EP2679823A1 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

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Publication number
EP2679823A1
EP2679823A1 EP11859605.5A EP11859605A EP2679823A1 EP 2679823 A1 EP2679823 A1 EP 2679823A1 EP 11859605 A EP11859605 A EP 11859605A EP 2679823 A1 EP2679823 A1 EP 2679823A1
Authority
EP
European Patent Office
Prior art keywords
suction
valve
bypass
room
discharge
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP11859605.5A
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English (en)
French (fr)
Inventor
Ryota Iijima
Masaki Koyama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
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
Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Publication of EP2679823A1 publication Critical patent/EP2679823A1/de
Withdrawn legal-status Critical Current

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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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • 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

Definitions

  • the present invention relates to a scroll compressor, and more appropriately to a scroll compressor adaptable to operation in a wide range from heavy load to light load.
  • scroll compressors used in air conditioners and water heaters are required to permit capacity control over a broad range by each individual unit. For instance, when an air conditioner is used for space cooling, it has to operate quickly because the temperature in the room is usually high at the time of staring the operation.
  • the conventional practice is to perform high-speed operation (high-speed rotation) with a larger capacity at the time of start by using inverter control and, when the room space is cooled to some extent and a shift to a regular operating state takes place, low-speed operation (low-speed rotation) with a smaller capacity is performed.
  • the low-speed operation in the regular operating state would mean operation at a very low rotating speed if in particular a case is assumed in which the air conditioner installed in a building to which today's energy saving is applied and provided with highly insulative materials.
  • a usual practice is to keep the rotational speed at not too low a level at the time of small-capacity operation and to control the capacity; for instance, when the room space is cooled to a certain temperature, the scroll compressor is stopped, when the room temperature rises, it is started again, and this operational pattern is repeated.
  • Patent Literature 1 For instance, a structural improvement of part of a scroll compressor to accomplish control to make the discharge volume variable while keeping the rotational speed constant is described in Patent Literature 1 and elsewhere.
  • a bypass passage is provided to let refrigerant gas on the way of compression bypass to the suction side, an electromagnetic valve to open and close this bypass passage is further provided, and the refrigerant gas on the way of compression is discharged to the suction side by opening this electromagnetic valve to accomplish capacity control thereby to make the discharge volume variable.
  • An object of the present invention is to obtain a scroll compressor that can realize highly efficient capacity control even under a light load operating condition by improving the delay in the discharge of the refrigerant to the discharge side when capacity- controlled operation is switched over to normal operation.
  • the invention provides a scroll compressor comprising a fixed scroll, an orbiting scroll disposed in a sealed vessel and meshed with each other to form a compression room, the fixed scroll having a release port with a discharge outlet formed toward the central part and causing the compression room and the discharge side to communicate with each other on the outer circumferential side and a release valve for preventing a reverse flow from the discharge side toward the compression room, and on the outer circumferential side of the fixed scroll a suction room and a suction passage communicating with the suction room, further provided with a bypass passage formed in the fixed scroll and causing the discharge side and the suction room or the suction passage to communicate with each other; a bypass valve for opening and closing this bypass passage; and a suction non-return valve that is disposed farther upstream from the suction room or part of the suction passage into which the bypass passage opens and prevents reverse flowing to the upstream side.
  • FIG. 1 is a longitudinal section showing the first embodiment of the scroll compressor according to the invention.
  • a scroll compressor 1 is configured of, among others, a compressing mechanism part 3 composed by meshing a fixed scroll 5 and an orbiting scroll 6 with each other, an electric motor 4 driving this compressing mechanism part 3, and a sealed vessel 2 housing the compressing mechanism part 3, the electric motor 4 and the like.
  • the compressing mechanism part 3 and the electric motor 4 are arranged in the upper part and the lower part, respectively, and further in the bottom part an oil sump 13 in which lubricating oil is deposited is provided.
  • the sealed vessel 2 is configured of a cylindrically shaped case 2a making up the trunk, a lid chamber 2b welded to the upper part of this case 2a, and a bottom chamber 2c welded to the lower part of the case 2a.
  • a suction pipe 2d is fitted to the lid chamber 2b, a discharge pipe 2e is fitted to the case 2a, and the inside of the sealed vessel 2 makes up a discharge chamber 2f.
  • the compressing mechanism part 3 is configured of, among others, the fixed scroll 5 having a spirally shaped lap 5c erected on a panel plate 5d, the orbiting scroll 6 having a spirally shaped lap 6a erected on a panel plate 6b, and a frame 9 that is integrally fixed to the fixed scroll 5 with a bolt 8 and supports the orbiting scroll 6.
  • 7 denotes a crankshaft that is rotatably supported by a main bearing 9a disposed in the frame 9, and an eccentric part 7b is linked to the orbiting scroll 6 via an orbiting bearing 6c disposed on a boss part of the rear face of the orbiting scroll 6.
  • an Oldham's ring 12 is disposed between the under face of the orbiting scroll 6 and the frame 9, and this Oldham's ring 12 is engaged with a groove formed in the under face of the orbiting scroll 6 and a groove formed in the frame 9 and causes the orbiting ring 6, without allowing it to rotate, to perform revolving (orbiting) motion in response to eccentric turning of the eccentric part 7b of the crankshaft 7.
  • the electric motor 4 is provided with a stator 4a and a rotor 4b; the stator 4a is fixed to the sealed vessel 2 by such means as pressing in or welding, and the rotor 4b is fixed to the crankshaft 7 and arranged rotatably within the stator 4a.
  • the eccentric part 7b is formed eccentrically relative to and integrally with the main shaft part 7a of the crankshaft 7, and is inserted into and engaged with the orbiting bearing 6c provided on the rear face of the orbiting scroll 6. Further, the crankshaft 7, driven by the electric motor 4, causes the orbiting scroll 6 to orbit by eccentrically rotating the eccentric part 7b.
  • an oiling passage 7c for guiding lubricating oil 13 to the main shaft part 7a, the sub-bearing 17, the orbiting bearing 6c and elsewhere.
  • Refrigerant gas of the freezing cycle when the orbiting scroll 6 is caused to orbit by the electric motor 4 via the crankshaft 7, is introduced from the suction pipe 2d into a compression room 11 partitioned by the fixed scroll 5 and the orbiting scroll 6, and is compressed by the contraction of the volume of the compression room 11 as it shifts toward the center of the spirally shaped laps 5c and 6a.
  • the compressed refrigerant gas is discharged from a discharge port 53 provided substantially at the center of a panel plate 5d of the fixed scroll 5 into the discharge chamber 2f within the sealed vessel 2, and flows out (toward the condenser of the freezing cycle) from the discharge pipe 2e.
  • Fig. 2 is a bottom view of the fixed scroll 5, also illustrating the lap 6a of the orbiting scroll 6; Fig. 3 , an enlarged view of the vicinities of the suction room in Fig. 2 ; and Fig. 4 , a section of an essential part illustrating on an enlarged scale the vicinities of the compressing mechanism part 3 of the scroll compressor shown in Fig. 1 .
  • a release port 5b that causes the compression room 11 to communicate with the discharge chamber 2f, which is the discharge side, and a bypass passage 5f that causes the suction room 10 to communicate with the discharge chamber 2f is formed;
  • the release port 5b is provided with a release valve 5a, which is a non-return valve to prevent flowing back from the discharge side to the compression room 11;
  • the bypass passage 5f is provided with a bypass valve 14 for opening and closing the bypass passage 5f.
  • a suction passage 5h upstream from the suction room 10 with which the bypass passage 5f communicates, a suction passage 5h is disposed, and farther upstream from this suction passage 5h, a suction non-return valve 15 is disposed.
  • This suction non-return valve 15 has to be disposed farther upstream than the suction room 10 or the suction passage 5h into which the bypass passage 5f opens, and is intended to prevent flowing back to the upstream side (evaporator side).
  • Fig. 3 which is an enlarged view of the vicinities of the suction room, a lap position 6a1 of the lap 6a of the orbiting scroll 6 at the moment of completion of suction by an outer line side compression room 21 and a lap position 6a2 of the same at the moment of completion of suction by an inner line side compression room 22 are shown, one superposed over the other virtually. It is preferable for the opening of the bypass passage 5f on the suction room side to be in a position not communicating with the suction space represented by halftone dot meshing in Fig.
  • the bypass valve 14 is provided with a valve element 14b for opening and closing the bypass passage 5f, a space 14a disposed on the rear face side (the side reverse to the fixed scroll 5) to cause the valve element 14b to work, and a spring 14c disposed in this space 14a. Further, the space 14a is provided with a communicating pipe 23 to be communicating with the suction pipe 2d (suction side) and the discharge pipe 2e (discharge side), and further a three-way valve 16 is provided on the way of this communicating pipe 23 in a part outside the sealed vessel 2.
  • the refrigerant under the suction pressure or the discharge pressure can be selectively switched over at any desired timing and introduced into the space 14a on the rear face of the valve element 14b.
  • the configuration is such that, when the refrigerant under the suction pressure is introduced, the valve element 14b so works as to open the bypass passage 5f with the difference in pressure working on the valve element 14b and the spring 14c or, when the refrigerant under the discharge pressure is introduced, the valve element 14b so works as to close the bypass passage 5f.
  • bypass valve 14 is opened and closed by switching over the destination of connection of the space 14a to the suction side or the discharge side of the compressor and thereby introducing the refrigerant under the suction pressure or the discharge pressure into the space 14a; for instance the configuration may as well use a plurality of electromagnetic valves.
  • Fig. 4 shows the state of the scroll compressor 1 in normal operation (the bypass valve closed), namely a state in which the space 14a communicates with the discharge pipe 2e and filled with the refrigerant under the discharge pressure and the bypass valve 14 is closed.
  • Arrows in Fig. 4 represent flows of the refrigerant.
  • the refrigerant passes the suction pipe 2d, is sucked from the suction room 10 into the compression room 11 formed by meshing of the fixed scroll 5 and the orbiting scroll 6; contraction of the volume of this compression room 11 while shifting toward the center of spiral scroll laps compresses the refrigerant to be discharged from a discharge outlet 5e to the discharge chamber 2f.
  • the refrigerant in the discharge chamber 2f further passes the discharge pipe 2e and is discharged out of the compressor (out of the sealed vessel).
  • Fig. 5 shows the state of the scroll compressor in bypass operation (the bypass valve open), namely a state in which the space 14a is continuous to the suction pipe 2d and filled with the refrigerant under the suction pressure and the bypass valve 14 is open.
  • Arrows in Fig. 5 represent flows of the refrigerant.
  • the discharge chamber 2f and the suction room 10 communicate with each other via the bypass passage 5f.
  • opening of the valve causes the refrigerant in the discharge chamber 2f to flow into the suction room 10, and the suction room 10 is placed under the discharge pressure.
  • the suction non-return valve 15 is provided between the suction room 10 and the suction pipe 2d, when the refrigerant in the discharge chamber 2f flows into the suction room 10, the suction non-return valve 15 is closed by the pressure difference between before and after it and closes the suction passage 5h. As the refrigerant in the discharge chamber 2f having flowed from the discharge chamber 2f into the suction room 10 can be prevented from flowing back from the suction room 10 side to the suction pipe 2d side, the suction room 10 is placed under the discharge pressure.
  • Fig. 6 illustrates the opening/closing control of the bypass valve 14 when capacity control is done in the scroll compressor of this embodiment.
  • the bypass valve 14 repeats opening and closing in a constant cycle. Normal operation and bypass operation, mentioned earlier, are thereby periodically switched over to each other to enable the average discharge flow rate of the compressed refrigerant to be reduced while keeping the compressive power at the necessary minimum.
  • the opening/closing control of the bypass valve 14 in this embodiment is so configured as to regulate steplessly the capacity at any desired level between 0 and 100% by making the time ratio between the open and closed states in one open/closed cycle variable. If, for instance, the open period of the bypass valve per cycle is 40% of the whole cycle duration, the capacity will be 60%. To add, the open/closed cycle may be constant, but it is desirable to make the cycle duration variable according to the time ratio between the open and closed states.
  • a low-pressure bypass valve (156) and a high-pressure bypass valve (157) perform the role of switching over between normal operation and bypass operation.
  • the low-pressure bypass valve (156) is closed, and compressed refrigerant is discharged toward the discharge side 109B past a discharge pipe or a high-pressure side bypass passage BH.
  • the low-pressure bypass valve (156) is opened in a state in which the high-pressure bypass valve (157) is closed.
  • This causes a space disposed in the upper part of the fixed scroll (a bypass mechanism (140) that bypasses fluid present in the intermediate area between the suction side and the discharge side) to be connected to the suction side to be placed under the suction pressure thereby to open a bypass valve (146) to be opened by the differential pressure, and the refrigerant in the compression room to be discharged to the suction side almost uncompressed.
  • the compression room is substantially filled with the suction pressure during bypass operation.
  • This embodiment significantly differs from the foregoing case in that both the suction room 10 and the compression room 11 are substantially filled during bypass operation with the discharge pressure.
  • a space in which the pressure differs between normal operation and bypass operation is present including the compression room.
  • Fig. 7 is a diagram illustrating relations among the low pressure bypass valve aperture control, the compressor discharge flow rate, input and pressure according to prior art.
  • "Bypass pressure” is the pressure in the space in which the pressure varies during bypass operation (hereinafter referred to as the bypass space), which in the above-cited prior art is the pressure in the space of the bypass mechanism (140) and the bypass passage BH.
  • the horizontal axis represents the lapse of time; along this lapse of time, relations among the discharge flow rate of the compressed refrigerant relative to the actions of the bypass valve and the compressor input and pressure will be described on a time series basis.
  • the compression room is filled with the refrigerant under the suction pressure by communicating with the suction side.
  • the bypass space is placed under the suction pressure by communicating with the suction side.
  • Fig. 8 is a diagram illustrating relations among the bypass valve aperture control, the discharge flow rate of the compressed refrigerant, the compressor input and pressure in this embodiment.
  • the bypass space comprises the suction room 10, the compression room 11 and the bypass passage 5f
  • "Bypass pressure" is the pressure in the suction room 10 and the bypass passage 5f.
  • Fig. 8 The diagram of Fig. 8 will be described along a time series.
  • the bypass valve 14 As the refrigerant is normally compressed and discharged, it is obtained at the required flow rate. Also, the normal compressor input is required as motive power for compressing the refrigerant.
  • the bypass pressure (the pressure in the bypass space) is the same as the suction pressure.
  • the suction room 10 communicates with the discharge chamber 2f, the suction room 10 and the bypass passage 5f are filled with the discharge pressure, and the compression room 11 is also placed under the discharge pressure.
  • the bypass pressure becomes substantially equal to the discharge pressure during bypass operation.
  • this embodiment can prevent the compressor input during operation under capacity control from falling and moreover, it can regulate steplessly the capacity at any desired level between 0 and 100% by making variable the time ratio between the open and closed states in one open/closed cycle of the bypass valve 14, thereby enabling a scroll compressor that can realize high-efficiency capacity control even under low-speed and light-load operating conditions to be obtained.
  • capacity control by this embodiment switches over between normal operation and bypass operation at a constant time ratio
  • the capacity can be made steplessly variable in a broad range of 0 to 100% by regulating the time ratio
  • the scroll compressor can be used under rotational speed conditions that permit high-efficiency and high-reliability operation.
  • Fig. 9 is a sectional view of the vicinities of the compression mechanism part of the scroll compressor, showing the second embodiment of the invention
  • Fig. 10 a bottom view of a fixed scroll of the scroll compressor shown in Fig. 9 , also showing orbiting scroll laps.
  • the opening/closing control of the bypass valve 14 is accomplished by utilizing the pressure of the refrigerant flowing through the suction pipe 2d and the discharge pipe 2e in the first embodiment described above, in this second embodiment the opening/closing control of the bypass valve 14 is accomplished by utilizing pressure variations in the suction room 10.
  • the fixed scroll 5 is provided with the bypass passage 5f that connects the suction room 10 and the discharge chamber 2f, and an opening on the discharge chamber side of this bypass passage 5f is provided with the bypass valve 14.
  • This bypass valve 14 is provided with the valve element 14b for opening and closing the bypass passage 5f, the space 14a on the rear face (the reverse side to the fixed scroll 5) of this valve element 14b, and the spring 14c disposed in this space 14a.
  • the space 14a is so configured as to communicate with the suction room 10 via a switching valve passage 5g formed in the fixed scroll 5. Also, on the aperture of the switching valve passage 5g on the discharge chamber 2f side a switching valve 18 for opening and closing this aperture is provided; the configuration is such that, when this switching valve 18 is opened, the space 14a communicates with the suction room 10 and, when the switching valve 18 is closed, the communication of the space 14a with the suction room 10 is cut off.
  • the switching valve 18 is provided with a valve element 18a for opening and closing the switching valve passage 5g, a spring 18b that presses the valve element 18a toward the switching valve passage 5g, and a coil 18c for causing the valve element 18a to perform opening or closing.
  • the switching valve passage 5g is used only for letting the refrigerant flow into the space 14a of the small-volume bypass valve 14 or letting it flow out of the space 14a, its passage area can be made very small and, as the pressure of the refrigerant on the valve element 18a is also small, the valve element 18a can be easily opened or closed.
  • the bypass passage 5f is disposed in a similar position to that in the first embodiment shown in Fig. 2
  • the switching valve passage 5g is disposed in a similar range to the destination range of connection of the suction room side opening of the bypass passage 5f represented by halftone dot meshing in Fig. 3 .
  • the switching valve passage 5g is connected to the space 14a in the bypass valve 14, can open or close the switching valve by turning on or off the current to the coil of the switching valve 18, and can switch over between communication and non-communication of the switching valve passage 5g. Description of other configurations is omitted because they are similar to those of the first embodiment.
  • Fig. 11 through Fig. 14 are enlarged views of the structures of the vicinities of the bypass valve in Fig. 9 ;
  • Fig. 11 shows the state during normal operation,
  • Fig. 12 the transitional state from normal operation to Fig. 13 , the state during bypass operation,
  • Fig. 14 the transitional state from bypass operation to normal operation.
  • the bypass valve 14 and the switching valve 18 are in the state shown in Fig. 11 .
  • the valve element 18a is pressed toward the fixed scroll 5 by the force of the spring 18b and closes the valve by blocking the switching valve passage 5g.
  • the bypass valve 14 is held in the closed state by the pressure difference between the space 14a on its rear face side and the suction room 10 side.
  • the bypass valve 14 opens, the discharge chamber 2f and the suction room 10 communicate with each other, and bypass operation during which the refrigerant under the discharge pressure in the discharge chamber 2f flows into the suction room 10 via the bypass passage is started.
  • the switching valve 18 is immediately closed as shown in Fig. 13 . For this reason, during the bypass operation, the pressure in the space 14a remains to be kept at the suction pressure level.
  • Fig. 15 is a diagram illustrating relations among bypass valve aperture variations the switching valve 18, pressure variations in the space 14a of the bypass valve 14 and pressure variations in the suction room 10 in response to the aperture control of the switch valve 18 in this second embodiment.
  • the scroll compressor can be operated under capacity control.
  • the pressure in the space 14a of the bypass valve 14 varies from the discharge pressure to the suction pressure; as the bypass valve 14 is thereby closed, the suction room 10 is placed under the discharge pressure to accomplish bypass operation.
  • electricity is supplied again to the switching valve 18 and the switching valve is opened for a short period of time the pressure in the space 14a of the bypass valve 14 varies from the suction pressure to the discharge pressure; thereby the bypass valve 14 is closed, the suction room 10 is placed under the suction pressure to return to normal operation.
  • the discharge volume can be freely regulated by controlling the ratio between the duration of normal operation and that of bypass operation (duty ratio), making possible operation under capacity control.
  • this embodiment allows arrangement of the bypass valve 14 and the switching valve 18, both needed for bypass operation, in the sealed vessel 2. Therefore, as structural components including the communicating pipe 23 and the three-way valve 16 disposed outside the sealed vessel 2, such as the one shown in the first embodiment, become dispensable, there is a further advantageous effect of making possible manufacture of compact products at low cost.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP11859605.5A 2011-02-22 2011-02-22 Spiralverdichter Withdrawn EP2679823A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2011/053841 WO2012114455A1 (ja) 2011-02-22 2011-02-22 スクロール圧縮機

Publications (1)

Publication Number Publication Date
EP2679823A1 true EP2679823A1 (de) 2014-01-01

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Application Number Title Priority Date Filing Date
EP11859605.5A Withdrawn EP2679823A1 (de) 2011-02-22 2011-02-22 Spiralverdichter

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EP (1) EP2679823A1 (de)
JP (1) JP5489142B2 (de)
WO (1) WO2012114455A1 (de)

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See references of WO2012114455A1 *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105697369A (zh) * 2014-12-16 2016-06-22 Lg电子株式会社 涡旋式压缩机
US9869315B2 (en) 2014-12-16 2018-01-16 Lg Electronics Inc. Scroll compressor having capacity varying valves
CN105697369B (zh) * 2014-12-16 2018-02-16 Lg电子株式会社 涡旋式压缩机
US10533555B2 (en) 2016-11-21 2020-01-14 Hitachi-Johnson Controls Air Conditioning, Inc. Scroll compressor
EP3339646A1 (de) * 2016-12-26 2018-06-27 Mitsubishi Heavy Industries Thermal Systems, Ltd. Spiralverdichter mit bypass

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WO2012114455A1 (ja) 2012-08-30
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