JPH08277785A - Vane pump - Google Patents

Abstract

PURPOSE: To obtain the large capacity without increasing the size in the radial direction of a vane pump. CONSTITUTION: A vane holding member 14 is attached to a driving rotary shaft 12 inserted in a casing. A cam member provided with a cam surface formed on end surface in the rotary shaft direction is attached to the casing. A plurality of slide grooves 16 for receiving vanes 18 are formed on the vane holding member 14 along the rotary shaft direction so as to be reciprocated. The end edges of the vanes are brought in contact with the cam surface. The annular hollow formed of the vane holding member 14, the cam surface and the casing is sectioned by the vanes 18, so as to form a plurality of cells. The cell in which the capacity is gradually increased with the rotation of the driving rotary shaft 12 and a fluid suction port 8 are connected to each other by sucking fluid passages 3A, 21A, and the cell in which the capacity is gradually decreased with the rotation of the driving rotary shaft 12 and the fluid discharge port 10 are connected to each other by discharge fluid passages 3b, 21B.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION This invention relates to vane pumps.

[0002]

2. Description of the Related Art Conventionally, the problems to be solved by the invention
As a vane pump, a rotor is mounted between two side plates so as to be rotatable about a rotation axis orthogonal to the two side plates, and a plurality of radial grooves arranged on the outer peripheral surface of the rotor along the rotor rotation direction (circumferential direction). And a vane is housed in each groove, a cam ring is provided on the rotor so as to come into contact with the outer edge of the vane radially outward, and the rotor is rotated so that two adjacent vanes are formed. The size of the chamber formed between the rotor outer surface and the cam ring inner surface (inner circumferential cam surface) and the two side plates is changed in accordance with the rotation of the rotor, so that fluid is sucked from the suction port and fluid is discharged from the discharge port. The thing which makes it discharge is used.

In such a vane pump, in order to obtain a large flow rate, the radial dimensions of the rotor and the casing are increased. However, when it is required to realize a large capacity without increasing the radial dimension, there has been a problem that it is not possible to satisfy the requirements.

Therefore, an object of the present invention is to provide a vane pump which can easily realize a large capacity without increasing the radial dimension.

[0005]

According to the present invention, in order to achieve the above object, a drive rotating shaft is inserted in a casing, and one of a vane holding member and a cam member is provided in the casing. A plurality of slide grooves are attached to the drive rotary shaft and the other is attached to the casing, and the vane holding member has a plurality of slide grooves for receiving the vanes so as to be reciprocally movable along the direction of the drive rotary shaft. The cam member has a cam surface formed along the circumferential direction on the end face in the direction of the drive rotary shaft, and the vane has an end edge in the drive rotary shaft direction as the cam face. A plurality of compartments are formed by partitioning an annular cavity formed by the vane holding member, the cam surface of the cam member, and the casing with the vane. The volume that gradually increases with the rotation of the drive rotary shaft and the fluid suction port that sucks fluid from the outside are connected by a suction fluid passage, and the volume increases with the rotation of the drive rotary shaft. There is provided a vane pump, characterized in that the gradually decreasing compartment and a fluid discharge port for discharging a fluid to the outside are connected by a discharge fluid passage.

In one aspect of the present invention, the vanes are arranged radially in the radial direction of the drive rotating shaft.

In one aspect of the present invention, a plurality of the annular cavities are formed at different positions in the drive rotation axis direction, and each of the annular cavities is partitioned by the vane to form a plurality of compartments. .

In one aspect of the present invention, the vane holding member has a large-diameter portion formed in the center in the drive rotation axis direction and two small-diameter portions formed on both sides thereof, and the two small-diameter portions. Two annular cavities are formed including each of the portions and the large diameter portion, and the vane is capable of reciprocating over the two annular cavities and contributes to formation of a compartment in the two annular cavities. ing.

In one aspect of the present invention, the cam members are arranged on both sides of the vane holding member with respect to the drive rotation axis direction, and the two cam members are provided at corresponding positions in the drive rotation axis circumferential direction. The distance between them is constant over the entire circumference.

In one aspect of the present invention, the vane is biased so as to be pressed against the cam surface of the cam member.

In one aspect of the present invention, the vane has two portions that are relatively movable in the drive rotation axis direction, and these two portions are attached so as to press each other in the drive rotation axis direction. It is energized.

In one aspect of the present invention, both the suction fluid passage and the discharge fluid passage are formed via the cam member and the casing.

In one aspect of the present invention, both the suction fluid passage and the discharge fluid passage are formed via the vane holding member and the drive rotary shaft.

In one aspect of the present invention, a check valve is interposed between the suction fluid passage and the discharge fluid passage and the compartment.

In one aspect of the present invention, the suction fluid passage and the discharge fluid passage each include a suction fluid flow chamber and a discharge fluid flow chamber formed in the casing.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Specific embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a partially cutaway exploded perspective view showing a first embodiment of a vane pump according to the present invention.
Each is a sectional view showing an assembled state of this vane pump.

In these figures, 2 is a cylindrical casing body, and 4 and 6 are casing lids, which are joined by bolts and integrated to form a casing. The casing has a fluid inlet 8
And the fluid discharge port 10 are formed. The fluid is oil, for example.

A drive rotating shaft 12 in the XY directions is inserted into the casing through the casing lid portion 4. The rotary shaft 12 is rotatably supported by the casing lid portions 4 and 6 via bearings. A portion of the rotary shaft 12 inside the casing is formed as a vane holding member 14. The holding member 14 has a large diameter portion 14a at the center in the XY direction and two small diameter portions 14b and 14c on both sides thereof.

The drive rotary shaft 12 is connected to the output shaft of the motor via a clutch or the like, if necessary.

In the present specification, the circumferential direction, the radial direction, and the axial direction all refer to the direction (or the direction corresponding thereto) with respect to the rotary shaft 12, unless otherwise specified.

The holding member 14 is formed with a plurality of slide grooves 16 formed on the outer peripheral surface along the entire length in the axial direction, and a part of the vanes 18 are slidably received in the grooves. There is. As shown in the drawing, 16 slide grooves 16 and vanes 18 are evenly arranged in the circumferential direction, and all of them are radially arranged in the radial direction. Each vane 18 has a slide groove 16
It is possible to reciprocate along the entire length of the holding member 14.

The ring-shaped first cam member 2 is provided in each of the casing lid portions 4 and 6 that faces the inside of the casing.
0 and the second cam member 22 are additionally formed. A first cam surface 20a is formed on the X-side end surface of the cam member 20, and a second cam surface 22a is formed on the Y-side end surface of the cam member 22.
Are formed. Then, the first cam surface 20a gradually recedes in the axial direction from the circumferential angular position (θ) of 0 degrees to 180 degrees and gradually in the axial direction of the circumferential angular position of 180 degrees to 360 degrees. It is shaped to move forward. Contrary to the cam surface 20a, the second cam surface 22a gradually advances in the axial direction from a circumferential angular position (θ) of 0 degrees to 180 degrees and has a circumferential angular position of 18 degrees.
The shape is such that it gradually recedes in the axial direction from 0 degree to 360 degrees. Then, the first cam surface 20a and the second cam surface 20a
The interval L ₁ at the corresponding circumferential angular position with the cam surface 22a is equal over the entire circumference.

The axial length L ₂ of the vane 18 is the above L ₁
Is equal to or slightly smaller than L _1.
0a and 22a are substantially brought into contact with each other. The radial height H of the vane 18 is slightly smaller than the distance between the bottom of the slide groove 16 and the inner surface of the casing body 2.

The outer peripheral surface of the large diameter portion 14a of the vane holding member is in contact with the inner peripheral surface of the casing body 2. Therefore, the Y-direction end surface of the vane holding member large diameter portion 14a, the outer peripheral surface of the vane holding member small diameter portion 14b, the first cam member cam surface 20a, and the inner peripheral surface of the casing body portion 2 form a first annular cavity. ing. The term "annular cavity" as used in the present invention may mean that a part of the annular shape is constricted. That is, as for the first annular cavity, the Y-direction end surface of the large diameter portion 14a of the vane holding member may be in contact with the first cam member cam surface 20a at a certain angular position in the circumferential direction. Like this first
The annular cavity is divided by vanes 18 to form a plurality of compartments. The first pump unit is configured to include these compartments.

Similarly, the large diameter portion 14a of the vane holding member is formed.
Of the vane holding member small diameter portion 14c, the second cam member cam surface 22a, and the inner peripheral surface of the casing body portion 2 form a second annular cavity. Are divided by vanes 18 to form a plurality of compartments. The second pump unit is configured to include these compartments.

The cam member 20 is formed with a suction fluid passage 21A and a discharge fluid passage 21B which are opened at the cam surface 20a. These communicate with the suction fluid passage 3A and the discharge fluid passage 3B formed in the casing body portion 2, respectively. Similarly, the cam member 22 is formed with a suction fluid passage 23A and a discharge fluid passage 23B which are opened at the cam surface 22a. These communicate with the suction fluid passage 3A and the discharge fluid passage 3B, respectively. The suction fluid passage 3A and the discharge fluid passage 3B communicate with the fluid suction port 8 and the fluid discharge port 10, respectively.

As shown in FIG. 3, the suction fluid passage 21A opens at the first cam surface 20a within a range from a position where the angular position θ in the circumferential direction is slightly larger than 0 ° to a position slightly smaller than 180 °. The discharge fluid passage 21B
Is the first in the range from the position where the circumferential angular position θ is slightly larger than 180 degrees to the position where it is slightly smaller than 360 degrees
It is opened at the cam surface 20a. Similarly, although not shown, the suction fluid passage 23A has a circumferential angular position θ of 1
Within the range from a position slightly larger than 80 degrees to a position slightly smaller than 360 degrees, the second cam surface 22a opens, and the discharge fluid passage 23B extends from the position where the circumferential angular position θ is slightly larger than 0 degrees to 180 degrees. The second cam surface 22a opens in a range up to a slightly smaller position.

Accordingly, when the drive rotary shaft 12 is rotated clockwise in FIG. 3, the first rotary shaft 12 is formed in the first annular cavity position.
In the pump portion, the circumferential angular position θ is 0 degrees to 180 degrees.
Between the degrees, the volume of the compartment gradually increases, so that the fluid is sucked from the fluid suction port 8 into the compartment through the suction fluid passages 3A and 21A, and the circumferential angular position θ is 180 degrees or more.
Between 360 degrees, the volume of the compartment gradually decreases,
Fluid is discharged from the compartment to the fluid discharge port 10 through the discharge fluid passages 21B and 3B.

Similarly, in the second pump portion formed at the second annular cavity position, the circumferential angular position θ is 0 ° to 18 °.
Since the volume of the compartment gradually decreases between 0 degrees, the fluid discharge port 1 is discharged from the compartment via the discharge fluid passages 23B and 3B.
The fluid is discharged to 0, and the angular position θ in the circumferential direction is 180 to
Between 360 degrees, the volume of the compartment gradually increases,
Fluid is sucked from the fluid suction port 8 into the compartment through the suction fluid passages 3A and 23A.

In the above pump operation, the vane 18 is pushed by the second cam surface 22a and moves in the slide groove 16 in the Y direction when the circumferential angular position θ is between 0 ° and 180 °, and the circumferential angular position is increased. When θ is between 180 degrees and 360 degrees, the vane 18 is pushed by the first cam surface 20a and moves in the slide groove 16 in the X direction.

In this embodiment, the change in the compartment volume is caused by the cam surfaces 20a, 2 formed on the axial end surfaces of the cam members 20, 22.
Since it is realized by 2a, it is possible to easily realize a large flow rate (pump capacity) while keeping the radial dimension small by making the axial dimension sufficient.

4 and 5 are partially exploded perspective views showing a second embodiment of the vane pump according to the present invention, and FIGS. 6 and 7 are sectional views showing the assembled state of the vane pump, and FIG. FIG. 4 is a partial cross-sectional view showing an assembled state of this vane pump. Incidentally, FIG. 5 shows a part forming a part of FIG. In these figures, FIG.
~ Members having the same functions as in Fig. 3 are designated by the same reference numerals.

In this embodiment, two splines 12A and 12 are provided on the drive rotary shaft 12 in the casing.
B is formed. The first cam member 20 and the second cam member 22 are rotatably arranged with respect to the casing, and these cam members have spline holes 20A, 2 that mesh with the rotary shaft splines 12A, 12B, respectively.
2A is formed.

The vane holding member 14 is fixed to the casing body 2 with bolts. Further, the vane holding member 14 has a circumferential angular position θ of 0 degree and
The slide groove 16 is arranged at a position of 0 degree. A through hole in the XY directions is formed in the center of the vane holding member 14, and the drive rotation shaft 12 is arranged so as to penetrate therethrough and can slide and rotate with respect to the holding member 14. A slide groove 16 'is also formed on the inner peripheral surface of the casing body portion 2.

As shown in FIG. 8A, the vane holding member small-diameter portion 14b has a diameter within a range from a position where the angular position θ in the circumferential direction is slightly larger than 0 ° to a position slightly smaller than 180 °. The first fluid passage 15A is formed so that the second fluid passage 15B can penetrate in the radial direction within the range from the position where the circumferential angular position θ is slightly larger than 180 degrees to the position where it is slightly smaller than 360 degrees. Has been formed. The drive rotary shaft 12 has a suction fluid passage 13A and a suction fluid passage 13A that are opened on the opposite side with the circumferential angular position θ shifted by 180 degrees at the axial positions where the first fluid passage 15A and the second fluid passage 15B are located. Fluid passage 13B
Are formed. The suction fluid passage 13A and the discharge fluid passage 13B are respectively the suction fluid passage 3A and the discharge fluid passage 3B formed in the casing lid portion 6.
Is in communication with The suction fluid passage 3A and the discharge fluid passage 3B communicate with the fluid suction port 8 and the fluid discharge port 10, respectively.

As shown in FIG. 8 (b), the vane holding member small diameter portion 14c has a circumferential angular position θ of 1.
A first fluid passage 15C that penetrates in the radial direction is formed within a range from a position slightly larger than 80 degrees to a position slightly smaller than 360 degrees, and the circumferential angular position θ is from 180 degrees to 180 degrees from a position slightly larger than 0 degrees. Second fluid passage 15D that can penetrate in the radial direction within a range up to a slightly smaller position
Are formed. The suction fluid passage 13A and the discharge fluid passage 13B of the drive rotary shaft 12 are opposite to each other with the circumferential angular position θ shifted by 180 degrees at the axial position where the first fluid passage 15C and the second fluid passage 15D are located. It opens to the side. The angular positions of these openings in the circumferential direction are determined by the second fluid passage 15B and the first fluid passage 15A, respectively.
Is the same as the opening corresponding to.

In the present embodiment, the vane 18 has two parts 18a and 18b which are relatively movable in the XY directions.
These two portions are urged by a compression coil spring 18c so as to press each other in the X and Y directions to give an extension force. Therefore, in this embodiment, both axial end edges of the vane 18 are brought into contact with the first cam surface 20a and the second cam surface 22a with an appropriate pressing force, and the fluid leakage between the compartments is small.
The vane 18 of this embodiment can also be used in the first embodiment.

In this embodiment, as in the first embodiment, the distance L ₁ between the first cam surface 20a and the second cam surface 22a at the corresponding circumferential angular position is equal over the entire circumference.

In this embodiment, the cam surface 20a of the first cam member 20 and the cam surface 22a of the second cam member 22 are formed at the first pump portion and the second annular cavity position which are formed at the first annular cavity position. Drive rotary shaft 12 in the second pump section that has been
And the openings of the fluid passages 13A and 13B for suction and discharge have the following relationship.

That is, the first formed in the first annular cavity position
In the pump section, the drive rotary shaft 12 is shown in FIGS.
When rotated clockwise in (a), the drive rotary shaft 12
The angular position θ in the circumferential direction of the opening of the suction fluid passage 13A is 0
Between 180 degrees and 180 degrees (that is, when the angular position θ in the circumferential direction of the opening of the discharge fluid passage 13B is between 180 degrees and 360 degrees), the volume of the compartment that can communicate with the first fluid passage 15A gradually increases. The volume of the compartment that can communicate with the two-fluid passage 15B is set to gradually decrease. Further, in the second pump portion formed in the second annular cavity position, when the drive rotation shaft 12 is rotated clockwise in FIGS. 7 and 8B, the suction fluid passage 13A of the drive rotation shaft 12 When the circumferential angular position θ of the opening is 180 degrees to 360 degrees (that is, the circumferential angular position θ of the opening of the discharge fluid passage 13B is between 0 degrees and 180 degrees), the first fluid passage 15C can be communicated. The volume of the compartment is set to gradually increase, and the volume of the compartment communicating with the second fluid passage 15D is set to gradually decrease.

Therefore, when the drive rotary shaft 12 is rotated clockwise in FIGS. 7 and 8, in the first pump portion formed at the first annular cavity position, the suction fluid passage 13A of the drive rotary shaft 12 is formed. The angular position θ in the circumferential direction of the opening is 0 degrees to 18
During 0 degree (that is, the circumferential angular position θ of the opening of the discharge fluid passage 13B is between 180 degrees and 360 degrees), the fluid suction port 8 causes the suction fluid passages 3A and 13A and the first fluid passage 1 to flow.
The fluid is sucked into the compartment via 5A, and the second fluid passage 15B and the discharge fluid passages 13B, 3 are discharged from the compartment.
Fluid is discharged to the fluid discharge port 10 via B, and the angular position θ in the circumferential direction of the opening of the suction fluid passage 13A of the drive rotary shaft 12 is between 180 degrees and 360 degrees (that is, the discharge fluid passage 13B). The angular position θ in the circumferential direction of the opening is 0 degrees to 18
(0 degree), the fluid intake port 8 to the intake fluid passage 3
A fluid is sucked into the compartment via A, 13A and the second fluid passage 15B, and the first fluid passage 15A is drawn from the compartment.
And the fluid discharge port 1 through the discharge fluid passages 13B, 3B.
Fluid is discharged to zero.

Similarly, when the drive rotary shaft 12 is rotated clockwise in FIGS. 7 and 8, in the second pump portion formed in the second annular cavity position, the suction fluid passage of the drive rotary shaft 12 is generated. The circumferential angular position θ of the opening of 13A is 180 degrees to
During 360 degrees (that is, the circumferential angular position θ of the opening of the discharge fluid passage 13B is between 0 degrees and 180 degrees), the fluid suction port 8 causes the suction fluid passages 3A and 13A and the first fluid passage 1 to flow.
Fluid is sucked into the compartment via 5C, and the second fluid passage 15D and the discharge fluid passages 13B, 3 are discharged from the compartment.
Fluid is discharged to the fluid discharge port 10 via B, and the angular position θ in the circumferential direction of the opening of the suction fluid passage 13A of the drive rotary shaft 12 is between 0 degrees and 180 degrees (that is, the discharge fluid passage 13B). The angular position θ in the circumferential direction of the opening is 180 degrees to 36
(0 degree), the fluid intake port 8 to the intake fluid passage 3
A fluid is sucked into the compartment through A, 13A and the second fluid passage 15D, and the first fluid passage 15C from the compartment.
And the fluid discharge port 1 through the discharge fluid passages 13B, 3B.
Fluid is discharged to zero.

In the above pump operation, the vane 18 is pushed by the first cam surface 20a and the second cam surface 22a and reciprocates in the slide grooves 16 and 16 'in the XY directions.

Also in this embodiment, as in the first embodiment, the change in the compartment volume is realized by the cam surfaces 20a and 22a formed on the axial end surfaces of the cam members 20 and 22, so that the shaft By making the directional dimension sufficient, a large flow rate (pump capacity) can be easily realized while keeping the radial dimension small.

FIG. 9 is an exploded perspective view showing a third embodiment of the vane pump according to the present invention, and FIGS. 10 and 11 are sectional views showing the assembled state of the vane pump. In these figures, members having the same functions as those in FIGS. 1 to 8 are designated by the same reference numerals.

In this embodiment, the drive rotary shaft 12 penetrates the casing lid 6 and is inserted into the casing.
A cam member 30 is additionally formed in the casing at the tip of the rotary shaft in the Y direction. A cam surface 30a is formed on the end surface of the cam member 30 on the Y direction side. The vane holding member 14 is attached to the casing body 2 with bolts. The holding member 14 includes a large diameter portion 14a and a small diameter portion 14
and a horizontal partition wall 3 on the Y direction side of the large diameter portion 14a.
2 is additionally formed. The horizontal partition wall 32 is orthogonal to the vanes 18 arranged so that the circumferential angular position θ is 0 degree and 180 degrees. The horizontal partition wall 32 divides the casing body 2 into upper and lower parts, the inner peripheral surface of the casing body 2, the Y-direction end surface of the large diameter portion 14a of the vane holding member, and the casing lid portion 4.
A suction fluid flow chamber 33A and a discharge fluid flow chamber 33B are formed by being surrounded by the inner surface of the.

In the holding member large diameter portion 14a, the circumferential angular position θ is in the range of 0 ° to 90 °, in the range of 90 ° to 180 °, in the range of 180 ° to 270 °, and in the range of 270 ° to 360 °.
Within the range of degrees, openings 34, which can penetrate in the XY directions,
35, 36 and 37 are formed. And opening 3
A first check valve 38, which allows only the fluid flow in the X direction, is attached to 4, 37, and a second check valve, which allows only the fluid flow in the Y direction, is attached to the openings 35, 36. Three
9 is attached.

The two vanes 18 are biased in the X direction by the compression coil springs 42, respectively, and are brought into contact with the cam surface 30a of the cam member 30 with an appropriate pressing force.

In this embodiment, the fluid suction port 8 and the fluid discharge port 10 are attached to the casing lid 4. The fluid suction port 8 and the fluid discharge port 10 communicate with the suction fluid flow chamber 33A and the discharge fluid flow chamber 33B, respectively.

In this embodiment, when the driving rotary shaft 12 is rotated, the vane holding member large diameter portion 14a and the cam member 3 are rotated.
In both of the two compartments defined by the two vanes 18 between 0 and 0, when the volume of the compartment increases, the fluid intake port 8 to the suction fluid flow chamber 3
Fluid is sucked into the compartment via 3A and the first check valve 38, and when the volume of the compartment decreases, the fluid is discharged from the compartment via the second check valve 39 and the discharge fluid flow chamber 33B. Fluid is discharged to the outlet 10.

In the present embodiment as well, similar to the first and second embodiments, the change in the compartment volume is realized by the cam surface 30a formed on the axial end surface of the cam member 30, so that the axial direction is changed. With sufficient dimensions, a large flow rate (pump capacity) can be easily achieved while keeping the radial dimension small.
Can be realized.

FIG. 12 shows a vane pump according to a fourth embodiment of the present invention.
FIG. 13, FIG. 14 and FIG. 15 are sectional views showing the assembled state of this vane pump. 1 to 11 described above.
The members having the same functions as in 1 are assigned the same reference numerals.

In this embodiment, three vanes 18 are used, and three compartments are formed by partitioning these vanes. Since the number of compartments is three, the configuration on the Y direction side of the vane holding member 14 and its large diameter portion 14a is different from that of the third embodiment. That is, the holding member 14 includes the medium diameter portion 14 on the Y direction side of the large diameter portion 14a.
d is additionally formed. A suction fluid circulation chamber 43A is formed on the outside in the radial direction of the intermediate diameter portion 14d,
A discharge fluid circulation chamber 43B is formed inside the middle diameter portion 14d in the radial direction. The suction fluid flow chamber 43A and the discharge fluid flow chamber 43B communicate with the fluid suction port 8 and the fluid discharge port 10, respectively. In addition, each of the compartments defined by the vanes 18 has the suction fluid distribution chamber 4 described above.
It communicates with 3A through a first check valve 38 that allows only the fluid flow in the X direction, and the discharge fluid flow chamber 4 described above.
It is in communication with 3B through a second check valve 39 which allows only fluid flow in the Y direction.

Therefore, also in this embodiment, as in the case of the third embodiment, when the drive rotary shaft 12 is rotated, fluid suction is performed in any of the three compartments when the volume of the compartment increases. Fluid is sucked into the compartment from the mouth 8 through the suction fluid flow chamber 43A and the first check valve 38,
When the volume of the compartment decreases, the fluid discharge port 1 is released from the compartment via the second check valve 39 and the discharge fluid flow chamber 43B.
Fluid is discharged to zero.

Also in this embodiment, the same effect as the third embodiment can be obtained.

[0057]

As described above, according to the present invention, since the change in the volume of the compartment is realized by the cam surface formed on the axial end surface of the cam member, the sufficient axial dimension can be obtained.
Provided is a vane pump which can easily obtain a large flow rate while keeping the radial dimension small.

[Brief description of drawings]

FIG. 1 is a partially cutaway exploded perspective view showing a first embodiment of a vane pump according to the present invention.

FIG. 2 is a sectional view showing an assembled state of the first embodiment of the vane pump according to the present invention.

FIG. 3 is a sectional view showing the assembled state of the first embodiment of the vane pump according to the present invention.

FIG. 4 is a partially exploded perspective view showing a second embodiment of the vane pump according to the present invention.

FIG. 5 is a partially exploded perspective view showing a second embodiment of the vane pump according to the present invention.

FIG. 6 is a sectional view showing an assembled state of the second embodiment of the vane pump according to the present invention.

FIG. 7 is a sectional view showing an assembled state of the second embodiment of the vane pump according to the present invention.

FIG. 8 is a partial sectional view showing the assembled state of the second embodiment of the vane pump according to the present invention.

FIG. 9 is an exploded perspective view showing a third embodiment of the vane pump according to the present invention.

FIG. 10 is a sectional view showing an assembled state of the third embodiment of the vane pump according to the present invention.

FIG. 11 is a sectional view showing the assembled state of the third embodiment of the vane pump according to the present invention.

FIG. 12 is an exploded perspective view showing a fourth embodiment of the vane pump according to the present invention.

FIG. 13 is a sectional view showing the assembled state of the fourth embodiment of the vane pump according to the present invention.

FIG. 14 is a sectional view showing the assembled state of the fourth embodiment of the vane pump according to the present invention.

FIG. 15 is a sectional view showing an assembled state of the fourth embodiment of the vane pump according to the present invention.

[Explanation of Codes] 2 Casing body part 3A Suction fluid passage 3B Discharging fluid passage 4,6 Casing lid part 8 Fluid inlet 10 Fluid outlet 12 Drive shaft 12A, 12B Spline 13A Suction fluid passage 13B Discharging fluid passage 14 vane holding member 14a large diameter portion 14b, 14c small diameter portion 14d medium diameter portion 15A first fluid passage 15B second fluid passage 15C first fluid passage 15D second fluid passage 16 slide groove 18 vanes 18a, 18b vane portion 18c compression coil spring 20 1st cam member 20a 1st cam surface 20A spline hole 21A suction fluid passage 21B discharge fluid passage 22 second cam member 22a 2nd cam surface 22A spline hole 23A suction fluid passage 23B discharge fluid passage 30 cam member 30a Cam surface 32 Horizontal partition wall 33A Inhalation Fluid flow chamber 33B discharge fluid flow chamber 34, 35, 36, 37 opening 38 first check valve 39 second check valve 42 the compression coil spring 43A inhalation fluid flow chamber 43B discharge fluid flow chamber

Claims (11)

[Claims] 1. A drive rotating shaft is inserted in a casing, and one of a vane holding member and a cam member is attached to the drive rotating shaft and the other is attached to the casing in the casing. The vane holding member is formed with a plurality of slide grooves for receiving the vanes so that the vane can reciprocate along the direction of the drive rotating shaft, and the cam member has a peripheral surface on the end face in the direction of the drive rotating shaft. A vane holding member and a cam face of the cam member. The vane holding member and the cam face of the cam member have a cam surface formed along a direction. An annular cavity formed by the casing and the casing is partitioned by the vane to form a plurality of compartments, and the volume gradually increases as the drive rotary shaft rotates. The compartment and a fluid suction port for sucking fluid from the outside are connected by a suction fluid passage, and the volume gradually decreases with the rotation of the drive rotating shaft and the fluid discharge port for discharging the fluid to the outside. A vane pump, characterized in that and are connected by a discharge fluid passage. 2. The vane pump according to claim 1, wherein the vanes are radially arranged in a radial direction of the drive rotating shaft. 3. A plurality of the annular cavities are formed at different positions with respect to the drive rotation axis direction, and each of the annular cavities is partitioned by the vane to form a plurality of compartments. The vane pump according to claim 1 or 2. 4. The vane holding member has a large-diameter portion formed in the center in the drive rotation axis direction and two small-diameter portions formed on both sides thereof, and each of the two small-diameter portions and the large-diameter portion. A plurality of the annular cavities including a diameter portion are formed, and the vane is capable of reciprocating over the two annular cavities and contributes to the formation of a compartment in the two annular cavities. The vane pump according to claim 3, wherein 5. The cam members are arranged on both sides of the vane holding member with respect to the drive rotation axis direction, and the distance between corresponding positions of the two cam members in the drive rotation axis circumferential direction is the entire circumference. Vane pump according to claim 4, characterized in that it is constant over time. 6. The vane pump according to claim 1, wherein the vane is biased so as to be pressed against the cam surface of the cam member. 7. The vane has two parts that can move relative to each other in the drive rotation axis direction, and these two parts are biased so as to press each other in the drive rotation axis direction. The vane pump according to claim 6, characterized in that 8. The method according to claim 1, wherein the suction fluid passage and the discharge fluid passage are both formed via the cam member and the casing. Vane pump. 9. The inhalation fluid passage and the ejection fluid passage are both formed through the vane holding member and the drive rotary shaft.
The vane pump according to any one of to 7. 10. The vane pump according to claim 1, wherein a check valve is interposed between the suction fluid passage and the discharge fluid passage and the compartment. . 11. The suction fluid passage and the discharge fluid passage each include a suction fluid flow chamber and a discharge fluid flow chamber formed in the casing, respectively. The vane pump according to any one of 7 and 10.