JP2003336589A - Displacement fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce mechanical loss caused by the frictional sliding of a vane in a slot in a displacement fluid machine such as a vane compressor. <P>SOLUTION: The vane 54 oscillates like a fan around a shaft part 52a in a sector space formed by a partition wall 2d in a cylinder 2. The sector space is partitioned by the vane 54, and two spaces are formed. When the two spaces are used as a control pressure chamber 2a and a working chamber 2b, the fluid is pressurized by the working chamber 2b, and the pressure of the control pressure chamber 2a is varied by a control valve. Thus, an angle oscillation width of the vane 54 is varied, and the delivery capacity of the displacement fluid machine, for example used as a refrigerant compressor, can be continuously varied to 0%. When the two spaces are used as the working chambers, the capacity cannot be varied but the delivery capacity can be doubled. The sliding part is only an edge part of the vane 54, and the oscillation of the vane 54 is also stopped when the capacity is 0%. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a positive displacement fluid machine (compressor, pump or prime mover) capable of handling an incompressible fluid or a compressible fluid, and uses a vane. Unlike the vane type fluid machine in which each vane slides in and out in the slots provided in the rotor etc. in the radial direction, each vane swings like a fan. Thus, for example, the present invention relates to a positive displacement fluid machine that can be used as a refrigerant compressor in an air conditioner.

[0002]

2. Description of the Related Art A conventional example of a vane type positive displacement compressor is described in Japanese Patent Application Laid-Open No. 11-13662. In this compressor, vanes are freely inserted into and removed from a plurality of slots formed in a cylindrical rotor attached to a shaft, and the tips of the vanes are attached to the inner surface of a cylinder having a substantially elliptical cross section. In a normal vane type compressor that forms a plurality of working chambers by sliding contact, the number of vanes and slots is limited to seven, and although it is not novel, the inner surface side of the side block A control plate having a substantially disk shape that can rotate around the shaft is provided, and a pair of recesses formed at opposite positions of the peripheral edge of the control plate allows the suction chamber and suction chamber to be located at positions corresponding to the recesses. It forms a bypass passage that communicates with the chamber, and changes the effective capacity of the compressor by bypassing the compressed refrigerant in the working chamber to the suction chamber. It has become to so that.

In recent years, in an air conditioner for a vehicle, in order to reduce the cost and the size and weight, the refrigerant compressor is of a variable capacity type, and normally, it is provided between a driving engine and the refrigerant compressor. The electromagnetic clutch that is often installed in the compressor is abolished, and the compressor shaft is constantly rotated by connecting them directly, and the capacity of the compressor is reduced from 0% to 100%.
%, The capacity of the air conditioner can be adjusted over a wide range, and the compressor can be adjusted to 0%.
It is considered that the same operating state as when the electromagnetic clutch is turned off is obtained by setting the capacity. However, when a vane type compressor like the above-mentioned conventional example is used for this purpose, in the conventional vane type compressor, not only the edge of the vane slides along the inner surface of the cylinder, but also the vane moves to the rotor. There is a large mechanical loss because it slides in and out in the formed slot, and in particular, in the above-mentioned conventional technology, the compression stroke becomes shorter as the capacity of the compressor is decreased, so that the torque fluctuation becomes large. The problem is that it adversely affects the engine. Further, according to such a configuration, there is a problem that the capacity control becomes difficult because the escape of the refrigerant in the bypass passage deteriorates in the high speed operation state.

[0004]

In view of the above-mentioned problems in the prior art, the present invention can be implemented not only as a fixed capacity type, but also as a capacity of 100% and 0% smoothly and continuously. It can be implemented as a variable capacity type that changes between the two, and each vane does not slide in and out in the slots formed in the rotor, etc. It is an object of the present invention to provide a vane type fluid machine of a new type, in which a mechanical loss due to sliding is extremely small, in particular, a compressor, in which a sliding portion of the above is completely eliminated.

[0005]

The present invention provides a positive displacement fluid machine according to claim 1 as a means for solving this problem.

In this positive displacement fluid machine, the vanes oscillate like a fan in the internal space of the cylinder to pressurize the fluid for pumping or compression.
Unlike the conventional vane type fluid machine, since the vane does not make a sliding motion such that it goes in and out of the slot formed in the rotor or the like, there is no mechanical loss due to sliding friction between the slot and the vane, and at least that Efficiency is improved by that amount.

More specifically, the positive displacement fluid machine of the present invention maintains airtightness with respect to a cylinder having at least one fan-shaped space formed therein and an inner wall surface of the fan-shaped space consisting of a part of a rotating surface. A plate-shaped vane that allows the sliding edges to come into contact with each other, and a shaft support that allows the vanes to swing around the central axis of the fan-shaped space by holding a part different from the sliding edges of the vane. And a fluid in at least one of the fan-shaped spaces partitioned by the vane into two parts can be configured to be pressurized together with the oscillating movement of the vane. In this case, a motion conversion mechanism having at least one revolving member for converting one of the oscillating motion and the rotating motion into the other is provided between the oscillating vane and the rotating shaft. Can be provided.

In the positive displacement fluid machine as described above, if one part of the fan-shaped space partitioned into two parts by the vane is configured as the working chamber and the other part is configured as the control pressure chamber, the control pressure is controlled. When the pressure in the chamber is changed by a control valve or the like, the angular amplitude of the vane forming the working chamber changes, so the capacity of the positive displacement fluid machine corresponding to the volume of the working chamber changes steplessly. As a result, when the positive displacement fluid machine is implemented as a refrigerant compressor of an air conditioner, for example, the discharge amount of the refrigerant compressor per unit time can be changed steplessly. It is possible to continuously control the cooling capacity of the vehicle over a wide range.

On the other hand, when both parts of the fan-shaped space divided into two parts by the vanes are configured as working chambers, the angular amplitude of the vanes cannot be changed, so that the positive displacement fluid The machine will be of the fixed displacement type, but instead, the volume of the working chamber will be double that of the variable displacement type described above, so the capacity of the displacement type fluid machine will be doubled. Of course, also in this case, the sliding friction of the vane is only generated between the sliding edge portion and the inner wall surface of the cylinder, so the mechanical loss is significantly smaller and higher than the conventional vane type positive displacement fluid machine. The efficiency is obtained in the same way as in the variable capacitance type.

The above-described motion converting mechanism prevents the rotation of the eccentric drive part which is eccentric with respect to the center axis of the shaft, the rotative plate which is rotatably supported by the eccentric drive part and revolves. The rotation prevention mechanism, a long groove in the radial direction in which a pin projecting from the swivel plate in the axial direction of the shaft engages, and a vane is attached and is rotatably supported by a shaft supporting portion. And a vane drive link composed of an existing shaft. Further, it is preferable that the shaft portion of the vane drive link is provided with a slot-shaped double-width portion to receive and support the vane therein.

The displacement volume of the positive displacement fluid machine can be changed by changing the eccentricity of the swivel plate with respect to the central axis of the shaft and the revolution radius to change the angular amplitude of the vane. In this case, a columnar swing having an eccentric hole so as to be rotatably attached to the eccentric drive part and rotatably supporting the swivel plate between the eccentric drive part of the shaft and the swivel plate. A bush can be interposed. Further, it is preferable that one of the generatrixes of the hole formed eccentrically in the swing bush is aligned with the central axis of the swing bush in order to smoothly change the capacity.

A rotation preventing mechanism for preventing rotation of the swivel plate is rotatably supported by a plurality of conical groove portions formed on the side surface of the swivel plate, balls engaging with the conical groove portions, and a part of the housing. And a disc having a hole for holding a plurality of balls, a means for urging the same in the rotational direction, and a plurality of balls respectively engaged with each other toward the conical groove portion of the swivel plate. For extruding, it is preferable to provide a plurality of ball groove portions having a wedge-shaped cross section formed on the surface of the housing.

With such a structure, when the ball engages with the center of the conical groove portion of the swivel plate, the revolution radius of the swivel plate becomes 0 and the angular amplitude of the vane becomes 0, and as a result, the displacement type fluid machine. Can be configured so that the discharge capacity of is zero. INDUSTRIAL APPLICABILITY The positive displacement fluid machine of the present invention is suitable for use as a compressor for compressing a fluid, and particularly for use as a refrigerant compressor in a refrigeration cycle of an air conditioner.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION Next, referring to the attached drawings of FIGS. 1 to 10, a refrigerant compressor for an air conditioner embodied as a first embodiment of a positive displacement fluid machine of the present invention. The details will be described. In the front housing 1 of the compressor,
A shaft 4 that receives a rotational driving force from a power source (not shown) is supported by a front thrust bearing 11 and a main bearing 13, and at a portion where the shaft 4 penetrates the front housing 1, the shaft seal 12 is a compressor of the compressor. It seals between the inside and the outside air.

The shaft 4 is integrally provided with an eccentric drive section 41 having a central axis decentered from the central axis thereof.
A swing bush 43 having a cylindrical outer shape is rotatably attached to the eccentric drive unit 41. Therefore, the swing bush 43 is provided with a hole 43a having a diameter substantially the same as that of the eccentric drive unit 41 at a position eccentric with respect to its own central axis.
One of the generatrix lines forming the inner surface of the hole 43a coincides with the central axis of the swing bush 43. This hole 4
3a is rotatably fitted to the eccentric drive portion 41 of the shaft 4, and is prevented from coming off by the circlip 42.
Since the swing bush 43 can swing like a pendulum about the eccentric drive unit 41 of the shaft 4,
When the distance between the central axis of the shaft 4 and the central axis of the swing bush 43 is referred to as "eccentricity amount e", the eccentricity amount e has a value that continuously changes.
Is the radius of the orbital movement of the orbiting plate 51 and the like (abbreviated as "orbital radius").

The swivel plate 51 may be a donut-shaped thick ring-shaped disc originally, but in the first embodiment, it does not block the plurality of suction holes 22.
As shown in FIG. 4, it has a shape with irregularities on the outer circumference.
The swivel plate 51 is rotated by the swing bush 43 via a needle bearing 44 mounted in a central circular hole so that the swing bush 4 can rotate.
Supported by 3. On the surface of the swivel plate 51 on the front housing 1 side, a plurality of conical groove portions 51a are uniformly arranged in a portion close to the outer periphery and are formed as conical recesses.
The inner surface of the front housing 1 corresponding to the plurality of conical groove portions 51a is inclined in the same circumferential direction as shown in FIGS. 5 and 6, and the depth thereof changes. The wedge-shaped ball groove portion 14 is formed, and the same number of balls 16 are sandwiched between the conical groove portion 51a and the ball groove portion 14 and are in rolling contact with the groove portions 14 and 51a.

A front plate 18 having a plurality of holes having substantially the same diameter as the balls 16 in order to maintain a predetermined space between the plurality of balls 16 serves as a retainer for the balls 16 inside the front housing 1. It is sandwiched between it and the swivel plate 51, is rotatably mounted around the central axis of the shaft 4, and is biased by the spring 19 in one direction of the rotational direction. Thereby,
Since the rotation plate 51 is restricted from rotating by the engagement of the conical groove portion 51a and the ball groove portion 14 with the ball 16 when the shaft 4 rotates, only the revolving motion including rotation does not occur. In FIG. 1, reference numeral 15 denotes a circlip for positioning the front bearing 11 on the shaft 4.

A plurality of pins 53 provided so as to project rearward from the swivel plate 51 in parallel with the central axis of the shaft 4 have the same number of vane drive links 52 having the shapes shown in FIGS. 1 and 3, respectively. Long groove portion 52c is engaged. As shown in FIG. 2, inside the substantially cylindrical cylinder 2 that is integrated with the front housing 1 with the front side plate 21 interposed therebetween, a central portion is formed in a radial direction from an outer shell portion that is a part of the housing. A plurality of plate-shaped partition walls 2d extending toward each other are formed. At a slightly eccentric position of the hub 2e at the central portion where the plurality of partition walls 2d are concentrated and integrated, a plurality of cylindrical shaft support portions 2c, which are mostly cylindrical, are formed parallel to the central axis of the shaft 4. In addition, the shaft portion 52a of the vane drive link 52 described above is attached to the shaft support portions 2c.
The vane drive links 52 are inserted through the holes of the same diameter formed in the shaft support portion 2c.
And the shaft portion 52a is supported so as to be freely rotatable around a common axis line.

The shaft portion 52a of the vane drive link 52 has
So-called "width across flats" 52b that form slots formed by two planes parallel to each other are provided, and each flat width vane 54 is supported by each width across flat 52b. The vane 54 may be fixed to the flat width portion 52b, or may be slidable along the flat width portion 52b in some cases. Of course, even though it is "sliding possible", the vane 54 does not slide in the flat width portion 52b and move largely in the radial direction, and the sliding edge portion of the vane 54 is Since the cross-sectional shape of a part of the rotating surface is slidably in contact with the arcuate inner surface, a large change of the vane 54 in the radial direction is prevented, and the sliding edge of the vane 54 is prevented. The contact surface pressure between the contact portion and the inner surface of the cylinder 2 is automatically adjusted by centrifugal force or the like acting on the vane 54, and only slightly moved to reduce wear while maintaining a sufficient sealed state. .

Therefore, when the revolving plate 51 revolves around the orbit, the long groove portion 52 engaged with the pin 53 integral with the revolving plate 51.
By c, the vane drive link 52 swings around the central axis of the shaft portion 52a. As a result, the vanes 54 attached to the shaft portion 52a swing like a fan around the same central axis line along the outer shell of the cylinder 2, so that any two adjacent vanes formed in the cylinder 2 can be swung. The fan-shaped space partitioned by the partition walls 2d is further divided into two parts by one vane 54 swinging between the partition walls 2d to form two spaces whose volumes change reciprocally. .

In the refrigerant compressor of the first embodiment, these two spaces are used as a control pressure chamber 2a and a working chamber 2b as shown in FIG. The control pressure introducing hole 24 is formed in the cylinder rear plate 2f on the control pressure chamber 2a side, and the cylinder rear plate 2f is formed on the working chamber 2b side.
2 and a suction hole 22 as shown in FIGS. 1 and 3 are formed in the front side plate 21. A suction valve 62 is provided at the opening of the suction hole 22 in the front side plate 21, and the suction valve 62 is protected by a suction valve stopper 61. In this way, the suction hole 22 communicates with the suction chamber 17 formed between the front housing 1 and the front side plate 21. The swivel plate 51, the front plate 18, and the like described above are provided in the suction chamber 17.

As shown in FIG. 1, the cylinder 2 has a bottom, and the cylinder rear plate 2f, which is the bottom thereof, has the discharge hole 23 opened as described above. A rear housing 3 is integrated in the rear part of the cylinder 2, and the rear housing 3
The rear end of the discharge hole 23 is opened in the discharge chamber 31 formed inside the discharge chamber 31, and the discharge valve stopper 63 is provided in the opening portion.
Is provided with a discharge valve 64. The rear housing 3 is provided with a control valve 65, and the detailed structure of the control valve 65 is the same as that used in a conventionally well-known variable displacement type swash plate compressor or the like. Although not shown because it may be present, the control valve 65 is duty-controlled by a means such as an electronic control device (not shown) so that the discharge pressure (high pressure) of the discharge chamber 31 and the suction chamber 17 are increased.
The control pressure having an arbitrary height intermediate to the suction pressure (low pressure) is generated and supplied to the control pressure adjusting chamber 67 through the control pressure introducing hole 66 formed in the rear housing 3. . The control pressure adjusting chamber 67 supplies the control pressure to the aforementioned control pressure chamber 2a through the control pressure introducing hole 24.

The front housing 1, which is a housing constituent member of the refrigerant compressor of the first embodiment, the front side plate 21, the cylinder 2 including the cylinder rear plate 2f, and the rear housing 3, the center of the shaft 4. They are integrated by fastening a plurality of through bolts 7 arranged parallel to the axis.

Since the refrigerant compressor of the first embodiment has such a structure, when the shaft 4 is driven by an internal combustion engine or the like to rotate, the swing bush 43 rotates in an eccentric state. As shown in FIGS. 5 and 6, the swivel plate 51 regulates its rotation by the ball 16 supported by the ball groove portion 14 whose depth changes in the circumferential direction and the conical groove portion 51a formed in the swivel plate 51. Therefore, the swing bush 43 and the shaft 4 revolve around the eccentric amount e.

When the swivel plate 51 revolves, the vane drive link 52 engaged by the pin 53 swings (swings) about the shaft portion 52a, and the vane 54 attached to the two-face width portion 52b. Rock like a fan. Since swinging of the vane 54 accompanies expansion and contraction (volume change) of the working chamber 2b, when the working chamber 2b expands, the suction chamber 1
The low-pressure refrigerant (generally, the fluid to be compressed) in 7 is sucked into the working chamber 2b through the suction hole 22 and the suction valve 62, and when the working chamber 2b shrinks, the refrigerant inside is compressed and discharged. Hole 2
3 and the discharge valve 64 to discharge into the discharge chamber 31.

In addition to this basic compression action, the compressor of the first embodiment is of a variable capacity type, so that the discharge capacity can be changed. Therefore, a part of the refrigerant adjusted to a control pressure of an arbitrary height by the control valve 65 provided in the rear housing 3 is supplied to the control pressure adjusting chamber 67, which passes through the control pressure introducing hole 24 and the cylinder 2. It is guided to the internal control pressure chamber 2a. When the pressure of the control pressure chamber 2a is the lowest like the suction pressure, a force that prevents the swing of the vane 54 when the vane 54 is driven via the pin 53 of the swivel plate 51 and the vane drive link 52. Since the vane 54 swings at the maximum angular amplitude and the revolution radius of the drive-side swivel plate 51 becomes maximum accordingly, the swing bush 43 is the most eccentric drive part 41 of the shaft 4. It rotates greatly and the amount of eccentricity e with respect to the shaft 4 becomes maximum. The state at this time is the operation state of 100% capacity shown in FIGS.

When the discharge capacity of the refrigerant compressor is reduced, the control valve 65 gradually increases the pressure in the control pressure chamber 2a, that is, the control pressure, to bring it closer to the discharge pressure. As the control pressure increases, the vane 54 is pushed toward the working chamber 2b side and slightly rotates around the shaft portion 52a according to the height, so that the vane 54 can swing in an angular range (angular amplitude). Becomes smaller due to restrictions. On the other hand, since the compression reaction force is generated by compressing the refrigerant in the working chamber 2b, the vane 54 is pushed back to the control pressure chamber 2a side to prevent the working chamber 2b from being reduced in size. Is determined in a state where their contradictory effects are balanced.

Further, as a result of the pressure rise in the control pressure chamber 2a and the compression reaction force increasing in the working chamber 2b thus antagonizing each other, when the force pushing the vane 54 toward the working chamber 2b exceeds the force resisting it. The moment of the force that pushes the vane 54 is transmitted to the vane drive link 52 from the two-face width portion 52b of the shaft portion 52a, and a force for suppressing the rotation of the vane drive link 52 around the shaft portion 52a is generated. The force for suppressing the rotation of the vane drive link 52 is the pin 5
Is transmitted to the swivel plate 51 through the swivel plate 5
1 is a force for suppressing the revolution, that is, a force for rotating the swing bush 43 with respect to the eccentric drive unit 41 to reduce the revolution radius. As described above, the swivel plate 51 has a difference between the force for increasing the revolution radius due to the compression reaction force and the force for decreasing the revolution radius due to the control pressure, and the revolution radius changes due to the difference force. At the same time, the discharge capacity of the refrigerant compressor, which is determined by the angular amplitude of the vane 54, changes steplessly.

When the revolving plate 51 tries to rotate in the direction in which the control pressure increases and the revolution radius decreases, the balls 16 held by the holes of the front plate 18 and the ball groove portions 14 of the front housing 1 are moved to the position shown in FIG.
Groove portion 14a on the 100% capacity side of the ball groove portion 14 shown in FIG.
To the groove portion 14b on the 0% capacity side shown in FIG. The cross-sectional shape of the ball groove portion 14 is tapered, and the depth of the groove is gradually shallowed from the groove portion 14a on the 100% capacity side to the groove portion 14b on the 0% capacity side to form a slope 14c. Therefore, when the ball 16 moves from the former direction to the latter direction, the ball 16 bids up due to the slope 14c, and the contact point with the conical groove portion 51a of the turning plate 51 moves toward the apex of the cone. Then
The revolution radius of the swivel plate 51 is reduced. At the same time, the rotation plate 5 is prevented from rotating during the revolution movement.
1 makes an orbital motion at an orbital radius adjusted by the control valve 65.

In this case, the ball 16 has a spring 19 for biasing the front plate 18 in the direction of increasing the revolution radius.
And the force acting on the swivel plate 51 in opposition thereto are rolled and moved to a position where they balance each other. As described above, by adjusting the control pressure of the control pressure chamber 2a by the control valve 65, the discharge capacity of the refrigerant compressor can be changed to an intermediate capacity of an arbitrary size. The operating state of such an intermediate capacity is shown in FIGS. 7 and 8. In this case, the vane 54 swings at a limited angular amplitude.

When the control pressure is maximized by operating the control valve 65, the control pressure becomes substantially equal to the discharge pressure. In this state, the ball 16 moves to the groove portion 14b on the 0% capacity side of the ball groove portion 14 as shown in FIG. At that time, the ball 16 comes to the center of the conical groove portion 51a of the orbiting plate 51 as shown in FIG. 9, so that the revolution radius becomes zero. At this time, the angular amplitude of the vanes 54 becomes 0, and as shown in FIG. 10, all of the vanes 54 have the partition walls 2d on the side of the working chamber 2b.
It will be in close contact with and will not swing. Therefore, the compressor does not perform the compression operation of the refrigerant even if the shaft 4 is provided with something like an electromagnetic clutch to shut off the power from the driving side. Further, at this time, since the vane 54 does not slide on the inner surface of the cylinder 2, power loss due to mechanical loss is extremely small. As a result, the power is significantly reduced compared to the operating state in which the conventional variable displacement compressor is set to 0% capacity, and the vane itself, the rotor slot, or the cylinder generated by sliding in the conventional vane compressor is reduced. Since the wear of the inner surface and the like is also reduced, the durability of the compressor is increased.

Further, in the refrigerant compressor of the first embodiment, since the pressure of the suction chamber 17 which is shut off from the outside air by the shaft seal 12 is always a relatively low suction pressure, the shaft seal 12 has a high pressure difference. Since it does not work, compared to a variable capacity swash plate compressor that uses the swash plate chamber as a control pressure chamber, etc., it has sufficiently high durability without using a particularly expensive shaft seal 12. Is obtained.

11 and 12 show a compressor as a second embodiment of the present invention. Unlike the refrigerant compressor of the first embodiment of the variable capacity type, the compressor of the second embodiment is of the fixed capacity type. However, some parts use substantially the same thing, so that they are given the same reference numerals or the reference numerals are omitted.

In the fixed displacement type compressor of the second embodiment, since it is not necessary to change the revolution radius of the swivel plate 51, the eccentric amount in which the eccentric drive section 41 'is integrated is used as the shaft 4'. Use a constant crankshaft. Further, in the first embodiment, the front housing 1 '
Corresponding to the wedge-shaped ball groove portion 14 provided in
In the second embodiment, it is a hemispherical recess 14 'that can hold the ball 16 in place.

As shown in FIG. 12, the cylinder 2'is also provided with a plurality of partition walls 2d, but since it is not necessary to provide the control pressure chamber 2a unlike the first embodiment, the compression of the second embodiment is performed. In the machine, the space is used as the second working chamber 2b '. Therefore, between the two adjacent partition walls 2d, 2 are formed on both sides of the swinging vane 54.
Each of the two spaces is a working chamber for compressing a fluid such as a refrigerant. As a result, the compressor of the second embodiment has approximately twice the discharge capacity of the compressor of the first embodiment.
Since the first working chamber 2b and the second working chamber 2b 'are formed, the cylinder rear plate 2f has a discharge hole 23' that communicates with the discharge chamber 31 'in the rear housing 3'from the working chamber 2b' and A discharge valve 64 'is additionally provided. For the same reason, the front side plate 21 'has a first
In addition to the suction hole 22 and the suction valve 62 similar to those of the embodiment, a suction hole 22 'and a suction valve 62' for connecting the working chamber 2b 'and the suction chamber 17 are provided.

Since the compressor of the second embodiment is constructed as a fixed capacity type in this way, the discharge capacity cannot be changed like the compressor of the first embodiment, but it has a double acting structure. And the action have the characteristic that the discharge capacity is almost doubled even if the compressor has the same size as the compressor of the first embodiment.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a variable displacement compressor as a first embodiment.

FIG. 2 is a cross-sectional view of the compressor of the first embodiment taken along the line AA in FIG.

FIG. 3 is a cross-sectional view of the compressor of the first embodiment taken along the line BB in FIG.

FIG. 4 is a transverse cross-sectional view of the compressor of the first embodiment taken along the line CC of FIG.

5A and 5B show a 100% capacity state of the compressor of the first embodiment, FIG. 5A is a cross-sectional view taken along the line DD of FIG. 1, and FIG. 5B is a partial enlargement of FIG. FIG.

6 shows a state of 0% capacity of the compressor of the first embodiment, (A) is a cross-sectional view taken along the line DD of FIG. 1, FIG.
(B) is a partially enlarged vertical sectional view of (A).

FIG. 7 is a partial vertical sectional view showing a state of an intermediate capacity of the compressor of the first embodiment.

FIG. 8 is a transverse cross-sectional view taken along the line AA of FIG. 1 showing a state of the intermediate capacity of the compressor of the first embodiment.

FIG. 9 is a partial vertical sectional view showing a state of 0% capacity of the compressor of the first embodiment.

FIG. 10 is a transverse cross-sectional view taken along the line AA of FIG. 1 showing the state of 0% capacity of the compressor of the first embodiment.

FIG. 11 is a vertical sectional view of a fixed displacement compressor according to a second embodiment.

FIG. 12 is a transverse cross-sectional view taken along the line A′-A ′ in FIG. 11 of the compressor according to the second embodiment.

[Explanation of symbols]

2 ... Cylinder 2a, 2a '... Control pressure chamber 2b ... Working chamber 4 ... Shaft 4 '... eccentric crankshaft 14 ... Ball groove 14 '... hemispherical depression 16 ... ball 17 ... Inhalation chamber 21 ... Front side plate 31 ... Discharge chamber 41 ... Eccentric drive 43 ... Swing bush 51 ... Swivel plate 51a ... Conical groove 52 ... Vane drive link 52a ... Shaft 52b ... Width across flats 52c ... long groove 53 ... pin 54 ... Vane 65 ... Control valve 67 ... Control pressure adjusting chamber

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Motohiko Ueda             1-1, Showa-cho, Kariya city, Aichi stock market             Inside the company DENSO (72) Inventor Mitsuo Matsuda             14 Iwatani Shimohakaku-cho, Nishio-shi, Aichi Stock Association             Company Japan Auto Parts Research Institute (72) Inventor Shigeru Kuninaga             1-1, Showa-cho, Kariya city, Aichi stock market             Inside the company DENSO F-term (reference) 3H029 AA02 AA05 AA17 AB01 BB21                       BB42 BB52 CC02 CC08 CC12                       CC16 CC17                 3H039 AA02 AA11 BB02 BB22 CC01                       CC13 CC15 CC39

Claims (15)

[Claims] 1. A positive displacement fluid machine, wherein fluid is pressurized and pumped or compressed by oscillating motion of a vane in an internal space of a stationary cylinder. 2. A cylinder in which at least one fan-shaped space is formed, and an inner wall surface of the fan-shaped space formed of a part of a rotating surface can be brought into contact with the sliding edge while maintaining airtightness. A plate-shaped vane, and a shaft support portion that holds the portion different from the sliding edge portion of the vane to allow the vane to swing around the central axis of the fan-shaped space, A positive displacement fluid machine, wherein fluid in at least one of the fan-shaped spaces partitioned into two parts by a vane is configured to be pressurized together with the swinging motion of the vane. 3. The at least one revolution for converting either one of the swinging motion and the rotating motion into the other between the vane performing the swinging motion and the rotating shaft according to claim 1 or 2. A positive displacement fluid machine characterized in that a motion conversion mechanism having a member that moves is provided. 4. The positive displacement fluid machine according to claim 2, wherein one part of the fan-shaped space partitioned by the vane into two parts is configured as a working chamber. 5. The positive displacement fluid machine according to claim 4, wherein the other part of the fan-shaped space partitioned by the vane into two parts is configured as a control pressure chamber. 6. A positive displacement fluid machine according to claim 2, wherein both of the fan-shaped spaces partitioned by the vane into two parts are configured as working chambers. . 7. The method according to any one of claims 3 to 6,
The motion conversion mechanism includes an eccentric drive unit that is eccentric with respect to the central axis of the shaft, a slewing plate that is rotatably supported by the eccentric drive unit and revolves, and a rotation that prevents the rotation of the slewing plate. The prevention mechanism and a long groove portion in the radial direction in which a pin protruding from the swivel plate in the axial direction of the shaft engages, and the vane is attached while extending in the axial direction of the shaft and rotatable by the shaft support portion. And a vane drive link including a shaft portion supported by the positive displacement fluid machine. 8. The displacement type fluid machine according to claim 7, wherein the shaft portion of the vane drive link is provided with a slot-shaped double-width portion for receiving the plate-shaped vane. 9. The structure according to claim 7, wherein the angular displacement of the vane is changed by changing the eccentric amount and the revolution radius of the swiveling plate with respect to the central axis of the shaft, thereby changing the discharge capacity. A positive displacement fluid machine characterized in that 10. The swivel plate according to claim 9, further comprising an eccentric hole for rotatably mounting the eccentric drive part between the eccentric drive part of the shaft and the swivel plate. A displacement type fluid machine characterized in that a cylindrical swing bush for rotatably supporting the rotor is interposed. 11. The displacement type fluid machine according to claim 10, wherein one of the generatrixes of the hole formed eccentrically on the swing bush is aligned with the central axis of the swing bush. 12. The rotation preventing mechanism for preventing rotation of the swivel plate according to claim 9, wherein a plurality of conical groove portions formed on a side surface of the swivel plate and the conical groove portion are provided. Balls that engage with each other,
A disc rotatably supported by a part of the housing and having a hole for holding the plurality of balls;
A means for urging the disc in the rotational direction and a wedge-shaped cross-sectional shape formed on the surface of the housing for respectively engaging the plurality of balls and pushing them toward the conical groove portion of the swivel plate. And a plurality of ball groove parts of the positive displacement fluid machine. 13. The discharge capacity according to claim 12, wherein when the ball engages with the center of the conical groove portion of the swivel plate, the revolution radius of the swivel plate becomes 0 and the angular amplitude of the vane becomes 0, whereby the discharge capacity is increased. A positive displacement fluid machine characterized in that 14. A displacement type fluid machine according to claim 1, wherein the displacement type fluid machine is configured as a compressor for compressing a fluid. 15. The positive displacement fluid machine according to claim 14, wherein the positive displacement fluid machine is configured as a refrigerant compressor in a refrigeration cycle of an air conditioner.