KR100724450B1 - Capacity modulation type rotary compressor - Google Patents

Abstract

A variable displacement type rotary compressor is provided to restrain a vane by a pressure difference between front and rear parts and side parts with respect to the vane, thereby simplifying the structure for easy assembling and improving the reliability of the vane restraining. A variable displacement type rotary compressor includes a casing(100) for keeping a discharge pressure, and a motor(200) fixed in the casing for generating driving force. At least one or more cylinder assemblies(300,400) are fixed in the casing, and each has a rolling piston(340,430) eccentrically coupled with a rotation shaft of the motor and carrying out orbiting motion, and a vane(350,440) for carrying out rectilinear motion in contact with the rolling piston to compress refrigerant in contact with the rolling piston. A vane chamber(412) is formed at a rear part of the vane(440) and separated from an internal space of the casing. A vane restraining unit(500) supplies suction pressure to the vane chamber, and promotes discharge pressure to at least one of side and upper/lower surfaces. The vane restraining unit has a stopper to be driven by discharge pressure at a side of the vane(440) to restrain the vane(440).

Description

CAPACITY MODULATION TYPE ROTARY COMPRESSOR}

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

2 is a cross-sectional view taken along line "I-I" of FIG. 1;

3 and 4 are longitudinal cross-sectional view showing the normal operation and the saving operation during the embodiment of the restraining vanes in the variable displacement double rotary compressor of the present invention;

Figure 5 is a longitudinal sectional view showing another embodiment of restraining the vanes in the present invention variable displacement double rotary compressor,

6 and 7 are a longitudinal sectional view showing another embodiment of restraining vanes in the variable displacement double rotary compressor of the present invention and a schematic view showing the restraining process,

8 and 9 are a longitudinal sectional view showing another embodiment of restraining vanes in the variable displacement double rotary compressor of the present invention and a schematic view showing the restraining process,

10 is a longitudinal sectional view of another embodiment of restraining vanes in the present invention of a variable displacement double rotary compressor.

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

100: casing 200: electric mechanism part

300: first compression mechanism 400: second compression mechanism

410: second cylinder 411: second vane slot

412: vane chamber 413: vane binding euro

420: lower bearing 422: vane restriction flow path

430: second rolling piston 440: second vane

450: second discharge valve 460: second muffler

500: vane restriction unit 510: suction pressure connection pipe

520: discharge pressure side connection pipe 530: common side connection pipe

540: pressure switching valve 541: valve housing

542: sliding valve 550: stopper

551: stopper pin 552: pin spring

610: suction pressure side connection pipe 620: discharge pressure side connection pipe

630: common side connector 640: cylinder side connector

650: pressure switching valve 651: valve housing

652: sliding valve 660: stopper

661: stopper pin 662: pin spring

DP: Gasoline discharge pipe SP1, SP2: First and second gas suction pipe

V1, V2: first and second compression space

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor, and more particularly, to a variable displacement rotary compressor for confining or releasing a vane while cross-feeding a pressure of suction pressure or discharge pressure to a side of a vane slot.

In general, an air conditioner (air-conditioner) keeps the room temperature in a set state to keep the room in a comfortable state. Such an air conditioner includes a refrigeration system, and the refrigeration system includes a compressor for compressing a refrigerant, a condenser for releasing heat to the outside while the refrigerant compressed in the compressor is condensed, and a pressure of the refrigerant condensed in the condenser. An expansion valve for lowering the pressure, and an evaporator for absorbing external heat while the refrigerant passing through the expansion valve evaporates.

As the refrigeration system is powered and the compressor is operated, the high temperature and high pressure refrigerant discharged from the compressor is sequentially passed through the condenser, the expansion valve and the evaporator, and then sucked into the compressor. In the process, heat is generated in the condenser and absorbs external heat from the evaporator to form cold air. The heat generated from the condenser and the cold air formed in the evaporator are selectively circulated and flowed into the room to keep the room in a comfortable state.

On the other hand, there are a variety of compressors constituting the refrigeration system, in particular, the compressor applied to the air conditioner is a rotary compressor (rotary compressor) and a scroll compressor (scroll compressor).

The most important factors in the process of researching and manufacturing the air conditioner as described above are to minimize the manufacturing cost and to minimize the energy consumption during operation of the air conditioner in order to increase the competitiveness of the product.

The condition for operating the air conditioner so as to minimize the power consumption of the air conditioner is to operate the air conditioner according to the load of the indoor space in which the air conditioner is installed, that is, the temperature condition. That is, when the temperature of the room rises sharply, the air conditioner is operated in a power mode so that a lot of cool air is generated in accordance with the excessive temperature change (excessive load) in order to maintain the set room temperature. When the change is small, the air conditioner is operated in a saving mode so that less cool air is generated to maintain the set room temperature.

One of the factors for satisfying such a condition is to change the refrigeration capacity of the refrigeration system by adjusting the amount of refrigerant compressed and discharged from the compressor which is a main component for operating the refrigeration system.

One of the methods of controlling the discharge capacity of the refrigerant discharged from the compressor is to apply an inverter motor capable of varying the number of rotations of the drive motor constituting the compressor. The discharge flow rate of the refrigerant discharged from the compressor is controlled by adjusting the rotation speed of the driving motor of the compressor according to the change of the condition of the room where the air conditioner is installed. The amount of heat and cold air generated in the condenser and the evaporator is adjusted according to the change in the discharge flow rate discharged from the compressor.

However, when the drive motor of the compressor is applied as an inverter motor, the price of the inverter motor becomes very expensive, thereby increasing the unit price of the product, which has a disadvantage in that the price competitiveness is lowered.

Accordingly, in recent years, instead of the inverter method, a portion of the refrigerant compressed in the cylinder of the compressor is bypassed to the outside of the cylinder to change the volume of the compression chamber or the vanes are separated from the rolling piston so that the compression chamber and the suction chamber communicate with each other. Techniques for idling have been widely developed. However, the former has a problem that the pipe system for bypassing the refrigerant to the outside of the cylinder is complicated to increase the flow resistance of the refrigerant to decrease the efficiency, the latter is usually used by using a magnet to constrain the vane to the vane slot The use of a tension spring is known, but this is difficult to install, and in particular, in the case of using a magnet, metal powder of the compressor or the refrigeration system may be attached to the vanes to damage the bearing surface.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a variable displacement rotary compressor that can be easily and reliably restrained when the vanes are spaced apart from the rolling piston at idle.

In order to achieve the object of the present invention, the casing for maintaining the discharge pressure; A motor fixedly installed in the casing to generate a driving force; The refrigerant is fixed to the inside of the casing, the refrigerant is compressed by a rolling piston eccentrically coupled to the rotating shaft of the motor and the vane in a linear motion in contact with the rolling piston, the back of the vane inside the casing At least one cylinder assembly having a vane chamber separated from the space; And a stopper for supplying suction pressure to the vane chamber, adding discharge pressure to at least one of the left and right sides and the top and bottom sides of the vane, and at the same time operating the discharge pressure at one side of the vanes to restrain the vanes. There is provided a variable displacement rotary compressor including a vane confinement unit.
Moreover, the casing which maintains a discharge pressure state; A motor fixedly installed in the casing to generate a driving force; The refrigerant is fixed to the inside of the casing, and the refrigerant is compressed by a rolling piston eccentrically coupled to the rotating shaft of the motor and a vane in linear motion in contact with the rolling piston, and the vane discharges the vane at the rear side of the vane. At least one cylinder assembly formed to communicate with an inner space of the casing so as to be supported by pressure; And a vane confinement unit for constraining or releasing the vanes from the rolling piston in contact with the rolling piston according to the pressure difference added to the vanes.

Hereinafter, a variable displacement rotary compressor according to the present invention will be described in detail with reference to an embodiment shown in the accompanying drawings.

1 is a longitudinal cross-sectional view showing a variable displacement double rotary compressor of the present invention, Figure 2 is a cross-sectional view "I-I" of Figure 1, Figure 3 and Figure 4 is a constrained vane in the variable displacement double rotary compressor of the present invention The longitudinal cross-sectional view showing the normal operation and the saving operation for the embodiment, Figure 5 is a longitudinal cross-sectional view showing another embodiment for restraining the vane in the variable displacement double rotary compressor of the present invention.

As shown in FIG. 1, the double rotary compressor according to the present invention includes a casing 100 in which a plurality of gas suction pipes SP1 and SP2 and one gas discharge pipe DP communicate with each other, as shown in FIGS. 1 and 2. And an electric mechanism part 200 installed above the casing 100 to generate rotational force, and a first compressor mechanism part installed under the casing 100 to compress the refrigerant with the rotational force generated by the electric mechanism part 200. The second vane (300) and the second compression mechanism 400, and the second compression mechanism 400 to the normal operation or saving operation at the same time the second compression mechanism 400 when the saving operation of the second vane ( 440 is composed of a vane confinement unit 500 to maintain the state accommodated in the second vane slot 411.

The motor mechanism 200 is a fixed speed drive or a variable speed (inverter) drive is fixed to the inside of the casing 100 to apply power from the outside and the inside of the stator 210 The rotor 220 is rotated while interacting with the stator 210 is disposed with a predetermined gap, and the first compression mechanism unit 300 and the second compression mechanism unit coupled to the rotor 220 to the rotational force It consists of a rotating shaft 230 for transmitting to (400).

The first compression mechanism (300) is formed in an annular shape is installed in the interior of the casing 100, the first cylinder 310 and the first cylinder 310 is covered on both sides of the first compression space ( V1) and the upper bearing plate (hereinafter referred to as the upper bearing) 320 and the intermediate bearing plate (hereinafter referred to as the middle bearing) 330 for supporting the rotating shaft 230 in the radial direction and the upper side of the rotating shaft 230 A first rolling piston 340 rotatably coupled to the eccentric part to compress the refrigerant while turning in the first compression space V1 of the first cylinder 310, and an outer circumferential surface of the first rolling piston 340. The first vane 350 is coupled to the first cylinder 310 so as to be pressurized in a radial direction so that the first inner space V1 of the first cylinder 310 is divided into a first suction chamber and a first compression chamber, respectively. ) And a vane made of a compression spring so that the rear side of the first vane 350 is elastically supported. It is coupled to the support spring 360 and the tip of the first discharge port 321 provided near the center of the upper bearing 320 so as to be opened and closed to discharge the refrigerant gas discharged from the compression chamber of the first internal space (V1). It consists of a first discharge valve 370 to adjust the, and a first muffler 380 coupled to the upper bearing 320 having an internal volume to accommodate the first discharge valve 370.

The second compression mechanism 400 is formed in an annular shape and is provided on the upper and lower sides of the second cylinder 410 and the second cylinder 410 installed below the first cylinder 310 inside the casing 100. And the second bearing 330 and the lower bearing 420 to support the rotary shaft 230 in the radial and axial directions while forming a second compression space (V2), and the lower eccentric portion of the rotary shaft 230 The second rolling piston 430 which is coupled to be capable of being compressed in the second compression space V2 of the second cylinder 410 and compresses the refrigerant, and is pressed or spaced apart from the outer circumferential surface of the second rolling piston 430. A second vane movably coupled to the second cylinder 410 to allow the second compression space V2 of the second cylinder 410 to be partitioned or communicated with the second suction chamber and the second compression chamber, respectively; 440 and a tip of the second discharge port 421 provided near the center of the lower bearing 420. The lower bearing is provided with a second discharge valve 450 coupled to open and close to control the discharge of the refrigerant gas discharged from the second compression chamber, and a predetermined internal volume to accommodate the second discharge valve 450. The second muffler 460 is coupled to the 420.

As shown in FIG. 2, the second cylinder 410 has a second vane slot 411 on one side of the inner circumferential surface constituting the second compression space V2 such that the second vane 440 reciprocates in a radial direction. The second vane slot 411 is formed at one side of the second vane slot 411 in a radial direction to guide the refrigerant into the second compression space V2. On the side, a second discharge guide groove (not shown) for discharging the refrigerant into the casing 100 is formed to be inclined in the axial direction. In addition, the radial vane side of the second vane slot 411 is connected to the common side connecting pipe 530 which will be described later, the vane is a closed space so that the rear side of the second vane 440 to achieve the suction pressure or discharge pressure atmosphere The chamber 412 is formed, and the second vane slot 411 communicates with the inside of the casing 100 in a direction orthogonal to the direction of movement of the second vane 440 or having a predetermined offset angle. A vane confinement passage 413 is formed to constrain the second vane 440 by the discharge pressure of the inner space of the casing 100.

The vane confinement passage 413 is located at the discharge guide groove (not shown) of the second cylinder 410 around the second vane 440 as shown in FIG. 2, and is disposed on the outer circumferential surface of the second cylinder 410. It is formed through the center of the second vane slot 411. In addition, the vane confinement passage 413 is formed to be stepped into two stages with a narrow second vane slot 411 using a two-stage drill. In addition, the vane confinement passage 413 has an outlet end formed substantially in the longitudinal direction of the second vane slot 411 so that the linear movement of the second vane 440 can be stably performed. In addition, the vane confinement passage 413 is formed in the cross-sectional area is equal to or narrower than the pressure surface applied to the back surface of the second vane 440 through the vane chamber 412, that is, the cross-sectional area of the second vane slot 411. The second vane 440 may be prevented from being excessively restrained, which is preferable. In addition, the vane confinement passage 413 may be formed in plural (in the drawings, upper and lower ends) in the height direction of the second vane 440.

The vane confinement passage 413 may be formed in the second cylinder 410 in a transverse direction to correspond to the left and right sides of the second vane 440 as shown in FIG. 2, but in some cases, the second vane 440. It may be formed in the transverse direction or the longitudinal direction on the intermediate bearing 330 or the lower bearing 420 to correspond to the left and right side or the upper and lower side of the).

The vane confinement unit 500 includes a suction pressure side connection pipe 510 branched from the second gas suction pipe SP2, a discharge pressure side connection pipe 520 connected to an inner space of the casing 100, and the second pressure suction connection pipe 520. The common side connection pipe 530 connected to the vane chamber 412 of the two cylinder 410 and cross-communicating with the suction pressure side connection pipe 510 and the discharge pressure side connection pipe 520, and the common side connection pipe 530. It consists of a pressure switching valve 540 connected to the vane chamber 412 of the second cylinder 410 through.

The suction pressure side connecting pipe 510 is branched between the suction side of the second cylinder 410 and the inlet side second gas suction pipe SP2 of the accumulator 110.

The discharge pressure side connecting pipe 520 may communicate with the lower half of the casing 100 so that oil inside the casing 100 may directly flow into the vane chamber 412, but in some cases, the gas discharge pipe DP You can also connect in the middle of). In this case, since the vane chamber 412 is sealed, oil may not be supplied between the second vane 440 and the second vane slot 411, so that a friction loss may occur. Therefore, oil is supplied to the lower bearing 420. A hole (not shown) may be formed to supply oil when the second vane 440 reciprocates.

In addition, the vane confinement unit 500 has a vane confinement passage 413 formed in the second cylinder 410, the intermediate bearing 330, or the lower bearing 420 so that suction pressure is supplied to the vane chamber 412. When the second vane 440 accommodated in the second vane slot 411 is configured to be pushed to the opposite side to restrain, or as shown in Figure 5 the second cylinder 410 or intermediate bearing 330 or lower bearing ( A stopper 550 formed of a stopper pin 551 and a pin spring 552 is installed in the 420 so that the stopper pin 551 beats the pin spring 552 when suction pressure is supplied to the vane chamber 412. The second vane 440 is pushed to the opposite side so that the second vane 440 is pressed while being in close contact with the opposite bearing, or is directly hanged by the second vane.

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

In the drawings, reference numeral 1 denotes a condenser, 2 an expansion mechanism, 3 an evaporator, 541 a valve housing, and 542 a sliding valve.

The effects of the present invention having a variable displacement double type rotary compressor as described above are as follows.

That is, when the rotor 220 rotates by applying power to the stator 210 of the power mechanism unit 200, the rotation shaft 230 rotates together with the rotor 220 while the power mechanism unit 200 is rotated. The rotational force of the first compression mechanism 300 and the second compression mechanism 400 is transmitted, and the first compression mechanism 300 and the second compression mechanism 400 together in accordance with the required capacity in the refrigeration system It generates a large amount of cold power by operating or only the first compression mechanism unit 300 is a normal operation and the second compression mechanism 400 performs a saving operation to generate a small capacity of cooling power.

Here, when the compressor or the refrigerating system to which the compressor is applied operates normally, as shown in FIG. 3, the suction pressure side connecting pipe 510 is blocked while the sliding valve 542 operates, while the discharge pressure side connecting pipe ( 520 is connected to the common side connecting pipe 530, the oil or refrigerant of a high discharge pressure is supplied to the vane chamber 412 of the second cylinder 410. Accordingly, the second vane 440 is pushed toward the second rolling piston 430 by the pressure of the vane chamber 412 while maintaining the state in which the second vane 440 is pressed against the second rolling piston 430. The refrigerant gas flowing into V2) is normally compressed and discharged. At this time, the high-pressure refrigerant gas or oil is supplied through the vane confinement passage 413 provided in the second cylinder 410, but the cross-sectional area of the vane confinement passage 413 is the radius of the second vane slot 411. As the cross-sectional area is narrower than the direction cross-sectional area, the pressing force at the side surface is smaller than the front-back pressing force in the vane chamber 412 to prevent the second vane 440 from being constrained, thereby causing the second vane 440 to have a second rolling piston 430. According to the turning movement of), it reciprocates continuously in the forward and backward direction. In addition, even when the stopper 550 is installed as shown in FIG. 5, the pressure between both ends of the stopper pin 551 is the same as the pressure of the vane chamber 412 maintains a high discharge pressure. As a result, the stopper pin 551 does not restrain the second vane 440.

In this way, the first vane 350 and the second vane 440 are pressed against each of the rolling pistons 340 and 430 to compress the first compression space V1 and the second compression space V2 with the suction chamber. The compressor or the refrigeration system to which the compressor is applied is 100% operated by compressing and discharging the entire refrigerant sucked into each suction chamber while dividing into a chamber.

On the other hand, in the case of saving operation, such as when the compressor or the refrigerating system to which the compressor is applied, the sliding valve 542 of the pressure switching valve 540 operates as opposed to the normal operation as shown in FIG. The connecting pipe 510 and the common side connecting pipe 530 communicate with each other, so that a low pressure refrigerant flows into the vane chamber 412 and the second pressure is caused by the pressure of the second compression space V2 having a relatively high pressure. The vane 440 is pushed toward the vane chamber 412 to be spaced apart from the second rolling piston 430 so that the suction chamber and the compression chamber of the second compression space V2 communicate with each other. As a result, the refrigerant sucked into the second compression space V2 is leaked into the suction chamber and thus cannot be compressed, so that the second compression mechanism 400 cannot work. At this time, the high-pressure oil or refrigerant gas flows into the vane confinement passage 413 provided in the second cylinder 410 to constrain the second vane 440 inside the second vane slot 411. The second vane 440 may not move in a state spaced apart from the second rolling piston 430. In addition, even when the stopper 570 is provided, as shown in FIG. 5, as the pressure of the vane chamber 412 maintains the suction pressure, the stopper pin 551 is formed due to the pressure difference between the stopper pins 551. The elasticity of the pin spring 552 is moved to the second vane 440 to restrain the second vane 440 to be in close contact with the intermediate bearing 330 on the opposite side.

In this way, as the compression chamber and the suction chamber of the second cylinder 410 communicate with each other, the entire refrigerant sucked into the suction chamber of the second cylinder 410 is not compressed and moves back to the suction chamber along the trajectory of the rolling piston 430. Since the second compression mechanism 400 does not work, the compressor or the refrigeration system to which the pressure is applied is operated only as much as the capacity of the first compression mechanism 300.

On the other hand, there is another embodiment of the vane confinement unit of the variable displacement rotary compressor according to the present invention is as follows.

That is, in the above-described embodiment, the suction pressure is supplied to the vane chamber 412 to push the vane by using the discharge pressure or the stopper while the second vane 440 is stored in the vane slot 411. In this embodiment, the second vane 440 is constrained by using the pressure difference between the compression space V2 of the second cylinder 410 and the pressure of the vane chamber 412.

For example, as shown in FIG. 6, the suction pressure side connecting pipe 510 branched from the first gas suction pipe SP1 is selectively connected to the common side connecting pipe 530 which connects to the vane chamber 412. 2 When the compression mechanism 400 performs the saving operation, the suction pressure of the first compression mechanism 300 that is in normal operation is kept the same as the pressure of the vane chamber 412 of the second compression mechanism 400 that performs the saving operation. The vane confinement unit 500 is configured to be.

In this case, a refrigerant having a suction pressure is supplied to each of the compression spaces V1 and V2 of the first compression mechanism 300 and the second compression mechanism 400, but is provided in the second compression mechanism 400. As the vane chamber 412 maintains the suction pressure, the second vane 440 retreats to the inside of the vane chamber 412. Thus, in the compression space V2 of the second compression mechanism 400, As the refrigerant leaks from the compression chamber to the suction chamber, idling occurs. In addition, as shown in FIG. 7, due to the refrigerant leakage occurring in the compression space V2 of the second cylinder 410, a kind of refrigerant retention occurs in the second gas guide pipe SP2 and the second cylinder 410. The pressure in the compression space V2 (approximately the intermediate pressure Pb) is higher than the suction pressure Ps of the first compression mechanism 300, that is, the pressure in the vane chamber 412, so that the second vane 440 is The second vane slot 412 is to be stored in the state.

Subsequently, when the sliding valve 542 in the pressure switching valve 540 is moved in reverse, the discharge pressure side connecting pipe 520 and the common side connecting pipe 530 are connected to the vane chamber of the second compression mechanism 400. The second compression mechanism 400 is in a state in which the second vane 440 is in pressure contact with the second rolling piston 430 while the pressure becomes high and is higher than the pressure in the compression space V2 of the second cylinder 410. Is normal operation.

On the other hand, there is another embodiment of the vane confinement unit of the variable displacement rotary compressor according to the present invention.

That is, all of the above-described embodiments are related to the case where the vane chamber 412 of the second compression mechanism 400 is a closed space separated from the internal space of the casing 100, but the second vane 440 Even when the rear side is formed as an open space to communicate with the inner space of the casing 100, the second vane 440 may be restrained by using the pressure difference.

To this end, as shown in FIG. 8, the rear side of the second compression mechanism 400 is always supported by the discharge pressure of the inner space of the casing 100. In communication with the lower bearing (or the intermediate bearing or the second cylinder) 420, a pressure difference between front and rear of the second vane 440 may be generated to restrain or release the second vane 440. A vane confinement passage 422 is formed to allow the vane confinement passage 422 and the suction space to connect the refrigerant of the suction pressure or the discharge pressure to the compression space V2 of the second cylinder 410. 610, the discharge pressure side connecting pipe 620, the common side connecting pipe 630 and the cylinder side connecting pipe 640 are connected to the pressure switching valve 650 is installed.

For example, the pressure switching valve 650 is provided with a sliding valve 652 to slide inside the valve housing 651 having four conduits, the sliding valve 652 is operated by an electromagnet (not shown) In order to selectively cross-combine four pipes, the first pipe line of the valve housing 651 is connected to the suction pressure side connection pipe 610 extending from the second gas suction pipe SP2, and the second pipe line is It is connected to the discharge pressure side connecting pipe 620 communicated to the inner space of the casing 100, the third pipe is connected to the common side connection pipe 630 communicated to the vane confinement passage 422, the fourth pipe It is connected to the cylinder-side connecting pipe 640 communicated with the inlet of the second cylinder (410).

The discharge pressure side connection pipe 640 has a rear side of the second vane 440 communicates with the inner space of the casing 100 so that oil is continuously supplied, so that the discharge pressure side connection pipe 640 is installed higher than the oil level so as to communicate with the vane confinement passage ( 422 may be supplied to the refrigerant.

In the variable displacement rotary compressor of the present invention as described above, the second vane is restrained as follows.

That is, when the sliding valve 652 of the pressure switching valve 650 moves to communicate the first and third pipes, the second and fourth pipes are automatically communicated with each other. Accordingly, the discharge pressure side connecting pipe 620 and the cylinder side connecting pipe 640 are connected to supply the high pressure discharge pressure to the compression space V2 of the second cylinder 410 and at the same time the suction pressure side connecting pipe 610. And the common side connecting pipe 630 is connected to the suction pressure of the low pressure is supplied to the vane confinement passage 422. Accordingly, the rear side of the second vane 440 maintains the same high pressure as the pressure of the inner space of the casing 100, while the compression space V2 of the front side of the second vane 440, that is, the second cylinder 410. ) The pressure is maintained at a high pressure to achieve a pressure balance, and in this state, as a low pressure is supplied to the side of the second vane 440, high pressure is formed at both front and rear sides of the second vane 440 as shown in FIG. 9. While the discharge pressure Pd of the gas tries to leak toward the suction pressure Ps of the low pressure formed in the vane confinement passage 422, the second vane 440 is strongly constrained.

On the other hand, when the sliding valve 652 of the pressure switching valve 650 moves to communicate the first and fourth pipes and communicate with the remaining second and third pipes, the second cylinder 410 is compressed. A refrigerant of suction pressure flows into the space V2, and a discharge pressure of high pressure is supplied to the vane confinement passage 422, so that the second vane 440 is second rolled according to the pressure difference between the front side and the rear side. Out of the piston 430 will be in normal operation while being pressed.

On the other hand, as shown in Figure 10 when the stopper 660 consisting of the stopper pin 661 and the pin spring 662 in the vane confinement passage 422, the second vane 440 is more firmly You can restrain. That is, when the suction pressure is supplied to the vane confinement passage 422 using the pressure switching valve 650, the force of the vane confinement passage 422 combined with the force of the elastic force of the pin spring 661 is combined. The stopper pin 661 is pushed toward the second vane 440 to restrain the second vane 440 while being smaller than the force caused by the pressure of the inner space of the casing 100. When the discharge pressure is supplied, the stopper pin 661 is pushed by the elastic force of the pin spring 662 to release the restraint of the second vane 440.

For reference, the present embodiments have been described as an example in which the vane confinement unit is installed in either cylinder assembly in a rotary compressor having a plurality of cylinder assemblies, but in some cases, the vane confinement unit is independently installed in each cylinder assembly. The same may be applied to a single stage rotary compressor having a single cylinder assembly.

The variable displacement rotary compressor according to the present invention is configured to constrain the vane by using the pressure difference added to the front and rear sides of the vane and the pressure difference added to the side, thereby simplifying the assembly process and simplifying the assembly process. Lower production costs and increase productivity. Further, as the vanes are restrained by using the pressure difference of the system, the reliability is high, and in particular, when the stopper is used, the reliability can be further increased.

Claims (12)

A casing for maintaining a discharge pressure state; A motor fixedly installed in the casing to generate a driving force; The refrigerant is fixed to the inside of the casing, the refrigerant is compressed by a rolling piston eccentrically coupled to the rotating shaft of the motor and the vane in a linear motion in contact with the rolling piston, the back of the vane inside the casing At least one cylinder assembly having a vane chamber separated from the space; And A vane provided with a stopper for supplying suction pressure to the vane chamber, adding discharge pressure to at least one of the left and right side surfaces and the upper and lower sides of the vane, and at the same time operating the discharge pressure at one side of the vane to restrain the vane. Capacity variable type rotary compressor including a restraining unit. delete delete delete A casing for maintaining a discharge pressure state; A motor fixedly installed in the casing to generate a driving force; The refrigerant is fixed to the inside of the casing, and the refrigerant is compressed by a rolling piston eccentrically coupled to the rotating shaft of the motor and a vane in linear motion in contact with the rolling piston, and the vane discharges the vane at the rear side of the vane. At least one cylinder assembly formed to communicate with an inner space of the casing so as to be supported by pressure; And And a vane confinement unit for constraining or releasing the vanes from the rolling piston in contact with the rolling pistons according to the pressure difference added to the vanes. The method of claim 5, A variable displacement rotary compressor for supplying a low pressure suction pressure to at least one of left, right, and up and down sides of the vane to constrain the vane. The method of claim 5, And at least one of the left and right sides and the top and bottom sides of the vanes, the stopper is further provided to stop the vanes by the suction pressure. delete delete delete The method of claim 5, The suction side pressure of the cylinder assembly which is variable in capacity among the cylinder assemblies may be selectively supplied as suction pressure or discharge pressure, and at least one of the left and right side surfaces and the upper and lower sides of the vane may be opposite to the suction side pressure of the cylinder assembly. A variable displacement rotary compressor that adds pressure to cause the vane to restrain or release. The method of claim 11, One side of the vane is a variable displacement rotary compressor further comprises a stopper to operate by the suction pressure to restrain the vane.

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