JP2002303283A - Fluid pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a miniaturizable pump with small torque fluctuation during pump operation in a rolling piston type pump. SOLUTION: In the fluid pump, fluid sucked from a suction hole into operation chambers 51, 52, and 53 is discharged from a discharge hole by change in volumes of the operation chambers 51, 52, and 53 following revolution of a rotor 30. By composing the fluid pump so that the operation chambers 51, 52, and 53 are plurally partitioned by a plurality of vanes 40 along a rotating direction of a rotary shaft 20 and suction and discharge of the fluid are carried out per each operation chamber 51, 52, and 53, the rolling piston type pump can be used as a multicylinder pump. By cylinder multiplication, torque fluctuation during pump operation can be reduced, and when providing a displacement as the same as a capacity of a single cylinder pump, size can be made smaller than the single cylinder pump.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid pump for sucking and discharging a fluid, and is suitable, for example, for a vacuum pump for generating a negative pressure in a vehicle brake booster.

[0002]

2. Description of the Related Art In a vehicle having no negative pressure source, such as a diesel engine vehicle or an electric vehicle, a vacuum pump for generating a negative pressure in a brake booster is required. As a vacuum pump, a vane type pump in which a rotor rotates integrally with a drive shaft (for example, Japanese Patent Laid-Open No. 5-215)
No. 089) or a rolling piston type pump in which a rotor revolves around a drive shaft (see, for example, Japanese Patent Application Laid-Open No. 7-2).
No. 33792) is well known.

[0003]

However, since the vane type pump has a high peripheral speed at the vane tip, it is necessary to use a lubricating oil or set a low rotational speed to secure the reliability of the vane. Was needed.

On the other hand, the rolling piston type pump has a lower vane tip peripheral speed than the vane type pump, so that the reliability of the vane is easily ensured. However, since the rolling piston type pump is a single cylinder type pump having only one vane, the pump operation is There is a problem that the torque fluctuation at the time is large and the physique also becomes large.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and an object of the present invention is to provide a rolling piston type fluid pump which has small torque fluctuations during pump operation and can be downsized.

[0006]

In order to achieve the above object, according to the first aspect of the present invention, a drive shaft (20) having an eccentric portion (201) is mounted on an outer peripheral side of the eccentric portion (201). Bearing (23) and a cylindrical rotor (30) mounted on the outer peripheral side of the bearing (23) and revolving around the drive shaft (20) as the drive shaft (20) rotates.
And a cylindrical inner peripheral surface (101).
The rotor (30) is housed in the inner peripheral surface (101).
A housing (10, 1, 1) forming a working chamber (51, 52, 53) between the outer peripheral surface (301) of the rotor (30).
1, 12, 14), suction holes (141, 251) and discharge holes (12) communicating with the working chambers (51, 52, 53).
1), and the working chamber (5) associated with the revolution of the rotor (30).
1, 52, 53), the suction hole (14
1, 251), the working chambers (51, 52, 53) are rotated in the direction of rotation of the drive shaft (20) in a fluid pump for discharging fluid sucked into the working chambers (51, 52, 53) from the discharge holes (121). A plurality of vanes (4
0) and a plurality of working chambers (51, 52,
53) It is characterized in that fluid is sucked and discharged every time.

[0007] According to this, by dividing the working chamber into a plurality of chambers by a plurality of vanes, a rolling piston pump in which the reliability of the vanes can be easily ensured can be a multi-cylinder pump. This multi-cylinder type can reduce torque fluctuation during pump operation, and can be smaller than a single-cylinder pump when obtaining the same displacement as a single-cylinder pump.

According to the invention described in claim 2, the rotor (3
0) and the working chambers (51, 52, 5) together with the rotor (30) and the housings (10, 11, 12).
3) a plate (25) forming the plate (2);
5) is configured to be driven by the drive shaft (20) to rotate integrally with the drive shaft (20), a suction hole (251) is formed in the plate (25), and the plate (25) is rotated. As a result, a plurality of working chambers (51, 5,
2, 53), the working chambers (51, 52,
53), the suction holes (251) are configured to communicate sequentially.

According to this, the communication relationship between the suction hole and each working chamber is automatically switched with the rotation of the rotary plate, so that the valve on the suction side can be eliminated.

According to the third aspect of the present invention, the rotor (3
Rotation prevention mechanism (103, 123,
306).

According to this, by restricting the rotation of the rotor, the peripheral speed of the vane tip can be further reduced, and the reliability of the vane can be further enhanced.

This rotation preventing mechanism is provided with a rotor (30) and a housing (10,
11, 12, 14) provided on one of the pins (3, 12, 14).
06), the rotor (30) and the housing (10, 1
1, 12 and 14) and a pin insertion hole (123) into which the pin (306) is inserted and which defines the movement range of the pin (306).

The anti-rotation mechanism is provided in the housing (10, 11, 12, 14).
A concave portion (103) is formed on the inner peripheral surface (101) of one of the plurality of vanes (40) and one of the vanes (4) is formed.
0) may be configured to be locked to the recess (103).

The reference numerals in parentheses of the above means indicate the correspondence with specific means described in the embodiments described later.

[0015]

(First Embodiment) FIG. 1 is a sectional view of a fluid pump according to a first embodiment of the present invention, FIG. 2 is a sectional view taken along line AA of FIG. 1, and FIG. 1 is a sectional view taken along the line BB, FIG. 4 is a sectional view taken along the line CC in FIG. 1, and FIG.
It is sectional drawing which follows the DD line of FIG. 6 (a) to 6
(D) is a cross-sectional view along the line AA in FIG. 1, in which a change in an operation state accompanying rotation of the drive shaft 20 is represented by a rotation angle of the drive shaft 20 of 90 °.
It is shown for each case. 7A to FIG.
(D) is a cross-sectional view taken along the line BB of FIG. 1, wherein a change in an operation state accompanying rotation of the drive shaft 20 is represented by a rotation angle of the drive shaft 20 of 90 °.
It is shown for each case.

This pump is used, for example, as a vacuum pump for generating a negative pressure in a vehicle brake booster.

1 to 5, the pump body comprises three housings 10 to 12, and a front housing 11 and a rear housing 12 are provided on both sides of a middle housing 10 having an inner peripheral surface 101 formed in a cylindrical shape. The housing 10 is arranged so as to close both side openings.

The outer surface on the right side of FIG. 1 of the rear housing 12 is formed as a flat surface, and the electric motor 1 is mounted on the flat surface portion with screws (not shown) or the like. One end of a drive shaft 20 of the electric motor 1 extends into the pump main body, and is rotatably supported by bearings 21 and 22 mounted on a front housing 11 and a rear housing 12.

The drive shaft 20 has an eccentric portion 201 in which a center axis b is eccentric with respect to a rotation axis a of the drive shaft 20. A rotor support bearing 23 is mounted on an outer peripheral side of the eccentric portion 201. Further, balance weights 24 for balancing the mass of the eccentric part 201 and the rotor supporting bearing 23 are arranged on both sides of the eccentric part 201 and fixed to the drive shaft 20.

A disk-shaped rotary plate 25 is mounted near the front housing 11 of the drive shaft 20. The rotary plate 25 has an arc-shaped long suction hole 251 that can communicate with a working chamber described later. (See FIG. 3). Further, the outer peripheral side surface of the rotating plate 25 is in close contact with the side surface of the middle housing 10.

A cylindrical rotor 30 is mounted on the outer peripheral side of the rotor supporting bearing 23. The outer peripheral surface 301 of the rotor 30, the inner peripheral surface 101 of the middle housing 10,
By the rear housing 12 and the rotating plate 25,
An operation chamber described later is formed. The center of the rotor support bearing 23 and the center of the rotor 30 coincide with the center axis b of the eccentric part 201.

As shown in FIG. 2, the middle housing 10 has a rotation angle of 120 ° along the rotation direction Z of the drive shaft 20.
Are formed at equal intervals. In each groove 102, one plate-shaped vane 40 is slidably housed, and one spring 41 for urging the vane 40 toward the outer peripheral surface 301 of the rotor 30 is housed. .

The tip of the vane 40 is formed in an arc shape, and the arc-shaped tip is formed on the outer peripheral surface 301 of the rotor 30.
Is in contact with And, with these three vanes 40,
The working chamber is partitioned into first to third working chambers 51, 52, 53. Further, on one side surface of the vane 40, a discharge groove 401 communicating the first to third working chambers 51, 52, 53 and the groove portion 102 is formed. The volumes of the first to third working chambers 51, 52, 53 are repeatedly expanded and reduced with a phase difference of 120 ° due to the revolving motion of the rotor 30.

The suction hole 251 of the rotary plate 25
When the rotating plate 25 rotates together with the drive shaft 20, the first to third working chambers 51, 52, and 53 sequentially communicate with the working chamber whose volume is expanding, and communicate with the working chamber whose volume is decreasing. Does not communicate.

The front housing 11 has an inlet 1 connected to a pressure chamber of a vehicle brake booster (not shown).
11 and a suction chamber 112 which communicates the suction port 111 with the suction hole 251 of the rotary plate 25. The pressure chamber of the vehicle brake booster is formed through the suction port 111, the suction chamber 112 and the suction hole 251. Can be sucked into the first to third working chambers 51, 52, 53.

On the other hand, three discharge holes 121 are formed in the rear housing 12 so as to communicate with one of the three grooves 102 of the middle housing 10. A donut-shaped discharge plate 13 is disposed between the rear housing 12 and the electric motor 1.
3 and the rear housing 12 form a donut-shaped discharge chamber 122. The discharge chamber 122
Are connected to all three discharge holes 121 and are opened to the atmosphere by discharge ports 131 (see FIG. 5) formed in the discharge plate 13.

In the discharge chamber 122, a mushroom-shaped discharge valve 60 for opening and closing the discharge hole 121 is disposed. The discharge valve 60 is connected to the discharge chamber 122 from the first to third working chambers 51, 52, 53. To prevent backflow of air from the discharge chamber 122 to the first to third working chambers 51, 52, and 53. Therefore, the first to third working chambers 51, 5
2, 53 air can be discharged into the atmosphere through the discharge groove 401 of the vane 40, the groove 102 of the middle housing 10, the discharge hole 121 of the rear housing 12, the discharge chamber 122, and the discharge port 131 of the discharge plate 13. Has become.

Next, the operation of the pump having the above configuration will be described.

As shown in FIGS. 6 (a) to 6 (d), when the electric motor 1 is operated, the drive shaft 20 and the eccentric part 201 rotate (rotation direction Z), and the eccentric part 201 and the rotor supporting bearing are rotated. The common center axis b of the rotor 23 and the rotor 30 moves about the rotation axis a of the drive shaft 20. That is, the rotor 30 is connected to the rotation axis a of the drive shaft 20.
Revolve around the drive shaft 20 with the center as the center.

At this time, since the rotor 30 is supported by the bearing 23, it does not rotate integrally with the eccentric part 201,
Rotor 30 rotates bearing 23 due to rotation of eccentric portion 201.
Slightly spins (rotates) under the friction of the ball.

The position of the rotor 30 changes in the order of FIG. 6A, FIG. 6B, FIG. 6C, and FIG. Working chamber 51, 5
The volumes 2 and 53 are repeatedly enlarged and reduced with a phase difference of 120 °.

On the other hand, together with the drive shaft 20, the rotating plate 25
7 (a) → FIG. 7 (b) → FIG.
(C) → Suction hole 2 of rotary plate 25 in the order of FIG.
The position of the suction hole 251 changes as described above.
Communicates in sequence with the working chamber whose volume is expanding among the first to third working chambers 51, 52, 53.

The first to third working chambers 51, 52, 53
Performs a similar pumping operation with a phase difference of 120 °, the pumping operation of the first working chamber 51 will be described below.

FIGS. 6A and 7A show a state in which the volume of the first working chamber 51 is substantially minimum. At this time, the first working chamber 51 and the suction hole 251 are not in communication.
Then, the volume of the first working chamber 51 is expanding (FIG. 6B),
7C and FIGS. 7B and 7C), the first working chamber 51 communicates with the suction hole 251. In addition, between FIG. 6 (c) and FIG. 6 (d) (= between FIG. 7 (c) and FIG. 7 (d)), the first
The capacity of the working chamber 51 is maximized, and when the capacity is maximized, the communication between the first working chamber 51 and the suction hole 251 is cut off. And, while the volume of the first working chamber 51 is expanding,
Air in the pressure chamber of the vehicle brake booster is sucked into the first working chamber 51 through the suction port 111, the suction chamber 112, and the suction hole 251.

Next, when the volume of the first working chamber 51 decreases and the pressure of the first working chamber 51 becomes higher than the pressure of the discharge chamber 122, the discharge valve 60 opens. Thereby, the first
The air in the working chamber 51 is discharged to the discharge chamber 122 through the discharge groove 401 of the vane 40, the groove 102 of the middle housing 10, and the discharge hole 121 of the rear housing 12,
Further, the gas is discharged into the atmosphere through the discharge ports 131 of the discharge plate 13.

Then, by repeating the above-described pumping operation, the pressure chamber of the vehicle brake booster is set to a negative pressure.

In this embodiment, three vanes 40
By partitioning the first to third working chambers 51, 52, and 53, the pump action can be performed with a phase difference of 120 ° for each of the first to third working chambers 51, 52, and 53.
That is, the rolling piston type pump can be made into a multi-cylinder (three cylinders in this example), and by this multi-cylinder type, the torque fluctuation during the pump operation can be reduced, and
When obtaining the same displacement as that of the single cylinder pump, the size can be made smaller than that of the single cylinder pump.

Further, since the rotor 30 is only slightly swung (rotated) by the friction of the ball of the bearing 23, the peripheral speed of the outer peripheral surface 301 of the rotor 30 which comes into contact with the tip of the vane 40 is low. The reliability of 40 is also ensured.

The suction hole 251 of the rotating plate 25
When the rotating plate 25 rotates together with the drive shaft 20, the first to third working chambers 51, 52, and 53 sequentially communicate with the working chamber whose volume is expanding, and communicate with the working chamber whose volume is decreasing. Are not connected, so that the valve on the suction side can be eliminated.

(Second Embodiment) FIG. 8 is a sectional view of a fluid pump according to a second embodiment of the present invention, FIG. 9 is a sectional view taken along line EE of FIG. 8, and FIG. Sectional view along line F,
11 is a sectional view taken along line GG of FIG. 8, FIG. 12 is a sectional view taken along line HH of FIG. 8, and FIG. 13 is a sectional view taken along line II of FIG. FIGS. 14A to 14D show FIGS.
5 is a cross-sectional view taken along line EE of FIG. 5, showing a change in an operation state accompanying rotation of the drive shaft 20 for each rotation angle of the drive shaft 20 of 90 °.

In the first embodiment, the working chamber is formed by contacting the distal end of the vane 40 housed in the middle housing 10 with the outer peripheral surface 301 of the rotor 30.
In contrast to the working chambers 51, 52, and 53, in the present embodiment, the working chambers are first to first by contacting the tip of the vane 40 housed in the rotor 30 with the inner peripheral surface 101 of the middle housing 10. The third working chambers 51, 52, and 53 are partitioned. In the present embodiment, a rotation prevention mechanism for restricting rotation of the rotor 30 is newly added.

The other points are common to the first embodiment, and the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals.

Hereinafter, the present embodiment will be described with reference to FIGS. The rotor 30 has a double cylindrical shape, and an inner cylindrical portion 302 and an outer cylindrical portion 303 are connected by a rib 304. As shown in FIG. 9, three grooves 305 are formed in the rib 304 at regular intervals of 120 ° along the rotation direction Z of the drive shaft 20. In each groove 305, a plate-shaped vane 40 is slidably housed one by one, and a spring 41 for urging the vane 40 toward the inner peripheral surface 101 of the middle housing 10 is provided in each groove 305.
Are stored one by one.

The arc-shaped tip of the vane 40 is in contact with the inner peripheral surface 101 of the middle housing 10.
The working chamber is partitioned into first to third working chambers 51, 52, and 53 by the three vanes 40.

The groove 305 of the rotor 30 communicates with the discharge hole 121 of the rear housing 12 (see FIG. 11).
Therefore, the air in the first to third working chambers 51, 52, 53 is
Discharge groove 401, groove portion 305, discharge hole 121, discharge chamber 1
The air can be discharged into the atmosphere via the discharge port 22 and the discharge port 131.

On the other hand, as shown in FIGS. 8 and 13, three cylindrical pins 306 are mounted on the surface of the rotor 30 on the side of the rear housing 12, and these pins 306 rotate the drive shaft 20. 120 ° along direction Z
Are arranged at equal intervals. Also, the rear housing 12
Are formed on the surface on the rotor 30 side in which three cylindrical pin insertion holes 123 into which the protruding portions of the pins 306 are inserted.

Then, the pin 3 is inserted through the pin insertion hole 123.
06 is defined, thereby preventing rotation of the rotor 30. Therefore, the pin insertion hole 123 and the pin 3
Reference numeral 06 forms a rotation preventing mechanism that restricts rotation of the rotor 30. Note that the pin insertion hole 123 and the pin 306 are
The size, relative position, and the like are set so as not to hinder the revolving motion of the rotor 30 associated with the zero rotation.

In the above configuration, the rotor 30 revolves around the rotation axis a of the drive shaft 20 with the rotation of the drive shaft 20, and the revolving motion of the rotor 30 causes the rotor 30 to rotate as shown in FIG.
The position of the rotor 30 changes in the order of (a) → (b) → (c) → (d) of FIG.
The volumes 1, 52 and 53 are repeatedly enlarged and reduced with a phase difference of 120 °.

Here, the suction hole 251 of the rotary plate 25
Is connected to the working chamber whose volume is increasing among the first to third working chambers 51, 52, 53 sequentially.
While the volume of the suction chamber 111 is increasing, the suction port 111 and the suction chamber 1
The air in the pressure chamber of the vehicle brake booster is sucked into the first working chamber 51 through the suction hole 12 and the suction hole 251.

Next, for example, while the volume of the first working chamber 51 is reduced, the discharge groove 401, the groove 305, and the discharge hole 12 are formed.
1. The air sucked into the first working chamber 51 through the discharge chamber 122 and the discharge port 131 is discharged into the atmosphere.

In the present embodiment, three vanes 40
By partitioning the first to third working chambers 51, 52, 53, the pump action can be performed with a phase difference of 120 ° for each of the first to third working chambers 51, 52, 53.
Therefore, similarly to the first embodiment, torque fluctuation during pump operation can be reduced, and the size of the pump can be reduced.

Further, since the rotation of the rotor 30 is prevented by the pin insertion holes 123 and the pins 306, the peripheral speed of the tip of the vane 40 that contacts the inner peripheral surface 101 of the middle housing 10 is extremely low, and therefore the reliability of the vane 40 is reduced. Properties can be further enhanced.

The suction hole 251 of the rotary plate 25
When the rotating plate 25 rotates together with the drive shaft 20, the first to third working chambers 51, 52, and 53 sequentially communicate with the working chamber whose volume is expanding, and communicate with the working chamber whose volume is decreasing. Are not connected, so that the valve on the suction side can be eliminated.

(Third Embodiment) FIG. 15 is a sectional view of a fluid pump according to a third embodiment of the present invention, and FIG.
17 is a sectional view taken along line KK in FIG. 15, FIG. 18 is a sectional view taken along line LL in FIG. 15, FIG.
FIG. 9 is a sectional view taken along the line MM in FIG. FIG.
20A to 20D are cross-sectional views taken along the line JJ of FIG. 15, and show changes in an operation state accompanying rotation of the drive shaft 20 at every rotation angle of the drive shaft 20 of 90 °.

This embodiment differs from the second embodiment in that the anti-rotation mechanism (pin insertion hole 123 and pin 306) is changed. The other points are common to the second embodiment.
The same or equivalent parts as those of the embodiment are denoted by the same reference numerals.

The anti-rotation mechanism according to the present embodiment is particularly shown in FIG.
As shown in FIG. 1, a recess 103 is formed in the inner peripheral surface 101 of the middle housing 10 at one place, and three vanes 4 are formed.
The tip of one of the vanes 40 is locked to the recess 103. Both the recess 103 and the tip of the vane 40 are formed in an arc shape.

In the above configuration, the rotor 30 revolves around the rotation axis a of the drive shaft 20 as the drive shaft 20 rotates. At this time, since the tip of one vane 40 is locked by the recess 103 to prevent the rotor 30 from rotating, the rotor 30 swings around the position of the recess 103. That is, FIGS. 20 (a) to 20 (d)
As shown in FIG.
Orbits while oscillating. Thus, the volumes of the first to third working chambers 51, 52, 53 repeatedly expand and contract with a phase difference of 120 °, and perform the same pumping action as in the second embodiment.

According to the present embodiment, as in the second embodiment, the torque fluctuation during the operation of the pump can be reduced, the pump can be downsized, and the valve on the suction side can be eliminated.

Further, the tip of the vane 40 is
The rotation of the rotor 30 is prevented by the rotation prevention mechanism locked to the inner surface 101 of the middle housing 10.
The peripheral speed of the tip of each vane 40 that contacts the vane 40 is extremely low, so that the reliability of the vane 40 can be further improved.

(Fourth Embodiment) FIG. 21 is a sectional view of a fluid pump according to a fourth embodiment of the present invention. In the first embodiment, when the rotating plate 25 rotates, the suction holes 251 of the rotating plate 25 are moved to the working chambers 51 and 52,
53, so that air is sequentially sucked into each of the working chambers 51, 52, 53 through the suction hole 251. In the present embodiment, the configuration of the air suction unit is changed (the rotary plate 25 is omitted), and the other points are common to the first embodiment, and are the same as those in the first embodiment or the same in the equivalent parts. Are given.

As shown in FIG. 21, the middle housing 1
A disc-shaped sub front housing 14 is fixedly assembled between the front housing 11 and the front housing 11.
The sub-front housing 14 is formed with three suction holes 141 that respectively communicate three working chambers (not shown) and the suction chamber 112, and each of the suction holes 141 has a suction valve 142 that opens and closes each of the suction holes 141. And this suction valve 14
And a spring 143 for urging the valve 2 in the valve closing direction.

The rotor 3 associated with the rotation of the drive shaft 20
By the orbital motion of 0, the volume of each working chamber expands and contracts, and the suction valve 142 corresponding to the working chamber whose volume is expanding is opened, whereby the suction port 111, the suction chamber 112, and the suction hole 14 are opened.
1 and the air in the pressure chamber of the vehicle brake booster is sucked. The air in the working chamber whose volume is decreasing is
It is discharged into the atmosphere as in the first embodiment.

(Other Embodiments) In the first and fourth embodiments, the discharge holes 121 of the rear housing 12 communicate with the grooves 102 of the middle housing 10, respectively.
The discharge hole 121 may be directly connected to each of the working chambers 51, 52, and 53, and the discharge groove 401 of the vane 40 may be omitted. In this case, the air in each of the working chambers 51, 52, 53 is
2 and directly through the discharge hole 121 through the discharge chamber 122.
Is discharged.

In the second and third embodiments, the discharge holes 121 of the rear housing 12 are communicated with the grooves 305 of the rotor 30, respectively.
1, 52, and 53, and the discharge groove 401 of the vane 40 may be omitted. In this case, each working chamber 51, 5
The air of 2 and 53 is directly discharged to the discharge chamber 122 through the discharge hole 121 without passing through the groove 305.

The anti-rotation mechanism (pin insertion hole 123 and pin 306) shown in the second embodiment may be applied to the pump of the first embodiment.

In the rotation preventing mechanism according to the second embodiment, the pin 306 is mounted on the rotor 30 and the pin insertion hole 123 is formed in the rear housing 12. However, the pin 306 is mounted on the rear housing 12 and the rotor 30 is mounted on the rotor 30. The pin insertion hole 123 may be formed, and the movement range of the pin 306 may be defined by the pin insertion hole 123 to prevent the rotor 30 from rotating.

Further, the configuration of the air suction section of the fourth embodiment can be applied to the second and third embodiments. That is, the suction hole 141, the suction valve 142, and the spring 143
The second and third sub-front housings 14 having
It can be used instead of the rotating plate 25 of the embodiment.

In each of the above embodiments, three vanes 40 are used.
Although an example of a three-cylinder pump using two pumps has been described, a two-cylinder pump using two vanes 40 may be used, or a four-cylinder pump using four or more vanes 40 may be used.

In each of the above embodiments, an example in which the pump is used as a vacuum pump has been described. However, the present invention can also be used as a fluid pump (for example, an air pump or an air conditioner compressor) that compresses a suctioned fluid to increase its pressure and discharge it.

[Brief description of the drawings]

FIG. 1 is a sectional view of a fluid pump according to a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a sectional view taken along line BB of FIG. 1;

FIG. 4 is a sectional view taken along line CC of FIG. 1;

FIG. 5 is a cross-sectional view taken along line DD of FIG.

FIG. 6 is a cross-sectional view taken along the line AA of FIG. 1, illustrating a change in an operation state due to rotation of the drive shaft 20;
It is shown for each case.

7 is a cross-sectional view taken along the line BB of FIG. 1, and illustrates a change in an operation state caused by rotation of the drive shaft 20;
It is shown for each case.

FIG. 8 is a sectional view of a fluid pump according to a second embodiment of the present invention.

FIG. 9 is a sectional view taken along line EE in FIG. 8;

FIG. 10 is a sectional view taken along line FF of FIG. 8;

FIG. 11 is a sectional view taken along line GG of FIG. 8;

FIG. 12 is a sectional view taken along the line HH in FIG. 8;

FIG. 13 is a sectional view taken along line II of FIG. 8;

FIG. 14 is a sectional view taken along line EE in FIG.
The change of the operating state due to the rotation of the
It is shown for each °.

FIG. 15 is a sectional view of a fluid pump according to a third embodiment of the present invention.

FIG. 16 is a sectional view taken along the line JJ of FIG. 15;

17 is a sectional view taken along the line KK of FIG.

18 is a sectional view taken along line LL in FIG.

FIG. 19 is a sectional view taken along the line MM of FIG. 15;

20 is a sectional view taken along line JJ of FIG.
The change in the operating state due to the rotation of 0 is determined by the rotation angle 9 of the drive shaft 20.
It is shown every 0 °.

FIG. 21 is a sectional view of a fluid pump according to a fourth embodiment of the present invention.

[Explanation of symbols]

10, 11, 12, 14 ... housing, 20 ... drive shaft,
23 ... bearing, 30 ... rotor, 40 ... vane, 5
1, 52, 53 ... working chamber, 101 ... inner peripheral surface, 121 ... discharge hole, 141, 251 ... suction hole, 201 ... eccentric part, 30
1 ... outer peripheral surface.

──────────────────────────────────────────────────の Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F04C 25/02 F04C 25/02 AL 29/00 29/00 D (72) Inventor Shin Sasaki Kariya, Aichi 1-1-1, Showa-cho, Ichiba F-term in Denso Co., Ltd. (reference)

Claims (7)

[Claims] A drive shaft (2) having an eccentric part (201)
0), a bearing (23) mounted on an outer peripheral side of the eccentric part (201), and a bearing (23) mounted on an outer peripheral side of the bearing (23), and the drive shaft (20) is rotated with the rotation of the drive shaft (20). 20) having a cylindrical rotor (30) orbiting around a cylindrical inner peripheral surface (101);
1) A housing for accommodating the rotor (30) therein and forming a working chamber (51, 52, 53) between the inner peripheral surface (101) and the outer peripheral surface (301) of the rotor (30). (10, 11, 12, 14) and the suction holes (1) communicating with the working chambers (51, 52, 53).
41, 251) and a discharge hole (121), and the working chamber (51, 5, 5) associated with the revolution of the rotor (30).
2, 53), the suction hole (141,
251) to discharge the fluid sucked into the working chambers (51, 52, 53) from the discharge holes (121), wherein the working chambers (51, 52, 53) are connected to the drive shaft (20).
A plurality of vanes (40) partitioned into a plurality of sections along the rotation direction of the working chamber (5);
1, 52, and 53), wherein the fluid is suctioned and discharged every time. 2. The rotor (30) and the housing (10, 1
1, 12) and a plate (25) forming the working chamber (51, 52, 53), wherein the plate (25) is driven by the drive shaft (20) to be integral with the drive shaft (20). The plate (25) is formed with the suction hole (251), and as the plate (25) is rotated, the plurality of working chambers (51) are partitioned. , 52, 53), wherein the suction hole (251) is configured to sequentially communicate with the working chamber (51, 52, 53) whose volume is expanding. pump. 3. The fluid pump according to claim 1, further comprising a rotation preventing mechanism (103, 123, 306) for restricting rotation of the rotor (30). 4. The rotation preventing mechanism according to claim 1, wherein the rotation preventing mechanism comprises:
0) and said housing (10, 11, 12, 14)
A pin (306) provided on one of the rotor, the rotor (30) and the housing (10, 11, 12,
14) and the pin (3)
The fluid pump according to claim 3, further comprising a pin insertion hole (123) into which the pin (306) is inserted to define a moving range of the pin (306). 5. A plurality of vanes (40) are housed in grooves (305) formed in the rotor (30), and ends of the plurality of vanes (40) are connected to the housing (10, 11, 12, 14) inner peripheral surface (101)
A fluid pump that contacts the housing (10, 11, 1, 1).
A recess (103) is formed in the inner peripheral surface (101) of the second and second vanes (2, 14), and an end of one of the vanes (40) is formed in the recess (103). The fluid pump according to claim 3, wherein the fluid pump is configured to be locked. 6. The housing (10, 11, 12, 1).
The plurality of vanes (40) are accommodated in the grooves (102) formed in the plurality of vanes (4).
The end of (0) is in contact with the outer peripheral surface (301) of the rotor (30).
4. A fluid pump according to claim 1. 7. A plurality of vanes (40) are housed in grooves (305) formed in the rotor (30), and ends of the plurality of vanes (40) are connected to the housing (10, 11, 12, 14) inner peripheral surface (101)
The fluid pump according to claim 1, wherein the fluid pump contacts the fluid pump.