WO2013140458A1 - Compresseur à volute - Google Patents

Compresseur à volute Download PDF

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Publication number
WO2013140458A1
WO2013140458A1 PCT/JP2012/002000 JP2012002000W WO2013140458A1 WO 2013140458 A1 WO2013140458 A1 WO 2013140458A1 JP 2012002000 W JP2012002000 W JP 2012002000W WO 2013140458 A1 WO2013140458 A1 WO 2013140458A1
Authority
WO
WIPO (PCT)
Prior art keywords
back pressure
scroll
chamber
slit
oil supply
Prior art date
Application number
PCT/JP2012/002000
Other languages
English (en)
Japanese (ja)
Inventor
近野　雅嗣
佐藤　英治
土屋　豪
柳瀬　裕一
Original Assignee
日立アプライアンス株式会社
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 日立アプライアンス株式会社 filed Critical 日立アプライアンス株式会社
Priority to JP2014505806A priority Critical patent/JP5771739B2/ja
Priority to PCT/JP2012/002000 priority patent/WO2013140458A1/fr
Priority to CN201280068982.7A priority patent/CN104105881B/zh
Publication of WO2013140458A1 publication Critical patent/WO2013140458A1/fr

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    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for 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
    • 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
    • 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F04C18/0261—Details of the ports, e.g. location, number, geometry
    • 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.
  • Patent Document 2 JP-A-2011-58439
  • the oil supply means for supplying the oil of the high pressure hydraulic chamber to the back pressure chamber side, and the orbiting scroll or frame are provided so as to open alternately to both sides of the high pressure hydraulic chamber. It is described as "a scroll compressor characterized by including an oil supply passage for supplying the oil of the hydraulic pressure chamber to the back pressure chamber side" (see claim 1).
  • Both of the patent documents 1 and 2 supply oil to the back pressure chamber by the differential pressure between the back pressure chamber and the discharge pressure space, so the pressure of the discharge pressure space becomes small under the low pressure ratio condition. There is a possibility that the back pressure and the discharge pressure become equal and it becomes impossible to supply the back pressure chamber from the discharge pressure space. If the back pressure chamber can not be lubricated in this way, the sliding portion of the Oldham ring can not be lubricated, and the amount of oil required to seal the compression chamber can not be secured, and the leakage loss increases, resulting in compressor efficiency descend. Therefore, it is an object of the present invention to provide a highly reliable scroll compressor that enables refueling of the back pressure chamber even under low pressure ratio conditions.
  • the configuration described in the claims is adopted.
  • the present application includes a plurality of means for solving the above-mentioned problems, if one example is given, “the fixed-side flat plate portion and a first wrap erected on one surface of the fixed-side flat plate portion And a second scroll which is erected while holding a spiral shape on one surface of the swing side flat plate portion, and the second wrap and the first wrap.
  • a rotating scroll forming a compression chamber by rotating with respect to the fixed scroll, and pressing the rotating scroll against the fixed scroll to the back side of the rotating scroll with respect to the fixed scroll
  • a back pressure chamber for adjusting the pressure of the back pressure chamber, and the back pressure chamber from a discharge pressure space through which the compressed refrigerant from the compression chamber is discharged.
  • a first oil supply means for supplying oil and a second oil supply means for supplying oil from the back pressure chamber to the compression chamber or a suction chamber formed on the suction side of the compression chamber are provided.
  • FIG. 7 is a plan view showing an engagement state of a fixed scroll and a revolving scroll. The figure which shows the slit provided in the turning scroll mirror plate surface.
  • FIG. 1 is a longitudinal sectional view of a scroll compressor according to the present embodiment.
  • the stationary scroll (stationary scroll member) 7 includes a disc-like stationary side flat plate portion 7a (base plate) and a first wrap which is erected on the stationary side flat plate portion 7a in a spiral manner. 7b, and a cylindrical support portion 7d located on the outer peripheral side of the fixed side flat plate portion 7a and having a mirror plate surface continuous with the tip end surface of the first wrap 7b and surrounding the first wrap 7b.
  • the surface of the fixed side flat plate portion 7a on which the first wrap 7b is erected is called a root 7c because it is between the first wrap 7b.
  • the surface of the support portion 7 d in contact with the turning side flat plate portion 8 a (end plate) of the turning scroll (turning scroll member) 8 is the end plate surface 7 e of the fixed scroll 7.
  • the fixed scroll 7 has its support 7 d fixed to the frame 17 by bolts or the like, and the frame 17 integrated with the fixed scroll 7 is fixed to the case (sealed container) 9 by a fixing means such as welding.
  • the orbiting scroll 8 is disposed to face the fixed scroll 7, and the first wrap 7 b of the fixed scroll and the second wrap 8 b of the orbiting scroll are engaged with each other and provided rotatably in the frame 17.
  • the orbiting scroll 8 includes a disc-shaped orbiting flat plate portion 8a, a second wrap 8b erected while holding a spiral shape from a bottom 8c which is a surface of the orbiting flat portion 8a, and a pivoting flat portion 8a. And a boss 8d provided at the center of the back of the Further, the surface of the outer peripheral portion of the turning side flat plate portion 8 a in contact with the fixed scroll 7 is the end plate surface 8 e of the turning scroll 8.
  • the compression chamber 13 is formed by revolving around the fixed scroll 7 while the second wrap 8 b and the first wrap 7 b are meshed with each other.
  • the case 9 has a sealed container structure in which a scroll unit including the fixed scroll 7 and the orbiting scroll 8, a motor unit 16 (16a: rotor, 16b: stator), lubricating oil, and the like are housed inside.
  • a shaft (rotational shaft) 10 fixed integrally with the rotor 16 a of the motor unit 16 is rotatably supported by the frame 17 via the main bearing 5 and coaxial with the central axis of the fixed scroll 7.
  • a crank portion 10 a is provided at the tip of the shaft 10, and the crank portion 10 a is inserted into a turning bearing 11 provided at a boss portion 8 d of the turning scroll 8, and the turning scroll 8 can be turned with the rotation of the shaft 10.
  • the central axis of the orbiting scroll 8 is eccentric to the central axis of the fixed scroll 7 by a predetermined distance.
  • the second wrap 8 b of the orbiting scroll 8 is superimposed on the first wrap 7 b of the fixed scroll 7 while being shifted by a predetermined angle in the circumferential direction.
  • Reference numeral 12 denotes an Oldham ring for relatively turning movement of the turning scroll 8 with respect to the fixed scroll 7 so as not to rotate automatically.
  • FIG. 6 is a plan view showing the engagement between the fixed scroll and the orbiting scroll.
  • a plurality of crescent-shaped compression chambers 13 (13a, 13b) are formed between the first wraps 7b, 8b,
  • the compression chambers are continuously reduced in volume as they move to the center. That is, on the inner line side and the outer line side of the second wrap 8b of the orbiting scroll 8, an orbiting extension side compression chamber 13a and an orbiting outer line side compression chamber 13b are formed, respectively.
  • Reference numeral 20 denotes a suction chamber, which is a space on the way of suction of fluid. The suction chamber 20 becomes the compression chamber 13 from the time when the phase of the turning motion of the turning scroll 8 advances and the confinement of the fluid is completed.
  • the suction port 14 is provided on the fixed scroll 7 as shown in FIGS. 1 and 6.
  • the suction port 14 is bored on the outer peripheral side of the fixed side flat plate portion 7 a so as to communicate with the suction chamber 20.
  • the discharge port 15 is bored in the vicinity of the spiral center of the fixed side flat plate portion 7 a of the fixed scroll 7 so as to communicate with the compression chamber 13 on the innermost circumferential side.
  • the shaft 10 When the shaft 10 is rotationally driven by the motor unit 16, it is transmitted from the crank 10a of the shaft 10 to the orbiting scroll 8 via the orbiting bearing 11, and the orbiting scroll 8 has a pivoting radius of a predetermined distance around the central axis of the fixed scroll 7. Make a swing movement with It is restrained by the Oldham ring 12 so that the orbiting scroll 8 does not rotate during this orbiting movement.
  • the compression chambers 13 formed between the first wrap 7b and the second wrap 8b are continuously moved to the center, and the volume of the compression chambers 13 is continuously reduced according to the movement.
  • the fluid for example, refrigerant gas circulating the refrigeration cycle
  • the compressed fluid is discharged from the discharge port 15 to the discharge space 54 in the upper part of the case. Be done.
  • the discharged fluid enters the motor chamber 52 in the case 9 from the discharge space 54, and is supplied from the discharge pipe 6 to the outside of the compressor, for example, to a refrigeration cycle.
  • the lubricating oil is stored at the bottom of the case 9, and the lower end of the shaft 10 is provided with a volumetric or centrifugal oil supply pump 21.
  • the lubrication pump 21 is also rotated along with the rotation of the shaft, and the lubricating oil is sucked from the lubricating oil suction port 25 provided in the lubrication pump case 22 and discharged from the discharge port 28 of the lubrication pump.
  • the discharged lubricating oil is supplied to the upper part through the through hole 3 provided in the shaft.
  • a portion of the lubricating oil lubricates the sub bearing 23 through a lateral hole 24 provided in the shaft 10 and returns to the oil reservoir 53 at the bottom of the case.
  • a space formed by the oil groove 57 and the orbiting bearing 11 and a space for containing the main bearing 5 (a frame 17, a shaft 10, a frame seal 56, and a rib-shaped orbiting boss provided on a boss 8 d of the orbiting scroll 8
  • a space formed by the member 34 and the seal member 32 is collectively referred to as a first space 33.
  • the first space 33 is a space having a pressure close to the discharge pressure. Most of the lubricating oil that has flowed into the first space 33 for lubrication of the main bearing 5 and the orbiting bearing 11 returns to the case bottom through the oil drain hole 26a and the oil drain pipe 26b.
  • the minimum amount necessary for the lubrication of the Oldham ring 12 and the lubrication and sealing of the sliding portion between the fixed scroll 7 and the orbiting scroll 8 is the first amount between the upper end face of the seal member 32 and the end face of the orbiting boss member 34.
  • the seal member 32 is inserted into the annular groove 31 provided in the frame 17 together with the wave spring (not shown), and the first space 33 serving as the discharge pressure and the middle of the suction pressure and the discharge pressure. It is separated from the back pressure chamber 18 which is pressure.
  • the first oil supply means is composed of one or more first slits 60 provided in the pivot boss member 34 and the seal member 32, and the first slit 60 is a seal member. Arrange so as to straddle 32. That is, the first oil supply means is constituted by the first slit provided on the surface opposite to the fixed scroll 7 of the orbiting scroll 8, and the first slit serves as the discharge pressure space (54, 52, 33) and the back It always communicates with the pressure chamber 18. As a result, due to the pressure difference between the first space 33 and the back pressure chamber 18, oil flows from the first space 33 to the back pressure chamber 18 through the first slit 60 which is a minute gap.
  • the arrangement of the first slits 60 may not always straddle the seal member 32 but may intermittently straddle with the turning movement of the turning scroll 8. That is, the first slit 60 may be configured to intermittently communicate the discharge pressure space (54, 52, 33) with the back pressure chamber 18 as the orbiting scroll 8 pivots.
  • first oil supply means for example, it is constituted by a plurality of holes 30 provided in the turning boss member 34 and the seal member 32, and the plurality of holes 30 are the orbiting scroll 8.
  • the circular motion over the seal member 32 is performed along with the pivoting motion of the above to move between the first space 33 and the back pressure chamber 18.
  • the lubricating oil in the first space 33 is accumulated in the hole 30 and intermittently transferred to and discharged from the back pressure chamber 18, whereby the minimum necessary oil can be introduced to the back pressure chamber 18.
  • the lubricating oil that has entered the back pressure chamber 18 passes through the back pressure valve 61 connecting the back pressure chamber 18 and the suction chamber 20 (or the compression chamber 13) to the suction chamber 20 (or the compression chamber 13).
  • the discharge port 15 and discharged from the discharge port 15. A part of the oil discharged from the discharge port 15 is discharged, for example, together with the refrigerant gas from the discharge pipe 6 to the refrigeration cycle, and the rest is separated from the refrigerant gas in the case 9 and stored in the oil reservoir 53 at the bottom of the case.
  • the amount of oil required for each bearing and the amount of oil needed for the compression chamber can be made independently. Since the control can be performed, it is possible to optimize the amount of oil supplied to the compression chamber, and a highly efficient compressor can be obtained. Further, as another configuration, the oil supply pump 21, the first space 33, and the first oil supply means are not provided, and the oil in the oil reservoir 53 which is the discharge pressure is used by utilizing the throttling in the small gap of the bearing portion. The pressure may be reduced and introduced into the back pressure chamber.
  • the compression action generates an axial force which tends to separate the fixed scroll 7 and the orbiting scroll 8 from each other.
  • a so-called detachment phenomenon of the orbiting scroll 8 occurs in which both scrolls are pulled apart due to the axial force, the sealing property of the compression chamber is deteriorated and the efficiency of the compressor is lowered. Therefore, a back pressure chamber 18 serving as a pressure between the discharge pressure and the suction pressure is provided on the back side of the turning side flat plate portion of the turning scroll 8 to cancel the separating force by the back pressure and fix the turning scroll 8 as a fixed scroll. I'm trying to press on 7.
  • the scroll compressor of FIG. 1 is provided with a back pressure valve 61.
  • the back pressure valve 61 is a space 61 c communicating with the suction chamber 20 (or the compression chamber 13) by a space 61 a communicating with the back pressure chamber 18 and a communication passage 61 b provided in the fixed scroll 7.
  • the valve 61d is disposed to separate the two spaces.
  • the valve 61d is pressed against the opening communicating with the space 61a by a spring 61f which is an elastic body fixed by the stopper 61e.
  • the valve 61d is configured such that the pressure in the space 61a, that is, the back pressure is the pressure of the suction chamber 20 (or the compression chamber 13) in the space 61c introduced through the communication passage 61b and the pressure corresponding to the pressing force of the spring 61f. When it becomes higher than the total, it moves upward to connect the space 61a and the space 61c. That is, when the pressure in the back pressure chamber 18 becomes higher than a certain value, the back pressure valve 61 releases the fluid in the back pressure chamber 18 to the suction chamber 20 or the compression chamber 13 to make the back pressure an appropriate value. It is to adjust. In addition, the back pressure value in the back pressure valve 61 becomes "suction pressure + alpha (pressure corresponding to the pressing force of the spring 61 f)".
  • a back pressure hole 35 may be used to obtain an optimum back pressure value.
  • the back pressure hole 35 is a U-shaped passage, and communicates the compression chamber 13 with the back pressure chamber 18 to introduce a pressure according to the pressure of the compression chamber into the back pressure chamber 18.
  • the pressure in the compression chamber 13 rises with the rotation of the crankshaft.
  • the value of the back pressure is determined depending on which section of the compression chamber 13 in the process of compression communicates with the back pressure chamber 18. Therefore, the back pressure value can be set to an optimum value by adjusting this communication section.
  • the back pressure value at the back pressure hole 35 is “suction pressure ⁇ ⁇ (compression ratio determined by communication section with the compression chamber 13)”.
  • the above is the basic structure of the scroll compressor.
  • oil can not be supplied to the back pressure chamber 18.
  • the value of the back pressure is determined by the back pressure valve 61 or the back pressure hole 35 as described above, and is represented by “suction pressure + ⁇ ” and “suction pressure ⁇ ⁇ ”, respectively.
  • the back pressure value represented by these equations may be equal to or larger than the discharge pressure.
  • the oil supply differential pressure between the first space 33 and the back pressure chamber 18 disappears, and it becomes impossible to supply the back pressure chamber 18 with the first slit 60 or the oil transfer hole 30.
  • the back pressure chamber 18 can not be refueled, the lubrication failure of the sliding portion of the Oldham ring 12 reduces the reliability.
  • the oil supplied to the compression chamber 13 via the back pressure chamber 18 disappears, the hermeticity of the compression chamber 13 is reduced, the leakage loss is increased, and the efficiency of the compressor is reduced.
  • one or a plurality of second slits 62 are provided in the end plate surface 8e of the orbiting scroll or the end plate surface 7e of the fixed scroll to provide a second oil supply means. That is, in addition to the first oil supply means (first slit 60) for supplying the oil to the back pressure chamber 18 from the discharge pressure space (54, 52, 33) where the compressed refrigerant from the compression chamber 13 is discharged, Second oil supply means (second slit 62) for supplying oil from the back pressure chamber 18 to the position of the compression initial stage of the compression chamber 13 or to the suction chamber 20 formed on the suction side to the compression chamber 13; Is provided.
  • the second oil supply means is constituted by a second slit 62 provided on one surface of the swing side flat plate portion 8a or on one surface of the fixed side flat plate portion 7a, and the second slit 62 is a back pressure chamber.
  • the position 18 and the position of the compression initial stage of the compression chamber 13 or the suction chamber are always communicated.
  • the second slit 62 may be provided to intermittently communicate the position of the back pressure chamber 18 and the initial stage of compression of the compression chamber 13 with the suction chamber 20 as the orbiting scroll 8 pivots.
  • the fluid is arranged to be always or intermittently communicated with the suction chamber 20, and the oil is made to flow from the back pressure chamber 18 to the suction chamber 20 (or the position of the compression initial stage of the compression chamber 13).
  • the back pressure is reduced, and the oil flows from the first space 33 into the back pressure chamber 18 as much as the oil flows out to the suction chamber 20.
  • a hole for oil transfer may be provided.
  • the back pressure hole 35 is adopted as a pressure adjusting means of the back pressure chamber 18, as shown in FIG. 5, the back pressure hole 35 is formed on the back pressure chamber 18 and the compression chamber 13 or the suction side of the compression chamber.
  • the back pressure value is set to an optimal back pressure value by constantly or intermittently communicating with the suction chamber 20 and adjusting the communication section as described above.
  • the pressure "suction pressure x ⁇ (compression ratio determined by the communication section with the compression chamber 13)" in the back pressure chamber 18 becomes high and becomes equal to the discharge pressure space Therefore, there is a possibility that oil can not be supplied to the back pressure chamber by the first oil supply means (first slit 60).
  • the position at which the oil is supplied to the compression chamber 13 or the back pressure chamber 18 by the second oil supply means is a position communicating with the compression chamber 13 or the back pressure chamber 18 by the back pressure hole 35 Since the pressure of the back pressure chamber 18 can be released by setting it to the outer peripheral side (suction side) more than that, the pressure of the back pressure chamber 18 is thereby reduced, and the back pressure by the first oil supply means (first slit 60) Allow oil supply to the room. Further, it is desirable that the cross sectional area of the oil supply flow path of the second oil supply means (second slit 62) be smaller than the cross sectional area of the oil supply flow path of the back pressure hole 35.
  • the flow resistance of the second slit 62 or the oil transfer hole is the flow resistance of the first slit 60 provided in the pivot boss member 34 or the oil transfer hole 30. It is better to make the size larger, and in this case, it is possible to suppress problems such as an abnormal decrease in back pressure.
  • the flow path resistance is greatly affected by the depth of the slit, so the depth of the second slit 62 provided in the orbiting scroll mirror plate surface 8 e is greater than the depth of the first slit 60 provided in the orbiting boss member 34, for example. It should be set to be shallow.
  • first slit 60 of the orbiting boss member 34 is provided so as to intermittently communicate the first space 33 with the back pressure chamber 18 along with the orbiting motion of the orbiting scroll 8, and the second slit of the orbiting scroll plate surface 8e. It is further preferable that the back pressure chamber 18 and the suction chamber 20 (or the compression chamber 13) be intermittently communicated with each other 62 so that the sections in which the two slits communicate with each other are equal. In other words, the timing of intermittent communication of each of the first slit 60 and the second slit 62 is made to be the same.
  • the slit depth can be made deeper than the slit that constantly communicates at 360 degrees.
  • the communication start angle (phase) when the first slit 60 and the second slit 62 communicate with each other at 90 degrees is matched, inflow and outflow of oil into the back pressure chamber 18 are made almost simultaneously. Therefore, it is possible to keep back pressure fluctuation small.
  • the back pressure hole 35 As the back pressure adjusting mechanism, when the back pressure is reduced by providing the second slit 62, oil flows from the first space 33 into the back pressure chamber 18, The pressure difference between the compression chamber 13 and the back pressure chamber 18 also increases, and the refrigerant gas and the oil flow into the back pressure chamber 18 through the back pressure hole 35. It becomes smaller than it was.
  • the back pressure valve 61 acts as a check valve even when the back pressure decreases, so the back pressure is increased only by the flow of oil from the first space 33 into the back pressure chamber 18. As a result, the effect of the present embodiment is enhanced.
  • a condenser 40 for condensing the refrigerant compressed by the scroll compressor 1 and a pressure reducing means for reducing the pressure of the refrigerant condensed by the condenser 40 (expansion
  • a pressure reducing means for reducing the pressure of the refrigerant condensed by the condenser 40
  • expansion valve 41 an evaporator 42 for evaporating the refrigerant decompressed by the decompression means
  • an air blower for blowing air to the evaporator 42. It is possible to provide a user-friendly air conditioner that consumes a small amount of power throughout the year and has a wide operating range.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention porte sur un compresseur à volute de grande fiabilité qui peut fournir de l'huile à une chambre de contrepression, même dans des conditions de faible rapport de pression. Un compresseur à volute comprend une volute fixe et une volute tournante qui forme une chambre de compression en tournant de façon relative par rapport à la volute fixe, une chambre de contrepression servant à pousser la volute tournante dans la volute fixe étant formée dans la surface arrière de la volute tournante par rapport à la volute fixe ; le compresseur à volute étant muni d'une soupape de contrepression ou d'un trou de contrepression pour régler la pression de la chambre de contrepression, un premier moyen de fourniture d'huile servant à fournir de l'huile à la chambre de contrepression en provenance d'un espace de pression de refoulement dans lequel un fluide frigorigène comprimé provenant d'une chambre de compression est refoulé, et un second moyen de fourniture d'huile servant à fournir de l'huile provenant de la chambre de contrepression, soit à la chambre de compression, soit à une chambre d'entrée formée dans le côté d'entrée de la chambre de compression.
PCT/JP2012/002000 2012-03-23 2012-03-23 Compresseur à volute WO2013140458A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2014505806A JP5771739B2 (ja) 2012-03-23 2012-03-23 スクロール圧縮機
PCT/JP2012/002000 WO2013140458A1 (fr) 2012-03-23 2012-03-23 Compresseur à volute
CN201280068982.7A CN104105881B (zh) 2012-03-23 2012-03-23 涡旋式压缩机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/002000 WO2013140458A1 (fr) 2012-03-23 2012-03-23 Compresseur à volute

Publications (1)

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WO2013140458A1 true WO2013140458A1 (fr) 2013-09-26

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JP (1) JP5771739B2 (fr)
CN (1) CN104105881B (fr)
WO (1) WO2013140458A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
WO2016031278A1 (fr) * 2014-08-28 2016-03-03 サンデンホールディングス株式会社 Machine à fluide à volute et machine frigorifique la comprenant

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Publication number Priority date Publication date Assignee Title
DE102015120151A1 (de) * 2015-11-20 2017-05-24 OET GmbH Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Fahrzeugklimaanlage und Fahrzeug
CN107893757B (zh) * 2017-11-06 2023-10-03 珠海格力电器股份有限公司 涡旋压缩机、空调器及涡旋压缩机的控制方法
JP7263554B2 (ja) * 2019-12-17 2023-04-24 日立ジョンソンコントロールズ空調株式会社 スクロール圧縮機

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JP2008196370A (ja) * 2007-02-13 2008-08-28 Sanden Corp 流体機械
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WO2010070790A1 (fr) * 2008-12-15 2010-06-24 パナソニック株式会社 Compresseur à spirale
JP2011027076A (ja) * 2009-07-29 2011-02-10 Panasonic Corp スクロール圧縮機
WO2011027480A1 (fr) * 2009-09-02 2011-03-10 日立アプライアンス株式会社 Compresseur à spirale, dispositif de cycle de réfrigération et réchauffeur d'eau de pompe à chaleur

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JP2008196370A (ja) * 2007-02-13 2008-08-28 Sanden Corp 流体機械
JP2009024664A (ja) * 2007-07-23 2009-02-05 Sanden Corp スクロール型流体機械
WO2010070790A1 (fr) * 2008-12-15 2010-06-24 パナソニック株式会社 Compresseur à spirale
JP2011027076A (ja) * 2009-07-29 2011-02-10 Panasonic Corp スクロール圧縮機
WO2011027480A1 (fr) * 2009-09-02 2011-03-10 日立アプライアンス株式会社 Compresseur à spirale, dispositif de cycle de réfrigération et réchauffeur d'eau de pompe à chaleur

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016031278A1 (fr) * 2014-08-28 2016-03-03 サンデンホールディングス株式会社 Machine à fluide à volute et machine frigorifique la comprenant
JP2016048056A (ja) * 2014-08-28 2016-04-07 サンデンホールディングス株式会社 スクロール型流体機械及びそれを用いた冷凍装置

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JPWO2013140458A1 (ja) 2015-08-03
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JP5771739B2 (ja) 2015-09-02

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