KR100795958B1 - Variable displacement rotary compressors - Google Patents

Abstract

A capacity variable rotary compressor is provided to cause a pressure difference at both sides of a vane in saving operation to restrict the vane by the pressure difference to prevent the vane from shaking when the compressor is converted into the saving operation from power operation. A rolling piston rotates eccentrically in an inner space of a sealed cylinder assembly. A vane contacting with the rolling piston defines the inner space into a compression chamber and a suction chamber, moving in a straight line in a radial direction. In saving operation, a suction pressure and a discharge pressure are added in a direction crossing a moving direction of the vane to restrict the vane by a pressure difference. A mode converting unit(500) contacts the vane with the rolling piston or separates the vane from the rolling piston in accordance with an operation mode of a compressor.

Description

Capacity variable rotary compressors {MODULATION TYPE ROTARY COMPRESSOR}

1 is a cross-sectional view showing an embodiment of a conventional variable displacement rotary compressor,

Figure 2 is a cross-sectional view showing another embodiment of a conventional variable displacement rotary compressor,

Figure 3 is a cross-sectional view showing another embodiment of a conventional variable displacement rotary compressor,

4 is a graph showing the noise characteristics when switching modes in the variable displacement rotary compressor of FIG.

Figure 5 is a longitudinal cross-sectional view showing an embodiment of the present invention variable displacement rotary compressor,

Figure 6 is a cross-sectional view showing the release state of the vanes at power all in the variable displacement rotary compressor of the present invention,

7 is a cross-sectional view showing an enlarged state of restraint of vanes in a saving mode of the present invention in a variable displacement rotary compressor;

8 is an enlarged view illustrating in detail the process of restraining the vanes in FIG. 7;

9 is a graph showing the noise characteristics when switching modes in the variable displacement rotary compressor of the present invention,

10 and 11 are longitudinal cross-sectional views showing other embodiments of the variable displacement rotary compressor of the present invention.

** 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: inlet 413: vane chamber

414: high pressure flow path 415: low pressure flow path

420: lower bearing 430: second rolling piston

440: second vane 500: mode switching means

510: low pressure side connector 520: high pressure side connector

530: common side connecting pipe 540: first mode switching valve

550: second mode switching valve 600: refrigerant switching valve

700: back pressure switching valve 800: vane control unit

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

V1, V2: first and second compression space

The present invention relates to a variable displacement rotary compressor, and more particularly to a variable displacement rotary compressor that can prevent the generation of noise when switching modes.

In general, the variable capacity rotary compressor is configured to increase or decrease the refrigeration capacity of the compressor according to the ambient conditions to maximize the efficiency compared to the input. Recently, a method of applying an inverter motor as one of methods for adding or subtracting a refrigeration capacity of a compressor has been known. However, when the inverter motor is applied, the price of the inverter motor is very expensive, which increases the production cost of the compressor. Moreover, the technique which changes the volume of a compression chamber by bypassing a part of refrigerant | coolant compressed by the cylinder of a compressor to the exterior of a cylinder instead of an inverter system is also introduced. However, this technique has a disadvantage in that the piping system for bypassing the refrigerant to the outside of the cylinder is complicated, which increases the flow resistance of the refrigerant, thereby degrading efficiency.

Therefore, a method of changing the compressor capacity while simplifying the piping system without using an inverter motor has been proposed. The first method is configured to change the internal space pressure of the cylinder to suction pressure or discharge pressure, so that the compression chamber is formed by allowing the vane to slide normally while the suction pressure is supplied to the internal space of the cylinder during power operation. On the other hand, during the shaving operation, the vane is retracted while the discharge pressure is supplied to the inner space of the cylinder so that the compression chamber is not formed (hereinafter, referred to as a first displacement variable method). Is configured to supply only refrigerant with suction pressure and to supply the suction pressure and the discharge pressure at the rear side of the vane so that the vane is normally sliding during power operation and a compression chamber is formed while the vane is operated during the saving operation. This retreat prevents the compression chamber from forming. (2nd capacity variable method)

However, the two methods described above are provided with a separate vane restraining device for restraining the vane since the vanes must be continuously restrained, especially in the saving operation mode.

In the first variable displacement method, as shown in FIG. 1, a magnet 4 is provided on the rear side of the vane 3 provided in the vane slot 2 of the cylinder 1, or the vane ( A back pressure switching valve 5 capable of supplying suction pressure on the rear side of 3) is provided to maintain the state in which the vane 3 is retracted. In the drawings, reference numeral 6 denotes a rolling piston, 7 denotes a mode switching valve, and 8 denotes a suction port.

In the second displacement variable method, as shown in FIG. 3, a side pressure flow path 8 is provided in the cylinder 1 so that the vane 3 is constrained by supplying discharge pressure from the side of the vane 3. to be. In the drawings, reference numeral 10 denotes a vane chamber, and 11 denotes a back pressure switching valve.

However, the conventional vane restraint apparatuses do not restrain the vanes 3 at the same time as the operation mode of the compressor is switched, and not only the performance of the compressor is lowered, but also the vibration of the vanes 3 is severely generated, resulting in compressor noise. There was a problem that is greatly weighted. For example, in the scheme shown in FIG. 1, the magnetic force of the magnet 4 cannot be made too large in order to smooth the mode switching of the compressor, so that the vane 3 does not quickly restrain the vane 3 during the saving operation. There is a limit to the noise generated by the jumping, the method shown in Fig. 2 is that the rolling is constrained simultaneously with the mode change of the compressor while the pressure on the back side of the vane 3 does not quickly change from the discharge pressure to the suction pressure during power operation. There is a limit that noise is generated due to the collision between the rolling piston 6 and the vanes 3, the method shown in Figure 3 is the side force (F2) transmitted to the vanes 3 through the side pressure passage (9) Not only is the vane 3 not sufficiently larger than the force F1 due to the pressure of the vane chamber 10, but also the back pressure of the vane 3 does not quickly change from the discharge pressure to the suction pressure, so that the vane 3Due able to be bound and which at the same time and de conversion there is a problem in that the vane (3) is the noise generated during collision and rolling piston (6). In particular, as shown in FIG. 4, under certain operating conditions of the compressor, when the compressor is switched from the power mode to the saving mode, severe noise is generated for a predetermined time t.

The present invention is to solve the problems described above, to provide a variable displacement rotary compressor that can significantly reduce the noise caused by the impact of the vanes and the rolling piston to be constrained quickly when switching the compressor mode. There is this.

In order to achieve the object of the present invention, the rolling piston in the inner space of the sealed cylinder assembly eccentric rotational movement, the vane in contact with the rolling piston is linearly radially partitioned the inner space into the compression chamber and the suction chamber The vane is provided with a variable displacement rotary compressor, characterized in that the vane is constrained by the pressure difference applied to the vane during the saving operation.

In addition, a cylinder assembly is installed in the sealed casing is formed in the inlet is formed in the inlet port is formed so that the compressed space in which the refrigerant is compressed to be in communication with the compression space and one side of the inlet port; A rolling piston for moving the refrigerant while making an eccentric rotational movement in the compression space of the cylinder assembly; A vane that is inserted into the vane slot of the cylinder assembly and has an inner end thereof in contact with the rolling piston to divide the compression space into a suction chamber and a compression chamber; And mode switching means for allowing the vanes to be in contact with or spaced apart from the rolling piston according to the operation mode of the compressor, wherein one side of the vane is provided with a suction pressure while the other side has a discharge pressure. A variable displacement rotary compressor is provided, wherein the vane is tightly confined within the vane slot.

In general, the rotary compressor may be classified into a single type or a double type according to the number of cylinders. For example, in the case of a single type, one compression chamber is formed by using the rotational force transmitted from the power mechanism unit, while in the case of the double type, a plurality of compression chambers having a phase difference of 180 ° using the rotational force transmitted from the power mechanism unit are both up and down. To be formed. Hereinafter, a plurality of compression chambers are formed above and below, and look at the center of a double displacement variable type rotary compressor in which at least one compression chamber capacity is variable.

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

Figure 5 is a longitudinal cross-sectional view showing an embodiment of the present invention variable displacement rotary compressor, Figure 6 is a cross-sectional view showing a state of release of the vane when the power is all in the variable displacement rotary compressor of the present invention, Figure 7 is a variable displacement rotary compressor of the present invention Is a cross-sectional view showing an enlarged state of the vane in the saving mode, Figure 8 is an enlarged view showing in detail the process of the vane is restrained in Figure 7, Figure 9 is a noise characteristic when switching modes in the variable displacement rotary compressor of the present invention It is shown.

As shown in FIG. 5, the multi-capacity variable type rotary compressor according to the present invention includes a casing 100 having a closed space and an electric mechanism part 200 installed at an upper side of the casing 100 to generate a constant speed rotation force or an inverter rotation force. And a first compression mechanism part 300 and a second compression mechanism part 400 installed under the casing 100 to compress the refrigerant by the rotational force generated by the power mechanism part 200, and the second compression mechanism part. 400 is configured as a mode switching means 500 for switching the operation mode to perform a power operation or a saving operation.

The casing 100 maintains the discharge pressure by the refrigerant discharged from the first compression mechanism 300 and the second compression mechanism 400, and the first compression is applied to the main surface of the lower half of the casing 100. The first gas suction pipe SP1 and the second gas suction pipe SP2 are respectively connected to the mechanism 300 and the second compression mechanism 400 so that the refrigerant is sucked in, and an upper portion of the casing 100 has a first compression mechanism ( One gas discharge pipe DP is connected to the refrigerant discharged from the 300 and the second compression mechanism 400 into the sealed space to the refrigeration system.

The electric drive unit 200 is fixed to the inside of the casing 100 is applied to the power from the outside and the stator 210 is disposed with a predetermined gap inside the stator 210 to interact with the stator 210 Rotator 220 which rotates while being coupled to the rotor 220 is coupled to the rotor 220 to transmit the rotational force to the compression mechanism.

The rotation shaft 230 has a shaft portion 231 coupled to the rotor 220, and the first eccentric portion 232 and the second eccentric portion 233 are formed eccentrically to both left and right sides at the lower end of the shaft portion 231 Is made of. The first eccentric portion 232 and the second eccentric portion 233 are formed symmetrically with a phase difference of approximately 180 ° so that the first rolling piston 340 and the second rolling piston 430, which will be described later, are rotatable, respectively. Combined.

The first compression mechanism 300 and the second compression mechanism 400 are disposed on the upper and lower sides of the casing 100, the capacity of the second compression mechanism 400 is disposed at the lower end of the casing 100 is variable It is configured to be.

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, the upper bearing) 320 and the intermediate bearing plate (hereinafter, the middle bearing) 330 for supporting the rotating shaft 230 in the radial direction and the upper side of the rotating shaft 230 The first rolling piston 340 is rotatably coupled to the core portion and compresses the refrigerant while turning in the first compression space V1 of the first cylinder 310, and press-contacts an outer circumferential surface of the first rolling piston 340. A first vane 350 coupled to the first cylinder 310 so as to be movable 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 such that the rear side of the first vane 350 is elastically supported. Discharge of the refrigerant gas discharged from the compression chamber of the first inner space (V1) is coupled to the g-spring 360 and the front end of the first discharge port 321 provided near the center of the upper bearing 320 so as to be opened and closed. 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.

As shown in FIG. 5, the first cylinder 310 has a first vane slot 311 formed at one side of an inner circumferential surface of the first compression space V1 such that the first vane 350 reciprocates in a radial direction. One side of the first vane slot 311 is formed with a first suction port (not shown) for guiding the refrigerant into the first compression space V1 in the radial direction, and the other side of the first vane slot 311 is provided. A first discharge guide groove (not shown) for discharging the refrigerant into the casing 100 is inclined in the axial direction.

The upper bearing 320 and the outer end of the first vane 350 (hereafter, mixed with the rear end) may be supported by the discharge pressure of the refrigerant filled in the sealed space of the casing 100. The diameter of either of the intermediate bearings 330 is formed smaller than the diameter of the first cylinder (310).

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. To form a second compression space (V2) together with the intermediate bearing 330 and the lower bearing 420 to support the rotary shaft 230 in the radial and axial directions, and the lower eccentric portion of the rotary shaft 230 can be rotated Coupled to the second rolling piston 430 to compress the refrigerant while turning in the second compression space V2 of the second cylinder 410 and the outer circumferential surface of the second rolling piston 430 to be pressed or spaced apart A second vane 440 coupled to the second cylinder 410 so as to be movable in a radial direction so that the second compression space V2 of the second cylinder 410 is partitioned or communicated with the second suction chamber and the second compression chamber, respectively. ) 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.

The second cylinder 410 may be formed to have the same volume as that of the compression space V1 of the first cylinder 310 or may be different from each other if necessary. For example, if the two cylinders 310 and 410 have the same volume, when the second cylinder 410 saves the compressor, the compressor works only as much as the volume of the other cylinders, so the compressor performance varies by 50%. In the case where the volumes of the cylinders 310 and 410 are formed differently, the compressor performance is varied by the ratio of the volume of the cylinder for power operation.

The second cylinder 410 is a second vane slot 411 so that the second vane 440 reciprocates in a radial direction on one side of an inner circumferential surface constituting the second compression space V2 as shown in FIGS. 5 to 7. ) Is formed, a second suction port 412 for guiding the refrigerant to the second compression space (V2) is formed at one side of the second vane slot 411, the second vane slot 411 On the other 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 radially rear side of the second vane slot 411 is connected to the common side connecting pipe 530 of the valve unit 500, which will be described later, so that the rear side of the second vane 440 has an intake pressure or a discharge pressure atmosphere. A vane chamber 413 is formed to be separated from the enclosed space of the casing 100, and is perpendicular to the movement direction of the second vane 440 or has a predetermined staggered angle of the casing 100. A high pressure passage 414 is formed to allow the second vane slot 411 to communicate with the inside of the casing 100 so that the second vane 440 is constrained by the discharge pressure of the inner space of the casing 100. The second vane slot 411 and the second suction port 412 communicate with each other so as to cause the pressure difference with the high pressure flow path 414, the low pressure flow path 415 to quickly restrain the second vane 440. ) Is formed.

The vane chamber 413 is in communication with the common side connecting pipe 530 to be described later, even if the second vane 440 is completely retracted and accommodated inside the second vane slot 411. The rear surface of the 440 is formed to have a predetermined internal volume to form a pressure surface with respect to the pressure supplied through the common side connecting pipe 530.

The high pressure passage 414 is located in the discharge guide groove (not shown) of the second cylinder 410 around the second vane 440 as shown in FIGS. It is formed through the outer circumferential surface to the center of the second vane slot 411.

The high-pressure flow path 414 is formed to be stepped narrowly to the second vane slot 411 in a two-stage using a two-stage drill, the exit end so that the linear movement of the second vane 440 can be stably made The second vane slot 411 is formed approximately in the middle of the longitudinal direction.

The second high pressure flow path 414 has a cross-sectional area that is formed to be equal to or narrower than a pressure surface applied to the rear surface of the second vane 440 through the vane chamber 413, that is, the cross-sectional area of the second vane slot 411. The vanes 440 may be prevented from being excessively restrained.

In addition, although not shown in the drawings, the high-pressure flow path 414 may be formed to be negatively formed at a predetermined depth on both sides of the second cylinder 410, and is coupled to both sides of the second cylinder 410. The bearing 420 or the intermediate bearing 330 may be formed in a negative shape or penetrates to a predetermined depth. Here, when the high pressure flow path is negatively formed on the upper surface of the lower bearing 420 or the upper bearing of the intermediate bearing 330, when the second cylinder 410 or each bearing 420, 330 is sintered together Forming can reduce production costs.

The low pressure flow path 415 causes a pressure difference between the discharge pressure and the suction pressure on both sides of the second vane 440 so that the second vane 440 is in close contact with the second vane slot 411 by the pressure difference. Preferably, it is preferably arranged on the same straight line as the high-pressure flow path 414, but in some cases, it may be formed on a parallel line or at least in an angle that can be crossed.

The low pressure passage 415 is in a position that can communicate with the vane chamber 413 through a gap between the second vane 440 and the second vane slot 411 during the saving operation of the compressor as shown in FIG. Preferably, the discharge is filled in the vane chamber 413 when the low pressure passage 415 communicates with the vane chamber 413 when the second vane 440 moves forward during the power operation of the compressor. As the pressure Pd leaks into the second suction port 412 through which the refrigerant of the suction pressure Ps flows, the low pressure flow path 415 may not support the second vane 440 sufficiently. It is preferably formed to be located within the reciprocating range of.

In addition, although not shown in the drawings, the high pressure passage 414 and the low pressure passage 415 may be formed in plural along the height direction of the second vane 440, and the high pressure passage 414 and the low pressure passage ( 415 may be formed with the same or different cross-sectional area.

The mode switching means 500 is a low pressure side connection pipe 510 branched from the second gas suction pipe SP2, a high pressure side connection pipe 520 connected to the inner space of the casing 100, and the first The common side connector 530 connected to the vane chamber 413 of the two cylinders 410 and cross-communicating with the low pressure side connector 510 and the high pressure side connector 520, and the common side connector 530. The first mode switching valve 540 connected to the vane chamber 413 of the second cylinder 410 and the first mode switching valve 540 connected to the opening / closing operation of the mode switching valve 540. It consists of a second mode switching valve 550 to control.

The low pressure side connecting pipe 510 is connected between the suction side of the second cylinder 410 and the inlet side gas suction tube or outlet side gas suction tube (second gas suction tube) SP2 of the accumulator 110.

The high-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 413, but in some cases, the gas discharge pipe DP You can also connect in the middle of). In this case, the oil is not supplied between the second vane 440 and the second vane slot 411 as the vane chamber 413 is sealed, so that a frictional loss may occur, thus supplying oil to the lower bearing 420. A hole (not shown) may be formed to supply oil when the second vane 440 reciprocates.

Effects of the present invention, such as the double displacement variable type double rotary compressor is 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. To transmit the rotational force of the first compression mechanism unit 300 and the second compression mechanism unit 400, and the first compression mechanism unit 300 and the second compression mechanism 400 together power operation according to the required capacity in the air conditioner By generating a large amount of cooling power or power operation only the first compression mechanism unit 300 and the second compression mechanism 400 performs a saving operation to generate a small capacity of the cooling force.

Here, when the compressor or the air conditioner applying the same, the power is applied to the second mode switching valve 550 as shown in Figure 6, the low pressure side connecting pipe 510 is cut off while the high pressure side The connector 520 is connected to the common side connector 530. Accordingly, the high pressure gas or the high pressure oil in the casing 100 is supplied to the vane chamber 413 of the second cylinder 410 through the high pressure side connecting pipe 520 so that the second vane 440 is vane. The refrigerant gas flowing into the second compression space S2 is normally compressed and discharged while maintaining the pressure contact with the second rolling piston 430 due to the pressure of the chamber 413.

At this time, the high pressure refrigerant gas or oil is supplied to the high pressure flow path 414 provided in the second cylinder 410 or the bearings 330 and 420 to add one side of the second vane 440. As the cross-sectional area of the high pressure passage 414 is narrower than that of the second vane slot 411, the pressing force at the side surface is smaller than the forward and backward pressure in the vane chamber 413 so as not to restrain the second vane 440. I can't.

In this way, the first vane and the second vane is pressed into each of the rolling pistons so as to partition the first compression space and the second compression space into the suction chamber and the compression chamber to compress and discharge the entire refrigerant sucked into the respective suction chambers. The air conditioner applied to this will drive 100%.

On the other hand, in the case of the saving operation such as when the compressor or the air conditioner applied thereto, the power is turned off to the second mode switching valve 550 as shown in FIG. The 510 and the common side connecting pipe 530 communicate with each other, and a portion of the low pressure refrigerant gas sucked into the second cylinder 410 flows into the vane chamber 413. Accordingly, the second vane 440 is pushed by the pressure of the second compression space S2 and received inside the second vane slot 411, so that the suction chamber and the compression chamber of the second compression space S2 communicate with each other. The refrigerant gas sucked into the compression space S2 is not compressed.

At this time, the pressure difference added to both sides of the second vane 440 is increased by the high pressure passage 414 and the low pressure passage 415 provided in the second cylinder 410 or the bearings 330 and 420. The second vane 440 is fastened and effectively restrained. For example, as shown in FIGS. 7 and 8, the high pressure oil or the refrigerant gas flows into the high pressure passage 414 and the refrigerant or the oil having the partial discharge pressure remaining in the vane chamber 413 is the second vane 440. The second vane 440 is restrained more quickly and stably when the operation mode of the compressor is switched by leaking into the second suction port 412 through the gap between the vane slot 411 and the low pressure flow path 415. In particular, when the discharge pressure Pd, which is filled in the vane chamber 413, does not fall quickly when the operation mode of the compressor is changed from the power operation to the saving operation, the second vane 440 through the high pressure passage 414. The constraining force (F2) transmitted to the narrower cross-sectional area of the high-pressure passage (414) is not much greater than the bearing force (F1) transmitted to the second vane (440) in the vane chamber 413 having a relatively large pressure area. Although the behavior of the second vane 440 may become unstable, the vane chamber when the low pressure passage 415 communicating with the second suction port 412 is formed on the opposite side of the high pressure passage 414 as in the present invention. As the discharge pressure Pd remaining at 413 becomes the intermediate pressure Pm and rapidly leaks through the low pressure passage 415, the bearing force F1 in the vane chamber 413 is rapidly lowered. To be able to restrain the second vane 440 quickly to be.

Experimental results are shown in FIG. 9. That is, in FIG. 9, as shown in FIG. 4, when the mode is switched from the power operation to the saving operation, the peak sound generated for about 2.5 seconds is not generated at all.

As the compression chamber and the suction chamber of the second cylinder communicate with each other, the entire refrigerant sucked into the suction chamber of the second cylinder is not compressed and moves back to the suction chamber along the trajectory of the rolling piston. As a result, the compressor or the air conditioner applying the same operates only as much as the capacity of the first compression mechanism.

Meanwhile, the vane restraint method according to the present invention can be applied to other variable displacement rotary compressors.

That is, in the above-described embodiment, when the refrigerant having the suction pressure Ps is always supplied to the suction port 412 regardless of the operation mode, the vane chamber 413 and the suction port 412 communicate with each other in the power saving mode. The discharge pressure Pd of the vane chamber 413 is rapidly leaked toward the suction port 412 during the switchover, but the present embodiments are connected to the suction port 412 as shown in FIGS. 10 and 11. Further comprising a refrigerant switching valve 600 in the gas suction pipe (unsigned) to selectively supply the refrigerant of the suction pressure (Ps) and the discharge pressure (Pd) to the suction port 412 according to the operation mode, saving In the mode, the refrigerant having the discharge pressure Pd flows into the compression space V2 of the cylinder 410 through the suction port 412 to restrain the second vane 440 as it is retracted.

In this case, the discharge side Pd and the suction pressure Ps may be selectively supplied to the rear side of the second vane 440 according to the operation mode of the compressor as shown in FIG. 10, or as shown in FIG. 11. The discharge pressure Pd can be configured to be always supplied.

For example, in the case of FIG. 10, a vane chamber 413 is formed at a rear side of the second vane 440 to be separated from the sealed space of the casing 100, and the vane chamber 413 is formed according to the operation mode of the compressor. Back pressure switching valve 700 that can selectively supply the suction pressure or the discharge pressure is connected. 11, the outer side of the second vane slot 411 communicates with the sealed space of the casing 100, and a vane confinement unit 800 such as a magnet or a tension spring is formed on the outer circumferential surface of the vane slot. Is installed.

Even in the above cases, the high pressure flow path 414 and the low pressure flow path 415 are respectively connected to both sides of the second vane slot 411 so that the second vane 440 is the high pressure flow path 414 in the saving mode. And the pressure difference between the low pressure passage 415 can be more effectively constrained.

However, in these cases, since the refrigerant of the discharge pressure Pd flows through the second suction port 412 in the saving mode, the high pressure passage 414 is different from the second suction port 412. While formed between the second vane slot 411, the low pressure passage 415 is formed to communicate with the low pressure side connection pipe (not shown) provided on the outer side of the casing 110 on the opposite side of the high pressure passage 414. desirable.

On the other hand, in the above-described embodiments, a double rotary compressor has been described as an example, but the same may be applied to a single rotary compressor, or may also be applied to all compression mechanisms in the double rotary compressor. Detailed configuration and operation effects thereof are similar to those of the above-described embodiment and thus will be omitted.

According to the present invention, the variable displacement rotary according to the present invention causes a pressure difference between both sides of the vane during a shaving operation so that the vane is constrained by the pressure difference, and the discharge pressure of the vane chamber leaks to the suction port through the low pressure passage. Compressor switches from power operation to saving operation by quickly and stably restraining the vane by allowing the vane chamber pressure to be rapidly lowered, thereby allowing the pressing force applied on the side of the vane to be relatively larger than the bearing force applied on the rear side. When the vane is weakly bound, the vane vibration is prevented in advance, thereby preventing noise from increasing in accordance with the installation conditions of the compressor, thereby improving comfort.

Claims (21)

The rolling piston makes an eccentric rotational movement in the inner space of the sealed cylinder assembly, and the vanes in contact with the rolling piston make linear movements in the radial direction to partition the inner space into the compression chamber and the suction chamber, and the vanes A variable displacement rotary compressor, characterized in that the vane is constrained by a pressure difference by adding suction and discharge pressures in a direction crossing the vane movement direction. The method of claim 1, The vane is variable displacement rotary compressor, characterized in that the suction and discharge pressure is added to both sides of the vane is constrained. The method of claim 1, A variable displacement rotary compressor is supplied to the vane in the direction of movement of the vane while the suction pressure and the discharge pressure are switched according to an operation mode. The method of claim 3, A variable flow type rotary compressor, characterized in that the communication flow path is formed so that the pressure in the direction crossing the back pressure of the vane can communicate. The method of claim 1, A variable displacement rotary compressor, characterized in that supplied to the inner space of the cylinder assembly while the suction pressure and discharge pressure is switched according to the operation mode. The method of claim 5, The vane is a variable displacement rotary compressor, characterized in that the discharge pressure supplied to the inner space of the cylinder assembly during the shaving operation is added in the direction crossing the vane movement direction, the suction pressure is added in the opposite direction. A cylinder assembly having a compression space through which the refrigerant is sucked and formed to be compressed, and a suction port formed to communicate with the compression space, and a vane slot formed at one side of the suction port, the cylinder assembly being installed in the sealed inner space; A rolling piston for moving the refrigerant while making an eccentric rotational movement in the compression space of the cylinder assembly; A vane that is inserted into the vane slot of the cylinder assembly and has an inner end thereof in contact with the rolling piston to divide the compression space into a suction chamber and a compression chamber; And mode switching means for allowing the vanes to contact or be spaced apart from the rolling piston according to an operation mode of the compressor. The suction pressure is added to one side of the vane, while the discharge pressure is added to the other side so that the vane is tightly constrained in the vane slot during the shaving operation. The method of claim 7, wherein The suction port is a variable displacement rotary compressor, characterized in that the gas suction pipe is connected so that the refrigerant of the suction pressure is always supplied. The method of claim 7, wherein The cylinder assembly has a high-pressure flow path is formed so that the inside of the casing and the vane slot is in communication, the low-pressure flow path is formed so that the vane slot and the suction port is in communication. The method of claim 9, The high pressure flow path and the low pressure flow path variable displacement rotary compressor, characterized in that formed in the reciprocating range of the vane. The method of claim 7, wherein The cylinder assembly is composed of a cylinder formed in an annular shape, and a plurality of bearings disposed on the upper and lower sides of the cylinder to form an inner space sealed together, The cylinder is a variable displacement rotary compressor, characterized in that the low pressure flow path is formed between the vane slot and the suction port, the high pressure flow path is formed so as to communicate the inner space of the vane slot and the casing opposite the low pressure flow path. The method of claim 7, wherein The cylinder assembly is composed of a cylinder formed in an annular shape, and a plurality of bearings disposed on the upper and lower sides of the cylinder to form an inner space sealed together, Wherein the cylinder is a low pressure flow path is formed between the vane slot and the suction port, the high-pressure flow path is formed in the bearing so as to communicate with the vane slot. The method of claim 9, The variable pressure type rotary compressor, wherein the high pressure flow passage has a cross sectional area greater than or equal to that of the low pressure flow passage. The method of claim 7, wherein The suction port is a variable displacement rotary compressor, characterized in that connected to selectively supply the refrigerant of the suction pressure or discharge pressure in accordance with the operation mode of the compressor. The method of claim 14, The cylinder assembly has a low pressure flow path in which suction pressure is added to one side of the vane, and a high pressure flow path in which the vane slot and the suction port communicate with each other to form a discharge pressure is added to the other side of the vane. Rotary compressor. The method of claim 15, The low pressure flow path and the high pressure flow path is a variable displacement rotary compressor, characterized in that formed in the reciprocating range of the vane. The method of claim 15, The cylinder assembly is composed of a cylinder formed in an annular shape, and a plurality of bearings disposed on the upper and lower sides of the cylinder to form an inner space sealed together, The cylinder has a high-pressure flow path is formed between the vane slot and the suction port, the low-pressure flow path is formed so as to communicate with the vane slot and the low pressure side connection pipe of the mode switching means opposite the high pressure flow path compressor. The method of claim 15, The cylinder assembly is composed of a cylinder formed in an annular shape, and a plurality of bearings disposed on the upper and lower sides of the cylinder to form an inner space sealed together, Wherein the cylinder is a high-pressure flow path is formed between the vane slot and the suction port, while the low pressure flow path is formed in the bearing so as to communicate with the vane slot. The method of claim 7, wherein The mode switching means is connected to the outer end of the vane slot and is separated from the enclosed space of the casing, and connected to the vane chamber to selectively intake or discharge pressure to the vane chamber according to the operation mode of the compressor. A variable displacement rotary compressor comprising a back pressure switching unit for supplying. The method of claim 7, wherein The mode switching means is connected to the suction port of the cylinder assembly and the refrigerant switching unit for selectively supplying the refrigerant of the suction pressure or discharge pressure to the compression space of the cylinder assembly in accordance with the operation mode of the compressor, and the outer end of the vane slot A vane chamber in communication with the vane chamber, the back pressure switching unit being connected to the vane chamber and selectively supplying suction or discharge pressure to the vane chamber according to the operation mode of the compressor. Variable displacement rotary compressors. The method of claim 7, wherein The mode switching means is connected to the suction port of the cylinder assembly and the refrigerant switching unit for selectively supplying the refrigerant of the suction pressure or the discharge pressure to the compression space of the cylinder assembly in accordance with the operation mode of the compressor, and communicating with the sealed space of the casing And a vane confinement unit installed at an outer end of the vane slot to constrain the vane.

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