KR100621027B1 - Modulation apparatus for rotary compressor - Google Patents

Abstract

The variable capacity apparatus of the rotary compressor according to the present invention is separated and installed by a bearing plate so as to independently form a plurality of compression spaces in a casing, and is sealed by a bearing plate on one side so that the suction pressure and the discharge pressure are supplied back crosswise. A plurality of cylinders having a space, a plurality of vanes which are in contact with each rolling piston while radially reciprocating in each cylinder, and one of which is installed to be supported by the pressure of the back pressure space, and a compressor operating mode Accordingly, the suction pressure or the discharge pressure is supplied to the back of the vane having the back pressure space to support the vane, and the pressure of the discharge pressure is supplied to the side of the vane to supply the pressure and the side to the back of the vane. The vane is constrained or released due to the pressure difference, which is pressed or spaced from the rolling piston In a rotary compressor including a vane control unit, the variable displacement control is facilitated by negatively forming a friction avoidance groove on the surface of the bearing plate that bisects a plurality of cylinders in contact with the vanes to reduce the friction area with the vanes. It is possible to simplify the piping and to easily change the mode of the air conditioner to improve the comfort and energy saving, improve the assembly of the air conditioner, and reduce the number of valves to reduce the production cost. In addition, the friction area between the vane and the bearing plate is reduced, thereby reducing the friction loss of the vane, thereby increasing the performance of the compressor.

Description

Capacity variable device of rotary compressor {MODULATION APPARATUS FOR ROTARY COMPRESSOR}

1 is a system diagram showing an example of a conventional variable displacement rotary compressor,

2A and 2B are schematic views showing a compression chamber area for normal operation and saving operation of a conventional variable displacement rotary compressor;

3 is a schematic diagram showing an example of the present invention of a variable displacement double type rotary compressor;

Figure 4 is a longitudinal sectional view showing a variable displacement double rotary compressor of the present invention;

5A and 5B are cross-sectional views showing a variable capacity state for normal operation and saving operation of the variable displacement double rotary compressor of the present invention;

Figure 6 is a longitudinal sectional view showing a friction state between the vane and the bearing plate in the variable displacement double rotary compressor of the present invention;

Figure 7 is a longitudinal sectional view showing a modification to the vane restricting portion in the variable displacement double rotary compressor of the present invention.

** Description of symbols for the main parts of the drawing **

10: casing 20: electric mechanism part

30: first compression mechanism part 33: intermediate bearing

33a: friction avoiding groove 40: second compressor section

41: 2nd cylinder 41a: 2nd vaneslit

41b: Back pressure space 41c: Side pressure flow path

42: lower bearing 43: second rolling piston

44: second vane 45: second discharge valve

46: second muffler 50: vane control unit

51: low pressure side connector 52: high pressure side connector

53: common side connecting pipe 54: back pressure switching valve

55: stopper pin 56: pin spring

SP1, SP2: First and second gas suction pipes V1, V2: First and second compression space

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable capacity apparatus of a rotary compressor, and more particularly, to a variable capacity apparatus of a rotary compressor that constrains the reciprocating motion of the vane by using the pressure difference inside the casing and the back pressure of the vane.

In general, a rotary compressor is mainly applied to an air conditioner such as an air conditioner. Recently, as the function of the air conditioner is diversified, the rotary compressor also requires a product that can vary in capacity. As a technique for varying the capacity of a rotary compressor, a so-called inverter method that controls the number of revolutions of the compressor by using an inverter motor is mainly known, but this technique is expensive because the inverter motor itself is expensive, and most of the air conditioners are statistically Considering that it is used as a cooler, it is difficult to increase the refrigerating capacity under heating conditions, which is more difficult in the cooling conditions, which is more important in the air conditioner compressor.

Accordingly, in recent years, the so-called "refrigeration capacity change technology" by changing the volume of the compression chamber by bypassing part of the refrigerant gas compressed in the cylinder to the outside of the cylinder (hereinafter referred to as "exchange volume switching"). Abbreviated as technology) is widely known.

1 is a system diagram showing an example of a conventional variable displacement rotary compressor, Figures 2a and 2b is a schematic diagram showing the compression chamber area for the normal operation and the saving operation of the conventional variable displacement rotary compressor.

As shown in the drawing, the conventional variable displacement rotary compressor forms a bypass hole 1a of the cylinder so that a part of the refrigerant compressed in the middle of the compression space of the cylinder 1 can be bypassed according to the operation state of the compressor. The bypass pipe P1 is connected to the bypass hole 1a to the outside of the casing 2, and is piped from the end of the bypass pipe P1, and one end thereof is discharged from the casing 2 and the condenser ( 3) connecting to the discharge side connecting pipe (P3) in the middle of the gas discharge pipe (P2) for connecting while the other end is the suction side connecting pipe in the middle of the gas suction pipe (P4) connecting the evaporator (4) and the accumulator (5) It is connected to (P5). In addition, a discharge side valve V1 and a suction side valve V2 are respectively provided in the middle of the discharge side connecting pipe P3 and the suction side connecting pipe P5, and at the inlet side end of the bypass pipe P1. The bypass valve V3 is provided to open and close the bypass hole 1a of the cylinder 1 in accordance with the opening and closing of the discharge side valve V1 and the suction side valve V2.

In the drawings, reference numeral 6 denotes a rotating shaft, 7 a rolling piston, and 8 a vane.

When the compressor operates normally in the conventional variable displacement rotary compressor as described above, a part of the refrigerant discharged to the gas discharge pipe P2 is discharged as the discharge valve V1 of FIG. 1 is opened and the suction valve V2 is closed. The high pressure refrigerant flows into the bypass pipe P1 along the solid arrow, and the high pressure refrigerant pushes the bypass valve V3 to block the bypass hole 1a of the cylinder 1, as shown in FIG. 2A. All of the refrigerant sucked into the compression space of the compression is repeated a series of processes discharged to the gas discharge pipe (P2) discharged.

On the other hand, when the compressor performs the saving operation, as the discharge valve V1 of FIG. 1 is closed and the suction valve V2 is opened, the pressure back side of the bypass valve V3 becomes the suction pressure environment, as shown in FIG. 2B. The bypass valve V3 is pushed to open the bypass hole 1a, and a part of the refrigerant compressed in the compression space through the open bypass hole 1a is connected to the suction side connection pipe P5 along the dotted arrow of FIG. 1. By bypassing to the accumulator 5 through only a portion of the refrigerant sucked into the compression space of the cylinder 1 was compressed and discharged.

However, the variable capacity device of the conventional rotary compressor as described above has a problem in that the refrigeration capacity decrease rate is small and the efficiency decreases as the resistance is increased when gas is bypassed during the saving operation by separately installing the bypass circuit on the side of the cylinder. .

In addition, as the bypass pipe P2, the discharge side connecting pipe P3 and the suction side connecting pipe P5 are installed outside the compressor casing 2 and connected to the air conditioning pipe, it is difficult to assemble the air conditioning pipe. In addition, since the discharge side valve (V1) and the suction side valve (V2) must be separately installed in the pipe, there is a problem in that the number of parts increases and the cost increases.

The present invention has been made in view of the problems of the conventional variable capacity of the rotary compressor as described above, to provide a variable capacity device of the rotary compressor that can increase the efficiency by increasing the refrigeration capacity reduction rate during the saving operation. have.

Another object of the present invention is to provide a variable capacity device of a rotary compressor that can easily and simply configure a variable capacity device of a compressor, as well as reduce production costs by reducing the number of parts.

In order to achieve the object of the present invention, the bearing plate is separated and installed to independently form a plurality of compression spaces inside the casing, and one of them is sealed by the bearing plate so that the suction pressure and the discharge pressure cross supply. A plurality of cylinders provided with a back pressure space, a plurality of vanes provided to be in contact with each rolling piston while radially reciprocating in each cylinder, and one of which is installed to be supported by the pressure of the back pressure space; The pressure to supply the suction pressure or the discharge pressure to the back of the vane having the back pressure space to support the vane and to supply the discharge pressure to the side of the vane to supply the back of the vane. The vane is restrained or released due to the difference in pressure supplied to the side and the side. In the variable capacity of the rotary compressor including the vane control unit to be contacted or spaced apart, in the bearing plate for dividing a plurality of cylinders, the friction avoiding grooves to reduce the friction area with the vanes on the surface in contact with the vanes Provided is a variable capacity device of a rotary compressor, characterized in that the forming.

EMBODIMENT OF THE INVENTION Hereinafter, the variable capacity apparatus of the rotary compressor by this invention is demonstrated in detail based on one Example shown in an accompanying drawing.

Figure 3 is a schematic diagram showing an example of the present invention variable displacement double type rotary compressor, Figure 4 is a longitudinal sectional view showing a variable displacement double type rotary compressor of the present invention, Figures 5a and 5b is a normal operation of the variable displacement double rotary compressor of the present invention. Figure 6 is a cross-sectional view showing a variable capacity state for saving operation, Figure 6 is a longitudinal cross-sectional view showing a friction state between the vane and the bearing in the variable displacement double rotary compressor of the present invention, Figure 7 is a vane restraint in the variable displacement double rotary compressor of the present invention The longitudinal cross-sectional view which showed the modification with respect to a part.

As shown in the drawing, the double rotary compressor according to the present invention includes a casing 10 for communicating a plurality of gas suction pipes SP1 and SP2 and one gas discharge pipe DP and an upper side of the casing 10. And a first compression mechanism 30 and a second compression mechanism 40 installed under the casing 10 to compress the refrigerant by the rotational force generated by the transmission mechanism 20. ) And the second vane, which is connected between the recovery dog gas suction pipes SP1 and SP2 and the gas discharge pipe DP, and switches the back surface of the second vane 44 to be described later into a high pressure atmosphere or a low pressure atmosphere. While supporting the 44 and supplying a high pressure to the side surface of the second vane 44, the above-described second pressure is caused by the difference between the pressure supplied to the rear surface of the second vane 44 and the pressure supplied to the side surface. The vane control unit 50 is configured to selectively restrain the vanes 44.

The electric drive unit 20 has a stator 21 fixed to the inside of the casing 10 by applying constant speed driving or inverter driving to apply power from the outside, and has a predetermined gap inside the stator 21. Rotor 22 that rotates while interacting with the stator 21, and the rotating shaft coupled to the rotor 22 to transmit the rotational force to the first compression mechanism 30 and the second compression mechanism 40 It consists of 23.

The first compression mechanism 30 is formed in an annular shape to cover the first cylinder 31 installed in the casing 10 and the upper and lower sides of the first cylinder 31 to cover the first compression space V1. While rotating the upper bearing plate (hereinafter, the upper bearing) 32 and the intermediate bearing plate (hereinafter, the middle bearing) 33 for supporting the rotating shaft 23 in the radial direction, and the upper eccentric portion of the rotating shaft 23 The first cylinder (34) and the first rolling piston (34) for compressing the refrigerant while pivoting in the first compression space (V1) of the first cylinder (31) and the outer circumferential surface of the first rolling piston (34). A first vane 35 and a first vane, each of which is radially movable to 31 to partition the first internal space V1 of the first cylinder 31 into a first suction chamber and a first compression chamber, respectively; A first vane spring 36 made of a compression spring and a central portion of the upper bearing 32 so as to elastically support the rear side of the back plate 35; A first discharge valve 37 and a first discharge valve 37 which are coupled to the front end of the first discharge port 32a so as to be opened and closed to regulate the discharge of the refrigerant gas discharged from the compression chamber of the first internal space V1. It is composed of a first muffler (38) having an inner volume to accommodate the upper bearing (32).

The upper bearing 32 is formed in the shape of a disc to form a first compression space V1 together with the first cylinder 31, the outer diameter of which is formed to a diameter where a part of the first vane 35 is always exposed.

The intermediate bearing 33 is formed in a disk shape to form a first compression space V1 together with the first cylinder 31, as shown in FIGS. 4 and 6, but the outer diameter of the intermediate bearing 33 is to form a second vane 44 to be described later. Wrapped to form approximately the same as the inner diameter of the casing 10 to seal the back pressure space (41b) of the second cylinder (41). In addition, the movement of the first vane 35 on the upper bearing surface of the intermediate bearing 33, that is, the bearing surface in contact with the bottom surface of the first vane 35, can reduce the friction area with the first vane 35. The friction avoiding groove 33a is formed to be negative in the radial direction along the trajectory. It is preferable to form the length of the friction avoiding groove 33a in the overlapping length within about 1/2 when the first vane 35 reaches the top dead center in view of the stability of the vanes 35.

The second compression mechanism 40 is formed in an annular shape to cover the second cylinder 41 installed below the first cylinder 31 in the casing 10, and both the upper and lower sides of the second cylinder 41. 2 to form a compression space (V2) rotatably coupled to the intermediate bearing 33 and the lower bearing 42 and the lower eccentric portion of the rotating shaft 23 to support the rotating shaft 23 in the radial and axial directions The second cylinder 41 to be pressed or spaced apart from the second rolling piston 43 that compresses the refrigerant while turning in the second compression space V2 of the second cylinder 41 and the outer circumferential surface of the second rolling piston 43. A second vane 44 which partitions or communicates the second compression space V2 of the second cylinder 41 to the second suction chamber and the second compression chamber, respectively, so as to be movable in a radial direction, and a lower bearing ( Refrigerant gas discharged from the second compression chamber by being coupled to the tip of the second discharge port 42a provided near the center of the chamber so as to be openable and closed. And second discharge valve 45 for controlling the discharge, so as to accommodate the second discharge valve (45) comprises a second muffler 46 is coupled to the lower bearing (42) having a predetermined internal volume.

As shown in FIG. 4, the second cylinder 41 forms a second vane slit 41a on one side of the inner circumferential surface of the second compression space V2 such that the second vanes 44 reciprocate in the radial direction. In addition, a second suction port (not shown) for guiding the refrigerant into the second compression space V2 is radially formed at one side of the second vane slit 41a, and the refrigerant is formed at the other side of the second vane slit 41a. A second discharge guide groove (not shown) discharged into the casing 10 is formed to be inclined in the axial direction. In addition, the radially back side of the second vane slit 41a communicates with the common side connecting pipe 53 of the vane control unit 50, which will be described later, so as to achieve a suction pressure or a discharge pressure atmosphere on the rear side of the second vane 44. A back pressure space 41b having a predetermined internal volume is formed, and the inside of the casing 10 and the second vane slit 41a in a direction orthogonal to the direction of movement of the second vanes 44 or having a predetermined offset angle. ), The side pressure flow passage 41c is formed so as to restrain the second vanes 44 by the discharge pressure.

The back pressure space 41b communicates with the common side connecting pipe 53 of the vane control unit 50, which will be described later, even if the second vane 44 is completely retracted and stored in the second vane slit 41a. The rear surface of the 44 is formed to have a predetermined internal volume so as to form a pressure surface with respect to the pressure supplied through the common side connecting pipe 53 described above.

The side pressure flow passage 41c is formed in the discharge guide groove 41c of the second cylinder 41 around the second vane 44, and a plurality of side vanes 44 are provided along the height direction of the second vane 44 (in the drawing). , Upper and lower ends are shown). The second vane 44 is excessively constrained to form the entire cross-sectional area of the side pressure passage 41c more than or equal to the width of the pressure surface applied to the back surface of the second vane 44 through the back pressure space 41b. It is preferable because it can prevent that.

Here, the second cylinder 41 may be formed to have the same volume as or different from the volume of the first cylinder 31 and the compression space V1 as necessary. For example, in the case where the two cylinders 31 and 41 have the same volume, if one cylinder is saved, the compressor performs only 50% of the volume of the other cylinder. In the case where the volume of 41 is formed differently, the compressor performance is varied by the ratio of the volume of the remaining cylinders in normal operation.

The vane control unit 50 communicates with the low pressure side connecting pipe 51 communicating with the suction side of the second cylinder 41, the discharge side of the second cylinder 41, more precisely with the inner space of the casing 10. The common side connection which connects to the high pressure side connection pipe 52, the low pressure side connection pipe 51, and the high pressure side connection pipe 52, respectively, and communicates with the back pressure space 41b of the said 2nd cylinder 41 mentioned above. It is installed at the connection point of the pipe 53, the low-pressure side connecting pipe 51, the high-pressure side connecting pipe 52 and the common side connecting pipe 53, the above-mentioned common side connecting pipe 53 is connected to both side connecting pipe 51 Back pressure switching valve (54) consisting of a three-way valve or a pilot valve alternately connected to the (52), and the second vane (44) is provided in the second cylinder (41). It consists of a vane constraining part which supplies a discharge pressure to the side surface of the said 2nd vane 44 so that the 2nd vaneslit 44 may be in close contact.

The low pressure side connecting pipe 51 is connected between the suction side of the second cylinder 41 and the inlet side gas suction tube or outlet side gas suction tube (second gas suction tube) SP2 of the accumulator 5.

The high pressure side connecting pipe 52 may communicate with the lower half of the casing 10 so that the oil inside the casing 10 may directly flow into the back pressure space 41b, but in some cases, the gas discharge pipe DP You can also connect in the middle of the branch.

As described above, at least one vane restraint portion (upper and lower sides in the drawing) of the second cylinder 41 is provided such that the discharge pressure inside the casing 10 is supplied to the side surface in the thickness direction of the second vane 44. Although the side pressure flow path 41c is formed, it is preferable to form the same cross-sectional area along the height direction of the vane toward the discharge guide groove 41c based on the second vane 44.

Meanwhile, as illustrated in FIG. 7, the vane restraining part is slidably inserted into the pin hole 42b provided in the lower bearing 42, so that the second vane 44 depends on the pressure difference between the back pressure space 41b and the casing 10. A stopper pin 55 which is pressed toward the pinned groove 44a of the second vane 44 and restrains the pinned groove 44a, and the stopper pin 55 is returned so as to be spaced apart from the second vane 44. It may also be configured as a spring (56).

In the drawings, the same reference numerals are given to the same parts as in the prior art.

In the drawings, reference numeral 3 denotes a condenser and 4 denotes an evaporator.

Effects of the variable capacity device of the rotary compressor of the present invention as described above are as follows.

That is, when the rotor 22 is rotated by applying power to the stator 21 of the power mechanism unit 20, the rotating shaft 23 rotates together with the rotor 22 to increase the rotational force of the power mechanism unit 20 first. It is transmitted to the compression mechanism unit 30 and the second compression mechanism unit 40, and the first compression mechanism unit 30 and the second compression mechanism unit 40 are normally operated together according to the required capacity of the air conditioner to generate a large amount of cooling force. Alternatively, only the first compression mechanism unit 30 performs normal operation, and the second compression mechanism unit 40 performs the saving operation to generate a small capacity cooling power.

Looking at this in more detail, when the compressor or the air conditioner applied to the normal operation, the back pressure switching valve 54 is operated as shown in Figure 5a to communicate the high-pressure side connecting pipe 52 and the common side connecting pipe 53. Part of the high pressure refrigerant gas discharged into the back pressure space 41b of the second cylinder 41 is pressed against the second rolling piston 43 by being pushed by the pressure of the back pressure space 41b. The refrigerant gas flowing into the second compression space V2 is normally compressed and discharged while maintaining the closed state. At this time, the refrigerant gas or oil inside the casing 10 which is a high pressure is also introduced through the side pressure passage 41c of the second cylinder 41 to press the side surface of the second vane 44 to the discharge pressure, and the second vane ( As the cross section of the side pressure passage 41c is narrower than that of the back pressure space 41b so that 44 is compressed to the side of the second vane slit 41a, the second vane 44 overcomes the side pressure and reciprocates normally. Will be Through this, the first vane 35 and the second vane 44 are pressed into the respective rolling pistons 34 and 43 to divide the first compression space V1 and the second compression space V2 into the suction chamber and the compression chamber. While compressing and discharging the entire refrigerant sucked into each suction chamber, the compressor or the air conditioner applying the same is operated 100%.

On the other hand, when the compressor or the air conditioner applying the same, the saving operation, such as when starting the back pressure switching valve 54 as shown in Fig. 5b operates in the opposite of the normal operation to the low pressure side connecting pipe 51 and the common side Part of the low-pressure refrigerant gas drawn into the second cylinder 41 by communicating with the connection pipe 53 is introduced into the back pressure space 41b of the second cylinder 41 so that the second vane 44 has a second compression space. The suction chamber and the compression chamber of the second compression space V2 communicate with each other by being pushed by the pressure of V2 to be inward of the second vane slit 41a so that the refrigerant gas sucked into the second compression space V2 cannot be compressed. do. At this time, the refrigerant gas inside the casing 10 at high pressure flows through the side pressure passage 41c of the second cylinder 41 to press the side surface of the second vane 44 to the discharge pressure, and the second vane 44. It is made to restrain inside this 2nd vane slit 41a. As a result of the communication between the compression chamber of the second cylinder 41 and the suction chamber, the entire refrigerant sucked into the suction chamber of the second cylinder 41 is not compressed and moves back to the suction chamber along the trajectory of the rolling piston 43. 2, the compression mechanism 40 does not work, so the compressor or the air conditioner applying the same operates only as much as the capacity of the first compression mechanism 30.

Here, while the first vane 35 reciprocates linearly along the first vane slit 31a, both upper and lower sides thereof contact the upper bearing 32 and the intermediate bearing 33, respectively, causing frictional losses, In the case of the bearing 33, the friction area with the first vane 35 is widened as it is formed to have a size that covers the entire first vane 35 to seal the back pressure space 41b of the second cylinder 41. Although the loss may increase, the first vane is formed by negatively forming the friction avoiding groove 33a on the bearing surface of the first vane side of the intermediate bearing 33 to reduce the friction area with the first vane 35. It is possible to improve the performance of the compressor by smoothly reciprocating the (35).

On the other hand, when the stopper pin is used as the vane constraining part as shown in FIG. 7, the sum of the force by the pressure of the back pressure space 41b of the second cylinder 41 and the elastic force of the pin spring 56 is the second muffler. (46) While the stopper pin 55 is pushed downward because it is larger than the force due to the internal pressure, the second vane 44 freely reciprocates freely in the second vane slit 41a, while saving. During operation, the stopper pin 55 is pushed up while the force by the pressure of the back pressure space 41b and the force of the elastic force of the pin spring 56 are smaller than the force by the pressure of the internal space of the second muffler 46. The pinned groove 44a of the second vane 44 is inserted to restrain the linear movement of the second vane 44.

The variable capacity device of the rotary compressor according to the present invention divides or communicates the compression space of the cylinder with the suction chamber and the compression chamber while selectively restraining by generating a pressure difference on the back and side of the vane or restraining the vane with a separate stopper pin. In addition, it is easy to change the capacity of the compressor and simplify the piping, and the mode can be easily changed when applying the compressor to an air conditioner, improving comfort and energy saving and preventing interference with other piping. By improving the assembly of the air conditioner can reduce the number of valves can reduce the production cost. In addition, by negatively forming the friction avoidance groove in the bearing plate contacting the bottom of the vane, it is possible to increase the performance of the compressor by reducing the friction area between the vane and the bearing plate, thereby reducing the frictional losses of the vane.

Claims (6)

A plurality of cylinders are provided by separating the bearing plate to form a plurality of compression spaces in the casing independently, one side of the casing is sealed by the bearing plate and provided with a back pressure space so that the suction pressure and the discharge pressure are supplied crosswise. And a plurality of vanes which are in contact with each rolling piston while radially reciprocating in each cylinder, one of which is installed to be supported by the pressure of the back pressure space, and a back pressure space according to the operation mode of the compressor. The pressure of suction pressure or discharge pressure is supplied to the back of the vane to support the vane, and at the same time, the pressure of the discharge pressure is supplied to the side of the vane and the pressure supplied to the back of the vane and the pressure to be supplied to the side Vane agent to be pressed or spaced with the rolling piston while the vane is restrained or released by In a capacity variable device for a rotary compressor, including a unit, A variable capacity device of a rotary compressor, characterized by negatively forming a friction avoiding groove on a surface contacting the vanes in a bearing plate for dividing a plurality of cylinders to reduce the friction area with the vanes. The method of claim 1, The friction avoidance groove is formed in the radial direction long along the movement trajectory of the vane, the length of the variable variable apparatus of the rotary compressor, characterized in that the length is formed to be within 1/2 of the vane length when the vane reaches the top dead center. The method according to claim 1 or 2, The vane control unit alternately connects the low pressure side connecting tube communicating at the suction side of the cylinder, the high pressure side connecting tube communicating at the discharge side of the cylinder, and the low pressure side connecting tube and the high pressure side connecting tube, respectively. A back pressure switch valve installed at a connection point of the common side connector communicating with the low pressure side connector, the high pressure side connector, and the common side connector to connect the common side connector to both side connectors alternately, and back pressure A variable capacity device of a rotary compressor, characterized in that the vane constraining portion restrains the vane inside the vaneslit when the pressure in the space is the suction pressure. The method of claim 3, The low pressure side connecting pipe is installed between the suction side and the gas suction pipe of the cylinder to connect to the inlet side or the outlet side of the accumulator separating liquid refrigerant and gas refrigerant, and the high pressure side connecting pipe is connected in the middle of the gas discharge pipe. A variable capacity device of a rotary compressor, characterized in that connected in communication with the inner space of the casing. The method of claim 4, wherein A vane constraining unit is formed by supplying the discharge pressure in the casing to the side of the thickness direction of the vane to form at least one side pressure passage so that the vane is in close contact with the vane slit. The method of claim 4, wherein The vane restraining part slides into the pin hole provided in the cylinder or the bearing plate, and is pressed toward the vane according to the pressure difference between the back pressure space and the casing and stops the vane to restrain the stopper pin, and the stopper pin is returned. A variable capacity device of a double rotary compressor, characterized in that the pin spring is spaced apart from the vane.

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