JPH0996285A - Variable displacement vane-type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To save wasteful power consumption by making a work, performed by a variable displacement vane type compressor, correspond to a communication condition of a suction port. SOLUTION: A plurality of suction holes 15, as viewed from a rotary shaft direction of a rotor, are opened between an external wall surface of the rotor and an internal wall surface of a cylinder block, and arranged so as to be along the internal wall surface of the cylinder block. Further, dimension in a direction of thickness(t) of a vane 6 in these suction holes 15 is formed smaller than the thickness(t) of the vane 6. In this constitution, a communication condition of adjacent operating chambers 16 can be interrupted, so as to equalize virtual suction volume formed by the vane 6 to the substantial suction volume, in its turn, the suction volume can be adjusted in accordance with a communication condition of the suction hole 15.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable capacity vane compressor, which is suitable for use in a vehicle air conditioner.

[0002]

2. Description of the Related Art As a variable capacity vane compressor, a suction throttle type compressor has been conventionally devised. This structure is, for example, as described in Japanese Utility Model Publication No. 61-25591.
By adjusting the amount of overlap between the piston portion of the spool valve and the suction hole, the opening area of the suction hole is adjusted,
The flow rate of the refrigerant supplied to the working chamber during the suction stroke is adjusted.

Further, the shape of the suction hole does not overlap the rotor and the cylinder block when viewed from the rotation axis direction of the rotor, as shown in FIG. 19, in order to secure the area of the suction hole under the maximum load condition. It was formed in a substantially oval shape along the inner wall of the cylinder block.

[0004]

By the way, conventionally, a variable displacement vane compressor of the suction throttle type consumes less power than the suction volume when it is operated by narrowing the suction hole to reduce the suction volume. Had the problem of being large. Then, as a result of various research investigations, the inventors have found the following points as the cause of the above-mentioned problems.

FIG. 18 is a diagram showing the positional relationship between the vanes 6 and the suction holes 15. As is clear from FIG. 18, the suction holes 1
Since the size of the vane 5 is larger than the thickness of the vane 6, when the vane 6 overlaps with the suction hole 15, the adjacent working chambers communicate with each other through the suction hole (arrows in FIG. 18 indicate. , Showing the flow of the refrigerant). Therefore, even if the working chamber A has finished sucking the refrigerant, as shown in FIG. 19, the refrigerant is sucked through the suction hole 15, so that the working chamber A has the vane 6 and the suction hole 15. Continues to suck the refrigerant until the overlap condition with is finished.

That is, even if the apparent suction volume is reduced by blocking the communication state of the suction holes 15, the substantial suction volume is substantially equal to the maximum suction volume (when all the suction holes 15 are in the communication state). Will be equal. The reference numerals shown in the drawings correspond to the reference numerals in the embodiments described later. By the way, the work done by the compressor is given by the sum of the value obtained by integrating the compression reaction force by the compression volume and the value obtained by integrating the suction resistance by the suction volume. If so, the amount of work done by the compressor also increases. Therefore, the power consumption is larger than the apparent suction volume.

In view of the above points, an object of the present invention is to eliminate unnecessary power consumption by setting the work amount of the variable displacement vane compressor as the work amount corresponding to the communication state of the suction holes.

[0008]

The present invention uses the following technical means in order to achieve the above object. In the invention according to claim 1, the suction hole (15) opens between the outer wall surface of the rotor (5) and the inner wall surface of the cylinder block (1) when viewed from the rotation axis direction of the rotor (5), A plurality of blocks are arranged along the inner wall surface of the block (1).

The vane (6) of the plurality of suction holes (15) is formed so that the dimension in the thickness (t) direction is smaller than the thickness (t) of the vane (6). . According to a second aspect of the present invention, in the variable capacity vane compressor according to the first aspect, among the suction holes (15), the suction holes (1) are viewed from the rotation axis direction of the rotor (5).
5) is an opening (15b) in the opening (15b) on the side of the working chamber (16) of the suction hole (15a) which is not located on the tubular spool hole (22) on which the spool valve (23) slides.
It is characterized in that the concave portion (15c) is provided so as to increase the opening area as compared with.

According to a third aspect of the present invention, in the variable displacement vane compressor according to the first or second aspect, the diameter of the first piston portion (23a) is the second piston portion (23).
It is characterized in that it is configured to be larger than the diameter of b). According to a fourth aspect of the invention, in the variable displacement vane compressor according to the first or second aspect, the diameter of the first piston portion (23a) is equal to the second piston portion (23).
It is configured to be smaller than the diameter of b), and further, on the circumferential side surface (23d) of the first piston portion (23a), the inner wall of the spool hole (22) and the first piston portion (23).
A seal member (22b) for sealing the gap (22a) with the circumferential side surface (23d) of (a) is mounted.

According to a fifth aspect of the present invention, in the variable displacement vane compressor according to the third or fourth aspect, the first piston portion (23a) is locked with the stepped portion (22a).
Are formed on the entire circumference of the inner wall surface of the spool hole (22). According to a sixth aspect of the invention, in the variable capacity vane compressor according to the first to fifth aspects, an introduction passage (25) is provided which communicates from the oil reservoir (18) to the bleed hole (17). It is characterized by

Next, the function and effect will be described. According to the invention described in claims 1 to 6, since the adjacent working chambers (16) are blocked from communicating with each other through the suction holes (15), the apparent formed by the vanes (6). The suction volume becomes substantially equal to the suction volume, and as a result, the suction volume can be increased or decreased according to the communication state of the suction holes (15).

Therefore, since the work amount of the compressor can be set to the work amount corresponding to the communication state of the suction hole (15), wasteful power consumption can be omitted and the power consumption of the compressor can be reduced. can do. According to the second aspect of the invention, the suction resistance when the fluid is sucked into the working chamber (16) from the suction hole (15a) can be reduced, so that the power consumption of the compressor can be reduced. You can

According to the third aspect of the invention, the pressure receiving area on which the control pressure acts becomes large, and the spool valve (23)
Responsiveness is improved. According to the invention described in claim 4,
Since the diameter of the first piston portion (23a) is smaller than the diameter of the second piston portion (23b), even if the spool hole (22) is distorted and formed, Inner wall of hole (22) and first piston part (23
The distortion of the spool hole (22) can be absorbed by the gap (22a) with the circumferential side surface (23d) of (a).

Further, although the cross-sectional area of the first piston portion (23a) is small, since the gap (22a) is sealed by the seal member (22b), it is possible to prevent the control pressure from leaking. Furthermore, since the pressure receiving area on which the control pressure acts does not decrease (equal to the cross-sectional area of the spool hole (22)), it is possible to prevent the spool valve (23) from malfunctioning while preventing the spool valve (23) from decreasing in responsiveness. Can be suppressed.

According to the fifth aspect of the invention, the first piston portion (23a) and the stepped portion (22a) are in surface contact over the entire circumference thereof, and the leakage of control pressure can be reduced. it can. Therefore, the spool valve (23) at the maximum capacity can be reliably controlled, and the control pressure does not leak into the working chamber during the suction stroke, so that the performance deterioration of the variable capacity vane compressor can be prevented.

Further, since the piston portion (23a) is locked by the stepped portion (22a), the spool valve (2
There is no need to newly provide the stopper mechanism of 3). Therefore, the structure is simplified and the manufacturing cost can be reduced. According to the invention of claim 6, the oil storage portion (1
8) can always be in communication with the working chamber (16). Therefore, the lubricating oil can be stably supplied to the sliding portion of the working chamber (16).

[0018]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments shown in the drawings will be described below by taking the case where the present invention is applied to a compressor for a refrigerator as an example. (First Embodiment) FIG. 1 is an axial sectional view of a variable capacity vane compressor (hereinafter, simply referred to as compressor) according to the present embodiment.

In FIG. 1, reference numeral 1 denotes a cast iron cylinder block, which is made of aluminum (Al--Si system) and forms a closed space 2 by shielding both sides of the hollow space of the cylinder block 1 in the axial direction. The side plate (first side plate) 3 and the rear side plate (second side plate) 4 are assembled to the cylinder block 1 by bolts (not shown).

Reference numeral 5 denotes a rotor made of high carbon chrome bearing steel and steel which rotates in the closed space 2, and two vanes 6 slidably pass through the rotor 5 and tolerance the rotor 5. It is assembled as follows. Both ends of the vane 6 are always in contact with the inner wall surface of the cylinder block 1, and the vane 6 slides in the rotor 5 as the rotor 5 rotates. It works as if it appears and disappears from the outer wall. Incidentally, the vane type compressor as described above is called a through-vane type compressor.

Reference numeral 7 denotes a shaft which is integrally formed with the rotor 5 and which transmits a driving force from an external drive source to the rotor 5. The shaft 7 is rotatably supported by a bearing 8 press-fitted in the front side plate 3. ing. On the opposite side of the shaft 7 with the rotor 5 in between, a shaft 9 formed separately from the rotor 5 is attached to the rotor 5 by a bolt 10 in order to attach the vane 6 to the rotor 5. . Reference numeral 11 is a bearing that rotatably supports the shaft 9.

Reference numeral 12 denotes a front housing, and a space 13 closed by the front housing 12 and the front side plate 3 is formed. This space 13
Is in communication with a suction port 14 (see FIG. 2) that guides the refrigerant into the compressor, and the fluid introduced into the space 13 is a suction hole 1 provided in the front side plate 3 as shown in FIG.
5 and is sucked into the working chamber 16 formed by the inner wall of the cylinder block 1 and the vane 6.

Then, as shown in FIG. 3, a plurality (five in this embodiment) of suction holes 15 are arranged along the inner wall of the cylinder block 1 without overlapping the rotor 5 and the cylinder block 1. They are provided side by side, and the size of the suction holes 15 is smaller than the thickness (t) of the vanes 6 as shown in FIG. 17 is a fluid for working chamber 1
6 is a hole that has both a suction hole 15 that leads into the inside of the working chamber 6 and a bleed hole that supplies lubricating oil into the working chamber 16, and is provided above the front side plate 3 in consideration of lubrication of the working chamber. (Hereinafter, referred to as a bleed hole 17.) The space 13
An oil storage portion 18 for storing lubricating oil is formed in the lower part of the.

Further, in FIG. 1, 19 is an oil separator made of an aluminum casting which separates and takes out the lubricating oil mixed in the compressed refrigerant. Here, the separated lubricating oil is an oil separator. 19 and rear side plate 4
It collects in the lower part of the space 20 between and. Next, the variable capacity mechanism 21 of this compressor will be described.

The variable capacity mechanism 21, as shown in FIG.
A spool hole 22 provided in the front side plate 3 so as to communicate with the suction hole 15 and the spool hole 22.
It is composed of a spool valve 23 that slides inside, and a coil spring 24 that is pressed against the spool valve 23. FIG. 5 is a schematic diagram showing the variable displacement mechanism 21. A first piston portion 23a and a second piston portion 23b are formed on both end sides of the spool valve 23, and between the piston portions 23a and 23b. The diameter of the portion 23c is smaller than the diameters of the piston portions 23a and 23b. When the spool valve 23 slides in the spool hole 22, the piston portion 23b opens and closes the suction hole 15, and the communication state of the suction hole 15 is controlled.

A control pressure for controlling the spool valve 23 acts on the first piston portion 23a side, and a coil spring 24 acts on the end side second piston portion 23b.
It is arranged so that an elastic force opposed to the control pressure acts. Further, the diameter of the first piston portion 23a is larger than the diameter of the second piston portion 23b on which the coil spring 24 acts, and the spool hole 22 has a step so that the first piston portion 23a is locked. The attached portion 22a is formed around the entire inner wall surface of the spool hole 22. Incidentally, in the present embodiment, the diameter of the piston portion 23a is about 13 mm and the diameter of the piston portion 23b is about 10 mm.

The control pressure changes according to the discharge pressure and the suction pressure, and when the suction hole 15 and the working chamber 16 are brought into communication with each other (the state shown in FIG. 5), the control pressure is changed by the elasticity of the coil spring 24. Greater than force. In addition, the suction hole 15
When disconnecting the communication between the working chamber 16 and the working chamber 16, the control pressure is made smaller than the elastic force of the coil spring 24. Further, as shown in FIG. 4, when viewed from the rotation axis direction of the rotor 5 in the suction hole 15, the suction hole 15a in which the suction hole 15 is not located on the spool hole 22 has an oblique direction as shown in FIG. A suction hole 15a is provided, and a recess 15c is provided in an opening 15b on the side of the working chamber 16 thereof.

Further, the bleed hole 17 is, as described above,
Since the lubricating oil is supplied into the working chamber 16, the bleed hole 17 is configured to always communicate with the working chamber 16. As shown in FIG. 7, the front housing 12 has an introduction passage 25 (shaded portion) for directly communicating the oil storage portion 18 formed in the lower portion of the space 13 with the bleed hole 17.
Are formed.

Next, the characteristic operation of this compressor will be described. 8 to 10 show a state in which the suction volume is at a minimum (the suction volume is most narrowed), and the piston portion 23b of the spool valve 23 blocks all the suction holes 15 from communicating with the working chamber 16. ing. Only the bleed hole 17 communicates with the working chamber 16. Here, the operation will be described focusing on the working chamber 16a formed by the vanes 6a and 6b.

FIG. 8 shows the state of the working chamber 16a at the beginning of the suction stroke, and as described above, the refrigerant is sucked only from the bleed hole 17. Then, as the rotation of the rotor 5 progresses and one end of the vane 6a reaches above the bleed hole 17, as shown in FIG. 9, the communication state of the bleed hole 17 is blocked by the vane 6a, and the suction of the refrigerant ends.

Then, the rotation of the rotor further progresses, and the working chamber 16a expands without the refrigerant flowing from the adjacent working chamber 16b into the working chamber 16a. FIG. 10 shows a state where the working chamber 16a is most expanded. After that, the working chamber 16a shifts to a normal compression stroke. Therefore, the suction volume in the state in which the suction volume is the smallest is the volume shown in FIG.

Similarly, the shaded area in FIG. 11 shows the suction volume when the two suction holes 15 and the bleed hole 17 are in the communicating state (intermediate capacity), and the shaded area in FIG. 12 shows all the suction holes. 15 shows the suction volume in the case where 15 and the bleed hole 17 are in communication (maximum capacity). As is clear from the above, the suction volume increases or decreases according to the communication state of the suction holes 15.

Next, the features of this embodiment will be described. As is clear from the above description of the operation, the adjacent working chambers 16
However, since they do not communicate with each other through the suction holes 15, the apparent suction volume formed by the vanes 6 becomes substantially equal to the substantial suction volume, and the substantial suction volume is
Increase or decrease according to the communication status of. Therefore, the work amount of the compressor can be set to the work amount corresponding to the communication state of the suction holes 15, so that wasteful power consumption can be omitted, and in turn, the power consumption for driving the compressor can be reduced. Power can be reduced.

The above effects will be quantitatively described below with reference to the pressure-suction volume (P-V) diagram shown in FIG. Note that FIG. 13 shows a P-V diagram of the working chamber 16 when the suction volume is the minimum (only the bleed hole 17 is in communication). That is, the expansion stroke of the compressor according to the present embodiment first changes along the line AB, and the refrigerant suction is completed at the point B (the state in FIG. 9). Then, without inhalation, adiabatic expansion is performed along the line BC. At this time, diagram A
The slope of B indicates the suction resistance (suction pressure loss).
Then, when the expansion stroke is completed, adiabatic compression is performed along the line CH, and when a predetermined pressure is reached, the discharge valve opens and the refrigerant is discharged.

Therefore, according to this diagram, the work of the compressor corresponds to the area surrounded by ABCJ in the expansion stroke, and the work equivalent to the area surrounded by JHIA in the compression stroke. do. In addition, P according to the conventional technology
Drawing a -V diagram, the expansion stroke changes along the diagram ABD, and the compression stroke changes along the diagram DG. Therefore, the work of the compressor according to the conventional technique is the work corresponding to the area surrounded by ABDK in the expansion stroke, and the work corresponding to the area surrounded by KGIA in the compression stroke.

As is clear from the above, in the compressor according to the present embodiment, as compared with the compressor according to the prior art, in the state where the suction volume is at a minimum, the wasteful work corresponding to the shaded portion shown in FIG. The amount can be reduced. Further, if the size of the bleed hole 17 of the compressor according to the prior art is reduced so that the discharge capacities of the compressor according to the present embodiment and the compressor according to the related art are equal, the P- of both compressors will be described. The V diagram is as shown in FIG.

That is, P of the compressor according to the present embodiment
The -V diagram will be ABCBFG and the PV diagram for the prior art compressor will be ACBFG. Therefore, in the compressor according to the present embodiment, the amount of useless work corresponding to the shaded portion shown in FIG. 14 can be reduced as compared with the compressor according to the conventional technique. Further, since the substantial suction volume is smaller than that of the compressor according to the related art, the substantial compression start pressure of the compressor according to the present embodiment is point B, and the compression start pressure of the compressor according to the related art is It is point C. Therefore, the compression rate of the compressor according to the present embodiment is smaller than that of the compressor according to the related art, and thus the temperature rise of the refrigerant can be reduced. By the way, O
The life of the sealing member such as the ring can be shortened.

When the flow velocity of the suction refrigerant reaches the sonic velocity and becomes constant, the suction refrigerant mass increases in accordance with the suction time. Further, according to the present embodiment, as described above, the suction time can be controlled by controlling the communication state of the suction holes 15, so that the suction stroke is controlled so as to save the unnecessary refrigerant suction time. be able to. Also,
Of the suction holes 15, when viewed from the rotation axis direction of the rotor 5, the suction hole 15 is not located on the spool hole 22.
Since the recess 15c is provided in the opening 15b on the side of the working chamber 16 of a, the opening area is increased as compared with the opening area of the opening 15b on the side of the working chamber 16, and the fluid is sucked into the suction hole 15a.
It is possible to reduce the suction resistance when the air is sucked into the working chamber 16 from. Therefore, the power consumption for driving the compressor can be reduced.

Further, since the diameter of the piston portion 23a on which the control pressure of the spool valve 23 acts is larger than the diameter of the piston portion 23b, the pressure receiving area on which the control pressure acts increases and the spool valve 23, the responsiveness is improved. Further, in the spool hole 22, the piston portion 23
Since the stepped portion 22a to be locked is formed on the entire circumference of the inner wall surface of the spool hole 22, the piston portion 23a and the stepped portion 22a of the spool hole 22 are in surface contact over the entire circumference. The leakage of the control pressure can be reduced, and the control pressure can be prevented from leaking into the working chamber during the suction stroke. Therefore, the spool valve 23 at the maximum capacity can be reliably controlled, and the performance of the compressor can be prevented from deteriorating.

Further, since the piston portion 23a is locked by the stepped portion 22a, it is not necessary to newly provide a stopper mechanism for the spool valve 23. Therefore, the structure is simplified and the manufacturing cost can be reduced. Further, since the introduction passage 25 that communicates from the oil storage portion 18 to the bleed hole 17 is provided, the oil storage portion 18 is connected to the working chamber 1
6 and the communication state can be always established. Therefore, the lubricating oil can be stably supplied to the sliding portion of the working chamber 16.

(Second Embodiment) This embodiment is a spool.
Deformation (distortion) of spool hole 22 due to machining error of hole 22
In consideration of the above, the malfunction of the spool valve 23 is reduced.
Of. Specifically, as shown in FIG. 15, the spool
The diameter of the piston portion 23a of the valve 23 is
It is smaller than the diameter of b and the circumference of the piston part 23a
A seal on which the seal member 22b is attached to the side surface 23d
The groove 23e is formed. That is, the piston portion 23a
The gap 22a between the piston and the inner wall of the spool hole 22 is
3b and the inner wall of the spool hole 22 smaller than the gap 22c.
(Δ₁> Δ ₂), The gap 22a is the seal member 22.
It is sealed by b.

In this embodiment, the seal member 22b is used.
Is a piston ring made of Teflon, but an O-ring made of nitrile rubber or the like may be used. Next, the features of this embodiment will be described. For example, as shown in FIG. 16, even when the spool hole 22 is distorted due to a processing error, a difference in thermal expansion, or the like, the distortion of the spool hole 22 can be absorbed by the gap 22a. On the other hand, both piston portions 23a,
When the diameters of 23b are the same, as shown in FIG. 17, the piston portion 23a and the inner wall of the spool hole 22 interfere with each other, so that the spool valve 23 malfunctions (sliding failure).

Further, with the above structure, although the gap 22a expands, it is sealed by the seal member 22b, so that the control pressure leaks and the control of the compressor is poor, and the control pressure leaks to the suction side of the compressor. It is possible to prevent the performance of the compressor from being deteriorated. Also, the piston portion 23a
Although the cross-sectional area is small, the pressure-receiving area on which the control pressure acts does not decrease (equal to the cross-sectional area of the spool hole 22) because the gap 22a is sealed by the seal member 22b. Therefore, malfunction of the spool valve 23 can be suppressed while preventing the responsiveness of the spool valve 23 from decreasing.

Incidentally, in this embodiment, both piston portions 2
The difference in diameter between 3a and 23b is about 50 μm, and the difference in diameter between these piston portions 23a and 23b is appropriately selected depending on the machining error of the spool hole 22. by the way,
The elastic body arranged on one end side of the spool valve 23 is not limited to the coil spring 24, and the present invention can be implemented by using an elastic body such as a leaf spring or rubber.

Further, the sectional shape of the suction hole 15 is not limited to the circular shape, and the present invention can be implemented with other shapes such as an ellipse. Further, the present invention is not limited to the through-vane type compressor, but can be implemented in an eccentric rotor or a concentric rotor type vane type compressor.

[Brief description of drawings]

FIG. 1 is an axial sectional view of a compressor according to a first embodiment of the present invention.

FIG. 2 shows a view on arrow A of FIG.

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

FIG. 4 is a schematic diagram showing states of an intake hole, a vane, and a working chamber.

FIG. 5 is a schematic view showing a variable capacity mechanism.

FIG. 6 is a sectional view taken along line DD of FIG. 4;

FIG. 7 is a front view of the front housing showing a lubricating oil introduction passage provided in the front housing.

FIG. 8 is an explanatory diagram illustrating the operation of the compressor in the initial state of the suction stroke.

FIG. 9 is an explanatory diagram illustrating the operation of the compressor in the intermediate state of the suction stroke.

FIG. 10 is an explanatory view for explaining the operation of the compressor showing the suction stroke end state.

FIG. 11 is an explanatory diagram illustrating an intermediate capacity state of the compressor.

FIG. 12 is an explanatory diagram illustrating a maximum capacity state of the compressor.

FIG. 13 is a P-V diagram for explaining the effect of the compressor according to the first embodiment.

FIG. 14 is a P-V diagram for explaining the effect of the compressor according to the first embodiment.

FIG. 15 is a schematic diagram showing a variable capacity mechanism according to a second embodiment of the present invention.

FIG. 16 is an explanatory diagram illustrating characteristics of the variable capacity mechanism according to the second embodiment.

FIG. 17 is an explanatory diagram illustrating characteristics of the variable capacity mechanism according to the second embodiment.

FIG. 18 is an explanatory diagram illustrating a positional relationship between a suction hole and a vane according to a conventional technique.

FIG. 19 is an explanatory diagram showing a compressor suction stroke initial state according to a conventional technique.

[Explanation of symbols]

1 ... Cylinder block, 2 ... Space, 3 ... Front side plate, 4 ... Rear side plate, 5 ... Rotor, 6 ...
Vane, 7 ... Shaft, 8 ... Bearing, 9 ... Shaft, 10
… Bolts, 11… Bearings, 12… Front housings, 1
3 ... Space, 14 ... Suction port, 15 ... Suction hole, 16 ... Working chamber, 17 ... Bleed hole, 18 ... Oil storage part, 19 ... Oil separator, 20 ... Space, 21 ... Variable capacity mechanism, 22 ... Spool hole, 22b ... Seal member, 23 ... Spool valve, 2
3a, 23b ... piston part, 24 ... coil spring,
25 ... Introduction passage.

Claims (6)

[Claims] 1. A cylinder block (1) having a hollow space, a first side plate (3) which shields both ends of the hollow space of the cylinder block (1) and forms a closed space (2), A second side plate (4), a rotor (5) rotatably housed in the closed space (2), and a plurality of vanes () provided on the rotor (5) so as to be retractable from its outer wall. 6) and the working chamber (16) provided on the first side plate (3) and formed by the outer wall surface of the rotor (5), the inner wall surface of the cylinder block (1), and the vanes (6). A plurality of suction holes (15) communicating with the working chamber (16) during the suction stroke, and a plurality of suction holes (15) provided in the first side plate (3) and the working chamber (16) during the suction stroke. Controls communication with the suction hole (15) And a plurality of suction holes (15) in the cylinder block (1) and the outer wall surface of the rotor (5) when viewed from the rotation axis direction of the rotor (5). It is provided between the wall surface and the cylinder block (1) so as to line up along the inner wall surface of the cylinder block (1), and the vane (6) of the suction hole (15) has a thickness (t) direction dimension, A variable capacity vane compressor characterized in that it is smaller than the thickness (t) of the vanes (6). 2. The valve means (23) is a spool valve (2).
3), the spool valve (23) is provided on the first side plate.
Of the suction hole (15) is not located on the spool hole (22) when viewed from the rotation axis direction of the rotor (5). The opening (15b) on the side of the working chamber (16) of the hole (15a) is provided with a recess (15c) so as to increase the opening area as compared with the opening (15b). The variable capacity vane compressor according to claim 1. 3. The spool valve (23) is provided on both ends thereof with
The first piston portion (23a) and the second piston portion (23
b) is formed, and the part (23) between the piston parts (23a, 23b) is formed.
The diameter of c) is smaller than the diameter of both piston parts (23a, 23b), and the working chamber (1) is formed in the first piston part (23a).
6) and a control pressure for controlling the communication state between the plurality of suction holes (15) act on the second piston portion (23b) so that an elastic force opposing the control pressure acts on the second piston portion (23b). Body (24) is arrange | positioned, The diameter of the said 1st piston part (23a) is larger than the diameter of the said 2nd piston part (23b), The variable capacity vane of Claim 1 or 2 characterized by the above-mentioned. Type compressor. 4. The both ends of the spool valve (23) are
The first piston portion (23a) and the second piston portion (23
b) is formed, and the part (23) between the piston parts (23a, 23b) is formed.
The diameter of c) is smaller than the diameter of both piston parts (23a, 23b), and the working chamber (1) is formed in the first piston part (23a).
6) and a control pressure for controlling the communication state between the plurality of suction holes (15) act on the second piston portion (23b) so that an elastic force opposing the control pressure acts on the second piston portion (23b). A body (24) is arranged, a diameter of the first piston portion (23a) is smaller than a diameter of the second piston portion (23b), and a circumferential side surface (23d) of the first piston portion (23a) is arranged. A seal member (22b) for sealing a gap (22a) between the inner wall of the spool hole (22) and the circumferential side surface of the first piston portion (23a) is attached to the seal member (22b). Alternatively, the variable capacity vane compressor described in 2. 5. The spool hole (22) has the first
The step portion (22) with which the piston portion (23a) is locked.
The variable capacity vane compressor according to claim 3 or 4, wherein a) is formed on the entire circumference of the inner wall surface of the spool hole (22). 6. A front housing (1), which is arranged outside the first side plate (3) and forms a closed space (13) between the first side plate (3) and the first side plate (3).
2), an oil storage part (18) formed in the lower part of the closed space (13) for accumulating the lubricating oil, and a space formed by the cylinder block (1) and the side plates (3, 4). (2) is provided in the upper part and has a bleed hole (17) for supplying lubricating oil to the working chamber (16), and an introduction passage (communication from the oil reservoir (18) to the bleed hole (17) ( 25) is provided, The variable capacity vane compressor of Claim 1 thru | or 5 characterized by the above-mentioned.