KR20100010294A - Variable capacity type rotary compressor - Google Patents

Abstract

PURPOSE: A variable capacitance rotary compressor is provided to reduce the number of assembly processes for connected an intake pipe to the casing and the accumulator. CONSTITUTION: A variable capacitance rotary compressor comprises a plurality of cylinders(310,410), a plurality of bearings(110,130), an intake pipe(140), a rolling piston(320), a plurality of vanes(330), and a vane restraining unit. The cylinders are installed inside a casing. The intake pipe distributes a coolant to the compression spaces of the cylinders. The rolling piston compresses the coolant. The vanes divide the compression space of each cylinder into an intake space and a discharge space. The vane restraining unit changes the operating mode of the compressor by restraining or releasing the vane of at least one of the cylinders.

Description

Variable Capacity Rotary Compressor {VARIABLE CAPACITY TYPE ROTARY COMPRESSOR}

The present invention relates to a variable displacement rotary compressor capable of selecting a power operation and a saving operation.

Generally, a refrigerant compressor is applied to a vapor compression refrigeration cycle (hereinafter, referred to as a refrigeration cycle) such as a refrigerator or an air conditioner. The refrigerant compressor has been introduced is a constant-speed compressor that is driven at a constant speed or an inverter compressor of which the rotational speed is controlled.

The refrigerant compressor is a hermetic compressor, in which a drive motor which is a motor and a compression unit operated by the drive motor are installed together in an inner space of a closed casing, is called a hermetic compressor. It can be called a compressor. Most domestic or commercial refrigeration equipment is a hermetic compressor. The refrigerant compressor may be classified into a reciprocating type, a scroll type, a rotary type, and the like according to a method of compressing the refrigerant.

The rotary compressor is a method of compressing a refrigerant by using a rolling piston that makes an eccentric rotation in a compression space of a cylinder and a vane that contacts the rolling piston and divides the compression space of the cylinder into a suction chamber and a discharge chamber. Recently, a variable displacement rotary compressor that can vary the refrigeration capacity of the compressor according to the load change has been introduced. As a technique for varying the refrigeration capacity of the compressor, a technique of applying an inverter motor and a technique of varying the volume of the compression chamber by bypassing a part of the refrigerant to be compressed to the outside of the cylinder are known. However, when the inverter motor is applied, the price of the driver for driving the inverter motor is about 10 times higher than that of the constant speed motor, which increases the production cost of the compressor. This complexity has the disadvantage that the efficiency of the compressor is lowered as the flow resistance of the refrigerant is increased.

In view of this, a so-called independent suction displacement variable rotary compressor (hereinafter, abbreviated as an independent suction rotary compressor) has been introduced, which includes a plurality of cylinders and at least one of the plurality of cylinders is capable of idling. In this case, the plurality of cylinders are configured so that the suction pipes are independently provided so that both cylinders can be operated independently.

However, in the case of the independent suction rotary compressor as described above, since the suction pipes must be independently connected to both cylinders, there is a problem in that the manufacturing cost increases as the assembly labor increases significantly.

In addition, as both cylinders are connected by both suction pipes, there is a problem in that a high-temperature refrigerant flows backward in the idle cylinder, thereby degrading compressor performance.

In addition, when a plurality of suction pipes are connected, the welding process is not secured in close proximity to other members, and thus, the assembly process cannot be automated, thereby increasing the manufacturing cost.

The present invention solves the problems of the conventional variable displacement rotary compressor as described above, by using a single suction pipe in a double rotary compressor having a plurality of cylinders in common to reduce the number of parts and assembly labor and to automate the assembly process It is an object of the present invention to provide a variable capacity rotary compressor that can improve the performance of the compressor by effectively varying the capacity of the compressor efficiently while reducing the manufacturing cost significantly.

In order to solve the object of the present invention, a plurality of cylinders installed in the inner space of the casing; A plurality of bearings covering the opening side of the cylinders to separate compression spaces of the cylinders from each other; A suction pipe configured to distribute and supply refrigerant to the compression spaces of the plurality of cylinders; At least one rolling piston for compressing the refrigerant while pivoting in the compression space of the cylinders; A plurality of vanes for separating the compression spaces of the cylinders together with the rolling pistons into suction and discharge spaces, respectively; And a vane confinement unit configured to change an operation mode of the compressor by restraining or releasing the vane of at least one cylinder among the vanes, wherein at least one of the cylinders includes the vane having a suction pressure or a discharge pressure. A chamber for supporting the refrigerant is formed, and an intermediate flow path interposed between the two cylinders among the bearings to separate the compression space of the two cylinders has a guide passage for guiding the refrigerant of the suction pressure or the discharge pressure to the chamber. It is formed, the guide flow path is provided with a variable displacement rotary compressor characterized in that the coupling pipe for guiding the refrigerant of the suction pressure or discharge pressure into the guide flow path is coupled.

In the variable displacement rotary compressor according to the present invention, the refrigerant sucked into one suction pipe is alternately sucked into each compression space through a communication flow path between the plurality of cylinders, so as to independently couple the suction pipes to the respective cylinders. Not only the number of parts can be reduced, but also the assembly cost for connecting the suction pipe to the casing and the accumulator can be reduced, thereby greatly reducing the production cost.

In addition, as the plurality of cylinders directly communicate with each other and one suction tube is connected therebetween, the refrigerant in the idle cylinder may be prevented from flowing back to the other cylinder, thereby improving the performance of the compressor.

In addition, when only one suction pipe is connected, a welding space necessary for the operation of the welding robot can be secured when connecting the suction pipe as well as other connection pipes (particularly, the common side connection pipe) constituting the mode switching unit. This can greatly reduce the manufacturing cost.

In addition, when the common side connecting pipe is connected to the chamber, the common side connecting pipe is not press-fitted into the cylinder to prevent deformation of the cylinder in advance, thereby preventing refrigerant leakage from the cylinder in which the chamber is formed. Can increase the performance.

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.

As shown in FIG. 1, the variable displacement rotary compressor 1 according to the present invention comprises the evaporator 4 to form part of a closed loop refrigeration cycle leading to the condenser 2, the expansion valve 3, and the evaporator 4. The suction side is connected to the outlet side of the outlet and the discharge side is connected to the inlet side of the condenser 2. The accumulator 5 is connected between the outlet side of the evaporator 4 and the inlet side of the compressor 1 to separate the gas refrigerant and the liquid refrigerant from the refrigerant transferred from the evaporator 4 to the compressor 1. do.

As shown in FIG. 2, the compressor 1 is provided with a transmission unit 200 generating a driving force in an upper side of the inner space of the closed casing 100, and the transmission unit 200 below the inner space of the casing 100. The first compression unit 300 and the second compression unit 400 for compressing the refrigerant by the power generated in the) is installed.

In addition, a mode switching unit 500 is installed outside the casing 100 to switch the operation mode of the compressor such that the first compression unit 300 idles if necessary.

The casing 100 maintains a state of the discharge pressure by the refrigerant discharged from the first compression unit 300 and the second compression unit 400 or the first compression unit 300, the inner space of the casing 100, One gas suction pipe 140 is connected to the lower main surface of the lower portion 100 so that the refrigerant is sucked between the first compression unit 300 and the second compression unit 400, and the first compression unit is connected to the upper end of the casing 100. One gas discharge pipe 150 is connected to deliver the refrigerant compressed and discharged by the unit 300 and the second compression unit 400 to the refrigeration system.

The gas suction pipe 140 is inserted into the intermediate connecting pipe (not shown) inserted into the second suction port 412 of the second cylinder 410 to be described later is welded.

The transmission unit 200 is a stator 210 fixed to the inner circumferential surface of the casing 100, a rotor 220 rotatably disposed inside the stator 210, and the rotor 220 Shrink is made of a rotating shaft 230 to rotate together. The electric motor 200 may be a constant speed motor or an inverter motor. However, in consideration of the cost, the electric motor 200 may vary the operation mode of the compressor by idling one of the first compression part 300 and the second compression part 400 while using a constant speed motor if necessary. Can be.

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

The first compression unit 300 is formed in an annular shape and rotatably coupled to the first cylinder 310 installed inside the casing 100 and the first eccentric portion 232 of the rotation shaft 230. A first rolling piston 320 that rotates in the first compression space V1 of the first cylinder 310 and compresses the refrigerant, and is coupled to the first cylinder 310 so as to be movable in a radial direction. A first vane 330 having a sealing surface contacting the outer circumferential surface of the first rolling piston 320 and partitioning the first compression space V1 of the first cylinder 310 into a first suction chamber and a first discharge chamber, respectively. Include. Reference numeral 340 denotes a first discharge valve, and 350 denotes a first muffler.

The second compression unit 400 is formed in an annular shape, the second cylinder 410 installed below the first cylinder 310 in the casing 100 and the second eccentric portion of the rotary shaft 230 ( A second rolling piston 420 rotatably coupled to 233 and compressing the refrigerant while turning in the second compression space V2 of the second cylinder 410, and radially to the second cylinder 410. The second compression space V2 of the second cylinder 410 is partitioned into a second suction chamber and a second discharge chamber, respectively, to be movable and coupled to the outer circumferential surface of the second rolling piston 420. A second vane 430 spaced apart from an outer circumferential surface of the piston 420 so that the second suction chamber and the second discharge chamber communicate with each other, and a vane made of a compression spring to elastically support the rear side of the second vane 430. A spring 440. Reference numeral 450 denotes a second discharge valve, and 460 denotes a second muffler.

Here, an upper bearing plate (hereinafter referred to as an upper bearing) 110 is covered on the upper side of the first cylinder 310, and a lower bearing plate (hereinafter referred to as a lower bearing) 120 is provided below the second cylinder 410. Is covered, and an intermediate bearing plate (hereinafter, intermediate bearing) 130 is interposed between the lower side of the first cylinder 310 and the upper side of the second cylinder 410 together with the first compression space V1 and the second. The rotation shaft 230 is supported in the axial direction while forming the compression space V2.

As shown in FIGS. 3 and 4, the upper bearing 110 and the lower bearing 120 are formed in a disc shape, and each of the footballs is supported such that the shaft portion 231 of the rotary shaft 230 is radially supported at the center thereof. The bearing parts 112 and 122 having the yokes 111 and 121 protrude.

The intermediate bearing 130 is formed in an annular shape having an inner diameter such that the eccentric portion of the rotating shaft 230 penetrates, and at one side thereof, the gas suction pipe 140 has a first suction port 312 and a second suction port. A communication flow passage 131 is formed to communicate with the 412, and one side of the communication flow passage is connected to the common side connecting pipe 530 to be described later, and is also in communication with the vane chamber 313 to be connected to the common side connecting pipe 530. A guide passage 132 is formed to guide the refrigerant of the suction pressure or the discharge pressure to the vane chamber 313 through the vane chamber 313.

The guide passage 132 is a radial guide passage (hereinafter referred to as a first guide passage) 136 is formed to a predetermined depth in the transverse direction as shown in Figs. 2 and 4 and the vane in the first guide passage 136 It consists of an axial guide flow path (hereinafter referred to as a second guide flow path) 137 penetrating to the bottom toward the chamber 313. The inlet end of the first guide passage 136 is connected to the intermediate connecting pipe (unsigned) for coupling the common side connecting pipe 530 is press-fitted. The intermediate connector may be formed of the same material as the common connector 530 in consideration of being welded to the common connector 530.

On the other hand, the guide passage 132 may be formed to be inclined from the outer peripheral surface to the bottom. In this case, the processing is relatively difficult, but when the refrigerant of the suction pressure or the discharge pressure is introduced into the vane chamber 313, the flow resistance is relatively small, so that the refrigerant can be smoothly introduced.

In the first cylinder 310, a first vane slot 311 is formed on one side of an inner circumferential surface of the first compression space V1 such that the first vane 330 linearly reciprocates, and the first vane slot is formed. A first suction port 312 is formed at one side of the 311 to guide the refrigerant into the first compression space V1, and the other side of the first vane slot 311 has a refrigerant inside the second muffler 360. A first discharge guide groove (not shown) for discharging into the space is formed to be inclined by chamfering at the corner opposite to the first suction port 312.

The second cylinder 410 has a second vane slot 411 is formed on one side of the inner peripheral surface constituting the second compression space (V2) so that the second vane 430 linearly reciprocates, the second vane slot A second suction port 412 is formed at one side of the 411 to guide the refrigerant into the second compression space V2, and at the other side of the second vane slot 411, the refrigerant is inside the second muffler 450. A second discharge guide groove (not shown) for discharging into the space is formed to be inclined by chamfering at the corner opposite to the second suction port 412.

The first suction port 312 is inclined by chamfering toward the inner circumferential surface of the first cylinder 310 from the bottom edge of the first cylinder 310 in contact with the upper end of the vertical path 133 of the intermediate bearing 130. Is formed.

The second suction port 412 is formed in a radial direction so as to communicate with the lower end of the communication passage 131 of the intermediate bearing 130.

Here, as shown in FIG. 5, the first suction port 312 is formed such that the radial center line L1 intersects the axial center O of the first cylinder 310 having the first suction port 312 in planar projection. do.

As shown in FIG. 3, the first vane slot 311 is formed by cutting the first vane 330 by a predetermined depth in a radial direction to reciprocate in a straight line, and the first vane slot 311. In the rear side, that is, the outer end side of the vane chamber 313 is formed to communicate with the common side connecting pipe 530 to be described later, as shown in Figs. The vane chamber 313 is hermetically coupled to be separated from the inner space of the casing 100 by the upper bearing 110 and the intermediate bearing 130 in contact with the upper and lower surfaces thereof.

And the vane chamber 313 is the front side is in communication with the vane chamber 313 while the rear side is the intermediate connection tube (not shown) to be welded and connected to the common side connection pipe 530 is press-fitted Can be. In addition, the vane chamber 313 has a rear side of the first vane 330 even when the first vane 330 is completely retracted to be stored inside the first vane slot 311. It is formed to have a predetermined internal volume to form a pressing surface with respect to the refrigerant supplied through.

The second vane slot 411 is formed by cutting the second vane 430 by a predetermined depth in a radial direction so that the second vane 430 reciprocates in a straight line, and is the rear side of the second vane slot 411, that is, the outer side. At the end side, a through hole 413 penetrated in the axial direction is formed to communicate with the inner space of the casing 100. The vane spring 440 is installed in the through hole 413 of the second cylinder 410.

Here, as shown in FIG. 6, the first vane 330 has the pressing surface 332 in contact with or spaced apart from the first rolling piston 320 according to the operation mode of the compressor. Since the vane chamber 313 is supported by the refrigerant of the suction pressure or the refrigerant of the discharge pressure, the first vane 330 is inside the first vane slot 311 in a certain operating mode of the compressor, that is, a saving mode. In order to prevent the compressor noise or the efficiency decrease due to the shaking of the first vane 330, it may be prevented. To this end, a method of restraining the first vane using the internal pressure of the casing as shown in FIG. 7 may be proposed.

For example, the first cylinder 310 has a high-pressure side vane constraining passage (hereinafter referred to as a 'first constraining passage') 314 perpendicular to the direction of movement of the first vane 330 or at least having a stagger angle. ) Is formed. The first restriction passage 314 allows the interior of the casing 100 to communicate with the first vane slot 311 so that the refrigerant having a discharge pressure filled in the inner space of the casing 100 is the first vane 330. To the opposite vane slot face to restrain. In addition, a low pressure side vane restriction flow passage (hereinafter referred to as a “second restraint flow passage”) in which the first vane slot 311 and the first suction port 312 communicate with each other is opposite to the first restriction flow passage 314 ( 315 may be formed. The second restraint flow path 315 causes a pressure difference with the first restraint flow path 314, so that the refrigerant having a discharge pressure flowing through the first restraint flow path 314 exits to the second restraint flow path 315. The first vane 330 may be quickly restrained while going.

The first restriction passage 314 is located at the discharge guide groove (unsigned) of the first cylinder 310 with respect to the first vane 330 to form a first vane slot on an outer circumferential surface of the first cylinder 310. It may be formed through the center of the 311. In addition, the first restraint flow passage 314 is narrowly formed in two stages in the first vane slot 311 using a two-stage drill, so that the linear movement of the first vane 330 can be stably performed. The outlet end may be formed approximately in the middle of the first vane slot 311 in the longitudinal direction. In addition, the first restriction passage 314 is formed at a position in communication with the vane chamber 313 through a gap between the first vane 330 and the first vane slot 311 during the power operation of the compressor. The refrigerant of the discharge pressure flowing through the first constraining passage 314 may flow into the vane chamber 313 to increase the rear pressure of the first vane 330, but during the saving operation of the compressor, When the first vane 330 is constrained and the first constraining flow passage 314 communicates with the vane chamber 313, the pressure of the vane chamber 313 is increased to push the first vane 330 to the first vane 330. Since the shaking of the 330 may occur, the first restriction passage 314 may be formed to be located within the reciprocating range of the first vane 330.

In addition, the first restriction passage 314 may have a cross-sectional area that is equal to or narrower than that of the pressing surface 332 of the first vane 330 through the vane chamber 313. Excessive restraint can be prevented. For example, the cross-sectional area of the first restraint flow passage 314 is the cross-sectional area of the first restraint flow passage as the vane area of the first vane 330, that is, the vane area of the side where the first vane 330 receives the restraint pressure. It may be desirable to form a specific range when dividing to minimize the mode switching noise.

In addition, although not shown in the drawings, the first restriction passage 314 may be formed to be negatively formed at a predetermined depth on the upper and lower sides of the first cylinder 310, and coupled to the upper and lower sides of the third cylinder 310. The upper bearing 110 or the intermediate bearing 130 may be formed in a negative shape or penetrates to a predetermined depth. Here, when the second restriction passage 315 is formed to be negative on the lower surface of the upper bearing 110 or the upper surface of the intermediate bearing 130, the first cylinder 310 or each bearing 110, 130 Forming together when sintering can reduce production costs.

The second constrained flow path 315 causes a pressure difference between the discharge pressure and the suction pressure on both side surfaces perpendicular to the moving direction of the first vane 330. Preferably, the first suction port 312 is inclined with respect to the axial direction. It may be inclined or bent to communicate with 312.

The third restriction passage 315 is formed at a position that can communicate with the vane chamber 313 through a gap between the first vane 330 and the first vane slot 311 during the saving operation of the compressor. Preferably, the discharge is filled in the vane chamber 313 when the second constrained passage 315 communicates with the vane chamber 313 when the first vane 330 moves forward during the power operation of the compressor. Since the refrigerant of the pressure Pd leaks to the first suction port 312 and may not sufficiently support the first vane 330, the second restriction passage 315 is located within the reciprocating range of the first vane 330. It may be desirable to be formed to.

Meanwhile, as shown in FIGS. 1 and 2, the mode switching unit 500 has one end connected to the low pressure side connecting pipe 510 branched from the gas suction pipe 140, and one end thereof to the inner space of the casing 100. One end thereof is connected to the high pressure side connecting pipe 520 and the vane chamber 313 of the first cylinder 310 to selectively connect the low pressure side connecting pipe 510 and the high pressure side connecting pipe 520. The common mode connecting pipe 530 communicates with, the first mode switching valve 540 connected to the vane chamber 313 of the first cylinder 310 through the common connecting pipe 530, and the first mode A second mode switching valve 550 is connected to the switching valve 540 to control the opening and closing operation of the first mode switching valve 540.

The other end of the low pressure side connecting pipe 510 is connected to the first inlet of the first mode switching valve 540, and the other end of the high pressure side connecting pipe 520 is the first mode switching valve 540. It is connected to the second inlet of, the common side connecting pipe 530 is the other end is connected to the outlet of the first mode switching valve 540. And both ends of the low pressure side connection pipe 510 is welded to the gas suction pipe 140 and the first mode switching valve 540, respectively, and both ends of the high pressure side connection pipe 520, respectively, more precisely, Intermediate pipe (100) and the first mode switch valve 540 is welded to the inner space of the casing is coupled, the both ends of the common-side connection pipe 530, respectively, the upper bearing (more precisely, Intermediate connecting pipe sealingly coupled to the upper bearing) 110 and the first mode switching valve 540 is welded. Here, as shown in FIGS. 8 and 9, at the first point A at which the gas suction pipe 140 is connected to the casing 100, a second point at which the common side connecting pipe 530 is connected to the casing 100. The distance L1 to (B) is not longer than the distance L2 from the point A to the third point C at which the high-pressure side connecting pipe 520 is connected to the casing, more preferably shorter. The first suction port 312 may be disposed at a position close to the first vane slot 311 even though the first suction port 312 is radially formed, thereby increasing the volume of the compression space.

In addition, the points, that is, the first point A, the second point B, and the third point C, are not overlapped with each other in planar space, that is, each point A, B, C is The gas suction pipe 140 and the respective connecting pipes 520 and 530 are arranged to have different longitudinal distances ΔH1 and ΔH2 and different lateral distances ΔS1 and ΔS2. When the spot welding robot has a gap to weld, it is possible to automate the above welding operation. In particular, the first point (A) and the second point (B) can be located in close proximity for this purpose, it is most important whether the gap between the two points (A) (B).

The high pressure side connecting pipe 520 may communicate with the lower half of the casing 100, that is, the lower side of the second compression unit 400. In this case, the oil of the casing 100 may be in the vane chamber 313. ) Is excessively introduced into the compressor to delay the pressure change of the vane chamber 313 to change the mode of the compressor, thereby increasing the noise of the vane, and the viscosity index between the first vane slot 311 and the first vane 330. By increasing the vane can inhibit the smooth operation. Therefore, the high-pressure side connecting pipe 520 is a height that is not submerged in oil so that the refrigerant of the discharge pressure filled in the inner space of the casing 100 can flow into the first mode switching valve 540, that is, in FIG. As described above, it may be preferable to communicate between the lower end of the transmission part 200 and the upper end of the first compression part 300. In this case, since a predetermined amount of oil must be supplied to the vane chamber 313 to lubricate between the first vane slot 311 and the first vane 330, a fine oil supply hole may be formed in the upper bearing 110. Not shown) may be provided so that the oil is supplied when the first vane 330 reciprocates.

The basic compression process of the variable displacement rotary compressor according to the present invention as described above is as follows.

That is, when the rotor 220 rotates by applying power to the stator 210 of the transmission unit 200, the rotation shaft 230 rotates together with the rotor 220 while the transmission unit 200 is rotated. The rotational force of the first compression unit 300 and the second compression unit 400, the first compression unit 300 and the second compression unit 400, respectively, the first rolling piston 320 and the first 2, the rolling piston 420 makes an eccentric rotational motion in each of the first and second compression spaces V1 and V2, and the first and second vanes 330 and 430 are respectively The refrigerant is compressed while forming compression spaces V1 and V2 having a phase difference of 180 ° together with the second rolling pistons 320 and 420.

For example, when the first compression space V1 starts the suction stroke, the refrigerant flows into the second suction port 412 of the second cylinder 410 through the accumulator 5 and the suction pipe 140, and this refrigerant Is sucked into the second compression space V2 through the second suction port 412 of the second cylinder 410 and is compressed.

The first compression space V1 of the first cylinder 310 having a phase difference of 180 ° with the second compression space V2 is the suction stroke while the second compression space V2 is in the compression stroke process. Will start. At this time, the first suction port 312 of the first cylinder 310 is in communication with the second suction port 412 of the second cylinder 410 by the communication passage 131 of the intermediate bearing 130, the refrigerant It is sucked into the first compression space (V1) and compressed.

On the other hand, in the variable capacity rotary compressor according to the present invention the process of varying the capacity is as follows.

That is, when the compressor or the air conditioner applying the same, the power is applied, the power is applied to the first mode switching valve 540 as shown in Figure 10 and 11 while the low pressure side connection pipe 510 is cut off The high pressure side connector 520 is connected to the common side connector (530). Accordingly, the high-pressure gas inside the casing 100 is supplied to the vane chamber 313 of the first cylinder 310 through the guide channel 132 of the common connector pipe 530 and the intermediate bearing 130. The first vane 330 is pushed by the high-pressure refrigerant filled in the vane chamber 313 to maintain the pressure contact with the first rolling piston 320 while the refrigerant gas flowing into the first compression space (V1) Normally compressed and discharged.

At this time, the high pressure refrigerant gas or oil is supplied to the first restraint passage 314 provided in the first cylinder 310 to add one side of the first vane 330, but the first restraint passage ( As the cross-sectional area of the 314 is narrower than the cross-sectional area of the first vane slot 311, the pressing force at the side surface is smaller than the front-backward pressing force in the vane chamber 313 to prevent the first vane 330 from being constrained. . Accordingly, the first vane 330 is press-contacted to the first rolling piston 320 to compress the entire refrigerant sucked into the first compression space V1 while partitioning the first compression space V1 into the suction chamber and the discharge chamber. Discharged. As a result, the compressor or the air conditioner using the same is 100% operated.

On the other hand, in the case of performing a saving operation such as when the compressor or the air conditioner to which the air is applied, the power is turned off to the first mode switching valve 540 as shown in FIGS. The low pressure side connector 510 and the common side connector 530 communicate with each other, and a portion of the low pressure refrigerant gas sucked into the first cylinder 310 is connected to the common side connector 530 and the intermediate bearing 130. The vane chamber 313 flows through the guide passage 132. Accordingly, the first vane 330 is pushed by the refrigerant compressed in the first compression space V1 and received inside the first vane slot 311, so that the suction chamber and the discharge chamber of the first compression space V1 communicate with each other. The refrigerant gas sucked into the first compression space V1 may not be compressed.

At this time, the pressure is added to one side of the first vane 330 by the first restraint flow passage 314 provided in the first cylinder 310 and the first vane by the second restraint flow passage 315. As a large pressure difference is generated between the pressures added to the other side of 330, the first constraint passage 314 and the first constraint passage 314 tend to move toward the second constraint passage 315. The first vane 330 can be quickly and surely restrained without shaking. In addition, when the pressure of the vane chamber 313 is switched from the discharge pressure to the suction pressure, the discharge pressure remains in the vane chamber 313 to form a kind of intermediate pressure Pm, but the vane chamber 313 The pressure of the vane chamber 313 is rapidly converted to the suction pressure Ps as the intermediate pressure Pm of the gas leaks through the second restraint flow passage 315 having a lower pressure than that of the first vane 330. It is possible to prevent the shaking phenomenon more quickly and thereby the first vane 330 is quickly and effectively restrained. Therefore, as the first compression space V1 of the first cylinder 310 communicates with one space, the entire refrigerant sucked into the first compression space V1 of the first cylinder 310 is not compressed, The first rolling piston 320 moves along the trajectory of the first rolling piston 320, and a part of the refrigerant moves to the second compression space V2 through the communication passage 131 and the second suction port 412 by the pressure difference. As a result, the first compression unit 300 does not work. As a result, the compressor or the air conditioner using the same is operated only by the capacity of the second compression unit. In this process, as the refrigerant of the first compression space V1 moves to the second compression space V2 without flowing back to the accumulator 5, the suction loss may be reduced by preventing overheating of the accumulator 5.

In this way, by allowing the refrigerant sucked into one suction tube to be alternately sucked into each compression space through the communication flow path between the plurality of cylinders, it is possible to reduce the number of parts compared to independently coupling the suction tube to each cylinder In addition, since the assembly labor for connecting the suction pipe to the casing and the accumulator can be reduced, the production cost can be greatly reduced.

In addition, as the plurality of cylinders directly communicate with each other and one suction tube is connected therebetween, the refrigerant in the idle cylinder may be prevented from flowing back to the other cylinder, thereby improving the performance of the compressor. For example, when the first cylinder and the second cylinder are connected to each other through an accumulator, the second compression space of the second cylinder, which idles during the saving operation of the compressor, is communicated with the accumulator, so that a certain amount of pressure is fixed in the second compression space. The compressed refrigerant flows back to the accumulator and is sucked into the first compression space of the first cylinder. As a result, the temperature of the accumulator is increased to increase the specific volume of the refrigerant, thereby reducing the amount of refrigerant sucked into the first compression space, thereby degrading compressor performance. However, when the first suction port and the second suction port are directly connected through the communication flow path of the intermediate bearing, as in the present invention, almost no refrigerant flows into the second compression space during the saving operation of the compressor. As most refrigerant is sucked into only the relatively low pressure first compression space, the performance of the compressor may be improved by preventing the specific volume of the refrigerant sucked into the first compression space from rising. As a result of measuring the internal temperature of the accumulator during the actual saving operation, when the two cylinders are connected to each other through the accumulator, the internal temperature of the accumulator is detected to be about 50 ℃, whereas when both cylinders are connected without the accumulator, The internal temperature was found to maintain approximately 35 ° C. This is because the refrigerant flows back to the accumulator through the suction pipe connected to the cylinder which idles during the saving operation as both cylinders are connected to each suction pipe and the plurality of suction pipes are connected through one accumulator. It can be judged that. On the other hand, when the two cylinders are connected by one suction pipe and both cylinders are directly connected, the refrigerant flows back to the cylinder where the refrigerant is continuously sucked only to the cylinder which maintains a relatively low pressure state between the two cylinders. It can be judged that the phenomenon that is rarely occurs. Accordingly, it can be seen that the performance of the overall compressor is improved.

In addition, when only one suction pipe is connected, a welding space necessary for the operation of the welding robot can be secured when connecting the suction pipe as well as other connection pipes (particularly, the common side connection pipe) constituting the mode switching unit. This can greatly reduce the manufacturing cost. As mentioned above, when there are a plurality of suction pipes, any one of the suction pipes of the spot welding robot is generally welded using 3 to 4 torches as the common side connection pipes are arranged in close proximity. It is impossible to automate the welding operation without securing the welding space. Accordingly, since the worker has to weld each suction pipe and the connection pipe by hand, the working speed may be slowed down and the manufacturing cost may be excessively increased. In this case, when only one suction tube is applied as in the present invention, the welding space for the suction tube and the connection tubes can be automated while the welding space of the spot welding robot is secured. This simplifies and speeds up the assembly process of assembling the mode switching unit when manufacturing a variable displacement rotary compressor, thereby greatly reducing the manufacturing cost.

In addition, when the common side connection pipe is connected to the chamber, the common side connection pipe may not be press-fitted into the cylinder to prevent deformation of the cylinder in advance, thereby preventing refrigerant leakage from the cylinder in which the vane chamber is formed. The performance of the compressor can be improved. That is, when connecting the common side connection pipe to the vane chamber, the connection portion of the common side connection pipe should be tightly sealed so that the refrigerant does not leak. To this end, rather than directly connecting the common connector to the vane chamber, a separate intermediate connector is press-fitted into the vane chamber and connected, and the common connector is welded to the intermediate connector. However, when hitting the intermediate tube in order to press the intermediate tube into the vane chamber, the cylinder with the vane chamber may be deformed by the impact, thereby changing the roundness of the cylinder and the rolling piston Friction loss may occur or refrigerant leakage may increase due to vane jumping. The present invention reduces the friction loss between the rolling piston and the cylinder and in particular the vane behavior by press-fitting the intermediate tube into the cylinder, i.e., the upper bearing having the guide flow path to be connected to the vane chamber without directly pressing it into the vane chamber. It can stabilize and prevent leakage of refrigerant. In addition, in the case of the upper bearing, the radial width is wider than that of the cylinder, so that the degree of deformation may be relatively low.

Meanwhile, in the above-described embodiment, the vane chamber is formed outside the first vane slot and configured to restrain or release the first vane. In some cases, the vane chamber is outside the second vane slot. It may be formed on the side and the outer side of the first vane slot may be configured to communicate with the inner space of the casing. In this case, the second vane is pressed or spaced apart from the second rolling piston according to the pressure difference applied to the pressing surface, so that the second compression unit normally compresses or idles the refrigerant. However, even in this case, only one gas suction pipe is provided, and the common side connection pipe and the gas suction pipe have regular intervals in the transverse direction and the longitudinal direction, respectively, and the effect thereof is similar to that of the above-described embodiment. . Therefore, the detailed description thereof is replaced by the description in the above-described embodiment.

In addition, in the above embodiments, the suction pipe is configured to be connected to the intermediate bearing, but in some cases, the suction pipe may be connected to the first cylinder or the second cylinder. Also in this case, a communication hole may be formed in the intermediate bearing in the axial direction, and the first suction port and the second suction port may be formed to be inclined in the first cylinder and the second cylinder, respectively. Operational effects thereof are also similar to those of the above-described embodiment, and thus a detailed description thereof will be omitted.

The variable displacement rotary compressor according to the present invention can be evenly applied to a refrigerating device such as a home or industrial air conditioner.

1 is a schematic diagram showing a refrigeration cycle including a variable displacement rotary compressor of the present invention;

Figure 2 is a longitudinal cross-sectional view showing the interior of the rotary compressor according to Figure 1 longitudinally around the vane,

3 is a longitudinal sectional view showing the inside of the rotary compressor according to FIG.

4 is a perspective view of the compression part of the rotary compressor shown in FIG.

Figure 5 is a cross-sectional view shown for explaining the proper position of the suction port in the rotary compressor according to FIG.

6 is a cross-sectional view shown for explaining the second vane in the rotary compressor according to FIG.

FIG. 7 is a cross-sectional view illustrating a constraining flow path for restraining the second vane in the rotary compressor of FIG. 1.

8 is an enlarged perspective view illustrating the positions of the suction pipes and the respective connection pipes in the rotary compressor according to FIG. 1;

9 is a plan view shown to explain the welding position of the suction pipe and each connection pipe in the rotary compressor according to FIG.

10 and 11 are a longitudinal cross-sectional view and a cross-sectional view showing a power operation mode of the rotary compressor according to FIG.

12 and 13 are a longitudinal cross-sectional view and a cross-sectional view showing a saving operation mode of the rotary compressor according to FIG.

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

100: casing 110: upper bearing

130: intermediate bearing 131: communication euro

132: guide flow path 136: first guide flow path

137: second guide flow path 140: gas suction pipe

310: first cylinder 312: first suction port

313: vane chamber 314,315: first and second restraint euros

320: first rolling piston 330: first vane

410: second cylinder 412: second suction port

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

530: common side connecting pipe 540, 550: mode switching valve

Claims (11)

A plurality of cylinders installed in the inner space of the casing; A plurality of bearings covering the opening side of the cylinders to separate compression spaces of the cylinders from each other; A suction pipe configured to distribute and supply refrigerant to the compression spaces of the plurality of cylinders; At least one rolling piston for compressing the refrigerant while pivoting in the compression space of the cylinders; A plurality of vanes for separating the compression spaces of the cylinders together with the rolling pistons into suction and discharge spaces, respectively; And And a vane confinement unit configured to change an operation mode of the compressor by restraining or releasing vanes of at least one of the vanes. At least one of the cylinders is formed with a chamber for supporting the vane with a refrigerant of suction pressure or discharge pressure, an intermediate bearing interposed between the two cylinders of the bearings to separate the compression space of the cylinders on both sides In the chamber is formed a guide passage for guiding the refrigerant of the suction pressure or discharge pressure, the guide flow path is variable capacity type, characterized in that the coupling pipe for guiding the refrigerant of the suction pressure or discharge pressure into the guide passage Rotary compressor. The method of claim 1, And a mode switching unit configured to selectively supply a suction pressure or a discharge pressure refrigerant to the pressurized surface of the vane outside the casing. The method of claim 2, The mode switching unit includes a mode switching valve for selecting a refrigerant of suction pressure or discharge pressure on the pressure surface of the vane, a low pressure side connecting pipe connecting the first inlet and the suction pipe of the mode switching valve, and the mode switching valve. The variable pressure type rotary compressor comprising: a high-pressure side connecting pipe connecting the second inlet of the casing and the inner space of the casing; and a common-side connecting pipe connecting the outlet of the mode switching valve and the pressing surface of the vane. The method of claim 3, The intake port of the cylinder in which the chamber is formed among the plurality of cylinders is a variable displacement rotary compressor is formed so that the radial center line crosses the axial center of the cylinder having the inlet in planar projection. The method of claim 3, The distance L1 from the point A at which the suction pipe is connected to the casing to the point B at which the common side connecting pipe is connected to the casing is the point at which the discharge side connecting pipe is connected to the casing at the point A. A variable displacement rotary compressor disposed no longer than the distance L2 to (C). The method of claim 3, And a point (A) at which the suction pipe is connected to the casing and a point (B) at which the common side connecting pipe is connected to the casing are disposed at different heights. The method of claim 3, The variable suction type rotary compressor is welded to the casing and the high-pressure side connection pipe and common side pipe. The method of claim 1, At least one of the vanes is variable displacement rotary compressor is constrained by the pressure of the inner space of the casing. The method of claim 8, At least one of the cylinders has a vane slot is formed to allow the vanes to move in a radial direction, the vane slot is formed so as to communicate with the inner space of the casing to communicate with the first restriction hole for restraining the vane Capacity variable rotary compressor. The method of claim 9, And the second confinement hole is formed in the cylinder so as to communicate with the intake port on the opposite side of the first confinement hole about its vane slot. The method according to any one of claims 1 to 10, The intermediate flow pipe is press-fitted into the guide flow path, the variable capacity type rotary compressor is connected to the connection pipe.

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