JPH03134280A - Oil pump for vehicle - Google Patents

Abstract

PURPOSE:To prevent an excessive load from acting on a bearing part in a pump drive shaft by providing a floating bearing part, which elastically displaceably supports the pump drive shaft in a radial direction, in a housing of an oil pump main unit. CONSTITUTION:A constitution is provided such that a floating bearing part 52, which elastically displaceably supports a pump drive shaft 26 in a radial direction, is provided in a pump housing 24 so as to elastically displaceably support the pump drive shaft 26 in the radial direction following the elastic deformation of an O ring 54 of this bearing part 52. In this way, for instance, at the time of manufacturing an oil pump, a manufacturing error or the like is generated, and at the time of assembly work, in the case of generating eccentricity between the axial center of the pump drive shaft 26 and the axial center of a pump drive shaft through hole 24a in the pump housing 24, an amount of this eccentricity can be absorbed by the elastic deformation of the O ring 54 in the floating bearing part 52. Consequently, concentration accuracy between the pump drive shaft 26 and the pump drive shaft through hole 24a in the housing 24 can be surely maintained.

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, hydraulic control devices such as a power steering device, a four-wheel steering system (4WS), an anti-skid brake system (ABS), a suspension control device, etc. are installed in vehicles such as automobiles. are increasing. 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 move to protrude and retract along the cam curved surface of the cam ring 2, thereby allowing oil to flow from the oil reserve tank (not shown) into the oil chamber 5 through the suction port of the pump body 1. 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/saucer drive pulley, and 14 is a drive belt installed between this drive pulley 13 and the crankshaft pulley 9. , 15 is a tension pulley of this drive belt 14.

(Problems to be Solved by the Invention) In the conventional configuration described above, the driving force of the engine 8 is transmitted to the pulley 7 of the pump body 1 via the belt 10, so the pump body 1 is placed on the side of the vehicle body. The mounting of the belt 10, the pulley 7, the tension pulley 12, and the mounting of these components requires a large number of components such as bolts, which complicates the configuration and increases costs. Ta. 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.

This invention was made in view of the above circumstances, and it is possible to reduce the number of component parts, simplify the configuration in the engine room, improve reliability, and improve engine drive efficiency. In addition, it is possible to reliably maintain concentricity between the pump drive shaft and the through hole of the pump drive shaft in the housing of the oil pump body, thereby preventing excessive load on the bearing part of the pump drive shaft. An object of the present invention is to provide a vehicle oil pump that can prevent the oil pump from operating.

[Structure of the Invention] (Means for Solving the Problems) This invention connects the pump drive shaft of the oil pump body to the drive shaft of the engine body, fixes the housing of the oil pump body to the housing side of the engine body, and The housing of the oil pump body is provided with a floating bearing portion that supports the pump drive shaft so as to be elastically displaceable in the radial direction.

(Function) When the engine is driven, the drive shaft of the pump body is directly driven integrally with the drive shaft of the engine, and the axis of the pump drive shaft and the axis of the pump drive shaft through hole of the housing of the oil pump body are aligned. If eccentricity occurs between the oil pump and the oil pump, the amount of eccentricity is absorbed by the elastic deformation of the floating bearing part, and the concentric accuracy between the pump drive shaft and the pump drive shaft through hole of the housing of the oil pump body is maintained reliably. This prevents an excessive load from being applied to the bearing portion of the pump drive shaft.

(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, at the shaft end of the crankshaft 22, there is a sprocket 28, which is a toothed belt for rotationally driving a camshaft of a valve mechanism, and a sprocket 28 for driving a toothed belt 27, and a common key 29 together with a drive shaft 26 of the pump body 23. Fixed by In this case, both ends of the pump drive shaft 26 have engagement recesses 26a at the shaft center, respectively.
26b is formed. And this pump drive shaft 2
Engagement recess 26 on the inner end side on the crankshaft 22 side in 6
The shaft end of the crankshaft 22 is removably inserted into a,
In this state, the sprocket 28 and the sprocket 28 are prevented from rotating relative to the crankshaft 22 by a common key 29.

Further, a plurality of fixing bolt receivers 30 are provided protruding from the pump/1 housing 24 of the pump body 23. Fixing bolts 32 are inserted into bolt insertion holes 31 formed in these bolt receivers 30 . This fixing bolt 32 is screwed into a bolt hole 34 formed in a front case 33 or the like of the engine 21, and the pump/1 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 pump 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. Further, the side plate 38 is fitted and fixed to the inner surface of the pump/1 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 ports 41.41 and discharge ports 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 surface 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-shaped bearing member 53 and an O-ring 54, and supports the pump drive shaft 26 so as to be elastically displaceable in the radial direction as the O-ring 54 is elastically deformed. It is supposed to be done. Incidentally, oil grooves are formed on the inner circumferential surface of the ring-shaped bearing member 53 at multiple locations in the circumferential direction to communicate between the leakage oil inflow chambers formed by the gaps on both sides of the ring-shaped bearing member 53. Therefore, leakage oil from the pump mechanism section of the pump body 23 can be returned to the suction port 41 side through this oil groove.

Further, through holes 24a and 25 of each pump drive shaft 26 of the pump housing 24 of the pump body 23 and the cover 25 are provided.
Oil seals 55, 55 for preventing oil leakage from inside the pump body 23 are respectively attached to the outer end of the inner circumferential surface of the pump body 23 at 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 is communicated with the discharge oil passage 58 and the inner end of the spool necking hole 60, 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 sprue 59 is slidably mounted inside the spool mounting hole 60. 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 a spring member 65.
The protruding portion 63 is constantly urged by the urging force 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 67 that is opened and closed by the spool 59 is provided on the peripheral wall surface of the spool mounting hole 60.
is formed.

This discharge oil outflow port 67 is a bypass passage 6 for discharge oil outflow.
8. The other end of this bypass passage 68 is connected to the suction port 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 of the spool 59 in the spool mounting hole 6o, 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 6o 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.

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
The integral rotating parts 49 such as 3 and 50 are 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 via suction boats 41, 41 in turn. The high-pressure discharge oil compressed within this oil chamber 4o is discharged from the discharge port 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 flow control mechanism 71 moves along the nospool mounting hole 60 according to the differential pressure between the upstream and downstream sides of the orifice 69 of the flow rate control mechanism section 71. In this case, when the flow rate of oil discharged from the pump body 23 is small, the spool 59 is moved by the spring member 65.
The protruding portion 63 is held in a biased state by the biasing force in a direction to bring it into contact with the stopper portion 66 of the valve end oil chamber 61. 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.

Furthermore, as the flow rate of the oil discharged from the pump body 23 increases, the differential pressure between the upstream and downstream sides of the orifice 69 increases.
Move away from 1. 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 way, the high pressure oil in the valve end oil chamber 61 is introduced into the suction boat 41 side of the pump body 23 on the low pressure side through the bypass passage 68.

Therefore, when the flow rate of discharged oil from the pump body 23 increases, unnecessary discharged oil is removed from the bypass passage 6 in the pump body 23.
Since the oil can be circulated through the discharge oil passage 58, the flow rate of oil discharged from the discharge oil passage 58 can be controlled to be constant.

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 driving force of the engine 21 is transferred to the pump body 23 via the belt 10 (shown in FIG. 10).
Belt 10 and pulley 7 required when transmitting to the side
, tension pulley 12 and their attachment can omit 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 10, there is no risk of slippage or breakage due to wear of the belt 10 as in the conventional case, and reliability can be improved. Further, since there is no risk of the load due to the tension of the belt 10 being input to the crankshaft 22 of the engine 21, 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, even if another oil pump is installed in the limited internal space of the engine room. It is possible to easily install a new oil pump.

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. Because it is supported so that it can be elastically displaced, for example, manufacturing errors may occur during the manufacture of the oil pump.
Pump drive shaft penetration port 24a of pump housing 24 of No. 3
When an eccentricity occurs between the axis of the floating bearing part 52 and the axis of the floating bearing part 52, the eccentricity in the ζ direction can be absorbed by elastic deformation of the 01J ring 54 of the floating bearing part 52. Therefore, the concentric precision between the pump drive shaft 26 and the pump drive shaft through hole 24a of the 71 housing 24 of the oil pump main body 23 can be maintained reliably, so that an excessive load is not applied to the bearing portion of the pump drive shaft 26. This can be prevented. In addition, for example, due to wear between the crankshaft 22 of the engine 21 and the main bearing 76, the axial center of the pump drive shaft 26 and the oil pump main body 2
3. Pump drive shaft penetration port 24 of Ponzino 1 housing 24
Even if eccentricity occurs between the shaft center of the pump drive shaft 26 and the shaft center of the pump drive shaft 26, the eccentricity between the two can be similarly absorbed by the elastic deformation of the O-ring 54 of the floating bearing section 52. It is possible to prevent an excessive load from being applied to the

Note that this invention is not limited to the above embodiments.

For example, as in the second embodiment shown in FIG. 4, a ring-shaped bearing mounting groove 81 is formed on the inner peripheral surface of the pump drive shaft through hole 25a of the cover 25 of the pump body 23 and communicates with the mounting groove of the oil seal 55. It is also possible to form a structure in which a floating bearing part 82 is mounted in this bearing mounting groove 81. In this case, the floating bearing part 82 is made of, for example, a metal ring-shaped bearing member 83 and an O-ring 8 made of an elastic body mounted in a ring-shaped O-ring mounting groove 83a formed on the outer peripheral surface of this bearing member 83.
4, and supports the pump drive shaft 26 so as to be elastically displaceable in the radial direction as the O-ring 84 is elastically deformed. Further, an oil groove 83b is formed on the inner circumferential surface of the ring-shaped bearing member 83, and communicates between the leaked oil inflow chambers formed by the gaps on both sides of the ring-shaped bearing member 83.
The leakage water from the pump mechanism can be returned to the suction port 41 side through this oil groove 83b.

Therefore, in this case as well, the same effects as in the first embodiment can be obtained.

Further, as in the third embodiment shown in FIG. 5, a floating bearing portion 91 is formed by integrally molding the ring-shaped bearing member 83 and the O-ring 84 of the second embodiment from an elastic material such as synthetic resin.
It is also possible to provide a structure in which the floating bearing portion 91 is mounted in the bearing mounting groove 81 of the second embodiment. In this case, an oil groove 91a is also formed on the inner circumferential surface of the floating shaft bearing part 91, which communicates between the leaked oil inflow chambers formed by the gaps on both sides of the floating bearing part 91. Leakage oil from the side of the pump machine can be returned to the suction boat 41 side through this oil groove 91a.

Further, FIGS. 6 and 7 show a fourth embodiment.

This includes pump drive shaft through holes 24a and 25 in the pump housing 24 and cover 25 of the pump body 23, respectively.
Ring-shaped bearing mounting grooves 101 and 102 are formed on the inner circumferential surface of a, and a ring-shaped bearing member 83 and an O-ring 84 of the second embodiment are respectively installed in these bearing mounting grooves 101 and 102.
For example, a structure may be adopted in which a floating bearing portion 103 integrally molded from an elastic material such as synthetic resin is attached. In this case, the floating bearing part 10 also has an inner circumferential surface of the floating bearing part 103.
An oil groove 104 is formed that communicates between the leaked oil inflow chambers formed by the gaps on both sides of the pump body 23, and the leaked oil from the pump mechanism section of the pump body 23 is returned to the suction boat 41 side through this oil groove 104. is now possible. Further, notches 105, 105 with chamfered corners are formed on both sides of the inner peripheral surface of the floating bearing portion 103, and these notches 105. ．． 105 prevents both sides of the inner peripheral surface of the floating bearing part 103 from being caught in the gap S between the pump drive shaft 26 and the cover 25 (or the pump housing 24) when the floating bearing part 103 is deformed. There is.

Therefore, even with the above configuration, the same effects as in the first embodiment can be obtained, and in this case, the floating bearing portion 103 is particularly attached to the pump body 23 and the cover 25. Therefore, the pump drive shaft 26 can be supported more stably. Therefore, for example, when assembling the oil pump, each pump drive shaft through-hole 2 of the pump 7X housing 24 of the oil pump main body 23 and the cover 25 is
The amount of eccentricity between the inner circumferential surfaces of 4a and 25a and the axis can be reduced.

Furthermore, it goes without saying that various other modifications can be made without departing from the gist of the invention.

[Effects of the Invention] According to the present invention, the pump drive shaft of the oil pump body is connected to the drive shaft of the engine body, the housing of the oil pump body is fixed to the housing side of the engine body, and the pump is connected to the housing of the oil pump body. A floating bearing section that supports the drive shaft so that it can be elastically displaced in the radial direction is provided, which reduces the number of component parts, simplifies the configuration inside the engine room, and improves reliability. This makes it possible to prevent a drop in engine drive efficiency, and also to ensure concentricity between the pump drive shaft and the through hole of the pump drive shaft in the housing of the oil pump main body. It is possible to prevent excessive loads from being applied to the bearing parts of the bearings.

[Brief explanation of the drawing]

1 to 3 show a first embodiment of the present invention, in which FIG. 1 is a cross-sectional view showing a schematic configuration of the main parts of an oil pump, FIG. 2 is a longitudinal sectional view of the same, and FIG. The figure is a schematic configuration diagram for explaining the pumping action of the oil pump, and FIG. 4 is a longitudinal sectional view of the oil pump showing a second embodiment of the invention.
FIG. 5 is a longitudinal cross-sectional view of the main parts of a third embodiment of the invention, FIGS. 6 and 7 are a fourth embodiment of the invention, and FIG. 6 is a longitudinal cross-section of an oil pump. 7 is a longitudinal cross-sectional view of the main parts, and FIGS. 8 to 1O show a conventional example. FIG. 8 is a vertical cross-sectional view of the oil pump, FIG. FIG. 10 is a schematic configuration diagram for explaining the driving state of the oil pump. 21...Engine, 22...Crank Idl, 23
- Pump body, 24... Pump housing, 25
...Cover 26...Kaku1JJITo, 33...
Front case, 52.82, 91, 103... Floating bearing part, 5383... Ring-shaped bearing member, 54.84
...0 ring.

Claims (1)

[Claims] The pump drive shaft of the oil pump body is connected to the drive shaft of the engine body, the housing of the oil pump body is fixed to the housing side of the engine body, and the pump drive shaft is radially connected to the housing of the oil pump body. A vehicle oil pump characterized by having a floating bearing part that is elastically displaceably supported.