JPH024796B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a rotary compressor, and particularly to a variable displacement rotary compressor suitable as a refrigerant compressor for an automobile cooler system.

[Prior art and problems to be solved by the invention]

A rotary compressor for compressing refrigerant used in an automobile cooler system is generally connected to an engine crank pulley via an electromagnetic clutch. For this reason, compressors are used in a wide rotation speed range of 700 to 6000 rpm. However, since the discharge capacity of the compressor is designed to provide sufficient cooling capacity mainly at low rotation speeds, the cooling capacity tends to be excessive at high rotation speeds or low heat loads. When the cooling capacity becomes excessive, the suction pressure of the compressor decreases, resulting in an increase in the compression ratio and a decrease in the efficiency of the compressor, resulting in a problem that the fuel efficiency of the automobile deteriorates. On the other hand, if the compressor is controlled on and off to reduce the cooling capacity during high rotation or low heat load, a problem arises in that the driving feeling of the automobile and the cooling feeling inside the vehicle are reduced.

Therefore, there is a need for a variable capacity rotary compressor that can change the discharge capacity as continuously and over a wide range as possible, and that has less compression loss.

Japanese Patent Publication No. 56-7079 discloses a variable displacement rotary compressor. This known variable displacement rotary compressor is equipped with one or more bypass holes opening in the cylindrical inner surface of the liner, and the bypass holes are connected to the suction side of the compressor by piping, and the bypass holes are connected to the suction side of the compressor by piping. A control valve is provided. According to this variable displacement rotary compressor, the discharge capacity of the compressor can be changed by switching the control valve in the middle of the piping. Since the length extends several times longer than the plate thickness, while the vane passes through the opening of the bypass hole, the compressed fluid compressed in the working chamber on the front side of the vane in the rotor rotational direction, that is, on the high pressure side, flows through the bypass hole. There is a drawback that the air flows back into the working chamber on the rear low pressure side of the vane through the opening of the vane, resulting in constant compression loss.

On the other hand, in Japanese Utility Model Application Publication No. 55-73588, a plurality of intermediate discharge holes, that is, bypass holes communicating with the suction side of the compressor are provided between the suction side and the discharge side of the cylinder chamber along the rotational direction of the rotor. A variable displacement rotary compressor is disclosed. However, even in this known variable displacement rotary compressor, the opening diameter of the bypass hole into the cylinder chamber is approximately twice the plate thickness of the vane, so while the vane passes through the opening of the bypass hole, the rotor rotation direction The disadvantage is that the gas compressed in the working chamber on the front side of the vane, that is, on the high-pressure side, flows back through the opening of the bypass hole into the working chamber on the rear side, that is, on the low-pressure side of the vane, and a compression loss always occurs.

On the other hand, in Japanese Utility Model Application Publication No. 55-142686, an intermediate discharge hole, that is, a bypass hole communicating with the suction side of the compressor is provided between the suction side and the discharge side of the cylinder chamber, and
A variable displacement compressor is disclosed in which the opening width of the cylinder chamber side opening of the bypass hole in the vane passage direction is smaller than the plate thickness of the vane.
A bypass hole with such an opening width was developed by the above-mentioned
If applied to multiple bypass holes of a variable displacement rotary compressor disclosed in Publication No. 56-7079 or Japanese Utility Model Application No. 55-73588, the working chamber of the bypass hole can be moved from the working chamber on the front side of the vane, that is, on the high pressure side. It is possible to eliminate the problem of gas flowing back into the working chamber on the rear side of the vane, that is, on the low pressure side, through the side opening.

However, if the opening width in the vane passing direction of the working chamber side opening of the plurality of bypass holes arranged along the rotational direction of the rotor is set to be approximately the same as the plate thickness of the vane at maximum, the opening of the bypass hole The small area increases fluid resistance, making it difficult for the compressed fluid in the working chamber to escape to the suction side of the compressor through the bypass hole. In other words, it becomes difficult for the bypass hole to perform its intended function. This tendency increases as the rotation speed of the compressor increases.

Therefore, the width of the opening in the vane passage direction of the working chamber side opening of the bypass hole is set to be approximately the same as the plate thickness of the vane at maximum, so that the required amount of compressed fluid in the working chamber can be passed through the bypass hole while preventing compression loss. In order to reliably release the water from the air, it is necessary to create a pressure difference greater than a predetermined value between the front and back of the bypass hole, that is, between the inlet side and the outlet side. However, since the change (reduction) in the volume of the working chamber is small for a while after the working chamber leaves the suction port for supplying compressed fluid into the working chamber, the bypass hole is located near the suction port. Then, it becomes impossible to create a pressure difference of more than a predetermined value before and after the bypass hole.

For this reason, the opening width of the working chamber side opening of the bypass hole in the vane passing direction is set to be approximately the same as the vane plate thickness at maximum, thereby preventing compression loss and allowing the multiple bypass holes to function effectively to increase the discharge capacity. In order to widen the variable range of It is necessary to arrange a plurality of bypass holes at positions where the working chamber to be formed does not open simultaneously to the suction port and the bypass hole.

However, in conventional variable displacement rotary compressors, no measures have been taken to satisfy the above-mentioned requirements regarding the opening width and location of the working chamber side openings of the multiple bypass holes, resulting in compression loss. It is difficult to make the bypass hole function effectively and widen the variable range of the discharge volume while preventing this.

In view of the above problems, an object of the present invention is to provide a vane-type rotary compressor that can prevent compression loss as much as possible and can change the discharge capacity almost continuously and over a wide range. .

[Means to solve the problem]

As a means for achieving the above object, the present invention includes a liner having a cylindrical inner surface, a rotor that is eccentrically arranged within the liner and rotates in one direction, and a rotor that is movably provided within a slit formed within the rotor. a plurality of vanes that move along the inner surface of the liner with one end in contact with the inner surface of the liner as the rotor rotates; a pair of side plates disposed to cover both ends of the liner; A plurality of working chambers are defined by vanes, liners, and side plates and change in volume as the rotor rotates, a suction chamber is provided at a position where the volume of the working chamber increases, and a suction chamber is provided where the volume of the working chamber increases. In a rotary compressor, a suction pressure chamber is provided on a side of one of the side plates opposite to the working chamber, and both ends of the one side plate are connected to the working chamber. A plurality of bypass holes opening to the side and the suction pressure chamber are spaced apart from each other at positions where the working chamber defined between the two vanes does not open simultaneously to the suction port and the bypass hole. The bypass holes are arranged in a straight line in the rotation direction of the rotor, and the opening width of the working chamber side opening of each bypass hole in the vane passing direction is at most approximately the same as the plate thickness of the vane, and the bypass holes are arranged in a straight line in the rotor rotation direction. A cylinder hole extending in the direction in which the bypass hole groups are arranged is provided in the one side plate, and the bypass hole groups can be sequentially opened and closed in the order of arrangement by a spool slidably provided in the cylinder hole. Provides a rotary compressor with

[Effect]

In the rotary compressor having the above configuration according to the present invention, the opening width dimension in the vane passing direction of the opening on the working chamber side of the plurality of bypass holes whose both ends open to the working chamber side and the suction pressure chamber is set to the maximum width of the vane. Since the thickness is approximately the same as the plate thickness, when the vane passes through the working chamber side opening of the bypass hole, the compressed fluid in the working chamber on the front side of the vane in the rotational direction of the rotor, that is, on the high pressure side, flows through the opening of the bypass hole. Through this, backflow into the working chamber on the rear side of the vane, that is, on the low pressure side, can be prevented as much as possible. Therefore, compression loss due to the presence of the bypass hole can be prevented, the compression efficiency of the compressor can be increased, and the maximum discharge amount of the compressor can be increased.

Further, the plurality of bypass holes, which can be sequentially opened and closed by the spool, are spaced apart from each other on the rotor so that the working chamber defined between the two vanes does not open simultaneously to the suction port and the bypass hole. Since they are arranged linearly in the rotational direction, the bypass holes can communicate with the working chamber after the working chamber is separated from the suction port as the rotor rotates. In other words, since the bypass hole communicates with the working chamber when internal compression occurs in the working chamber, it is possible to create a pressure difference of more than a predetermined level before and after the bypass hole closest to the suction port. It becomes possible to make all of the bypass holes function effectively.
Therefore, by controlling the opening and closing of the plurality of bypass holes by the spool, the discharge capacity from the compressor can be changed almost continuously and over a wide range.

Preferably, the spool in the present invention is adapted to move within the cylinder bore in response to a differential pressure between the discharge pressure and the suction pressure of the rotary compressor and a spring force acting to move the spool in a direction that reduces the capacity. The discharge pressure is guided from a high pressure section within the rotary compressor to the spool via a control valve. In such a configuration, when the compressor is stopped, the high pressure part inside the compressor and the suction pressure are at the same pressure, so the spool moves in a direction to reduce the capacity due to the spring force. Therefore,
When the compressor is started, it can be started with the minimum capacity, and shocks to vehicles etc. equipped with the compressor can be reduced.

〔Example〕

Embodiments of the present invention will be described below with reference to the drawings.

1 and 2 show a first embodiment of the present invention. In the figure, 100 is a compressor main body, and the compressor main body 100 is equipped with a liner 110 having a cylindrical inner wall.
The front and rear opening ends of are respectively covered by two side plates 120 and 130. A cylindrical rotor 200 is provided in the liner 110 so as to be rotatable eccentrically, and a rotating shaft 210 made integrally with the rotor 200 is rotatably supported by the side plates 120 and 130 via bearings 220 and 230. has been done.

The rotor 200 has four slits 20 here.
1 are formed approximately radially, and each slit 20
1, a vane 240 is inserted so as to be movable forward and backward. The space between the liner 110 and the rotor 200 is divided into four working chambers 140 by four vanes 240.
Each working chamber 140 is divided into rotor 20
It is designed to move and change its volume as it rotates.

The side plate 120 has the working chamber 14 in the volume increase stage.
A suction port 121 that opens to 0 is formed in the liner 110, and the working chamber 1 that has reached the minimum volume stage is formed in the liner 110.
A discharge port 111 opening at 40 is formed.

A housing 150 is disposed in close contact with the outer surface of the side plate 120, and the housing 150 and the side plate 12
0,130 and the liner 110 are fixed together with bolts (not shown). A suction pressure chamber 151 is formed between the housing 150 and the side plate 120, and the suction pressure chamber 151 communicates with the working chamber 140 in the volume increase stage via the suction port 121. The housing 150 has a suction pressure chamber 151.
A suction port 152 is formed that communicates with the.
One end of the rotating shaft 210 of the rotor 200 extends outside through the housing 150, and receives the driving force of the automobile engine through an electromagnetic clutch (not shown). A seal member 153 is provided between the rotating shaft 210 and the housing 150 to prevent compressed fluid and lubricating oil from flowing out along the rotating shaft 210.

The liner 110 is provided with a housing 160, and a discharge pressure chamber 161 is provided within the housing 160.
is formed. The discharge pressure chamber 161 is connected to the discharge port 1
Working chamber 140 reaches the minimum volume stage via 11
The discharge pressure chamber 161
A discharge valve 162 and a stopper 163 for regulating the opening stroke of the discharge valve 162 are provided inside. A discharge port 164 communicating with a discharge pressure chamber 161 is formed in the housing 160 .

The side plate 120 is provided with three bypass holes 122, 123, and 124 that open at both ends into the working chamber 140, which has entered the volume reduction stage, and the suction pressure chamber 151. Three bypass holes 122, 123, 12
4, as is clear from FIG. 1, the working chamber 140 defined between the two vanes 240 is connected to the suction port 121 and the bypass holes 122, 123, 124.
They are arranged in a straight line in the rotational direction of the rotor 200, spaced apart from each other and at positions that do not open at the same time.

In addition, these bypass holes 12 are provided in the side plate 120.
Bypass hole 12 intersects with 2, 123, 124
A cylinder hole 170 extending in the direction in which the cylinders 2, 123, and 124 are arranged is provided. A spool 180 is provided in the cylinder hole 170 so as to be slidable in the longitudinal direction.
By moving within 0, the bypass hole 122,
123 and 124 are opened and closed in sequence.

As can be seen from FIG. 1, each bypass hole 122,
The maximum opening diameter of the working chamber side of the bypass holes 123 and 124 is approximately the same as the plate thickness of the vane 240, but the opening diameter or cross-sectional area of the working chamber side of the bypass holes 122, 123, and 124 depends on the rotation of the rotor 200. It gradually increases in size in the direction. This allows spool 1
When the bypass holes 122, 123, and 124 are sequentially opened and closed at 80, the effective compression volume of the working chamber 140 is decreased or increased by approximately the same amount.

A piston 182 is integrally connected to the spool 180 via a rod 181.
An O-ring 183 for sealing is attached to the outer peripheral groove 82. A suction pressure introduction chamber 171 is formed between one end of the cylinder hole 170 and the spool 180, and this suction pressure introduction chamber 171 is communicated with the suction pressure chamber 151 via a passage (not shown). On the other hand, a cap 172 equipped with an air vent is attached to the other end of the cylinder hole 170, and an air introduction chamber 1 is provided between the cap 172 and the piston 182.
73 is formed. Further, a compression spring 174 is disposed between the cap 172 and the piston 182, and the spring force of this spring 174 causes the spool 180 to move into the bypass holes 122, 123, 12.
4 is biased in the direction of opening.

Next, the operation of the rotary compressor having the above configuration will be explained with reference to FIGS. 3A to 3D. Note that in FIGS. 3A to 3D, the rotor 200 is assumed to rotate clockwise (in the direction of the arrow).

When the rotor 200 is rotated by engine output or the like, fluid to be compressed is sucked into the working chamber 140 from the suction port 121, while the compressed fluid is discharged to the outside from the discharge port 111.

As shown in FIG. 3A, when the spool 180 closes all the bypass holes 122 to 124, the discharge amount of the compressed fluid is confined within the working chamber 140 immediately after the vane 240 passes the suction port 121. The amount of fluid to be compressed is _V1 .

On the other hand, as shown in FIG. 3B, the bypass hole 12
2 is open and the bypass holes 123 and 124 are closed, the actual discharge amount of the compressed fluid is equal to the amount of compressed fluid trapped in the working chamber 140 immediately after the vane 240 passes through the bypass hole 122. amount
It becomes V ₂ .

Similarly, in the states shown in FIGS. 3C and 3D, the actual discharge amount of the fluid to be compressed is The amounts of compressed fluid are V ₃ and V ₄ .

As is clear from FIGS. 3A to 3D, as the bypass holes 122 to 124 open sequentially, the actual discharge amount of the compressed fluid decreases (V ₁ >V ₂ >V ₃ >
_V4 ).

In this embodiment, bypass holes 122 to 124
The position of the working chamber 140 can be appropriately set within the range of the position where the working chamber 140 does not open to the suction port 121 and the bypass holes 122 to 124 at the same time. width) can be appropriately set within a limit that is approximately the same as the plate thickness of the vane 240 at maximum, but for example, as shown in FIG. 4, the discharge amount in the state of FIG. 3A (Maximum discharge amount) V ₁ to 1
In this case, the discharge amount in the state shown in Figure 3 B
Discharge amount when V ₂ becomes 3/4 and the state shown in Figure 3 C
V ₃ becomes 1/2 and the discharge amount when the state shown in Fig. 3 D
Bypass holes 122 to 124 so that V ₄ is 1/4
The position and opening diameter of the working chamber 140 can be set. Therefore, as the spool 180 moves, the discharge amount of the compressed fluid can be changed almost continuously and over a wide range.

The spool 180 moves in response to changes in the suction pressure introduced into the suction pressure introduction chamber 171. That is,
When the suction pressure is constant, the spool 180 is moved by the spring 17.
4 to keep all bypass holes 122-124 closed, and as suction pressure decreases, spool 180 sequentially opens bypass holes 122-124.

When the rotary compressor according to this embodiment is used as a refrigerant compressor for an automobile cooler system, when the heat load of the cooler system is high, that is, when the temperature inside the vehicle is high, the pressure inside the evaporator (not shown) increases. Therefore, the suction pressure of the rotary compressor is increased. Therefore, the spool 180 has bypass holes 124 to 12.
2 are closed one after another, the discharge amount from the compressor increases, and the cooling capacity increases. On the other hand, when the heat load decreases or when the compressor is operated at high speed, the pressure inside the evaporator decreases and the suction pressure of the compressor also decreases. Therefore, the spool 180 is connected to the bypass hole 12.
2 to 124 are sequentially opened, the discharge amount from the compressor decreases, and the cooling capacity decreases.

In a cooler system using Freon R12 as a refrigerant, the pressure inside the evaporator is preferably approximately 1.8 kg/cm ² or higher to prevent freezing of the evaporator.
A drop below at least about 1.7 Kg/cm ² should be avoided. Therefore, in this example,
The spring 174 is configured such that all the bypass holes 122 to 124 are opened when the suction pressure is about 1.7 Kg/cm ² or less, and all the bypass holes 122 to 124 are closed when the suction pressure is about 1.8 Kg/cm ² or more. Load and spool 18
0 and the pressure receiving area of the piston 182 are set.

As a result of the above, in this example, the discharge volume was reduced to 1 for small fluctuations in suction pressure (1.8 to 1.7 Kg/cm ² ).
It can be changed over a wide range of up to 1/4 and almost continuously, and it is possible to perform cooling commensurate with the heat load without deteriorating the operating feeling or cooling feeling.

Note that if the opening width of the bypass hole is formed to be larger than the plate thickness of the vane along the rotational direction of the rotor (for example, if it is formed several times larger), when the vane passes through the bypass hole, the front side of the vane, i.e. The fluid to be compressed (refrigerant gas) in the working chamber on the high-pressure side will flow back into the working chamber on the rear side (low-pressure side) of the vane through the bypass hole, but such a problem was not solved in the above-mentioned embodiment. does not occur.

Furthermore, if the bypass hole is provided at a position near the suction port such that the working chamber defined between the two vanes opens simultaneously to the gas suction port for the working chamber and the bypass hole, the bypass hole However, in this embodiment, it is difficult to obtain the effect of reducing the discharge amount of the compressor, especially when the compressor rotates at high speed.
The positions 124 to 124 are such that the working chamber 140 does not open to the suction port 121 and the bypass holes 122 to 124 at the same time. 122 to 124 can communicate with the working chamber 140. That is, when internal compression occurs in the working chamber 140, the bypass holes 122 to 124 communicate with the working chamber 140. Therefore, the bypass holes 122 to 124 communicating with the working chamber 140
It is possible to create a pressure difference of more than a predetermined value between the front and back (on the gas inlet side and the gas outlet side) (in particular, the bypass hole 122 near the suction port 121). Therefore, even if the opening diameter of the bypass holes 122 to 124 on the working chamber 124 side is reduced to approximately the same level as the plate thickness of the vane 240 at most, the bypass holes 122 to 124
The compressed fluid in the working chamber 140 can be released from the bypass holes 122 to 124 to the suction pressure chamber 151 side of the compressor due to the pressure difference before and after the compressor. Even during rotation, the discharge volume reduction effect by the bypass holes 122 to 124 can be reliably performed. Therefore, by effectively utilizing all the bypass holes 122 to 124, the discharge capacity of the compressor can be changed almost continuously and over a wide range.

FIG. 5 shows a second embodiment of the invention. In this figure, the same reference numerals are given to the same components as those in the above embodiment.

In this embodiment, the open end of the cylinder hole 170 is closed with a blind post 175, and the inside of the cylinder hole 170 is divided by a spool 180 into a suction pressure introduction chamber 176 and a discharge pressure introduction chamber 177. , a bypass hole 12 is provided in the suction pressure introduction chamber 176.
A compression spring 178 is provided for biasing the spool 180 in the direction of opening 2-124. Note that between the outer periphery of the spool 180 and the cylinder hole 170, there is a connection between the discharge pressure introduction chamber 177 and the suction pressure introduction chamber 1.
A gap exists to allow leakage of compressed fluid into 76.

The discharge port 111 and the discharge pressure introducing chamber 177 are communicated via a pressure guiding passage 179.
A solenoid valve 300 as a control valve is provided in the middle.

In this embodiment, when the solenoid valve 300 is operated to open the pressure guiding passage 300, discharge pressure is introduced into the discharge pressure introduction chamber 177, and the spool 180 moves against the spring 178, thereby creating a bypass. Close holes 124-122. On the other hand, when the pressure guiding passage 179 is closed by the solenoid valve 300, the pressure in the discharge pressure introducing chamber 177 is transferred to the suction pressure introducing chamber 17 through the gap between the spool 180 and the cylinder hole 170.
It leaks to the 6 side and approaches the suction pressure. Therefore, the spool 180 is pushed by the spring 178 and moves to sequentially open the bypass holes 122 to 124.

FIG. 6 shows an example in which the compressor shown in FIG. 5 is applied to an automobile cooler system. In the figure, the refrigerant discharged from the discharge port 164 of the compressor main body 100 releases heat when passing through the condenser 310, and then passes through the liquid receiver 320 and the expansion valve 33.
0, enters the evaporator 340, absorbs external heat within the evaporator 340, and is guided to the suction port 152 of the compressor main body 100.

A temperature sensor 350 is provided near the evaporator 340 to detect the temperature of the air to be cooled that has passed through the evaporator 340 (temperature on the outlet side). Therefore, the solenoid valve 300 is controlled to be turned on and off. That is, when the heat load of the cooler system is high and the temperature on the outlet side of the evaporator 340 is higher than the set value, the control circuit 360 that receives a signal from the sensor 340 turns on the solenoid valve 300 to open the pressure passage. 179 is opened, and discharge pressure is introduced into the discharge pressure introduction chamber 177. As a result, the spool 180 moves in a direction that compresses the spring 178 and sequentially closes the bypass holes 124 to 122. Therefore, the compressor is operated at maximum displacement. On the other hand, when the temperature on the outlet side of the evaporator 340 falls below the set temperature, the solenoid valve 300 turns off and closes the pressure guiding passage 179, so the pressure in the discharge pressure introduction chamber 177 gradually approaches the suction pressure, and the spool 180 is pushed by the spring 178 and moves to gradually open the bypass holes 122 to 124. Therefore, the discharge capacity of the compressor decreases. In this way, when the discharge capacity of the compressor decreases, the temperature on the outlet side rises within a relatively short period of time and becomes equal to or higher than the set value, so that the discharge capacity of the compressor increases again.

Since the above cycle is actually repeated in a short time, the compressor according to this embodiment can also perform cooling commensurate with the heat load.

In this embodiment, the relationship between the opening positions of the bypass holes 122 to 124 with respect to the working chamber 140 and the opening widths of the bypass holes 122 to 124 on the working chamber side with respect to the vane 240 is the same as in the first embodiment, so that the bypass The effects regarding the positions of the holes 122 to 124 and the width of the opening on the working chamber side are the same as in the first embodiment.

Although the illustrated embodiments have been described above, the present invention is not limited to the aspects of the above embodiments. For example, the number of bypass holes is not limited to three, but may be two or four or more. good. Further, it is preferable that the bypass hole formed in the side plate has a circular cross section from the viewpoint of workability, but the desired effect can be obtained even if the bypass hole is formed in the side plate with a cross section other than circular. In addition, the maximum discharge capacity of the compressor is not limited to 1/4 of the maximum discharge volume, but may vary depending on the usage status of the cooler system to which the compressor is applied, for example.
It may be 3 or 1/2.

〔Effect of the invention〕

As is clear from the above description, in the present invention, the working chamber defined between two vanes has a plurality of bypass holes whose both ends open to the working chamber side and the suction pressure chamber. A suction port for supplying compressed fluid to the bypass hole and the bypass hole are arranged in a straight line in the rotational direction of the rotor at intervals from each other at positions that do not open at the same time, and each bypass hole has an opening on the working chamber side. The maximum opening width in the vane passage direction is approximately the same as the plate thickness of the vane, so that the compressed fluid in the working chamber on the high-pressure side of the vane always flows through each bypass hole into the working chamber on the low-pressure side of the vane. It is possible to provide a rotary compressor that can prevent compression loss from always occurring due to backflow, and can make a plurality of bypass holes function effectively to make the variable range of discharge capacity wide.

[Brief explanation of drawings]

FIG. 1 is a sectional view taken along line - in FIG. 2 of a rotary compressor showing a first embodiment of the present invention, and FIG. 2 is a sectional view taken along line - in FIG. 1 of the rotary compressor shown in FIG. 1. 3A to 3D are schematic sectional views showing the operating state of the rotary compressor shown in FIG. 1, and FIG. 4 is a diagram showing the operating characteristics of the rotary compressor shown in FIG. 1,
FIG. 5 is a sectional view similar to FIG. 1 of a rotary compressor showing a second embodiment of the present invention, and FIG. 6 is a configuration showing an example in which the rotary compressor shown in FIG. 5 is applied to an automobile cooler system. It is a diagram. 100... Compressor main body, 110... Liner, 1
20, 130...Side plate, 122, 123, 124
...Bypass hole, 140...Working chamber, 150...
Housing, 151... Suction pressure chamber, 161... Low discharge pressure chamber, 170... Cylinder hole, 180... Spool, 200... Rotor, 240... Vane,
300...Solenoid valve (control valve).

Claims (1)

[Claims] 1. A liner having a cylindrical inner surface, a rotor that is eccentrically arranged within the liner and rotates in one direction, and a rotor that is movably provided in a slit formed in the rotor and has one end that is movably disposed within a slit formed in the rotor as the rotor rotates. A plurality of vanes move along the inner surface of the liner with the vanes in contact with the inner surface of the liner, a pair of side plates arranged to cover both ends of the liner, and a rotor, vanes, liner, and side plates. A plurality of working chambers are formed into sections and change in volume as the rotor rotates, an inlet is provided at a position where the volume of the working chamber increases, and an outlet is provided at a position where the volume of the working chamber is minimum. In a rotary compressor having an outlet, a suction pressure chamber is provided on a side of one of the side plates opposite to the working chamber side, and both ends of the one side plate are connected to the working chamber side and the suction pressure chamber side. A plurality of bypass holes opening in 2
A working chamber defined between the two vanes is arranged in a straight line in the rotational direction of the rotor at a position where the suction port and the bypass hole do not open at the same time, and are spaced apart from each other in a straight line in the rotational direction of the rotor. The width of the opening in the vane passing direction of the chamber side opening is at most approximately the same as the plate thickness of the vane, and extends within the one side plate in the alignment direction of the bypass hole group, intersecting with the bypass hole group. A rotary compressor, characterized in that a cylinder hole is provided, and the group of bypass holes can be sequentially opened and closed in the order of arrangement by a spool slidably provided in the cylinder hole. 2. The cross-sectional area of the bypass hole group gradually increases in the direction of rotation of the rotor,
The rotation according to claim 1, wherein when the bypass hole group is sequentially opened and closed by the spool, the effective compression volume of the working chamber decreases and increases by approximately equal amounts. compressor. 3. The rotary compressor according to claim 1, wherein the spool is adapted to move within the cylinder hole in response to changes in suction pressure of the rotary compressor. 4. The spool is configured to move within the cylinder hole in response to a differential pressure between the discharge pressure and suction pressure of the rotary compressor and a spring force that acts to move the spool in a direction that reduces capacity. 2. The rotary compressor according to claim 1, wherein the projecting pressure is guided from a high pressure section within the rotary compressor to the spool via a control valve.