WO2012042825A1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
WO2012042825A1
WO2012042825A1 PCT/JP2011/005395 JP2011005395W WO2012042825A1 WO 2012042825 A1 WO2012042825 A1 WO 2012042825A1 JP 2011005395 W JP2011005395 W JP 2011005395W WO 2012042825 A1 WO2012042825 A1 WO 2012042825A1
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WO
WIPO (PCT)
Prior art keywords
compression chamber
refrigerant
oil
rotary compressor
orbiting scroll
Prior art date
Application number
PCT/JP2011/005395
Other languages
English (en)
Japanese (ja)
Inventor
啓晶 中井
信吾 大八木
裕文 吉田
健 苅野
大輔 船越
竜一 大野
飯田　登
Original Assignee
パナソニック株式会社
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 パナソニック株式会社 filed Critical パナソニック株式会社
Priority to US13/824,694 priority Critical patent/US20130189080A1/en
Priority to JP2012516405A priority patent/JPWO2012042825A1/ja
Priority to CN2011800466082A priority patent/CN103154521A/zh
Publication of WO2012042825A1 publication Critical patent/WO2012042825A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0292—Ports or channels located in the wrap
    • 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
    • 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
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/263—HFO1234YF

Definitions

  • the present invention uses a refrigerant that does not contain chlorine atoms, has a low global warming potential, and contains at least a hydrofluoroolefin having a carbon double bond, such as a room air conditioner, a car air conditioner, a refrigerator, and other air conditioners.
  • the present invention relates to a rotary compressor incorporated in a refrigeration cycle apparatus.
  • HFC-based refrigerant hydrofluorocarbon
  • This HFC-based refrigerant has a very high global warming potential. Therefore, development of a compressor using a refrigerant having a low ozone depletion coefficient and a global warming coefficient has been performed.
  • a refrigerant with a low global warming potential is generally low in stability. For this reason, when used in a refrigeration cycle apparatus such as a room air conditioner, car air conditioner, refrigerator, or other air conditioner for a long period of time, it is necessary to ensure the stability and reliability of the refrigerant.
  • the refrigerant evaporated in the evaporator is sucked into the compressor and compressed to a specified pressure by the compressor. At that time, the state of the refrigerant largely changes from low pressure to high pressure and from low temperature to high temperature. Therefore, it is necessary to configure the compressor so as to ensure the stability and reliability of the refrigerant.
  • Patent Document 1 discloses a compressor that uses a refrigerant having a low global warming potential, and supplies the refrigerant directly to the suction port in order to start compression of the refrigerant sucked into the compressor from as low a temperature as possible.
  • a compressor having a direct suction path for the same is disclosed.
  • the temperature of the refrigerant after being compressed to a specified pressure by the compressor is lower than the case where the refrigerant is not directly supplied to the suction port because the temperature rise is suppressed before the compression is started.
  • the decomposition of the refrigerant is suppressed, and the failure of the compressor or the decrease in the service life due to the decomposition product (for example, sludge) of the refrigerant is suppressed. That is, the reliability and durability of the compressor are improved.
  • Re-expansion heating means that high-pressure refrigerant in the middle of compression leaks into a low-pressure space and re-expands in the low-pressure space to a high temperature, and as a result, heats the low-pressure refrigerant existing in the low-pressure space. To tell. By such re-expansion heating, the temperature of the refrigerant after being compressed to a specified pressure becomes higher than necessary. In addition, when re-expansion heating occurs, a part of the compression power (energy) spent to obtain the high-temperature / high-pressure refrigerant is used for heating the low-temperature / low-pressure refrigerant. descend.
  • the present invention is a rotary compressor that uses a refrigerant having a low global warming potential, and uses refrigerating machine oil to improve the sealing performance of the compression chamber to re-expand.
  • An object of the present invention is to provide a highly efficient rotary compressor excellent in reliability and durability, capable of suppressing heating and suppressing the heating of the refrigerant by the refrigerating machine oil.
  • the present invention is configured as follows.
  • a single refrigerant of hydrofluoroolefin having a carbon double bond or a mixed refrigerant containing the hydrofluoroolefin is used, and the refrigerant is compressed.
  • a rotary compressor having a compression chamber and a first compression chamber oil supply passage for supplying refrigeration oil to the compression chamber after the refrigerant is confined.
  • the sealing performance of the compression chamber is improved, and re-expansion heating caused by leakage of the refrigerant in the middle of compression is suppressed. Heating is suppressed as compared with the case of supplying refrigeration oil in the suction process. As a result, the temperature of the refrigerant after being compressed to a specified pressure is reduced as compared with the case where the refrigerating machine oil is supplied in the suction process, thereby suppressing the decomposition of the refrigerant.
  • the refrigerant that is being sucked into the compression chamber has the lowest temperature.
  • high-temperature refrigeration oil is supplied to such a refrigerant, the refrigerant is strongly heated because the temperature difference between the refrigerant and the refrigeration oil is large (as a result, the decomposition of the refrigerant greatly proceeds).
  • the refrigerant in the middle of compression has a small temperature difference from the supplied refrigerating machine oil because the temperature of the refrigerant itself increases with compression. Further, in the case of the refrigerant compressed to near the discharge pressure, the temperature of the refrigerant is higher than the temperature of the supplied refrigeration oil.
  • heating the refrigerant by the refrigerating machine oil can be suppressed by supplying the refrigerating machine oil to the compression chamber after confining the refrigerant (compression process).
  • the refrigerating machine oil improves the sealing performance of the compression chamber after confining the refrigerant while suppressing the heating of the refrigerant.
  • the rotary compressor in the rotary compressor, it is possible to suppress an increase in the temperature of the refrigerant that causes the decomposition of the refrigerant while using the refrigerant having a low ozone layer depletion coefficient and a global warming coefficient. As a result, it is possible to provide a highly efficient rotary compressor that is excellent in reliability and durability while taking the global environment into consideration.
  • a rotary compressor according to the present invention uses a single refrigerant of hydrofluoroolefin having a carbon double bond or a mixed refrigerant containing the hydrofluoroolefin, a compression chamber for compressing the refrigerant, and confining the refrigerant And a first compression chamber oil supply passage for supplying refrigeration oil to the compression chamber after the first compression chamber.
  • the temperature of the refrigerant after being compressed to the specified pressure is lower than that in the case where the refrigerating machine oil is supplied in the suction process, and the decomposition of the refrigerant is suppressed.
  • the compressor may be configured to intermittently block the first compression chamber oil supply path.
  • Refrigerating machine oil can be supplied to the compression chamber at an optimal timing and with an optimal amount capable of effectively realizing improvement in the sealing performance of the compression chamber and suppression of the temperature rise of the refrigerant caused by supply of the refrigerator oil.
  • coolant can be suppressed more reliably.
  • the compression chamber When the compression chamber is formed between the fixed scroll and the orbiting scroll by meshing the fixed scroll and the orbiting scroll each having an end plate and a wrap which is a spiral wall formed on the end plate And providing at least one second compression chamber oil supply passage for supplying the refrigerator oil to the compression chamber from an oil storage section for storing the refrigerator oil, wherein at least one of the second compression chamber oil supply passages is the first compression chamber oil supply. It may be a route.
  • a rotary compressor that includes a plurality of compression chambers and compresses refrigerants in a plurality of compression chambers at the same time
  • refrigerant in the middle of compression that has been compressed to a certain high pressure leaks into the compression chamber on the low-pressure side
  • the refrigerant is refrigerant. It is easy to leak into the compression chamber in the middle of the compression after one step rather than the compression chamber in the middle of sucking (so-called internal leakage occurs). In that case, the re-expansion of the leaked refrigerant not only heats the refrigerant in the leaked compression chamber, but also increases the pressure in the leaked compression chamber. Due to such internal leakage, the temperature of the refrigerant rises.
  • the compression chamber includes a first compression chamber formed outside the orbiting scroll wrap and a second compression chamber formed inside the orbiting scroll wrap
  • the first compression chamber Of the second compression chamber the supply amount of the refrigerating machine oil to the compression chamber having the longer leak length may be made larger than the supply amount to the other compression chamber.
  • the amount of refrigeration oil supplied to improve the sealing performance corresponding to the length of the leak point in the compression chamber can be optimized, so extra refrigeration oil that occurs when an excessive amount of refrigeration oil is supplied. Heating of the refrigerant due to can also be suppressed.
  • the compression chamber has a first compression chamber formed outside the wrap of the orbiting scroll and a second compression chamber formed inside the wrap of the orbiting scroll, the first compression chamber Of the second compression chambers, the amount of the refrigerating machine oil supplied to the compression chamber having the higher volume change rate may be increased compared to the amount of oil supplied to the other compression chamber.
  • the optimum amount of refrigerating machine oil can improve the sealing performance of the compression chamber where refrigerant leakage is likely to occur because the pressure difference from the compression chamber on the low pressure side is large.
  • the heating of the refrigerant by the extra refrigeration oil that occurs when an excessive amount of refrigeration oil is supplied can also be suppressed.
  • the first compression chamber oil supply path is provided on the back surface of the orbiting scroll and is introduced into the wrap of the orbiting scroll and communicated with the introduction path portion provided in the wrap of the orbiting scroll.
  • the refrigerant includes at least one of tetrafluoropropene or trifluoropropene, which is a kind of hydrofluoroolefin, and may have a global warming potential of 5 or more and 750 or less, preferably 5 or more and 350 or less. . According to such a refrigerant, it is possible to effectively provide a rotary compressor having a low environmental load and high reliability and high efficiency.
  • the refrigerant is mainly composed of tetrafluoropropene or trifluoropropene, which is a kind of hydrofluoroolefin, and difluoromethane and pentafluoroethane preferably have a global warming potential of 5 or more and 750 or less, preferably 5 or more and 350 or less. What was mixed so that it may become may be sufficient. According to such a refrigerant, the environmental load is small, and the temperature can be lowered by suppressing the flow rate, so that a highly reliable and highly efficient rotary compressor can be effectively provided.
  • refrigerating machine oils (1) polyoxyalkylene glycols, (2) polyvinyl ethers, (3) poly (oxy) alkylene glycols or their monoether and polyvinyl ether copolymers, (4) polyol esters and polycarbonates
  • a synthetic oil containing the oxygen-containing compound of (5), a synthetic oil mainly composed of alkylbenzenes, or (6) a synthetic oil mainly composed of ⁇ -olefins may be used.
  • Such a refrigerating machine oil can effectively provide a highly reliable and highly efficient rotary compressor.
  • a single refrigerant of hydrofluoroolefin having a carbon double bond or a mixed refrigerant containing the hydrofluoroolefin is used.
  • FIG. 1 is a longitudinal sectional view of a scroll compressor according to Embodiment 1 of the present invention
  • FIG. 2 is a partially enlarged sectional view of the compression mechanism shown in FIG. 1
  • FIG. 3 shows a plurality of states of the orbiting scroll of the compression mechanism.
  • action are demonstrated about a scroll compressor.
  • the scroll compressor according to the first embodiment has a sealed container 1.
  • the scroll compressor also has a compression mechanism 2, a motor unit 3, and an oil storage unit 20 inside the sealed container 1.
  • the compression mechanism 2 includes a main bearing member 11 fixed to the sealed container 1 by welding or shrink fitting, a shaft 4 supported by the main bearing member 11, and a fixing fixed on the main bearing member 11 by bolts or the like.
  • the scroll 12 is configured between a main scroll member 11 and a fixed scroll 12, and a revolving scroll 13 that meshes with the fixed scroll 12.
  • the fixed scroll 12 includes an end plate 12a and a wrap 12b that is a spiral wall formed on the end plate 12a.
  • the orbiting scroll 13 includes an end plate 13a and a wrap 13b that is a spiral wall formed on the end plate 13a. Is provided. Between the orbiting scroll 13 and the main bearing member 11, there is provided an Oldham ring or the like that prevents the orbiting scroll 13 from rotating and guides the orbiting scroll 13 driven by the shaft 4 to move in a circular orbit.
  • a restraining mechanism 14 is provided.
  • the eccentric shaft portion 4 a located at the upper end of the shaft 4 rotates the orbiting scroll 13 eccentrically, whereby the orbiting motion of the orbiting scroll 13 is realized.
  • the compression chamber 15 formed between the fixed scroll 12 and the orbiting scroll 13 moves while reducing the volume from the outer peripheral side toward the center.
  • Refrigerant gas
  • the suction pipe 16 communicating with the outside of the hermetic container 1 and the suction port 17 in the outer peripheral portion of the fixed scroll 12 (suction process).
  • the refrigerant is compressed (compression step).
  • the refrigerant that has reached a specified pressure by compression pushes open the reed valve 19 provided in the discharge hole 18 in the center of the fixed scroll 12 and moves from the compression chamber 15 into the sealed container 1 through the discharge hole 18.
  • a pump 25 is provided at the other end of the shaft 4.
  • the pump 25 is arranged so that the suction port exists in the oil storage part 20 provided at the bottom of the sealed container 1. Since the pump 25 is driven in synchronization with the compression mechanism 2, the pump 25 can reliably suck up the refrigeration oil (oil) 6 stored in the oil storage unit 20 regardless of the pressure condition or the operation speed. And it can supply to the compression mechanism 2 stably.
  • the oil 6 sucked up by the pump 25 is supplied to the compression mechanism 2 through an oil supply hole 26 penetrating the shaft 4. Note that foreign matter in the oil 6 is removed by an oil filter or the like before or after being sucked up by the pump 25, so that foreign matter can be prevented from entering the compression mechanism 2. As a result, the reliability of the compressor is further improved. Improvements can be made.
  • the pressure of the oil 6 introduced into the compression mechanism 2 is substantially the same as the discharge pressure of the scroll compressor, it becomes a back pressure source for the orbiting scroll 13. That is, the oil 6 functions to press the back surface of the orbiting scroll 13 (the surface facing the main bearing member 11) and press the orbiting scroll 13 against the fixed scroll 12. Thereby, the orbiting scroll 13 is maintained in a state in which it is in contact with the fixed scroll 12 without leaving the fixed scroll 12 and without being in partial contact with the fixed scroll 12. As a result, the compression mechanism 2 can stably exhibit a predetermined compression capacity.
  • the seal member 78 between the back surface of the orbiting scroll 13 and the main bearing member 11, the high pressure region 30 is defined inside the seal member 78, and the back pressure chamber 29 is disposed outside the seal member 78. Defined. Since the pressure in the high pressure region 30 and the pressure in the back pressure chamber 29 can be completely separated, the pressure on the back surface of the orbiting scroll 13 can be stably controlled.
  • a recess 12d is formed in a portion 12c of the end plate 12a between the wraps 12b of the fixed scroll 12.
  • the orbiting scroll 13 is formed with an in-lap oil supply passage 55.
  • the in-lap oil supply passage 55 communicates with the back pressure chamber 29 through one opening 55a.
  • the back pressure chamber 29 communicates with the oil storage section 20 via an introduction path 54 provided on the back side of the orbiting scroll 13 and an oil supply hole 26 provided in the shaft 4.
  • the other opening 55 b of the in-wrap oil supply passage 55 is formed on the top surface of the wrap 13 a that is in sliding contact with the end plate 12 a of the fixed scroll 12. As shown by a broken line in FIG. 3, the opening 55 b of the in-lap oil supply passage 55 moves relative to the fixed scroll 12 so as to draw a circular turning locus by a turning motion of the turning scroll 13.
  • FIG. 3 shows a plurality of states of the orbiting scroll 13 meshed with the fixed scroll 12, and specifically shows the states of the orbiting scroll 13 whose phases are different by 90 degrees.
  • a first compression chamber 15a formed outside the wrap 13a of the orbiting scroll 13 and formed inside the wrap 13a.
  • a second compression chamber 15b Each of the first compression chamber 15a and the second compression chamber 15b moves toward the center while reducing the volume by the orbiting motion of the orbiting scroll 13.
  • the refrigerant in the compression chamber 15 reaches the discharge pressure and the compression chamber 15 and the discharge hole 18 communicate with each other, the refrigerant in the compression chamber 15 moves into the discharge chamber 31 by opening the reed valve 19.
  • the opening 55 b of the in-lap oil supply passage 55 and the recess 12 d formed in the portion 12 c of the end plate 12 a of the fixed scroll 12 communicate intermittently.
  • the in-lap oil supply passage 55 and the second compression chamber 15b are intermittently communicated with each other through the recess 12d.
  • the second compression chamber 15b As shown in FIG. 3A, the second compression chamber 15b formed on the outermost side of the orbiting scroll 13 and the suction port 17 communicate with each other, and introduction of the refrigerant into the second compression chamber 15b is started. (Start of inhalation process). And as shown in FIG.3 (c), the 2nd compression chamber 15b is closed by the turning motion of the turning scroll 13, and a refrigerant
  • the opening 55b of the in-lap oil supply passage 55 communicates with the second compression chamber 15b through the recess 12d by the orbiting motion of the orbiting scroll 13, and the in-lap oil supply passage 55
  • the oil 6 is supplied to the second compression chamber 15b after confining the refrigerant from the back pressure chamber 29 via
  • FIGS. 3A to 3C when the opening 55b and the recess 12d are not in communication, almost no oil is supplied from the back pressure chamber 29 to the second compression chamber 15b.
  • the second compression chamber 15b is connected to the second compression chamber 15b through the in-lap oil supply passage 55 by intermittently communicating the opening 55b of the in-lap oil supply passage 55 and the second compression chamber 15b through the recess 12d of the fixed scroll 12. Oil 6 is intermittently supplied to the chamber 15b. The reason for supplying the oil 6 to the second compression chamber 15b will be described later.
  • Embodiment 1 by using a single hydrofluoroolefin refrigerant or a mixed refrigerant containing the hydrofluoroolefin having a low ozone depletion coefficient and a low global warming coefficient, The influence on can be suppressed. Further, by supplying the oil 6 to the second compression chamber 15b after the refrigerant is confined (compression process), the temperature of the refrigerant after being compressed to a predetermined pressure is communicated with the suction process (that is, the suction port 17). Compared to the case of supplying the oil 6 in the state).
  • the temperature of the refrigerant after being compressed to the specified pressure is higher when the oil 6 is supplied to the second compression chamber 15b in the suction process.
  • the reason why is low is as follows.
  • the temperature of the refrigerant that is being sucked into the second compression chamber 15b has the lowest temperature.
  • the refrigerant is strongly heated because the temperature difference between the refrigerant and the oil 6 is large (as a result, the refrigerant is greatly decomposed).
  • the refrigerant in the middle of compression has a small temperature difference from the supplied oil 6 because the temperature of the refrigerant itself increases with compression.
  • the temperature of the refrigerant is higher than the temperature of the supplied oil 6.
  • heating the refrigerant by the oil 6 can be suppressed by supplying the oil 6 to the second compression chamber 15b after the refrigerant is confined (compression process).
  • the sealing performance of the second compression chamber 15b after confining the refrigerant is suppressed while suppressing the heating of the refrigerant. It can be improved by the oil 6.
  • the oil 6 is desirably supplied at a timing at which the temperature difference from the refrigerant is as small as possible.
  • the oil 6 improves the sealing performance of the second compression chamber 15b (between the end plate 12a of the fixed scroll 12 and the wrap 13b of the orbiting scroll 13 and between the wrap 12b and the end plate 13a). That is, the leakage of the refrigerant from the second compression chamber 15b can be suppressed.
  • the oil 6 on the rear surface of the orbiting scroll 13 is secondly passed through the oil supply passage 55 in the lap and the recess 12d.
  • the shape of the wrap provided in the fixed scroll 12 and the turning scroll 13 will be described.
  • the spiral shape of the fixed scroll and the orbiting scroll wrap is defined by an involute curve.
  • the involute curve is expressed by the following function in the Cartesian coordinate system, where ⁇ is the expansion angle and a is the base circle radius.
  • Equation 1 The curve represented by Equation 1 is used as the reference curve.
  • the outer envelope is expressed by the following function.
  • the inner envelope is expressed by the following function.
  • the fixed scroll By defining the outer surface of one of the fixed scroll 12 and the orbiting scroll 13 as a function of the above-mentioned reference curve and defining it as a function of the above-mentioned outer envelope of the inner surface of the other lap combined therewith, the fixed scroll The plurality of minimum radial gaps on the inner surface side of the wrap 13b of the orbiting scroll 13 or the plurality of minimum radial gaps on the outer surface side of the wrap 13b of the orbiting scroll 13 formed simultaneously by meshing the laps of the lap and the orbiting scroll lap. Will be equal.
  • the volume of the compression chamber 15 is increased by forming the asymmetric compression chamber 15 by forming the wrap 12b of the fixed scroll 12 and the wrap 13b of the orbiting scroll 13 so that the number of turns is different. I am trying.
  • the volume change rate of the second compression chamber 15b formed on the inner surface side of the wrap 13b of the orbiting scroll 13 is the first compression chamber formed on the outer surface side of the wrap 13b. Larger than the volume change rate of 15a.
  • the pressure of the refrigerant rapidly increases as compared with the first compression chamber 15a, so that the pressure difference with the compression chamber 15 on the low pressure side becomes large. Therefore, the refrigerant is liable to leak from the second compression chamber 15b to the low-pressure side compression chamber 15 between the wrap and the end plate, and it is necessary to improve the sealing performance.
  • the in-lap oil supply passage 55 and the recess 12d are appropriately provided so that more oil 6 is supplied to the second compression chamber 15b having a large volume change rate.
  • leakage of the refrigerant from the second compression chamber 15b to the low-pressure side compression chamber 15 is suppressed, re-expansion heating to the refrigerant in the low-pressure side compression chamber 15 is suppressed, and internal leakage is caused.
  • An increase in pressure can be suppressed.
  • the temperature rise of the refrigerant used in the scroll compressor according to the first embodiment which is easily decomposed at a high temperature, is suppressed.
  • another compression chamber oil supply path (second compression chamber oil supply path excluding the first compression chamber oil supply path) for supplying the oil 6 to the first compression chamber 15a is provided, and the second compression chamber 15b is provided.
  • a small amount of oil 6 compared to the amount of oil 6 supplied intermittently may be supplied to the first compression chamber 15a via another compression chamber oil supply path.
  • another compression chamber oil supply path for example, a compression chamber oil supply path 57 shown in FIG. 2 is provided.
  • the compression chamber oil supply path 57 is formed in the orbiting scroll 13. Further, one opening of the compression chamber oil supply passage 57 is formed on the top surface of the wrap 13b.
  • the other opening communicates with the oil storage section 20 through an introduction path 54 provided on the back surface of the orbiting scroll 13, an oil supply hole 26 provided in the shaft 4, and the like.
  • a small amount of oil 6 can be supplied from the gap between the end plate 12 a of the fixed scroll 12 and the top surface of the wrap 13 b of the orbiting scroll 13.
  • a small amount of oil compared to the amount of oil supplied after confining the refrigerant (after the second compression chamber 15b is closed) It may be supplied before the refrigerant is confined (before the second compression chamber 15b starts to close) or during the confinement of the refrigerant (from the time when the second compression chamber 15b starts to close until it completely closes). That is, if most of the necessary amount of oil 6 is supplied after confining the refrigerant, the temperature rise of the refrigerant, that is, the decomposition of the refrigerant can be suppressed.
  • FIG. 4 is a partially enlarged cross-sectional view of the compression mechanism of the scroll compressor according to Embodiment 2 of the present invention.
  • FIG. 5 is a diagram showing a plurality of states of the orbiting scroll.
  • Components other than the compression chamber oil supply path 56 are the same as those in the first embodiment. 4 and 5, the same reference numerals are used for the same components as those in FIGS. 2 and 3. Moreover, only the description regarding the compression chamber oil supply path
  • the compression chamber oil supply path 56 is formed in the end plate 13 a of the orbiting scroll 13. Further, the compression chamber oil supply path 56 communicates the back pressure chamber 29 and the first compression chamber 15 a formed on the outer surface side of the wrap 13 b of the orbiting scroll 13. However, the compression chamber oil supply passage 56 communicates with the first compression chamber 15a and supplies the oil 6 to the first compression chamber 15a when the orbiting scroll 13 is in the state shown in FIG. In the states shown in (a), 5 (c), and 5 (d), the oil 6 is not supplied to the first compression chamber 15a because it is blocked by the end plate 12a of the fixed scroll 12.
  • the compression chamber on the outer side has a larger volume than the compression chamber located on the center side. Therefore, the leakage length (in other words, the required seal length), which is the length of the location where the refrigerant leaks from the high-pressure side compression chamber with a small volume to the low-pressure side compression chamber with a large volume, is the wrap 13b of the orbiting scroll 13.
  • the first compression chamber 15a formed outside is longer than the second compression chamber 15b formed inside. Therefore, a larger amount of oil 6 than the amount of oil 6 supplied to the second compression chamber 15b is supplied to the first compression chamber 15a having a long leakage length via the compression chamber oil supply passage 56.
  • the first compression chamber 15a having a long leakage length is sufficiently sealed. Thereby, the temperature rise of the refrigerant
  • the pressure increase due to re-expansion heating of the refrigerant and internal leakage can be suppressed, and the amount of oil 6 supplied to the first compression chamber 15a having a long leak length is reduced to the second compression chamber 15b. Since the amount of oil 6 for improving the sealing performance can be optimized in accordance with the length of the leaking portion of the compression chamber, an excessive amount of refrigerating machine oil is supplied. The heating of the refrigerant by the extra refrigeration oil which occurs by this can also be suppressed.
  • FIG. 6 is a longitudinal sectional view of a rotary compressor according to Embodiment 3 of the present invention.
  • FIG. 7 is an enlarged cross-sectional view of a compression mechanism of the rotary compressor.
  • FIG. 8 is an assembly configuration diagram of the compression mechanism of the rotary compressor.
  • FIG. 9 is a figure which shows the several state of the compression mechanism of a rotary compressor.
  • the electric motor 102 and the compression mechanism 103 are housed in the hermetic container 101 in a state of being connected via a crankshaft 131.
  • the compression mechanism 103 includes a cylinder 130, a suction chamber 149 and a compression chamber 139 formed by the end plate 134 of the upper bearing 134a and the end plate 135 of the lower bearing 135a that block both end faces of the cylinder 130, And a vane 133 that contacts the outer peripheral surface of the piston 132 and divides the cylinder 130 into a suction chamber 149 and a compression chamber 139.
  • the piston 132 is fitted into the eccentric portion 131a of the crankshaft 131 supported by the side bearing 134a and the lower bearing 135a, and is eccentrically rotated by the crankshaft 131.
  • the vane 133 is configured to reciprocate toward the piston 132 in response to the eccentric rotation of the piston 132 in order to maintain contact with the outer peripheral surface of the piston 132 that rotates eccentrically.
  • the crankshaft 131 is formed with an oil hole 141 along the central axis that draws oil from the oil storage section 20.
  • Oil supply holes 142 and 143 communicating with the oil hole 141 are provided in the portion of the crankshaft 131 that faces the upper bearing 134a and the lower bearing 135a.
  • An oil supply hole 144 that communicates with the oil hole 141 and an oil groove 145 that communicates with the oil supply hole 14 are formed in the portion of the eccentric portion 131 a of the crankshaft 131 that faces the piston 132.
  • the cylinder 130 is formed with a suction port 140 for sucking gas refrigerant into the suction chamber 149.
  • the suction chamber 149 gradually expands, whereby the refrigerant flows from the suction port 140 to the suction chamber. 149 is inhaled.
  • a discharge port 138 for discharging the refrigerant from the compression chamber 139 is opened in the upper bearing 134a.
  • the discharge port 138 is formed as a hole having a circular cross section passing through the upper bearing 134a.
  • On the upper surface of the discharge port 138 there are provided a discharge valve 136 that opens when a pressure equal to or higher than a predetermined pressure is received, and a cup muffler 137 that covers the discharge valve 136.
  • the compression chamber 139 is gradually reduced.
  • the discharge valve 136 is opened.
  • the refrigerant flows out from the discharge port 138 and is discharged into the sealed container 101 by the cup muffler-137.
  • the eccentric portion 131a of the crankshaft 131, the end plate 134 of the upper bearing 134a, the space 146 surrounded by the inner peripheral surface of the piston 132, the eccentric portion 131a of the crankshaft 131, the end plate 135 of the lower bearing 135a, and A space 147 surrounded by the inner peripheral surface of the piston 132 is formed. Oil leaks into the spaces 146 and 147 from the oil holes 141 through the oil supply holes 142 and 143. The pressures in the spaces 146 and 147 are almost always higher than the pressure in the compression chamber 139 and are almost the same as the discharge pressure.
  • the height of the cylinder 130 is set to be slightly larger than the height of the piston 132 so that the piston 132 can slide inside the cylinder 130. Therefore, there is a gap between the end surface of the piston 132 and the end plate 134 of the upper bearing 134a and the end plate 135 of the lower bearing 135a. Oil in the spaces 146 and 147 leaks into the compression chamber 139 through this gap.
  • FIG. 9 shows the positional relationship between the piston 132 and the oil supply passage 155 when viewed from the central axis direction of the crankshaft 131.
  • the crankshaft 131 crankshaft in which the inlet 155a of the compression chamber oil supply passage 155 and the inside of the piston 132 communicate with each other and the outlet 155b of the compression chamber oil supply passage 155 and the compression chamber 139 communicate with each other.
  • the compression chamber 139 is refueled in the angular section.
  • the compression chamber oil supply passage 155 By providing the compression chamber oil supply passage 155 so that the angle positions of the inlet 155a and the outlet 155b with respect to the crankshaft center are different, it is possible to determine a crank angle section in which oil flows into the inlet 155a. Thereby, the freedom degree of the position of the exit 155b increases. As a result, the outlet 155b of the compression chamber oil supply path 155 can be provided in the vicinity of the location where the refrigerant leaks.
  • the influence on the global environment can be suppressed by using a refrigerant having a low ozone layer depletion coefficient and a global warming coefficient.
  • a refrigerant having a low ozone layer depletion coefficient and a global warming coefficient by supplying oil to the compression chamber 139 after confining the refrigerant, re-expansion heating of the refrigerant is suppressed, and the refrigerant is heated by the refrigerating machine oil in the suction process (before the refrigerant is confined in the compression chamber). Is suppressed as compared with the case of supplying refrigeration oil. As a result, the decomposition of the refrigerant is suppressed.
  • the rotary compressor according to the first to third embodiments has been described above.
  • a single refrigerant of hydrofluoroolefin having a carbon double bond or a mixed refrigerant containing the hydrofluoroolefin is used.
  • a mixed refrigerant a refrigerant obtained by mixing hydrofluoroolefin and hydrofluorocarbon having no carbon double bond may be used.
  • HFO1234yf or HFO1234ze tetrafluoropropene
  • HFO1243zf trifluoropropene
  • HFC32 difluoromethane
  • HFO1234yf or HFO1234ze tetrafluoropropene
  • HFO1243zf trifluoropropene
  • HFC125 pentafluoroethane
  • HFO1234yf or HFO1234ze tetrafluoropropene
  • HFO1243zf trifluoropropene
  • HFC125 pentafluoroethane
  • HFC32 difluoromethane
  • the above mixed refrigerant is preferably a mixture of two or three components mixed so that the global warming potential is 5 or more and 750 or less, preferably 5 or more and 350 or less.
  • the refrigerating machine oil used in the rotary compressor according to the present invention includes (1) polyoxyalkylene glycols, (2) polyvinyl ethers, (3) poly (oxy) alkylene glycols or monoethers thereof and polyvinyl ethers. (4) Synthetic oils containing oxygenated compounds of polyol esters and polycarbonates, (5) Synthetic oils based on alkylbenzenes, or (6) Synthetic oils based on ⁇ -olefins Is preferred.
  • the rotary compressor has high reliability, High durability and high efficiency can be realized. Therefore, this invention is applicable also to uses, such as an air conditioner, a heat pump type water heater, a refrigerator-freezer, a dehumidifier, provided with a rotary compressor.

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

Abstract

L'invention concerne un compresseur caractérisé en ce que, du fait de l'utilisation d'un agent frigorigène comportant au moins une hydrofluorooléfine caractérisée par des doubles liaisons carbone, un faible facteur d'appauvrissement de la couche d'ozone et un faible potentiel de réchauffement planétaire, et de l'aménagement d'un premier circuit d'alimentation en huile de la chambre de compression qui alimente en huile de réfrigération une chambre (15) de compression dans laquelle est confiné l'agent frigorigène, il est possible de limiter l'effet sur l'environnement planétaire et également de limiter les hausses de la température de l'agent frigorigène, qui ont pour conséquence la re-dilatation et l'échauffement ainsi que l'alimentation en huile de réfrigération à une température élevée ; autrement dit, il est possible de limiter la décomposition de l'agent frigorigène.
PCT/JP2011/005395 2010-09-27 2011-09-26 Compresseur rotatif WO2012042825A1 (fr)

Priority Applications (3)

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US13/824,694 US20130189080A1 (en) 2010-09-27 2011-09-26 Rotary compressor
JP2012516405A JPWO2012042825A1 (ja) 2010-09-27 2011-09-26 回転式圧縮機
CN2011800466082A CN103154521A (zh) 2010-09-27 2011-09-26 旋转式压缩机

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JP2010-214877 2010-09-27
JP2010214877 2010-09-27

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CN104047849A (zh) * 2014-07-03 2014-09-17 湖南联力精密机械有限公司 润滑油路内置的涡旋空气压缩机
WO2017168672A1 (fr) * 2016-03-31 2017-10-05 三菱電機株式会社 Compresseur à volute et dispositif à cycle de réfrigération

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CN204126898U (zh) * 2013-06-27 2015-01-28 艾默生环境优化技术有限公司 压缩机
WO2016173319A1 (fr) 2015-04-30 2016-11-03 艾默生环境优化技术(苏州)有限公司 Compresseur à spirale

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JPS59185892A (ja) * 1983-04-05 1984-10-22 Toyoda Autom Loom Works Ltd スクロ−ル型圧縮機
JPH06167287A (ja) * 1992-12-01 1994-06-14 Hitachi Ltd ロータリ圧縮機
JPH06346878A (ja) * 1993-06-04 1994-12-20 Hitachi Ltd ロータリ圧縮機
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CN104047849B (zh) * 2014-07-03 2017-01-18 湖南联力精密机械有限公司 润滑油路内置的涡旋空气压缩机
WO2017168672A1 (fr) * 2016-03-31 2017-10-05 三菱電機株式会社 Compresseur à volute et dispositif à cycle de réfrigération
JPWO2017168672A1 (ja) * 2016-03-31 2018-11-01 三菱電機株式会社 スクロール圧縮機、および冷凍サイクル装置
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JPWO2012042825A1 (ja) 2014-02-03
CN103154521A (zh) 2013-06-12

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