WO2008023962A1 - Compresseur rotatif du type à capacité variable - Google Patents

Compresseur rotatif du type à capacité variable Download PDF

Info

Publication number
WO2008023962A1
WO2008023962A1 PCT/KR2007/004090 KR2007004090W WO2008023962A1 WO 2008023962 A1 WO2008023962 A1 WO 2008023962A1 KR 2007004090 W KR2007004090 W KR 2007004090W WO 2008023962 A1 WO2008023962 A1 WO 2008023962A1
Authority
WO
WIPO (PCT)
Prior art keywords
connection pipe
vane
casing
rotary compressor
pressure side
Prior art date
Application number
PCT/KR2007/004090
Other languages
English (en)
Inventor
Seoung-Yeon Cho
Sang-Myung Byun
Jeong-Min Han
Original Assignee
Lg Electronics Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from KR1020060081322A external-priority patent/KR20080018735A/ko
Priority claimed from KR1020060114770A external-priority patent/KR100795958B1/ko
Application filed by Lg Electronics Inc. filed Critical Lg Electronics Inc.
Priority to CN2007800315512A priority Critical patent/CN101506527B/zh
Publication of WO2008023962A1 publication Critical patent/WO2008023962A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F04C28/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/13—Noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/12—Magnetic properties

Definitions

  • the present invention relates to a rotary compressor.
  • a rotary compressor is applied to air-conditioning system such as air- conditioners.
  • air-conditioners or the like have various functions, products by which capacity of the rotary compressor is to be varied are required.
  • Several techniques are well known to vary the capacity of the rotary compressor. Examples thereof can be a technique in which an inverter motor is employed to control the number of rotation times (i.e., RPM) of the compressor, a technique in which a vane is mechanically controlled to perform an idling, and the like. Disclosure of Invention Technical Problem
  • the inverter motor requires high cost to buy. Also, it is more difficult to increase refrigerating capacity under a cooling condition than to increase the refrigerating capacity under a heating condition.
  • the technique in which the vane is mechanically controlled to perform the idling adapts two methods.
  • the first method is implemented such that pressure of refrigerant applied to a compression space of a cylinder is varied to restrain/release the vane.
  • the second method is implemented such that pressure applied to a rear surface of the vane is varied to restrain/release the vane.
  • the conversion of pressure applied to a front or rear surface of the vane should be rapidly performed in order to drastically reduce chattering noise of the vane.
  • variable capacity type rotary compressor in which pressure applied to a front or rear surface of a vane is allowed to be rapidly converted by preventing excessive oil from flowing into the front or rear surface of the vane, thereby enabling reduction of chattering noise of the vane.
  • a variable capacity type rotary compressor comprising: a casing having an inner space to contain oil therein; a driving motor disposed inside the inner space of the casing to generate driving force; a cylinder assembly disposed inside the inner space of the casing and having a compression space to compress refrigerant; at least one rolling piston orbiting in the compression space of the cylinder assembly; at least one vane coupled to the cylinder assembly to be separated from or contacted with the rolling piston to partition the compression space into a suction area and a compression area; and at least one connection pipe allowing the inner space of the casing to be connected to the cylinder assembly such that an inner pressure of the casing can be applied to the vane, wherein the connection pipe is coupled to the casing such that an end thereof can be connected to the casing at a location higher than a surface of the oil contained in the inner space of the casing.
  • a connection pipe connected to a front or rear side of a vane is disposed to be higher than a surface of oil, thereby avoiding oil from flowing into the front or rear surface of the vane. Accordingly, pressure of the front or rear surface of the vane is fast varied to enable a rapid conversion of the operation mode of the compressor. Also, the pressure of the front or rear surface of the vane can be constantly maintained so as to effectively decrease chattering noise of the vane.
  • FIG. 1 is a perspective view showing an exemplary variable capacity type rotary compressor according to the present invention
  • FIG. 2 is a longitudinal sectional view showing an exemplary variable capacity type rotary compressor according to the present invention
  • FIG. 3 is a sectional view taken along the line I-I in the compressor of Fig. 2;
  • FIG. 4 is a horizontal sectional view showing a connected location of a high pressure side connection pipe in the compressor of Fig. 2;
  • FIG. 5 is a horizontal sectional view showing a power mode of the compressor of Fig.
  • FIG. 6 is a horizontal sectional view showing a saving mode of the compressor of Fig.
  • FIG. 7 is a horizontal sectional view showing another embodiment of the compressor of Fig. 2;
  • FIG. 8 is a longitudinal sectional view showing another embodiment of a connected location of the high pressure side connection pipe in the compressor of Fig. 2;
  • FIG. 9 is a longitudinal sectional view showing another embodiment of a connected location of the high pressure side connection pipe in the compressor of Fig. 2. Best Mode for Carrying Out the Invention
  • a variable capacity type rotary compressor comprises a casing 100 with which a plurality of gas suction pipe s SPl and SP2 and one gas discharge pipe DP are communicated, a motor part 200 which is disposed at an upper side of the casing 100 to generate rotation force, a first compression part 300 and a second compression part 400 which are disposed at a lower side of the casing 100 to compress refrigerant by the rotation force generated from the motor part 200, a valve unit 500 which converts a rear surface of a second vane 440 of the second compression part 400 into a high pressure atmosphere or a low pressure atmosphere and thus allows the second compression part 400 to be operated in a power mode or a saving mode, and a connection unit 600 which enables the valve unit 500 to be connected to both the casing and the second compression part 400 such that the second compression part 400 can be controlled by the valve unit 500.
  • the motor part 200 denotes a motor which is driven at constant speed or in an inverter method.
  • the motor part 200 comprises a stator 210 fixed to the inside of the casing 100 and receiving power applied from the outside, a rotor 220 disposed inside the stator 210 with a certain air gap to be rotated with cooperating with the stator 210, and a rotation shaft 230 coupled to the rotor 220 to transfer rotation force to the first and second compression parts 300 and 400.
  • the first compression part 300 comprises a first cylinder 310 partially constructing a first cylinder assembly, having an annular shape, and disposed inside the casing 100, and an upper bearing plate 320 (i.e., referred to as an upper bearing hereafter) and a middle bearing plate 330 (i.e., referred to as a middle bearing) respectively coupled to upper and lower sides of the first cylinder 310 so as to construct the first cylinder assembly with a first compression space Vl together with the first cylinder 310.
  • an upper bearing plate 320 i.e., referred to as an upper bearing hereafter
  • a middle bearing plate 330 i.e., referred to as a middle bearing
  • the first compression part 300 may further comprise a first rolling piston 340 rotatably coupled to an upper eccentric portion of the rotation shaft 230 to compress refrigerant by orbiting (pivoting) in the first compression space Vl of the first cylinder 310, and a first vane 350 movably coupled to the first cylinder 310 in a radial direction so as to be pressed onto an outer circumferential surface of the first rolling piston 340 and partitioning the first compression space Vl of the first cylinder 310 into a first suction chamber and a first compression chamber.
  • the first compression part 300 may further comprise a vane supporting spring 360 implemented as a compression spring such that a rear side of the first vane 350 is elastically supported, a first discharge valve 370 switchably coupled to an end of a discharge hole 321 formed near a central portion of the upper bearing 320 so as to adjust the discharge of refrigerant gas discharged from the first compression chamber of the first compression space Vl, and a first muffler 380 having a certain inner volume to allow the first discharge valve 370 to be accommodated therein and coupled to the upper bearing 320.
  • a vane supporting spring 360 implemented as a compression spring such that a rear side of the first vane 350 is elastically supported
  • a first discharge valve 370 switchably coupled to an end of a discharge hole 321 formed near a central portion of the upper bearing 320 so as to adjust the discharge of refrigerant gas discharged from the first compression chamber of the first compression space Vl
  • a first muffler 380 having a certain inner volume to allow the first discharge valve 370 to be
  • the second compression part 400 as shown in Fig. 2, comprises a second cylinder
  • the second compression part 400 may further comprise a second rolling piston 430 rotatably coupled to a lower eccentric portion of the rotation shaft 230 to compress refrigerant by orbiting (pivoting) in the second compression space V2 of the second cylinder 410, and a second vane 440 movably coupled to the second cylinder 410 in a radial direction so as to be pressed onto or spaced apart from an outer circumferential surface of the second rolling piston 430 and partitioning the second compression space V2 of the second cylinder 410 into a second suction chamber and a second compression chamber or communicating the second suction chamber with the second compression chamber.
  • the second compression part 400 may further comprise a second discharge valve 450 switchably coupled to an end of a second discharge hole 421 formed near a central portion of the lower bearing 420 so as to adjust the discharge of refrigerant gas discharged from the second compression chamber, and a second muffler 460 having a certain inner volume to allow the second discharge valve 450 to be accommodated therein and coupled to the lower bearing 420.
  • the second cylinder 410 as shown in Fig. 3, comprises a second vane slot 411 disposed at one side of an inner circumferential surface forming the second compression space V2 to allow the second vane 440 to reciprocate in a radial direction, a second suction hole 412 formed in one side of the second vane slot 411 in a circumferential direction to induce refrigerant into the second compression space V2, and a second discharge guiding groove (not shown) formed in the other side of the second value slot 411 to be inclined in an axial direction so as to allow refrigerant to be discharged into the casing 100.
  • a vane chamber 413 is disposed at a radially rear side of the second vane slot 411 to be communicated with a common connection pipe 630 of the connection unit 600 in a sealed state. Also, the vane chamber 413 is disposed at the inside of the casing 100 without being communicated with the inside of the casing 100 to thus provide suction pressure Ps or discharge pressure Pd to the rear side of the second vane 440.
  • the vane chamber 413 has a particular inner volume to allow the rear surface of the second vane 440 to form a pressure surface with respect to pressure applied through the common connection pipe 630, even if the second vane 440 is completely moved back to thusly be accommodated inside the second vane slot 411.
  • the second cylinder 410 may comprise a first passage 414 formed in a direction to cross the motion direction of the second vane 440 orthogonally or with a certain angle to allow the inside of the casing 100 to be communicated with the second vane slot 411, and a second passage 415 disposed at the other side of the first passage 414 based on the second vane slot 411, such that the second vane slot 411 is communicated with the second suction hole 412, by which pressure difference is generated between the first and second passages 414 and 415, thereby rapidly restraining the second vane 440.
  • the first passage 414 and the second passage 415 may be disposed on the same line and have the same sectional area.
  • the valve unit 500 may comprise a main valve portion 510 connected to the vane chamber 412 of the second cylinder 410, and a sub valve portion 520 connected to the main valve 510 to control a switching operation of the main valve portion 510.
  • connection unit 600 may comprise a lower pressure side connection pipe 610 diverged from the second gas suction pipe SP2 to be connected to the main valve portion 510, a high pressure side connection pipe 620 making the inner space 101 of the casing 100 connected to the main valve portion 510, and a common connection pipe 630 connected to the vane chamber 413 of the second cylinder 410 and connected to the main valve portion 510 to allow the vane chamber 413 to be selectively communicated with the low pressure side connection pipe 610 or the high pressure side connection pipe 620.
  • one side connected to the casing 100 is preferably located between a lower end (i.e., E.L.) of the motor part 200 and an upper end of the first cylinder 310 of the first compression part 300 so as to be connected to the casing 100 at a higher portion than the surface (i.e., O.L.) of oil, thereby avoiding oil from flowing into the vane chamber 412.
  • the surface of oil denotes a surface of oil in a state where the compressor is not operated.
  • a mesh type oil blocking member or an oil blocking plate having one end downwardly opened may further be disposed at an inlet of the high pressure side connection pipe 620, so as to effectively avoid oil from flowing inside thereof.
  • the high pressure type connection pipe 620 may be connected to the casing 100 to be upwardly inclined with respect to the connected portion with the casing 100, and accordingly oil flowing into the high pressure type connection pipe 620 can be introduced into the casing 100 to thusly effectively avoid the oil from flowing into the high pressure side connection pipe 620.
  • Reference numeral 110 denotes an accumulator.
  • the rotation shaft 230 rotates together with the rotor 220 to transfer rotation force of the motor part 200 to the first and second compression parts 300 and 400. Accordingly, depending on capacity required in an air-conditioner, the first and second compression parts 300 and 400 are all operated in a power mode to generate large refrigerating capacity, or only the first compression part 300 is operated in the power mode and the second compression part 400 is operated in a saving mode so as to generate small refrigerating capacity.
  • refrigerant of low pressure sucked into the second cylinder 410 via the gas suction pipe SP2 is introduced into the vane chamber 413 via the low pressure side connection pipe 610 by the main valve portion 510 and the sub valve portion 520. Accordingly, the refrigerant of the low pressure introduced into the vane chamber 413 supports a rear surface of the second vane 440 and also compression force of the second compression space V2 is applied to a front surface of the second vane 440 such that the second vane 440 can be spaced apart from the second rolling piston 430.
  • difference between each pressure applied to both side surfaces of the second vane 440 increases by the first passage 414 and the second passage 415 disposed at the second cylinder 410, thereby effectively rapidly restraining the second vane 440.
  • refrigerant or oil of the discharge pressure Pd partially remaining in the vane chamber 413 is fast leaked into the second suction hole 412 via the gap between the second vane 440 and the vane slot 411 and the second passage 415.
  • the second vane 440 can be restrained more rapidly and stably.
  • the compression can normally be performed only in the first compression part 300, not in the second compression part 400.
  • the high pressure side connection pipe 620 is connected to the casing 100 at a higher portion than the surface (i.e., O.L.) of oil, which can preventing oil from be introduced into the vane chamber 412 when the compressor is operated in the power mode. Accordingly, refrigerant is contained in the vane chamber 413 with rarely containing oil therein such that the inner pressure of the vane chamber 413 is rapidly varied, thereby enabling the operation mode of the compressor to be rapidly converted.
  • pressure of the vane chamber 413 can be constantly maintained in a high pressure atmosphere or a low pressure atmosphere, by which the fluctuation of the second vane 440 can be avoided, thereby effectively reducing noise of the compressor.
  • the aforementioned first embodiment is implemented such that pressure applied to the rear side of the second vane is varied to allow the second vane to come in contact with the second rolling piston or be separated therefrom, thereby enabling the operation mode of the compressor to be varied.
  • a second embodiment is implemented such that pressure applied to the front side of the second vane is varied to allow the second vane to come in contact with the second rolling piston or be separated therefrom, thereby enabling the operation mode of the compressor to be varied.
  • a low pressure side inlet of the main valve portion 510 and the second gas suction pipe are connected to each other via the low pressure side connection pipe 610.
  • a high pressure side inlet of the main valve portion 510 and the inner space 101 of the casing 100 are connected to each other via the high pressure side connection pipe 620.
  • a common outlet of the main valve portion 510 and the second suction hole 412 of the second cylinder 410 are connected to each other via the common connection pipe 630.
  • the vane chamber 413 disposed in the inner space 101 of the casing 100 without being communicated with the inner space 101 is disposed at an outer side of the second vane slot 411.
  • the vane chamber 413 can be connected to a second common connection pipe 640 such that suction pressure Ps or discharge pressure Pd can selectively be provided into the vane slot 411.
  • the main valve portion 510 may be implemented as a four- way valve such that the low pressure side connection pipe 610, the high pressure side connection pipe 620, the common connection pipe 630 (referred to as a first common connection pipe in this embodiment) and the second common connection pipe 640 can all be connected to the main valve portion 510.
  • the main valve portion 510 can be constructed such that the second common connection pipe 640 is connected to the low pressure side connection pipe 610 when the first common connection pipe 630 is connected to the high pressure side connection pipe 620, while the second common connection pipe 640 is connected to the high pressure side connection pipe 620 when the first common connection pipe 630 is connected to the low pressure side connection pipe 610.
  • main valve portion 510 may be implemented as a three-way valve as shown in the first embodiment and a back pressure converting unit may separately be disposed in the vane chamber 413.
  • the vane chamber 413 may have a magnet for restraining the second vane.
  • the second cylinder 410 may comprise the second vane slot 411, the second suction hole 412 and the first and second passages 414 and 415 at both sides of the second vane slot 411.
  • Other components required for the operation of the compressor are the same as or similar to those in the first embodiment, and thus the detailed explanation thereof will be omitted.
  • variable capacity type rotary compressor according to the second embodiment will be operated in the following manner.
  • the 610 is connected to the first common connection pipe 630 by the main valve portion 510, thus to allow refrigerant of suction pressure Ps to be introduced into the second compression space V2 of the second cylinder 410.
  • the high pressure side connection pipe 620 is connected to the second common connection pipe 640 by the main valve portion 510, thus to allow refrigerant of discharge pressure Pd to be introduced into the vane chamber 413. Accordingly, the second vane 440 is pressed and supported by the discharge pressure Pd to keep contacted with the second rolling piston 430. Refrigerant introduced into the compression space V2 of the second cylinder 410 is compressed by the second rolling piston 430 and the second vane 440 to be then discharged, operations of which are repeatedly performed.
  • the high pressure side connection pipe 620 is connected to the first common connection pipe 630 by the main valve portion 510, thus to allow refrigerant of discharge pressure Pd to be introduced into the second compression space V2 of the second cylinder 410.
  • the low pressure side connection pipe 610 is connected to the second common connection pipe 640 by the main valve portion 510, thus to allow refrigerant of suction pressure Ps to be introduced into the vane chamber 413. Accordingly, the second vane 440 is pressed by the pressure of the second compression space V2 so as to be spaced apart from the second rolling piston 430.
  • suction chamber and compression chamber of the second compression space V2 are communicated with each other, and thereby the second compression part 400 is not operated.
  • refrigerant of the discharge pressure Pd is introduced from the second suction hole 412 into the second passage 415 disposed between the second suction hole 412 and the second vane slot 411.
  • the refrigerant of the discharge pressure Pd then rapidly flows through the first passage 414.
  • the second vane 440 is pressed toward the first passage 414 by the difference between pressure applied onto both side surfaces thereof so as to be restrained inside the second vane slot 411, thereby allowing the second compression part 400 to keep operated in the saving mode.
  • the high pressure side connection pipe 620 is connected to a middle portion of the casing 100, in more detail, between the lower end of the motor part 200 and the upper end of the first cylinder 310 the first compression part 300 which are higher than a surface (i.e., O.L.) of oil, such that oil in the casing 100 can be previously avoided from flowing into the second cylinder 410.
  • the high pressure side connection pipe 620 may have an oil blocking member for blocking oil outside the inlet of the high pressure side connection pipe 620, or be implemented such that the height of the high pressure side connection pipe 620 can gradually be higher as being farther from the portion connected to the casing 100.
  • the high pressure side connection pipe 620 may be constructed to be communicated with the inner space 101 of the casing 100 at the upper side of the motor part 200 as shown in Fig. 8. Also, the high pressure side connection pipe 620 may be constructed to be connected to a middle portion of the discharge pipe DP as shown in Fig. 9. In this case as well, the introduction of oil into the rear or front surface of the second vane 440 can be decreased, which allows a rapid change in pressure at the rear or front surface of the second vane 440. Accordingly, the modes of the compressor can be smoothly converted. In addition, the pressure at the rear surface and the front surface of the second vane 440 can be constantly maintained, so as to avoid increase in noise due to fluctuation of the second vane 440.
  • the configuration can also be applied to the first compression part 300.

Abstract

La présente invention concerne un compresseur rotatif du type à capacité variable. Une entrée d'une conduite de connexion connectée à une surface arrière ou une surface avant d'une ailette est disposée à une hauteur supérieure à la surface de l'huile. En conséquence, on peut faire varier rapidement la pression appliquée à la surface arrière et à la surface avant de l'ailette, ce qui permet d'effectuer une conversion rapide du mode de fonctionnement du compresseur. En outre, la pression appliquée sur la surface arrière ou la surface avant de l'ailette peut être maintenue constante, ce qui permet de réduire la fluctuation de l'ailette et ainsi de réduire le bruit produit par le compresseur.
PCT/KR2007/004090 2006-08-25 2007-08-24 Compresseur rotatif du type à capacité variable WO2008023962A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN2007800315512A CN101506527B (zh) 2006-08-25 2007-08-24 可变容量式旋转式压缩机

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR10-2006-0081322 2006-08-25
KR1020060081322A KR20080018735A (ko) 2006-08-25 2006-08-25 용량 가변형 로터리 압축기
KR1020060114770A KR100795958B1 (ko) 2006-11-20 2006-11-20 용량 가변형 로터리 압축기
KR10-2006-0114770 2006-11-20

Publications (1)

Publication Number Publication Date
WO2008023962A1 true WO2008023962A1 (fr) 2008-02-28

Family

ID=39106998

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2007/004090 WO2008023962A1 (fr) 2006-08-25 2007-08-24 Compresseur rotatif du type à capacité variable

Country Status (1)

Country Link
WO (1) WO2008023962A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101629569A (zh) * 2008-07-16 2010-01-20 Lg电子株式会社 容量调节压缩机和具有该容量调节压缩机的空调系统
EP2146419A1 (fr) * 2008-07-16 2010-01-20 Lg Electronics Inc. Moteur, compresseur et système de climatisation d'air doté de ceux-ci
WO2010011081A1 (fr) * 2008-07-22 2010-01-28 (주)엘지전자 Compresseur et appareil de conditionnement d’air comportant ce dernier
WO2010011082A2 (fr) * 2008-07-22 2010-01-28 (주)엘지전자 Compresseur rotatif à capacité variable
CN102132045A (zh) * 2008-08-05 2011-07-20 Lg电子株式会社 旋转式压缩机
CN102338514A (zh) * 2010-07-15 2012-02-01 珠海格力节能环保制冷技术研究中心有限公司 旋转式压缩机及其气液分离器
EP2318716A4 (fr) * 2008-08-22 2015-05-06 Lg Electronics Inc Compresseur rotatif de type à capacité variable, appareil de refroidissement comprenant celui-ci et procédé de commande dudit compresseur

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20060014845A (ko) * 2004-08-12 2006-02-16 엘지전자 주식회사 용량가변형 복식 로터리 압축기 및 그 운전 방법 및 이를 구비한 에어콘 및 그 운전 방법
KR20060035491A (ko) * 2004-10-22 2006-04-26 엘지전자 주식회사 용량가변형 복식 로터리 압축기의 오일 공급 구조
KR100595766B1 (ko) * 2005-02-23 2006-07-03 엘지전자 주식회사 로터리 압축기의 용량 가변 장치 및 이를 적용한 에어콘

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20060014845A (ko) * 2004-08-12 2006-02-16 엘지전자 주식회사 용량가변형 복식 로터리 압축기 및 그 운전 방법 및 이를 구비한 에어콘 및 그 운전 방법
KR20060035491A (ko) * 2004-10-22 2006-04-26 엘지전자 주식회사 용량가변형 복식 로터리 압축기의 오일 공급 구조
KR100595766B1 (ko) * 2005-02-23 2006-07-03 엘지전자 주식회사 로터리 압축기의 용량 가변 장치 및 이를 적용한 에어콘

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101629569A (zh) * 2008-07-16 2010-01-20 Lg电子株式会社 容量调节压缩机和具有该容量调节压缩机的空调系统
EP2146419A1 (fr) * 2008-07-16 2010-01-20 Lg Electronics Inc. Moteur, compresseur et système de climatisation d'air doté de ceux-ci
EP2146420A1 (fr) * 2008-07-16 2010-01-20 Lg Electronics Inc. Compresseur à capacité variable et système de climatisation d'air doté de celui-ci
CN102105693A (zh) * 2008-07-22 2011-06-22 Lg电子株式会社 容量可变型旋转式压缩机
WO2010011082A2 (fr) * 2008-07-22 2010-01-28 (주)엘지전자 Compresseur rotatif à capacité variable
WO2010011082A3 (fr) * 2008-07-22 2010-03-18 (주)엘지전자 Compresseur rotatif à capacité variable
WO2010011081A1 (fr) * 2008-07-22 2010-01-28 (주)엘지전자 Compresseur et appareil de conditionnement d’air comportant ce dernier
CN102119277A (zh) * 2008-07-22 2011-07-06 Lg电子株式会社 压缩机及具有该压缩机的空气调节器
US8579597B2 (en) 2008-07-22 2013-11-12 Lg Electronics Inc. Variable capacity type rotary compressor
US9429158B2 (en) 2008-07-22 2016-08-30 Lg Electronics Inc. Air conditioner and compressor having power and saving modes of operation
CN102132045A (zh) * 2008-08-05 2011-07-20 Lg电子株式会社 旋转式压缩机
US8517702B2 (en) 2008-08-05 2013-08-27 Lg Electronics Inc. Rotary compressor with enhanced sealing between mode switching device and chamber thereof
EP2318716A4 (fr) * 2008-08-22 2015-05-06 Lg Electronics Inc Compresseur rotatif de type à capacité variable, appareil de refroidissement comprenant celui-ci et procédé de commande dudit compresseur
CN102338514A (zh) * 2010-07-15 2012-02-01 珠海格力节能环保制冷技术研究中心有限公司 旋转式压缩机及其气液分离器

Similar Documents

Publication Publication Date Title
EP1851434B1 (fr) Compresseur rotatif a capacite variable et systeme de refrigeration le comprenant
JP4473310B2 (ja) 容量可変型ツインロータリ圧縮機及びその運転方法、並びにそれを備えたエアコン及びその運転方法
EP2097648B1 (fr) Compresseur rotatif à capacité variable
KR100595766B1 (ko) 로터리 압축기의 용량 가변 장치 및 이를 적용한 에어콘
US7611341B2 (en) Capacity varying type rotary compressor
EP1653085B1 (fr) Compresseur rotatif multi-étagé à capacité variable
KR100795958B1 (ko) 용량 가변형 로터리 압축기
WO2008023962A1 (fr) Compresseur rotatif du type à capacité variable
EP1923571B1 (fr) Compresseur rotatif à capacité variable
US8517702B2 (en) Rotary compressor with enhanced sealing between mode switching device and chamber thereof
KR20100023632A (ko) 용량가변형 로터리 압축기 및 이를 적용한 냉동기기 및 그 운전 방법
KR100620044B1 (ko) 로터리 압축기의 용량 가변 장치
KR100724452B1 (ko) 용량 가변형 로터리 압축기
KR20060120387A (ko) 로터리 압축기의 용량 가변 장치
KR101587174B1 (ko) 로터리 압축기
KR100621026B1 (ko) 로터리 압축기의 용량 가변 장치
KR100585809B1 (ko) 용량 가변형 다중 로터리 압축기 및 그 운전 방법
KR101194608B1 (ko) 용량 가변형 로터리 압축기
EP2317142B1 (fr) Compresseur rotatif
KR100585810B1 (ko) 이중 셀을 구비한 용량 가변형 로터리 압축기 및 그 운전방법
KR100677527B1 (ko) 로터리 압축기
KR20070000329A (ko) 밸브조립체 및 이를 적용한 로터리 압축기
KR20060136299A (ko) 밸브조립체 및 이를 적용한 로터리 압축기

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 200780031551.2

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 07793686

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

NENP Non-entry into the national phase

Ref country code: RU

122 Ep: pct application non-entry in european phase

Ref document number: 07793686

Country of ref document: EP

Kind code of ref document: A1