact with the terminal part 80 to generate conduction between the terminal part 80 of a pressure switch main unit 79 and a body. Further, when the differential pressure is detected to reach the preset value following connecting action of the pressure switch main unit 79, an idle-up control, in which, for instance, a fuel injection amount during idling operation of an engine is increased, is performed by an engine controller unit.

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial Application Field) The present invention relates to an improvement in a vehicle oil pump that generates drive oil pressure for driving, for example, a vehicle power steering device.

(Prior Art) Generally, vehicles such as automobiles are equipped with hydraulic equipment such as a power steering system, a four-wheel steering system (4WS), an anti-skid brake system (ABS), a suspension control system, etc. There are more and more things happening. The hydraulic circuits of these hydraulic control devices are formed by an independent vehicle oil circulation path different from the engine oil circulation path. An oil pump is interposed in this hydraulic circuit, and each of these hydraulic control devices is driven by the working hydraulic pressure fed from this oil pump.

Incidentally, vane-type oil pumps as shown in FIGS. 4 and 5 have been known for some time now as this type of oil pump. In this case, a cam ring 2 is installed inside the pump body 1. A rotor 3 is rotatably mounted inside the cam ring 2. Furthermore, a plurality of vanes 4 are attached to the outer circumference of the rotor 3 so as to be protrusive and retractable in the radial direction. Also, inside the pump body 1 are these cam rings 2, rotors 3, and vanes 4.
...An oil chamber 5 is formed between them. Then, as the rotor 3 rotates, the vanes 4 are caused to protrude and retract along the cam curved surface of the cam ring 2, thereby drawing oil from an oil reserve tank (not shown) into the oil chamber 5 through the suction port of the pump body 1. Suction, this pump body 1
A pumping action is performed to discharge the fluid to the outside through the discharge port.

Further, a pulley 7 is attached to the shaft end of a drive shaft 6 that rotationally drives the rotor 3 . This pulley 7 is connected via a belt 10 to a crankshaft pulley 9 fixed to the crankshaft of an engine 8, as shown in FIG. The rotor 3 of the pump body 1 is driven to rotate. In FIG. 6, 11 is an alternator drive pulley, 12 is a tension pulley, 13 is an air conditioner compressor drive pulley, 14 is a drive belt installed between this drive pulley 13 and the crankshaft pulley 9, 15 is the tension pre of this drive belt 14.

(Problems to be Solved by the Invention) la In the conventional configuration, the driving force of the engine 8 was transmitted to the pulley 7 of the pump body 1 via the belt 10, so the pump body 1 was connected to the vehicle body side. For installation, use a bracket or belt 10. The pulley 7, the tension pulley 12, and their attachment require a large number of components such as bolts, complicating the structure and increasing costs. Furthermore, when the belt 10 is used for a long period of time, there is a risk of slippage or breakage due to wear, which poses a problem in improving reliability.

Furthermore, since there is a risk that a load due to the tension of the belt 10 will be input to the crankshaft of the engine 8, there is a risk that the frictional force acting on the main bearing of the engine 8 will increase, and the driving efficiency of the engine 8 may decrease. there were. moreover,
Since the engine and a large number of various auxiliary equipment are installed in the limited internal space of the engine room, there is a problem in that the installation of the oil pump in the engine room is restricted in its position. There was a problem that it was difficult to install the pump.

Further, the engine 8 for a vehicle such as a car is maintained at a low rotation speed of about 700 to 800 rpm during idling. Therefore, since the torque generated from the engine 8 is small during this idling operation, when the load on the engine 8 increases, for example when the steering wheel is operated during idling and the oil pump of the power steering device is driven. There was a risk of engine stalling.

This invention was made in view of the above-mentioned circumstances, and it is possible to reduce the number of component parts, simplify the structure in the engine compartment, and improve the reliability of the engine. An object of the present invention is to provide an oil pump for a vehicle that can prevent a decrease in drive efficiency and also prevent the occurrence of engine stalling due to an increase in engine load even when the engine is idling. It is something.

[Structure of the Invention] (Means for Solving the Problems) This invention provides a pump body in which a pump drive shaft is connected to an end of the drive shaft of an engine, and the pump drive shaft is directly driven by the drive shaft of the engine; A control valve body is provided with a control valve body in which a discharge oil passage through which hydraulic oil discharged from the pump body flows and a mounting hole for a flow rate control spool are formed substantially parallel to each other; an orifice that narrows the path area; a bypass passage for discharged oil that is connected to the spool mounting hole; and a bypass passage that moves according to the pressure difference between upstream and downstream of the orifice as the spool in the spool mounting hole moves. a flow rate control mechanism for opening and closing a discharge oil outlet of a passage to control a constant flow rate of oil discharged from the discharge oil passage; a pressure switch mounting hole formed substantially parallel to the bypass passage; and a pressure switch mounting hole. A terminal part fixed to one end of the hole, a movable member mounted in the pressure switch mounting hole so as to be movable in a direction toward and away from the terminal part, and a direction in which the movable member is moved away from the terminal part. a pressure switch body that detects a driving state of the pump body as the terminal portion and the movable member move toward and away from each other according to a pressure difference between a high pressure side and a low pressure side of the pump body; It has been established that

(Function) When the engine is running, the drive shaft of the engine directly drives the drive shaft of the pump body, and the control valve body spools in response to the differential pressure upstream and downstream of the orifice installed in the discharge oil passage. is moved within the spool mounting hole, and as the spool operates, the discharge oil outlet of the bypass passage is opened and closed to control the discharge oil flow rate from the discharge oil passage to a constant level, and the high pressure side and low pressure side of the pump body are The terminal section of the pressure switch body and the movable member are moved toward and away from each other according to the pressure difference between the terminal section and the movable member, and the driving state of the pump body is detected as the terminal section and the movable member move toward and away from each other. .

(Embodiment) An embodiment of the present invention will be described below with reference to FIGS. 1 to 3.

FIG. 1 and FIG. 2 show the main structure of an oil pump. In FIGS. 1 and 2, 21 is an engine;
22 is a crankshaft of this engine 21, and 23 is a main body of an oil pump interposed in an independent vehicle oil circulation path different from the engine oil circulation path.

Further, the casing of this pump body 23 is formed by a pump housing 24 and a cover 25. Further, through holes 24a and 24b are formed in the axial center of the pump housing 24 and the cover 25, respectively. The pump body 2 is inserted into these through holes 24a and 24b.
No. 3 drive shaft 26 is installed in a penetrating state. The drive shaft 26 is connected to the shaft end of the crankshaft 22 of the engine 21, forming a pump drive mechanism in which the crankshaft 22 of the engine 21 directly drives the drive shaft 26 of the pump body 23. In this case, a sprocket 28 for driving a cooked belt 2, which is a toothed belt that rotationally drives a camshaft of a valve mechanism, is attached to the shaft end of the crankshaft 22, for example, with a common key together with the drive shaft 26 of the pump body 23. 29. In this case, both ends of the pump drive shaft 26 have engagement recesses 26a and 2 at the shaft center, respectively.
6b is formed. And this pump drive shaft 26
Engagement recess 26a on the inner end side of the crankshaft 22 in
The shaft end of the crankshaft 22 is removably inserted into the shaft, and in this state, it is prevented from rotating with respect to the crankshaft 22 by a common key 29 together with the sprocket 28 .

Furthermore, a central number of fixing bolt receivers 30 are protruded and recessed into the pump housing 24 of the pump body 23. Fixing bolts 32 are inserted into bolt insertion holes 31 formed in these bolt receivers 30 . The fixing bolt 32 is screwed into a bolt 634 formed on the front case 33 or the like of the engine 21, and the pump housing 24 is removably attached to the engine 21 side. Further, the cover 25 is removably attached to the pump housing 24 by fixing bolts 35.

On the other hand, a bomb housing 24 is provided inside the pump body 23.
A cam ring 36 is formed on the inner surface of the cam ring 36. Inside this cam ring 36 is a rotor 37 and a side plate 3.
8 is installed. This rotor 37 is connected to the pump body 23
For example, the drive shaft 26 is spline-fitted to the drive shaft 26, and is driven to rotate integrally with the drive shaft 26. Furthermore, the side plate 38 is fitted and fixed to the inner surface of the pump housing 24.

Further, a plurality of vanes 39 are provided on the outer circumference of the rotor 37.
... is installed so that it can be protruded and retracted in the radial direction.

In addition, these cam rings 3 are installed inside the pump body 23.
6. An oil chamber 40 is formed between the rotor 37 and the vane 39. Furthermore, this pump body 23 has a third
As shown in the figure, each pair of suction boats 41.41 and discharge boats 42.42 are formed. As the rotor 37 rotates, the vanes 39 are moved to protrude and retract along the cam curved surface of the cam ring 36, so that the pump body 23 is pumped from an oil reserve tank (not shown).
Oil is sucked into the oil chamber 40 through the suction boat 41.41 of the pump body 23, and the oil is sucked into the oil chamber 40 through the suction boat 41.41 of the
A pumping action is performed to discharge water to the outside through the pump.

In addition, the engagement recess 2 at the external extending end of the pump drive shaft 26
6b is the central shaft portion 4 of the outer pulley 43 for driving auxiliary equipment.
4 is removably inserted.

In this case, a knock pin 45 is inserted into the joint between the central shaft portion 44 of the drive pulley 43 and the externally extending end portion of the pump drive shaft 26, and the knock pin 45 prevents rotation between the two. .

Further, a fixing bolt 46 is attached to the central shaft portion 44 of the pulley 43.
A portion 47 is formed for attachment. In this case, pulley 4
A bolt insertion hole for the fixing bolt 46 is provided in the center shaft portion 44 of the pump drive shaft 26 and the center shaft portion of the pump drive shaft 26, and a bolt hole 48 for screwing with the fixing bolt 46 is provided in the shaft end of the crankshaft 22.
are formed respectively. And this fixing bolt 4
6, the pulley 43, pump drive shaft 26, and sprocket 28 are integrally fixed to the shaft end of the crankshaft 22, and as the crankshaft 22 of the engine 21 rotates, the sprocket 28, pump drive shaft 26, pulley 43, etc. An integral rotation section 49 is provided that integrally rotates the components. Further, an inner pulley 50 is fixed to the inner end of the pulley 43 by a fixing bolt 51. This inner pulley 50 is arranged at a position surrounding the pump housing 24 of the pump body 23. Note that a drive belt for driving an air conditioner, for example, is wound around the outer pulley 43, and a drive belt for driving an alternator, for example, is wound around the inner pulley 50.

Further, the pump housing 24 is provided with a floating bearing portion 52 that supports the pump drive shaft 26 so as to be elastically displaceable in the radial direction. The floating bearing portion 52 is formed of, for example, a metal ring member 53 and an O-ring 54, and supports the pump drive shaft 26 elastically in the radial direction with the elastic deformation of the O-ring 54. It looks like this.

Furthermore, each pump drive shaft 26 through hole 24a, 25a of the pump housing 24 of the pump body 23 and the cover 25 is
Oil seals 55, 55 for preventing oil leakage from inside the pump body 23 are attached to the outer end of the inner circumferential surface of the pump body 23, respectively, on the joint surface with the pump drive shaft 26.

Further, the pump housing 24 is provided with a control valve 56 for controlling the operation of the pump body 23. The control valve 56 is spaced an appropriate distance from the pump mechanism parts such as the cam ring 36, rotor 37, vane 39, etc. of the pump body 23 in the direction of the shaft end of the crankshaft 22, as shown in FIG. placed in position. moreover,
The valve body 57 of this control valve 56 has a pump body 2.
A discharge oil passage 58 through which hydraulic oil discharged from the third side flows and a mounting hole 60 for a flow rate control spool 59 are formed substantially parallel to each other. These discharge oil passages 58 and spool mounting holes 60 extend approximately in the radial direction of the pump drive shaft 26 as shown in FIG. placed in a position to avoid

Further, the valve end oil chamber 61 on the pump drive shaft 26 side of the control valve 56 is connected to the discharge portion side of the pump body 23. The valve end oil chamber 61 communicates with the discharge oil passage 58 and the inner end portions of the spool mounting hole 6o, respectively. The outer end of the discharge oil passage 58 is connected to a connecting pipe of an external device such as a power steering device (not shown). Further, a closing cap 62 is screwed onto the outer end of the spool mounting hole 60, and the outer end of the spool mounting hole 60 is closed by the closing cap 62.

Further, the spool 59 is provided inside the spool mounting hole 6o.
is slidably attached. This spool 59 has a protruding portion 63 formed on the inner end side and a spring receiving portion 64 on the outer end side. Further, inside the spool mounting hole 60, a spring member 65 formed of a coil spring is disposed between the closing cap 62 and the spring receiving portion 64 of the spool 59. This spool 59 is connected to the spring member 6
The protruding portion 63 is constantly urged by the urging force of 5 in a direction to bring the protruding portion 63 into contact with a stopper portion 66 formed in the valve end face oil chamber 61. Further, a discharge oil outlet 6 that is opened and closed by the spool 59 is provided on the peripheral wall surface of the spool mounting hole 60.
7 is formed.

This discharge oil outflow port 67 is a bypass passage 6 for discharge oil outflow.
8. The other end of the high pressure passage 68 is connected to the suction boat 41 side of the pump body 23.

Further, an orifice 69 is provided in the discharge oil passage 58 to narrow down the area of the flow passage. One end of a communication passage 70 is connected to the downstream side of the orifice 69 in the discharge oil passage 58 . The other end of this communication path 7° is the spool mounting hole 6.
It is connected to the end on the closing cap 62 side inside o. The hydraulic pressure on the upstream side of the orifice 69 acts on the inner end surface of the spool 59 in the spool mounting hole 60, and the hydraulic pressure on the downstream side of the orifice 69 acts on the outer end surface of the spool 59. The spool 59 in the spool mounting hole 60 moves along the spool mounting hole 60 in accordance with the differential pressure between the upstream and downstream sides of the orifice 69.

Therefore, this control valve 56 has a spool mounting hole 6.
With the operation of the spool 59 in 0, the bypass passage 68
A flow rate control mechanism section 71 is formed to open and close the discharge oil outlet 67 to control the flow rate of oil discharged from the discharge oil passage 58 to a constant level.

Note that 72 is a suction nozzle of the pump body 23, and this suction nozzle 72 is connected to the oil reserve tank side via a connecting pipe. Further, 73 is an oil pan of the engine 21, 74 is a tension pulley of the tightened belt 27, 75 is an oil pump interposed in the engine oil circulation path, and 76 is a main bearing of the crankshaft 22.

Further, as shown in FIG. 4, a pressure switch mounting hole 78 is formed in the valve body 57 of the control valve 56, substantially parallel to the bypass passage. A pressure switch main body 79 is mounted in this pressure switch mounting hole 78 . This pressure
The switch body 79 includes a terminal portion 80 fixed to one end side of the pressure switch mounting hole 78, and a movable member mounted within the pressure switch mounting hole 78 so as to be movable in directions toward and away from the terminal portion 80. 81 and a spring member 82 formed by a coil spring that biases the movable member 81 in a direction away from the terminal portion 80. In this case, one end of a lead wire 83 is connected to the terminal portion 80. The other end of this lead wire 83 is connected to, for example, an engine control unit (ECU) (not shown) formed by a microcomputer and its peripheral circuits. Furthermore, this terminal portion 80 is inserted into a mounting hole 85 of a cylindrical body 84 formed of an insulator such as synthetic resin. A terminal portion 8 is provided in the mounting hole 85 of this cylinder body 84.
A sealing material 86 such as rubber or resin is injected into the opening on the connection side between the terminal unit 80A and the lead wire 83, and the integrated terminal unit 80A is sealed with a snap ring 87 into the pressure switch mounting hole. It is fixed to one end side of 78. In addition, 88 is this terminal unit 80
This is an O-ring placed on the outer periphery of A.

Furthermore, the movable member 81 is formed by a rod 89 made of a conductive material such as metal, and a cap 90 attached to one end of the rod 89. in this case,
The other end side of the pressure switch mounting hole 78 (terminal part 8o
A small-diameter rod #1n manhole 91 is formed on the opposite side), and a rod 89 is inserted into this rod insertion hole 91 so as to be slidable in the axial direction. Furthermore, cap 9o
A flange-shaped spring receiving portion 92 is formed in the flange-like spring receiving portion 92 . A spring member 82 is disposed between the spring receiving portion 92 of the cap 90 and the terminal unit 80A.

Further, one end portion of the low pressure oil passage 93 is connected to the first hydraulic chamber 78a on the terminal portion 80 side of the pressure switch mounting hole 78. The other end of this low pressure oil passage 93 is the bypass passage 6
It is connected to the downstream side of 8. Furthermore, one end of a high-pressure oil passage 94 is connected to the second hydraulic chamber 78b on the other end side of the pressure switch mounting hole 78 (on the terminal end side of the rod insertion hole 91). The other end of this high pressure oil passage 94 is connected to the inside of the spool mounting hole 60. Then, the movable member 81 moves toward and away from the terminal portion 80 according to the pressure difference between the high pressure side and the low pressure side of the pump body 23, and as the movable member 81 and the terminal portion 80 move toward and away from each other. The pressure state of the discharge oil passage 58 is detected.

Next, the operation of the above configuration will be explained.

First, when the engine 21 is operating, the crankshaft 22, the sprocket 28, the pump drive shaft 26, and the pulley 4
An integral rotating part 49 such as 3.50 is integrally driven to rotate. Further, as the pump drive shaft 26 rotates, the rotor 37 is rotationally driven, and as the rotor 37 rotates, the vanes 39 are moved to protrude and retract along the cam curved surface of the cam ring 36. In this case, the oil chamber 4 between the cam ring 36, rotor 37 and vane 39...
0 becomes negative pressure as the rotor 37 rotates, so it is connected from an oil reserve tank (not shown) maintained at atmospheric pressure to the connecting pipe, the suction nozzle 72 of the pump body 23,
Oil is sucked into the oil chamber 40 by sequentially valving the suction boats 41, 41. The high-pressure discharge oil compressed within this oil chamber 40 is discharged from the discharge boat 42 of this pump body 23,
42, a series of pump actions are performed in which the oil is discharged through the valve end oil chamber 61 of the control valve 56 and the discharge oil passage 58 to a connecting pipe of an external device on the outside.

Also, during operation of this pump body 23, the spool mounting hole 6
The spool 59 in the spool 59 moves along the spool mounting hole 60 according to the differential pressure upstream and downstream of the orifice 69 of the bullet mechanism 71. In this case, when the flow rate of the oil discharged from the pump body 23 is small, the spool 59 moves the protrusion 63 into the valve end oil chamber 6 by the urging force of the spring member 65.
It is held in a state where it is biased in the direction of contacting the first stopper portion 66 . In this state, the discharge oil outlet 67 of the bypass passage 68 is held in a closed state by the spool 59, so that all the discharge oil from the pump body 23 is forced to the outside via the discharge oil passage 58.

Further, as the 'tttm of the oil discharged from the pump body 23 increases, the differential pressure between the upstream and downstream sides of the orifice 69 increases, so the spool 59 in the spool mounting hole 60 moves away from the valve end oil chamber 61. As the spool 59 moves within the spool mounting hole 60, the discharge oil outlet 67 of the bypass passage 68 is opened. When the discharge oil outlet 67 is opened in this manner, the high pressure oil in the valve end oil chamber 61 is introduced into the suction port 41 of the pump body 23 on the low pressure side through the bypass passage 68. Therefore, when the flow rate of oil discharged from the pump body 23 increases, unnecessary discharge oil can be circulated through the bypass passage 68 in the pump body 23, so that the flow rate of oil discharged from the discharge oil passage 58 can be controlled to be constant. be able to.

Furthermore, during operation of this pump body 23, the bypass passage 6
Hydraulic pressure in a low pressure state on the downstream side (suction side) of 8 or low pressure oil line 9
3 through the terminal portion 80 of the pressure switch mounting hole 78
It acts within the first hydraulic chamber 78a on the side, and the spool mounting hole 6
0 (discharge side) acts in the second hydraulic chamber 78b of the pressure switch mounting hole 78 through the high pressure oil passage 94. Therefore, the movable member 81 moves toward and away from the terminal portion 80 according to the pressure difference between the high pressure side and the low pressure side of the pump body 23. That is, when the flow rate of the pump body 23 is low, the pressure difference between the high pressure side and the low pressure side of the pump body 23 is maintained in a small state. In this state, the movable member 81 is held apart from the terminal portion 80 by the biasing force of the spring member 82, so the terminal portion 80 of the pressure switch body 79 is held in an open state.

Furthermore, when the flow rate of the pump body 23 increases, the pump body 2
3, the pressure difference between the high pressure side and the low pressure side increases. In this state, the movable member 81 is pressed toward the terminal portion 80 by the high-pressure hydraulic pressure acting in the second hydraulic chamber 78b of the pressure switch mounting hole 78, and the movable member 81 resists the biasing force of the spring member 82. The terminal section 80 is moved in the direction of the terminal section 80. Then, when the pressure difference between the high pressure side and the low pressure side of the pump body 23 reaches the set value, the movable member 81
contacts the terminal portion 80, and conduction occurs between the terminal portion 80 of the pressure switch main body 79 and the body. moreover,
As the terminal section 80 of the pressure switch body 79 and the movable member 81 are connected, the engine control unit detects that the pressure difference between the high pressure side and the low pressure side of the pump body 23 has reached a set value. Then,
For example, idle up control is performed by the engine control unit to increase the fuel injection amount while the engine 21 is idling. Therefore, even if the rotation speed of the engine 21 is maintained in a low rotation range, such as during idling, when the load on the engine 21 increases, such as when the oil pump of the power steering device is driven, In addition, since the torque generated from the engine 21 can be increased accordingly, it is possible to reduce the risk of the engine stalling as in the conventional case, for example, when the steering wheel is operated during idling.

Therefore, in the above configuration, the drive shaft 26 of the pump body 23 is connected to the shaft end of the crankshaft 22 of the engine 21, and when the engine 21 is driven, the pump body 26 is integrally connected to the crankshaft 22 of the engine 21. Since the drive shaft 26 of the engine 21 is directly driven, the belt 1o, pulley 7, and
Tension pulleys 12 and their attachment can eliminate numerous components such as bolts.

Therefore, the number of component parts can be reduced compared to the past, and the configuration inside the engine room can be simplified. Furthermore, since there is no need to use the belt 1o, there is no risk of slipping or breakage due to wear of the belt 1o as in the prior art, and reliability can be improved. In addition, since there is no possibility that the crankshaft 22 of the engine 21 is subjected to a manual load due to the tension of the belt 1o, the engine 21
It is possible to prevent an increase in the frictional force acting on the main bearing 76 of the engine 21, thereby preventing a decrease in driving efficiency of the engine 21. Furthermore, since the pump body 23 can be attached to the shaft end of the crankshaft 22 of the engine 21, it is easy to install another oil pump in a limited internal space in the engine room. A new oil pump can be installed.

Furthermore, the control valve main body 57
The spool 59 is moved within the spool mounting hole 60, and as the spool 59 moves, the discharge oil outlet 67 of the bypass passage 68 is opened and closed, so that the discharge oil flow rate from the discharge oil passage 58 can be controlled at a constant level. can be done. Therefore, the t pressure I11 of the power steering device, etc., which is driven by the discharge hydraulic pressure from this oil pump.
The controlled equipment can be operated stably.

Further, the terminal portion 80 of the pressure switch body 79 and the movable member 81 are moved toward and away from each other according to the pressure difference between the high pressure side and the low pressure side of the pump body 23, and the terminal portion 80 and the movable member 81 are moved toward and away from each other. Accordingly, since the driving state of the pump body 23 is detected, this pump body 23
When the load on the engine 21 increases, the engine control unit can perform, for example, idle-up control to increase the fuel injection amount during idle-link operation of the engine 21. Therefore, even if the rotational speed of the engine 21 is maintained in a low rotational speed range, such as during idling, when the load on the engine 21 increases, such as when the oil pump of the power steering device is driven, Since the torque generated from the engine 21 can be correspondingly increased, it is possible to prevent the engine from stalling due to an increase in the load on the engine 21 even when the engine 21 is idling. Furthermore, a pressure switch mounting hole 78 is formed in the valve body 57 of the control valve 56 (approximately parallel to the entrance passage), and this pressure switch mounting hole 7
Since the pressure switch main body 79 is mounted within the control valve 56, the overall size can be reduced compared to the case where the pressure switch main body 79 is provided separately from the control valve 56.

It should be noted that the present invention is not limited to the above-mentioned embodiments, and it goes without saying that various modifications can be made without departing from the gist of the present invention.

〔Effect of the invention〕

According to this invention, when the engine is driven, the pump body is provided which directly drives the drive shaft integrally with the engine drive shaft, so the number of component parts of the pump body can be reduced, and the configuration in the engine room can be simplified. In addition, it is possible to improve reliability and prevent a decrease in engine drive efficiency. Furthermore, the spool of the control valve body is moved within the spool mounting hole according to the differential pressure between the upstream and downstream sides of the orifice installed in the discharge oil passage, and the discharge oil outlet of the bypass passage is opened and closed as the spool moves. Since the flow rate control mechanism is provided, the flow rate of oil discharged from the discharge oil passage can be controlled to be constant, and hydraulic control equipment such as a power steering device can be stably operated. In addition, we have installed a pressure switch body that detects the driving state of the pump body according to the pressure difference between the high-pressure side and low-pressure side of the pump body, so even when the engine is idling, engine stalling due to an increase in engine load can be prevented. It is possible to prevent the occurrence of (if).

[Brief explanation of the drawing]

Figures 1 to 4 show one embodiment of the present invention, in which Figure 1 is a schematic cross-sectional view of the main parts of the oil pump + a cross-sectional view showing a thin acid, Figure 2 is a vertical cross-sectional view of the same, and Figure 3 is a cross-sectional view of the main parts of the oil pump. The figure is a schematic configuration diagram for explaining the pumping action of the oil pump, FIG. 4 is a vertical cross-sectional view showing the schematic III configuration of the pressure switch, and FIGS. 5 to 7 (showing the conventional f11, Fig. 5 is a longitudinal cross-sectional view of the oil pump, Fig. 6 is a cross-sectional view thereof, and Fig. 7 is a schematic configuration diagram for explaining the driving state of the oil pump. 21...Engine, 22... Crankshaft, 23-・
・Pump body, 26... Drive shaft, 56... Control〕<
Lube, 57...Valve body, 58...Discharge oil passage,
59...Spool for flow rate control, 60...Spool mounting hole, 67...Discharge oil outlet, 68...No.
(Inlet passage, 69...orifice, 71...48 parts of flow rate controller, 78...pressure switch mounting hole, 7...
Pressure switch body, 80...Terminal section, 81.
...Movable member, 82...Spring member.

Claims (1)

[Claims] A pump body in which a pump drive shaft is connected to an end of the drive shaft of an engine, and the pump drive shaft is directly driven by the drive shaft of the engine, and a discharge oil passage and flow rate through which hydraulic oil discharged from the pump body side flows. A control valve body in which a control spool mounting hole is formed substantially parallel to the control valve body, an orifice interposed in the discharge oil passage to narrow the flow area of the discharge oil passage, and a discharge oil connected to the spool attachment hole. A bypass passage for outflow and a discharge oil outlet from the discharge oil passage are opened and closed in accordance with the operation of the spool in the spool mounting hole that moves according to the differential pressure between upstream and downstream sides of the orifice. A flow rate control mechanism section that controls oil flow rate to a constant level, a pressure switch mounting hole formed substantially parallel to the bypass passage, a terminal section fixed to one end side of the pressure switch mounting hole, and the pressure switch mounting hole. A movable member is mounted inside the pump body so as to be movable in a direction toward and away from the terminal portion, and a spring member biases the movable member in a direction away from the terminal portion. 1. A vehicle oil pump comprising: a pressure switch body that detects a driving state of the pump body as the terminal portion and a movable member move toward and away from each other according to a pressure difference between the terminal portion and the movable member.