JPH0324904Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a vane pump, and particularly to a vane pump suitable for use in a front and rear wheel drive coupling device of a vehicle.

[Conventional technology]

In general, in a four-wheel drive (4WD) vehicle where the front and rear wheels are driven by the same engine, there is a slight difference in the effective radius of the front and rear tires, and due to differences in the rolling path of the wheels when turning. Since the tires slip and unreasonable force is applied to the drive system, it is necessary to provide a means to prevent this.

For this reason, conventionally, in full-time four-wheel drive vehicles, even if there is a difference in rotational speed between the first rotating shaft that transmits driving force to the front wheels and the second rotating shaft that transmits driving force to the rear wheels, the drive A differential device called a center differential is used to transmit power, which is disadvantageous compared to part-time 4-wheel drive vehicles in terms of weight, size, and cost. There are cases where four-wheel drive cannot be achieved when a drive is required, and the device becomes even more complex, such as requiring a deflock mechanism.

On the other hand, many part-time 4-wheel drive vehicles do not have a center differential, and if there are problems with 4-wheel drive such as tight corner braking caused by cornering, the driver must operate 2-wheel drive. However, there is a drawback that the driving operation is complicated.

Therefore, a four-wheel drive coupling device may be considered that includes a vane pump type coupling mechanism that can mutually transmit driving force between the first rotation shaft and the second rotation shaft.

In a four-wheel drive coupling device equipped with such a vane pump type coupling mechanism, the vane pump is the first
As shown in FIGS. 0 and 12, the main parts thereof include a housing 20, a rotor 19 connected to a rotating shaft and housed in the housing 20, and a rotor 19 attached to an outer circumferential surface 19a of the rotor 19 and an inner circumference of the housing 20. A plurality of pump chambers 36 to 3 are formed by being surrounded by a large number of vanes 18' that are in sliding contact with the surface 20d, the rotor 19, the housing 20, and the vanes 18'.
8, and a pair of suction and discharge ports 2 that suck and discharge hydraulic oil into each of the plurality of pump chambers 36 to 38.
2 to 27 (see FIG. 4), and is in sliding contact with the inner circumferential surface 20d of the housing 20.
The tips 18'a and 18'c have a ridge line (maximum radius) in the center of the rotation direction B.
(see Fig. 10), or an edge shape whose radius increases as it goes from the high-pressure discharge-side suction and discharge port 24 to the low-pressure suction-side suction and discharge port 23 (see Fig. 10). 12th
(see figure).

Note that the discharge side and the suction side of the suction and discharge ports are reversed depending on the relative rotation direction of the rotor 19 and the housing 20, but an example in the rotation direction B shown in each figure will be described below.

The bottom part 18'b of the vane 18' checks the discharge pressure _P1 from the discharge side suction and discharge port 24 at the check valve 3.
2 and the working pressure P ₂ reduced through the flow path 40
(<P ₁ ), the tip 18'a of the vane 18'
is urged toward the inner peripheral surface 20d of the housing 20.

[Problem that the invention attempts to solve]

However, in such a conventional vane pump, when a small centrifugal force acts on the vane 18' when the rotational speed of the rotor 19 is low, that is, when the rotation speed of the rotor 19 is low,
When the pressing force of the tip 18'a of the vane 18' against the inner circumferential surface 20d of the housing 20 is small, if the vane 18' is once separated from the housing 20 at the discharge side suction/discharge port 24, the vane 1
The pressure distributions at the curved tip 18'a and the edge-shaped tip 18'c of 8' are as follows.
As shown in Figures 1 and 13, the circumferential position
The pressure is not sufficiently small between A ₁ and _{A 2} .

This allows the vane 18' and the housing 20
(cam ring part 20a) cannot be completely attached,
Between the tip portions 18'a, 18'c and the housing 20
High-pressure hydraulic oil from the discharge-side suction-discharge port 24 leaks to the low-pressure suction-side suction-discharge port 23 from between.

After that, the vane 18' is moved to the suction side suction discharge port 23.
When approaching the vane 18', the vane 18' is pushed up and
There is no time left, and the pressure at the discharge side suction and discharge port 24 increases.

Since such a phenomenon occurs for each vane 18', there is a problem that pulsations occur in the discharge pressure discharged from the vane pump.

That is, when the relative rotation speed between the rotor 19 and the housing 20 is low, the flow rate is small, so the pressure P ₁ (its average pressure) at the suction side suction discharge port 23 and the pressure P ₂ at the discharge side suction discharge port 24 are small. Therefore, the ratio (/S ₂ ) of P 2 does not decrease sufficiently, and therefore ≧P ₂ .

Therefore, in a four-wheel drive coupling device equipped with such a conventional vane pump, since it is mainly used at extremely low rotation speeds (30 rpm or less), the flow rate is small and there is no flow between the vane 18' and the cam ring part 20a. 〓There is a gap, which causes the oil pressure to drop extremely. At this time, the hydraulic pressure P ₂ for pushing up the vane 18' also decreases, causing the above-mentioned pulsation, resulting in the problem that the output torque periodically fluctuates greatly as shown in FIG. 14.

The present invention aims to solve these problems, and aims to provide a vane pump that can reliably prevent fluctuations in discharge oil pressure when the rotor rotates at low speed.

[Means for solving problems]

Therefore, the vane pump of the present invention includes a housing, a rotor that is housed in the housing and rotates relative to the housing by a rotating shaft, and a cam ring portion of the housing that is attached to the outer peripheral surface of the rotor. A pair of pumps comprising a large number of vanes slidingly in contact with the inner peripheral surface and a plurality of pump chambers formed by being surrounded by the rotor, housing, and vanes, and sucking and discharging hydraulic oil into each of the plurality of pump chambers. A suction and discharge port is formed, and the tip of the vane that is in sliding contact with the inner circumferential surface of the housing receives low pressure from the high pressure discharge side of the suction and discharge port during relative rotation between the rotor and the housing. It is characterized by being formed into an edge shape whose radius decreases as it goes toward the suction side.

[Effect]

In the above-mentioned vane pump of the present invention, the vane is pressed against the inner circumferential surface of the housing so that there is no gap between the tip of the vane and the inner circumferential surface of the housing, and the discharged hydraulic pressure is maintained at a high level. is,
Fluctuations in this oil pressure become smaller.

[Example]

Hereinafter, a practical example of the present invention will be explained with reference to the drawings. Figures 1 to 9 show a four-wheel drive coupling device equipped with a vane pump as an example of the present invention, and Figure 1 shows the present device. Front view of the main parts of the 2nd
3 is a front view showing the vane, FIG. 4 is a cross-sectional view of the device, and FIG. 5 is a schematic diagram showing the drive system of the vehicle.
Fig. 6 is a longitudinal sectional view of the device, Fig. 7 is a graph for explaining the operation of the device, Fig. 8 is a front view of the main parts of the device showing a modification of the vane, and Fig. 9 is a graph for explaining the operation of the device. It is a graph for explaining the effect in a modified example.

As shown in FIG. 5, a transmission 2 is connected to an engine 1 placed horizontally, and driving force is taken out from a drive gear (or 4-speed counter gear) 4 attached to an output shaft 3 of the transmission 2, which is connected by a vane pump type. The signal is transmitted to the gear cam ring 20e of the four-wheel drive coupling device main body 13 as a mechanism.

The gear cam ring 20e rotationally drives the housing 20, and the driving force is transmitted from the gear 7 to the differential device 10 for the front wheels 9 via the first rotating shaft (outer shaft) 11 connected to the housing 20. and the front wheels 9 are driven.

That is, the driving force transmitted to the four-wheel drive coupling device main body 13 is transmitted directly to the first rotating shaft 11 via the gear cam ring 20e, and further,
The signal is transmitted to the front wheels 9 via a gear 7 and a differential 10.

The driving force passing through this four-wheel drive coupling device main body 13 is transferred to a second rotary shaft coaxially disposed on the first rotating shaft.
The bevel gear mechanism 1 converts the direction of rotation.
The driving force is transmitted to the differential gear 17 for the rear wheels 16 via the rear wheels 5 and 15', and drives the rear wheels 16.

This four-wheel drive coupling device main body 13 includes a first,
As shown in Figures 4 and 6, it is composed of a vane pump VP as a hydraulic pump (hydraulic coupling mechanism) and a hydraulic circuit 21 attached to it, and the rotor 19 of the vane pump VP applies driving force to the rear wheels 16. A cam ring portion 20 a and a flange 20 c that constitute the housing 20 are connected to the first rotating shaft 11 that transmits driving force to the front wheels 9 .

This vane pump VP as a hydraulic pump has
A large number (10 holes in this case) of holes 19b are formed at equal intervals in the circumferential direction on the outer peripheral surface 19a of the rotor 19, and each of the large number of holes 19b is provided on the inner peripheral surface of the cam ring portion 20a. A vane 18 that can be slidably contacted with 20d is fitted.

Furthermore, each part is formed such that the distance between the cover 20b of the housing 20 and the vanes 18 and rotor 19 in the axial direction is equal to or less than a predetermined value, so that the oil film does not break.
Similarly, each part is formed so that the axial distance between the pressure retainer 20f, the vane 18, and the rotor 19 is equal to or less than a predetermined value. The sum of these values is set to be less than or equal to a predetermined value.

Further, the vane pump VP discharges an amount of oil proportional to its rotation speed, and there is a relative rotation between the rotor 19 and the cam ring part 20a, that is,
When relative rotation occurs between the first rotating shaft 11 and the second rotating shaft 14, it functions as a hydraulic pump and generates hydraulic pressure.

By blocking the discharge ports of the vane pump VP (corresponding to the suction and discharge ports 22 to 27 at the tips of the vanes 18 in the relative rotational direction with respect to the housing 20), the rotor 19 and the cam ring portion 20a are connected to each other by the static pressure through the oil. It becomes like a rigid body and rotates as one.

Therefore, three pump chambers 36 to 38 are formed between the cam ring part 20a and the rotor 19 at intervals of 120 degrees from the rotation center line, and when located on the proximal side in the rotational direction, they become suction ports and on the distal side. Six suction/discharge ports 22 to 27, which become discharge ports when located at , are formed at approximately 120° intervals. , 25, and 27 are connected to the first oil passage OL ₁ and the second oil passage OL ₂ through a mechanism that allows oil to be passed to the stationary side even when the cam ring portion 20a is in rotation.
It is communicated with.

Moreover, between the first oil path OL ₁ and the second oil path OL ₂ ,
The oil reservoirs 30 are communicated with each other through check valves 28, 29, and 29', and only flow from the oil reservoirs 30 to the respective oil passages OL ₁ and OL ₂ is allowed, and the flow between the first oil passage OL 1 and the second oil passage OL ₁ and the Two check valves 31 facing each other that allow only outflow between the oil passage OL ₂ and the oil passage OL 2;
Both the oil passages OL ₁ and OL ₂ are communicated through the oil passage 40 and the intermediate portion between the two check valves 31 and 32
It communicates with the relief valve 33 via.

Through the middle part of the relief valve 33 on the spring 34 side, there is a connection between the oil reservoir 30 and the check valve 29' and the two check valves 28 and 29.
A communication path 35 is provided.

With such a hydraulic circuit 21, the discharge pressure always acts on the valve body of the relief valve 33, regardless of the relative rotation direction between the rotor 19 and the cam ring portion 20a, and the oil reservoir 30 communicates with the suction port. become.

Further, the cover 20b and flange 20c that constitute the housing 20 of the vane pump VP are pivotally supported by the transmission case 44 via bearings 41 and 42, respectively.

A second rotating shaft 14 connected to the rotor 19 of the vane pump VP via a spline engagement portion 14a.
are pivotally supported by the cover 20b and the pressure retainer 20f via bushings (bearings) 45 and 46, respectively, on both sides of the spline engagement portion 14a.

Further, the radius of the tip portion 18a of the vane 18 that is in sliding contact with the inner circumferential surface 20d of the housing 20 decreases in the direction of rotation B as it goes from the high pressure discharge side suction discharge port 24 to the low pressure suction side suction discharge port 23. It is formed into an edge shape.

The bottom portion 18b of the vane 18 checks the discharge pressure P ₁ from the discharge side suction discharge port 24 using the check valve 32.
and the working pressure P ₂ (<
P ₁ ), the tip portion 18a of the vane 18 is urged toward the inner circumferential surface 20d of the housing 20.

That is, the tip portion 18a of the vane 18
As shown in the figure, for the circumferential thickness D (0.2
~0.1) A plane 60 with a thickness of D and an inclination angle θ ₁
(≧10°).

Further, an axial sliding portion 56 where the rotor 19 and the cover 20b are in sliding contact, and an axial sliding portion 56 where the rotor 19 and the pressure retainer 20f are in sliding contact with each other.
As shown in FIG. 6, there is an annular hydraulic chamber 5.
9, 59 are formed so that the oil passage 40 communicates with each hydraulic chamber 59, 59.

That is, the hydraulic chambers 59, 59 communicate with the first oil passage OL ₁ connected to each suction/discharge port 22, 24, 26 via the check valve 32 and receive high oil pressure, and also , 27 through _a check valve 31 to receive high oil pressure.

In addition, the reference numeral 43 in FIG. 6 indicates a bearing that supports the first rotating shaft, 47 is a pulsation volume, 48 is an oil guide, 49 is a filter, 50 is a magnet, 51 is a bolt, 5
Reference numeral 4 indicates an oil passage, and reference numeral 55 indicates a pulsation damper.

Alternatively, it may be attached to both end surfaces of the rotor 19 via a shaft portion 62 such as a spring 63 or a ring as shown by the two-dot chain line in FIG.

Since the vane pump as a practical example of the present invention is constructed as described above, in the four-wheel drive coupling device equipped with this vane pump, when the vehicle is in a normal straight-ahead state, the tires of the front wheels 9 and rear wheels 16 are Since the effective radius of the four-wheel drive coupling device body 13 is the same and the slip rotation speed of the tire is small
A first rotating shaft 11 and a second rotating shaft 14 connected to
There is no difference in rotational speed between the two.

Therefore, the vane pump VP does not generate hydraulic pressure, the driving force is not transmitted to the rear wheels 16, and the front wheels 9
Front-wheel drive only.

However, in a situation where the front wheels 9 normally slip within about 1% even if there is no large slip, such as when the vehicle is accelerating straight ahead, the rotational speed difference due to this is the first.
When the rotational speed difference is generated between the rotational shaft 11 and the second rotational shaft 14, the vane pump VP functions to generate oil pressure corresponding to this rotational speed difference, and the rotor 19 and the cam ring part 20a rotate as one. A driving force corresponding to this oil pressure and the pressure-receiving area of the vane is transmitted to the rear wheels 16, resulting in a four-wheel drive state.

In this case, the flow of oil in the vane pump VP is caused by the relative rotation of the rotor 19 (see symbol B in FIGS. 1 and 4), and the suction and discharge ports 23,
25 and 27 serve as suction ports, and oil is sucked in from the oil reservoir 30 via the check valve 28, while suction and discharge ports 22, 24, and 26 serve as discharge ports, and the check valves 29 and 31 are closed and the oil is checked at the same time. Valve 3
2. Oil is led to the relief valve 33 via the oil passage 40.

In FIG. 4, solid line arrows indicate the flow of discharged oil, and broken line arrows indicate the flow of suction oil.

In this actual rotating example, relative rotation direction B shown in FIG.
, the first oil passage OL ₁ receives a discharge pressure, but the discharge pressure in which the peak phase of the pulsation of each suction discharge port 22, 24, 26 is different is superimposed on this discharge pressure,
The pulsations are also superimposed, but since the peak phases of the pulsations are different, the variation value of the superimposed pulsations is equal to the variation value of the pulsations at each discharge pressure.

Further, since the oil passage 40 and the inner diameter side bottom portion 19c are in communication, the vane 18 is always connected to the cam ring portion 20.
The driving force transmission characteristics of the vane pump VP at the time of starting the engine 1 are improved by being biased toward the inner circumferential surface 20d of the vane pump VP.

Furthermore, although the pressure receiving area on the discharge side of each suction and discharge port 22 to 27 is different for each port, the second
Since the rotating shaft 14 of the rotor 19 is supported by the housing 20 via bushings (bearings) 45 and 46, the rotor 19 can be supported even if an imbalance occurs in the radial force applied to the rotor 19. ,
In this example, the positions and sizes of the suction and discharge ports 22 to 27 and the shape of the inner circumferential surface 20d of the cam ring portion 20a are determined so that the sum of the radial load vectors at the discharge ports becomes zero. .

Then, when the vane 18 is separated from the housing 20 as shown by the solid line in FIG.
As shown in FIG. 2, the pressure distribution at the tip 18a of 8 is sufficiently small at circumferential positions A ₁ to _{A 2} due to the edge effect, so , the hydraulic pressure _P2 for pushing up the vane becomes larger, and as shown by the two-dot chain line in Fig. 1, the vane 18 instantly comes into close contact with the housing 20, and the high hydraulic pressure is transferred from the discharge side of the suction and discharge port to the suction side. There will be no leakage.

Next, when the rotational speed of the front wheels 9 becomes very large compared to the rotational speed of the rear wheels 16, for example, when the front wheels 9 slip on a snowy road, or when the rear wheels 16 tend to lock up during sudden acceleration or braking. , there is a first rotating shaft 1 connected to the four-wheel drive coupling device main body 13.
The difference in rotational speed between the first and second rotating shafts 14 becomes very large.

As a result, in the vane pump VP, an oil flow as shown in Fig. 4 occurs and a large hydraulic pressure is generated, but when a predetermined value is exceeded, the relief valve 33 opens against the spring 34 and the discharge pressure becomes almost constant. A four-wheel drive state is established in which a constant driving force corresponding to a constant discharge pressure is transmitted to the rear wheels 16.

Then, as the rotational speed of the front wheels 9 decreases, the rotational speed of the rear wheels 16 increases, reducing the rotational speed difference (same function as a non-slip differential).
I come to do it.

In this way, when the front wheel 9 is in a slip state, the rear wheel 1
In addition, when the rear wheels 16 tend to lock up, the brake torque of the front wheels 9 is increased to prevent the rear wheels 16 from locking up.

On the other hand, when the rotational speed of the rear wheels 16 becomes very large compared to the rotational speed of the front wheels 9, for example, when the brake state of the front wheels 9 becomes slightly locked, the first Rotating axis 1
A very large rotational speed difference occurs between the first and second rotating shafts 14 in the opposite direction to that described above.

As a result, in the vane pump VP, an oil flow occurs in the opposite direction to the oil flow shown in FIG. While oil is sucked in from the suction and discharge ports 23, 25, and 27, it becomes a discharge port and passes through the first oil path _OL1 to the check valve 28,
32, and check valve 32 to relief valve 3.
A large oil pressure guided to the rear wheels 16 is applied, but this oil pressure is also held constant by the relief valve 33, and a constant driving force is transmitted to the rear wheels 16, resulting in a four-wheel drive state.

Then, the brake torque to the rear wheels 16 is increased to prevent the front wheels 9 from locking.

Furthermore, during normal cornering, the rotational speed of the front wheels 9 is slightly higher than the rotational speed of the rear wheels 16, resulting in a four-wheel drive state in which brake torque is applied to the front wheels 9 and drive torque is applied to the rear wheels 16. A turning run is made.

In this way, by controlling the discharge pressure in the four-wheel drive coupling device main body 13 using the relief valve 33 so that it does not exceed a certain value, it is possible to control the discharge pressure in the four-wheel drive coupling device main body 13 so that it does not exceed a certain value. The system used to require operation by the driver, but it now automatically switches between four-wheel drive and two-wheel drive, and now has four-wheel drive with a driving force that corresponds to the difference in rotational speed between the front wheels 9 and rear wheels 16. The state is obtained.

Furthermore, compared to a center differential that is always installed in conventional full-time four-wheel drive vehicles, this device can be made smaller and more compact, as well as reducing weight and cost.

As described above, according to the four-wheel drive coupling device equipped with the vane pump as this practical example, the following effects and advantages can be obtained with a simple configuration.

(1) Differential rotation between the front and rear wheels is allowed, which eliminates problems such as tight corner braking of part-time four-wheel drive vehicles and the complexity of driving operations.

(2) Since force is transmitted between the first rotating shaft and the second rotating shaft from the one that is rotating faster to the one that is rotating slower, it is possible for either the front or rear wheels to over-rotate. This can reliably prevent wheel spin and contribute to vehicle safety.

(3) Compared to the center differential conventionally equipped on full-time four-wheel drive vehicles, it can be made smaller and lighter, and can also contribute to lower costs.

(4) The vane 18 is located on the inner peripheral surface 20a of the housing 20.
The tip 18a of the vane 18
The distance between the inner circumferential surface 20a of the housing 20 and the inner circumferential surface 20a of the housing 20 is always kept small, and fluctuations in the discharged oil pressure are small, and as shown in FIG. The output torque in a certain case is approximately constant.

(5) The differential pump type four-wheel drive coupling device is used in a region where the difference in rotation between the front and rear wheels 9, 16 is small, and the absolute speed of the front wheels 9 (or rear wheels 16) is proportional to the vehicle speed. Good differential torque can be generated over the entire engine rotation speed range (for example, 0 to 5000 rpm).

In addition, as shown in Fig. 8, the vane is
Two vanes 1 with chamfers facing in opposite directions
In this case, the vane 1 at the circumferential position A ₂ to _{A 3} may be
8'' receives an edge effect, and as shown in FIG.
It comes into close contact with the inner circumferential surface 20d of.

In this modification, vanes 18'', 18''
However, the above-mentioned effects can be obtained regardless of whether the relative rotation direction of the rotor 19 with respect to the housing 20 is forward or reverse.

Furthermore, it is known from experimental results that a sufficient effect can be achieved by setting the inclination angle θ ₁ to 10° or more.

[Effect of idea]

As detailed above, the vane pump of the present invention includes a housing, a rotor housed in the housing and rotated relative to the housing by a rotating shaft, and a rotor attached to the outer peripheral surface of the rotor. The housing includes a large number of vanes that are in sliding contact with the inner peripheral surface of the cam ring portion, and a plurality of pump chambers that are formed by being surrounded by the rotor, housing, and vanes, and each of the plurality of pump chambers is activated. A pair of suction and discharge ports are formed for sucking and discharging oil, and the tips of the vanes that are in sliding contact with the inner circumferential surface of the housing absorb high pressure at the suction and discharge ports during relative rotation between the rotor and the housing. This vane pump has a simple structure in which the radius decreases as it goes from the discharge side to the low-pressure suction side, reliably preventing fluctuations in the discharge oil pressure when the rotor rotates at low speed. In a four-wheel drive coupling device equipped with this, the output torque is stable.

[Brief explanation of the drawing]

Figures 1 to 9 show a four-wheel drive coupling device equipped with a vane pump as an example of the present invention. Figure 1 is a front view of the main parts of this device, and Figure 2 shows its operation. Graph for explanation, Figure 3 is a front view showing the vane, Figure 4 is a cross-sectional view of the device,
Fig. 5 is a schematic configuration diagram showing the drive system of the vehicle, Fig. 6 is a longitudinal sectional view of the device, Fig. 7 is a graph for explaining the operation of the device, and Fig. 8 is a modification of the vane. FIG. 9 is a graph for explaining the operation of a modified example, and FIGS. 10 and 11 show a conventional vane pump, and FIG. 10 is a cross-sectional view of the main part. The top view and Fig. 11 are graphs for explaining the effect, and the first
Figures 2 and 13 show other conventional vane pumps, Figure 12 is a cross-sectional view of its main parts, Figure 13 is a graph for explaining its action, and Figure 14 is a graph for explaining its operation.
The figure is a graph for explaining the operation of each conventional device. DESCRIPTION OF SYMBOLS 1... Horizontal engine, 2... Transmission, 3... Output shaft, 4... Drive gear (or 4-speed counter gear), 7... Gear, 9... Front wheel, 10... Differential device, 11 ...First rotating shaft (outer shaft), 13...
Main body of a four-wheel drive coupling device as a vane pump type coupling mechanism, 14...Second rotating shaft (inner shaft), 14
a... Spline engagement part, 15, 15'... Bevel gear mechanism, 16... Rear wheel, 17... Differential device,
18, 18''...Vane, 18a, 18''a...Edge-shaped tip, 18b, 18''b...Bottom, 19
... Rotor, 19a ... Outer circumferential surface, 19b ... Hole, 19c ... Inner diameter side bottom, 20 ... Housing, 20a ... Cam ring part, 20b ... Cover, 20c ... Flange, 20d ... Inner circumference ,2
0e... Gear cam ring, 20f... Pressure retainer, 21... Hydraulic circuit, 22-27... Suction/discharge port, 28, 29, 29'... Check valve,
30... Oil reservoir, 31, 32... Check valve,
33...Relief valve, 34...Spring, 35
...Communication path, 36-38...Pump chamber, 40...
Oil passage, 41 to 43... Bearing, 44... Transmission case, 45, 46... Bushing (bearing), 47... Pulsation volume,
48...Oil guide, 49...Filter, 50
... Magnet, 51 ... Bolt, 54 ... Oil path, 55 ... Pulsation damper, 56 ... Axial sliding part, 59 ... Hydraulic chamber, 59a ... Inside,
59b...outside, 60...plane, 61...inclined surface, 62...shaft, 63...spring, OL ₁ ...
...First oil path, OL ₂ ...Second oil path, VP...Vane pump.

Claims (1)

[Scope of utility model registration request] A housing, a rotor housed in the housing and rotated relative to the housing by a rotating shaft, and a number of vanes that are attached to the outer peripheral surface of the rotor and come into sliding contact with the inner peripheral surface of a cam ring portion of the housing. and a plurality of pump chambers formed by being surrounded by the rotor, housing, and vanes, and a pair of suction and discharge ports for sucking and discharging hydraulic oil are formed in each of the plurality of pump chambers. , the radius of the tip of the vane in sliding contact with the inner circumferential surface of the housing decreases as it moves from the high-pressure discharge side of the suction and discharge port toward the low-pressure suction side during relative rotation between the rotor and the housing; A vane pump characterized by being formed into an edge shape.