WO2019044349A1 - Compresseur - Google Patents

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Publication number
WO2019044349A1
WO2019044349A1 PCT/JP2018/028953 JP2018028953W WO2019044349A1 WO 2019044349 A1 WO2019044349 A1 WO 2019044349A1 JP 2018028953 W JP2018028953 W JP 2018028953W WO 2019044349 A1 WO2019044349 A1 WO 2019044349A1
Authority
WO
WIPO (PCT)
Prior art keywords
insulating member
fixed scroll
heat insulating
discharge port
refrigerant
Prior art date
Application number
PCT/JP2018/028953
Other languages
English (en)
Japanese (ja)
Inventor
渡邊　健司
昭徳 福田
大輔 船越
秀人 岡
圭佑 野場
Original Assignee
パナソニックＩｐマネジメント株式会社
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Ｉｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Priority to US16/641,523 priority Critical patent/US20210156381A1/en
Priority to JP2019539105A priority patent/JPWO2019044349A1/ja
Priority to CN201880053178.9A priority patent/CN111033046A/zh
Publication of WO2019044349A1 publication Critical patent/WO2019044349A1/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
    • 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
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • 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
    • F04C29/06—Silencing
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers
    • 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
    • F04C29/06—Silencing
    • F04C29/068—Silencing the silencing means being arranged inside the pump housing

Definitions

  • the present disclosure relates to a cooling device such as a cooling and heating air conditioner and a refrigerator, and a compressor used for a heat pump water heater and the like.
  • a hermetic compressor used for a cooling device, a hot water supply device or the like plays a role of compressing the refrigerant gas returned from the refrigeration cycle by the compression mechanism and feeding it to the refrigeration cycle.
  • the refrigerant gas returned from the refrigeration cycle is supplied to the compression chamber formed in the compression mechanism section through the suction path. Thereafter, the refrigerant gas compressed to a high temperature and high pressure state is discharged from the compression mechanism into the closed container, and is sent from the discharge pipe provided in the closed container to the refrigeration cycle (see, for example, Patent Document 1) .
  • FIG. 5 is a cross-sectional view showing a compression mechanism portion of a conventional scroll compressor described in Patent Document 1. As shown in FIG.
  • the low-temperature low-pressure refrigerant gas is introduced to the suction chamber of the fixed scroll 102 through the suction pipe 101, and is compressed by the volume change of the compression chamber 103 to become a high-temperature high-pressure. Thereafter, the high-temperature and high-pressure refrigerant gas is discharged through the discharge port 104 at the upper portion of the fixed scroll 102 to the muffler space 106 constituted by the fixed scroll 102 and the muffler 105 covering the upper portion. It passes through the inside of 107 and is delivered from the discharge pipe 108 to the refrigeration cycle.
  • the low temperature refrigerant led to the suction chamber of the fixed scroll 102 is the highest temperature and high pressure refrigerant gas discharged to the muffler space 106 from the discharge port 104 above the fixed scroll 102. Of the heat of (eg, being heated).
  • the refrigerant gas expands when it is trapped in the compression chamber 103. Therefore, the circulation amount of the refrigerant gas is reduced.
  • the refrigerant gas in the process of compression in the compression chamber 103 also passes from the muffler space 106 through the fixed scroll 102, it is affected by the heat of the high temperature / high pressure refrigerant gas. Therefore, the refrigerant gas expands and the compression loss of the refrigerant increases.
  • the present disclosure has solved the above-described conventional problems, and an object thereof is to provide a highly efficient compressor by suppressing the decrease in the circulating amount of refrigerant and reducing the compression loss of the refrigerant.
  • the compressor of the present disclosure includes a fixed scroll and a orbiting scroll, a compression chamber formed between the fixed scroll and the orbiting scroll, and a suction chamber provided on an outer peripheral side of the stationary scroll, which constitute a compression mechanism portion.
  • a discharge port provided at a central portion of the scroll, a muffler provided to cover the discharge port at the upper portion of the fixed scroll, and a heat insulating member provided between the fixed scroll and the muffler.
  • the refrigerant gas sucked into the suction chamber is compressed by the orbiting scroll turning and the compression chamber moving while changing the volume, and then the refrigerant gas is discharged from the discharge port.
  • the refrigerant gas discharged from the discharge port is discharged into a muffler space formed by the muffler.
  • the heat insulating member includes a heat insulating member discharge port provided in a portion facing the discharge port, a reed valve provided on the surface of the heat insulating member opposite to the side facing the fixed scroll, and fixing of the heat insulating member And a recessed portion provided on the surface facing the scroll and provided in a region of 360 ° in the circumferential direction facing the suction chamber.
  • the high-temperature and high-pressure refrigerant gas compressed in the compression chamber is discharged from the heat-insulating member discharge port to the muffler space. Therefore, the high-temperature and high-pressure refrigerant gas discharged to the muffler space exerts the influence of heat from the muffler space to the suction chamber.
  • the heat insulating member provided between the fixed scroll and the muffler plays the role of a heat insulating layer.
  • the refrigerant gas and the oil in the refrigerant gas infiltrate into the recess provided in the heat insulating member and stay there, the recess plays a role of the second heat insulating layer.
  • this double thermal insulation layer suppresses the influence of heat from the muffler space through which the highest temperature and high pressure refrigerant passes to the suction chamber and compression chamber before the start of compression, which is the lowest temperature of the fixed scroll.
  • the recess is provided in an area of 360 ° in the circumferential direction of the surface of the heat insulating member facing the fixed scroll. Therefore, the influence of the heat from the muffler space is suppressed widely and effectively over substantially the entire suction chamber and the compression chamber connected thereto.
  • the heat insulation member suppresses the influence of heat from the high temperature refrigerant in the container space above the muffler space as well as the muffler space to the compression chamber.
  • the temperature rise of the refrigerant is strongly suppressed (for example, shut off), so that the decrease of the refrigerant circulation amount is prevented, and the increase of the compression loss of the refrigerant is suppressed.
  • a highly efficient compressor can be realized.
  • FIG. 1 is a figure showing an example of the section which looked at the compressor in the 1st embodiment of this indication from the side.
  • FIG. 2 is a view showing an example of the main part of the same compressor.
  • FIG. 3 is a plan view showing an example of the configuration of the compressor.
  • FIG. 4 is a view showing an example of a heat insulating member of the same compressor.
  • FIG. 5 is a view showing an example of a cross section of the scroll compressor of the comparative example as viewed from the side.
  • the compressor according to the first aspect of the present disclosure includes a fixed scroll and a orbiting scroll, a compression chamber formed between the fixed scroll and the orbiting scroll, and a compression chamber that constitutes a compression mechanism, and is provided on the outer peripheral side of the stationary scroll.
  • a suction chamber, a discharge port provided at a central portion of the fixed scroll, a muffler provided to cover the discharge port at the upper portion of the fixed scroll, and a heat insulating member provided between the fixed scroll and the muffler Prepare.
  • the refrigerant gas sucked into the suction chamber is compressed by the orbiting scroll turning and the compression chamber moving while changing the volume, and then the refrigerant gas is discharged from the discharge port.
  • the refrigerant gas discharged from the discharge port is discharged into a muffler space formed by the muffler.
  • the heat insulating member includes a heat insulating member discharge port provided in a portion facing the discharge port, a reed valve provided on the side of the heat insulating member opposite to the side facing the fixed scroll, and the heat insulating member. And a recessed portion provided on the surface facing the fixed scroll and provided in a region of 360 ° in the circumferential direction facing the suction chamber.
  • the high-temperature and high-pressure refrigerant gas compressed in the compression chamber is discharged from the heat-insulating member discharge port to the muffler space. Therefore, the high-temperature and high-pressure refrigerant gas discharged to the muffler space exerts the influence of heat from the muffler space to the suction chamber.
  • the heat insulating member provided between the fixed scroll and the muffler plays the role of a heat insulating layer.
  • the refrigerant gas and the oil in the refrigerant gas infiltrate into the recess provided in the heat insulating member and stay there, the recess plays a role of the second heat insulating layer.
  • this double thermal insulation layer suppresses the influence of heat from the muffler space through which the highest temperature and high pressure refrigerant passes to the suction chamber and compression chamber before the start of compression, which is the lowest temperature of the fixed scroll.
  • the recess is provided in an area of 360 ° in the circumferential direction of the surface of the heat insulating member facing the fixed scroll. Therefore, the influence of the heat from the muffler space is suppressed widely and effectively over substantially the entire suction chamber and the compression chamber connected thereto.
  • the heat insulation member suppresses the influence of heat from the high temperature refrigerant in the container space above the muffler space as well as the muffler space to the compression chamber. Therefore, by suppressing the temperature rise of the refrigerant strongly, the decrease of the circulating amount of the refrigerant is prevented, and the increase of the compression loss of the refrigerant is suppressed. Thereby, a highly efficient compressor can be realized.
  • At least one of a heat insulating member, a rim portion of a heat insulating member discharge port provided corresponding to the discharge port, and an opening edge portion of a recess is a fixed scroll
  • the configuration may be a convex shape that protrudes most toward the side.
  • the convex portion of the heat insulating member is in pressure contact with the upper surface of the fixed scroll. Therefore, the space between the discharge port and the recess is strongly shut off. As a result, a circulation action is generated between the high temperature and high pressure refrigerant in the discharge port and the refrigerant in the recess, and the heat insulating effect by the recess is prevented from being reduced. Thereby, the high heat insulation effect by a recessed part is maintained. Therefore, the effect of preventing the decrease in the refrigerant circulation amount due to the temperature rise of the refrigerant and the effect of suppressing the increase of the compression loss of the refrigerant become higher. Therefore, a highly efficient compressor can be realized.
  • the third aspect of the present disclosure may be configured such that a portion in the vicinity of the heat-insulating member discharge port of the heat-insulating member is bolted to the fixed scroll.
  • the rim portion of the heat insulating member discharge port closely contacts the fixed scroll. Therefore, the airtightness between the discharge port and the recess where the refrigerant of the highest temperature and high temperature is discharged is improved.
  • the heat insulating effect of the concave portion is prevented from being reduced by the circulation of the high-temperature and high-pressure refrigerant in the discharge port and the refrigerant in the concave portion. Therefore, the high heat insulation effect by the recess is maintained. Therefore, the effect of preventing the decrease in the refrigerant circulation amount due to the temperature rise of the refrigerant and the effect of suppressing the increase in the compression loss of the refrigerant become higher. Therefore, a highly efficient compressor can be realized.
  • the heat insulating member may be formed of a porous material such as a sintered metal.
  • the heat insulating member has a low thermal conductivity. Therefore, the heat insulating effect of the heat insulating member itself is enhanced. Thereby, the influence of the heat from the high-temperature and high-pressure refrigerant in the muffler space and the influence of the heat from the refrigerant in the container space above the muffler space are more strongly suppressed. Therefore, the decrease in the amount of circulation due to the temperature rise of the refrigerant is more effectively suppressed, and the increase in the compression loss of the refrigerant is suppressed. Thereby, a highly efficient compressor can be realized.
  • the heat insulating member may have a configuration formed by laminating a plurality of plates.
  • the thermal insulation member reduces the heat conduction between the plates. Therefore, the heat insulating effect of the heat insulating member itself is enhanced. Thereby, the influence of the heat from the high-temperature and high-pressure refrigerant in the muffler space and the influence of the heat from the refrigerant in the container space above the muffler space are more strongly suppressed. Furthermore, when the plate thickness of the plate facing the fixed scroll among the plurality of plates is thin, the plate facing the fixed scroll has high adhesion to the upper surface of the fixed scroll. Therefore, the circulation of the refrigerant in the recess and the high-temperature and high-pressure refrigerant in the discharge port is more reliably prevented. Therefore, the decrease in the amount of circulation due to the temperature rise of the refrigerant is more effectively suppressed, and the increase in the compression loss of the refrigerant is suppressed. Thereby, a highly efficient compressor can be realized.
  • the plurality of plates may include a plate having a recess.
  • the member for heat insulation which has a recessed part is formed, without cutting etc. Furthermore, when the plate thickness of the plate facing the fixed scroll among the plurality of plates is thin, the adhesion of the plate having the recess to the fixed scroll becomes high. Therefore, the circulation of the refrigerant in the recess and the high temperature and high pressure refrigerant in the discharge port is strongly prevented. Therefore, it is possible to more efficiently prevent the decrease of the circulating amount of the refrigerant due to the temperature rise and to suppress the increase of the compression loss of the refrigerant. Thereby, a highly efficient compressor can be realized.
  • FIG. 2 is a view showing an example of the main part of the compressor 50. As shown in FIG. The part of (a) of FIG. 2 is a cross-sectional view, and the part of (b) of FIG. 2 is a detailed view showing an example of the configuration of the heat insulating member and the fixed scroll.
  • FIG. 3 is a plan view showing an example of the configuration of the compressor 50. As shown in FIG. The part of (a) of FIG. 3 is a top view which shows an example of the member 24 for heat insulation of the compressor 50. FIG. The part of (b) of FIG.
  • FIG. 3 is a top view which shows an example of the compression chamber 9 of the same compressor 50.
  • FIG. 4 is a view showing an example of the heat insulating member 24 of the compressor 50.
  • FIG. Part (a) of FIG. 4 is a plan view.
  • the part of (b) of FIG. 4 is a figure which shows an example of a cross section.
  • the part of (c) of FIG. 4 is a bottom view.
  • the compressor 50 includes a sealed container 1, a compression mechanism unit 2 disposed inside the sealed container 1, and a motor unit 3 disposed inside the sealed container 1. Equipped with
  • the main bearing member 4 is fixed in the sealed container 1 by welding or shrink fitting.
  • the shaft 5 is pivotally supported by the main bearing member 4.
  • the fixed scroll 6 is bolted onto the main bearing member 4. Between the fixed scroll 6 and the main bearing member 4, the orbiting scroll 7 meshing with the fixed scroll 6 is sandwiched, and the scroll-type compression mechanism unit 2 is configured.
  • a rotation restraint mechanism 8 including an Oldham ring or the like is provided which guides the orbiting scroll 7 so that it orbits circularly while preventing the rotation of the orbiting scroll 7.
  • the rotation restraint mechanism 8 causes the orbiting scroll 7 to make a circular orbit motion by causing the orbiting scroll 7 to be eccentrically driven by the eccentric shaft portion 5 a at the upper end of the shaft 5.
  • the compression chamber 9 formed between the fixed scroll 6 and the orbiting scroll 7 moves from the outer peripheral side toward the central portion while reducing the volume of the compression chamber 9.
  • the suction pipe 10 connected to the refrigeration cycle outside the closed container 1 is provided on the fixed scroll between the suction pipe 10 and the compression chamber 9 and passes through the suction chamber 11 which is always suction pressure.
  • Refrigerant gas is drawn.
  • the sucked refrigerant gas is compressed after being confined in the compression chamber 9.
  • the refrigerant gas that has reached the predetermined pressure is discharged from the discharge port 12 at the central portion of the fixed scroll 6 by pushing the reed valve 13 open.
  • the refrigerant gas discharged by pushing open the reed valve 13 is discharged to the muffler space 14 and is delivered from the discharge pipe 17 to the refrigeration cycle via the in-container space 15 of the closed container 1.
  • the muffler space 14 is formed by the muffler 16 whose periphery is fixed to the fixed scroll 6 and covers the discharge port 12 and the reed valve 13.
  • a pump 18 is provided at the lower end of the shaft 5 for driving the orbiting scroll 7 to pivot.
  • the inlet of the pump 18 is arranged to be present in the oil reservoir 19.
  • the pump 18 operates simultaneously with the scroll compressor. Therefore, the pump 18 reliably sucks up the oil in the oil reservoir 19 provided at the bottom of the closed vessel 1 regardless of the pressure condition and the operating speed.
  • the oil sucked up by the pump 18 is supplied to the compression mechanism 2 through an oil supply hole 20 passing through the shaft 5.
  • foreign matter is prevented from being mixed with the compression mechanism 2 by removing foreign matter from the oil with an oil filter or the like. Therefore, the reliability of the compression mechanism 2 can be improved.
  • the pressure of the oil introduced to the compression mechanism 2 is substantially equal to the discharge pressure of the scroll compressor.
  • the pressure of the oil introduced to the compression mechanism 2 also serves as a back pressure source for the orbiting scroll 7.
  • the orbiting scroll 7 stably exerts the predetermined compression function without leaving the fixed scroll 6 or coming into contact with it.
  • a part of the oil is determined by the supply pressure and the weight thereof so as to obtain a relief area, so that the fitting portion between the eccentric shaft 5a and the orbiting scroll 7 and the bearing between the shaft 5 and the main bearing member 4 After entering into 21 and lubricating each part, it falls and returns to the oil reservoir 19.
  • Another part of the oil supplied from the oil supply hole 20 to the high pressure area 22 is formed in the orbiting scroll 7 and passes through the path 7a having one open end in the high pressure area 22 so that the rotation restraint mechanism 8 is positioned.
  • the oil that has infiltrated plays a role of applying a back pressure to the orbiting scroll 7 in the back pressure chamber 23 in addition to lubricating the thrust sliding portion and the sliding portion of the rotation restraint mechanism 8.
  • the refrigerant gas compressed by the compression mechanism portion 2 is sucked into the compression chamber 9 between the fixed scroll 6 and the orbiting scroll 7 through the suction chamber 11 provided in the fixed scroll 6 as described above, and compressed. Be done. However, the refrigerant gas compressed by the compression mechanism portion 2 is affected by the heat of the highest temperature and high pressure refrigerant gas discharged to the muffler space 14 from the discharge port 12 of the fixed scroll 6.
  • a plate-like heat insulating member 24 is provided between the fixed scroll 6 and the muffler 16, and the heat insulating member 24 is positioned between the muffler space 14 and the suction chamber 11. Be done. Further, the heat insulating member 24 is provided with a recess 27 (see FIGS. 3 and 4) in a region (range) of 360 ° in the circumferential direction facing the suction chamber 11 on the surface on the fixed scroll 6 side. ing.
  • the region of 360 ° in the circumferential direction is 360 ° in the circumferential direction around the substantially central portion when the surface on the fixed scroll 6 side of the heat insulating member 24 is viewed from the front, That is, it means that the recessed part 27 is formed over the entire circumference.
  • the recess 27 includes a substantially annular portion and a portion protruding from the portion, but the present disclosure is not limited to this example.
  • the recess 27 is in communication with the in-container space 15 (see FIG. 2) via the recess 27a.
  • the member discharge port 25 for heat insulation is formed in the position facing the discharge port 12 of the fixed scroll 6 of the member 24 for heat insulation.
  • a reed valve 13 for opening and closing the heat-dissipating member discharge port 25 is provided on the surface of the heat-insulating member 24 opposite to the surface facing the fixed scroll 6.
  • the heat insulating member 24 is fastened together with the muffler 16 and fixed to the fixed scroll 6 by passing a bolt (not shown) through a hole 26 provided in the outer peripheral portion.
  • the high-temperature and high-pressure refrigerant gas compressed in the compression chamber 9 is discharged from the heat-insulating member discharge port 25 of the heat-insulating member 24 to the muffler space 14 .
  • the high-temperature and high-pressure refrigerant gas discharged to the muffler space 14 affects the heat from the muffler space 14 to the suction chamber 11.
  • the heat insulating member 24 is located between the suction chamber 11 of the fixed scroll 6 and the muffler space 14 and plays a role of a heat insulating layer. As a result, the influence of heat on the suction chamber 11 of the high-temperature and high-pressure refrigerant in the muffler space 14 is suppressed.
  • a recess 27 is formed in the heat insulating member 24.
  • the recess 27 is at a lower temperature than the highest temperature and pressure refrigerant in the muffler space 14. Therefore, the accumulation of the refrigerant and the oil in the recess 27 plays a role of the second heat insulating layer. Thereby, a strong heat insulating effect is exhibited by combining the first heat insulating function by the heat insulating member 24 and the second heat insulating function in the recess 27.
  • the recess 27 is provided over an area of 360 ° in the circumferential direction on the surface of the heat insulating member 24 facing the fixed scroll 6. Therefore, the influence of the heat from the muffler space 14 is suppressed widely and effectively over the suction chamber 11 and substantially the entire compression chamber 9 connected to the suction chamber 11.
  • the heat insulating member 24 suppresses the influence of heat from the high temperature refrigerant on the fixed scroll 6 in the container space 15 above the muffler space as well as the muffler space 14.
  • the temperature of the fixed scroll 6 itself is also kept low. From this point as well, the decrease of the refrigerant circulation amount due to the increase of the refrigerant temperature is prevented, the volumetric efficiency is improved, and the increase of the compression loss of the refrigerant is suppressed. Thereby, a highly efficient compressor can be realized.
  • the heat insulating member 24 is formed of a sintered metal. Therefore, the rise of the refrigerant temperature is efficiently suppressed.
  • the sintered metal has low thermal conductivity and has a large number of micro-spaces. Since the sintered metal has high thermal insulation, the heat insulating member 24 made of sintered metal can efficiently suppress the influence of heat from the high temperature refrigerant in the muffler space 14 and the container space 15.
  • the heat insulating member 24 By forming the heat insulating member 24 of a sintered metal, the heat insulating effect of the heat insulating member 24 is enhanced. Therefore, the rise of the refrigerant temperature is more efficiently suppressed, the decrease of the refrigerant circulation amount is prevented, and the increase of the compression loss of the refrigerant is suppressed. Thereby, a highly efficient compressor can be realized.
  • the material of the heat insulating member 24 is not limited to a porous material such as a sintered metal.
  • any material such as a resin material may be used.
  • the heat insulating member 24 may be a single sheet or may be configured by laminating a plurality of plates.
  • the laminated type heat insulating member 24 configured by laminating a plurality of plates heat conduction between the plates is strongly suppressed. Therefore, the heat insulation effect is improved and effective.
  • the plate thickness of the plate facing the fixed scroll 6 is thin, for example, to about 1 mm among a plurality of plates constituting the heat insulating member 24, to the upper surface of the fixed scroll 6 of the plate facing the fixed scroll 6 Adhesion is improved.
  • the circulation of the refrigerant in the recess 27 and the high-temperature and high-pressure refrigerant in the discharge port 12 is more reliably prevented. Therefore, the heat insulating effect by the recessed part 27 is exhibited more effectively.
  • the heat insulating member 24 is a member having a predetermined shape in advance.
  • the heat insulating member 24 may be formed, for example, by injection molding between the fixed scroll 6 and the muffler space 14.
  • the heat insulating member 24 is fastened together with the muffler 16 and fixed to the fixed scroll 6 through a bolt in a hole 26 provided in the outer peripheral portion thereof.
  • the edge portion of the heat insulating member discharge port 25 and the fixed scroll 6 are in close contact with each other, and the space between the discharge port 12 and the recess 27 is strongly blocked. Therefore, the airtightness between the discharge port 12 from which the highest temperature and high pressure refrigerant is discharged and the recess 27 is improved. Therefore, the reduction of the heat insulation effect of the recess 27 due to the circulation of the high temperature and high pressure refrigerant discharged from the discharge port 12 of the fixed scroll 6 and the refrigerant in the recess 27 is prevented.
  • the rim portion of the heat insulating member discharge port 25 provided corresponding to the discharge port 12 of the fixed scroll 6 has a convex shape 28 that most protrudes toward the fixed scroll ( See Figure 2). Therefore, the convex shape 28 is in pressure contact with the upper surface of the fixed scroll 6. Therefore, the space between the discharge port 12 and the recess 27 is strongly shut off. Therefore, the reduction of the heat insulating action by the refrigerant and oil in the recess 27 due to the circulation of the high temperature and high pressure refrigerant in the discharge port 12 and the refrigerant in the recess 27 is more reliably prevented. Thereby, the heat insulation effect by the recessed part 27 becomes favorable.
  • the convex shape 28 may be, for example, not an edge portion of the heat-insulating member discharge port 25 but an opening edge portion of the concave portion 27 on the upper surface side of the fixed scroll. That is, at least one of the edge portion of the heat-insulating member discharge port 25 and the opening edge portion on the fixed scroll upper surface side of the recess 27 may have a convex shape 28. Then, by combining the provision of the convex shape 28 and the use of the bolt fixing position as the edge portion of the heat insulating member discharge port 25, the high temperature and high pressure refrigerant can be more reliably intruded into the recess 27. It is prevented and effective.
  • the heat insulating member 24 by laminating a plate provided with the recess 27 and a plate without the recess, the recess 27 is formed without cutting. Therefore, the heat insulating member 24 is provided inexpensively.
  • a plurality of recesses 27 are formed in the stacking direction by alternately laminating a plurality of plates provided with the recesses 27 and a plate without the recesses. Thereby, the heat insulation effect by the recessed part 27 becomes still higher.
  • the influence of heat from the muffler space 14 and the container space 15 to the suction chamber 11 and the compression chamber 9 is further suppressed by forming the heat insulating layer on the heat insulating member 24 and the muffler 16 itself.
  • the heat insulating layer include, but are not limited to, a resin coating, or a coating process including hollow beads of vacuum or air inside, and the like.
  • the rise of the refrigerant temperature is suppressed, the decrease of the refrigerant circulation amount is prevented, and the increase of the compression loss of the refrigerant is suppressed.
  • a highly efficient compressor can be realized.
  • the present disclosure is not limited to the form of this embodiment. That is, the embodiment disclosed this time should be considered as illustrative in all points and not restrictive.
  • the scope of the present disclosure is indicated not by the above description but by the scope of the claims, and is intended to include all modifications within the meaning and scope equivalent to the scope of the claims.
  • a highly efficient compressor is realized by suppressing the temperature rise of the refrigerant, preventing the decrease of the circulating amount of the refrigerant, and suppressing the increase of the compression loss of the refrigerant. Can. Therefore, it can be widely used for various apparatuses using a refrigeration cycle.

Landscapes

  • 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 comprenant : une volute fixe (6) et une volute tournante (7), qui constituent une section de mécanisme de compression (2) ; une chambre de compression (9) ; une chambre d'admission (11) ; un orifice de décharge (12) ; un silencieux (16) ; et un élément d'isolation thermique (24) disposé entre la volute fixe (6) et le silencieux (16). Après qu'un gaz frigorigène introduit dans la chambre d'admission (11) a été comprimé en raison de la rotation de la volute tournante (7) et du déplacement de la chambre de compression (9) tout en changeant la capacité, le gaz frigorigène est évacué par l'orifice de décharge (12). Le gaz frigorigène évacué par l'orifice de décharge (12) est évacué vers un espace de silencieux (14) formé par le silencieux (16). L'élément d'isolation thermique (24) comporte un orifice de décharge d'élément d'isolation thermique (25), une vanne de dérivation (13) et un évidement (27).
PCT/JP2018/028953 2017-09-04 2018-08-02 Compresseur WO2019044349A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US16/641,523 US20210156381A1 (en) 2017-09-04 2018-08-02 Compressor
JP2019539105A JPWO2019044349A1 (ja) 2017-09-04 2018-08-02 圧縮機
CN201880053178.9A CN111033046A (zh) 2017-09-04 2018-08-02 压缩机

Applications Claiming Priority (2)

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JP2017-169078 2017-09-04
JP2017169078 2017-09-04

Publications (1)

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WO2019044349A1 true WO2019044349A1 (fr) 2019-03-07

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CN (1) CN111033046A (fr)
WO (1) WO2019044349A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021076072A (ja) * 2019-11-11 2021-05-20 パナソニックＩｐマネジメント株式会社 スクロール圧縮機

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7117608B2 (ja) 2017-09-04 2022-08-15 パナソニックＩｐマネジメント株式会社 圧縮機

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6195997U (fr) * 1984-11-30 1986-06-20
JPS62265487A (ja) * 1986-05-09 1987-11-18 Mitsubishi Electric Corp スクロ−ル圧縮機
JPH0533784A (ja) * 1991-07-31 1993-02-09 Kubota Corp スクロール圧縮機
JP2005201114A (ja) * 2004-01-14 2005-07-28 Toyota Industries Corp 圧縮機
WO2014002456A1 (fr) * 2012-06-26 2014-01-03 パナソニック株式会社 Compresseur rotatif
JP2016094824A (ja) * 2014-11-12 2016-05-26 パナソニックＩｐマネジメント株式会社 圧縮機
JP2017075538A (ja) * 2015-10-13 2017-04-20 三菱重工業株式会社 ロータリ圧縮機、ロータリ圧縮機の製造方法

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57206786A (en) * 1981-06-12 1982-12-18 Hitachi Ltd Scroll compressor
JPH10220382A (ja) * 1997-02-05 1998-08-18 Sanyo Electric Co Ltd スクロール圧縮機
JP5255157B2 (ja) * 2011-03-18 2013-08-07 パナソニック株式会社 圧縮機
CN206035817U (zh) * 2016-06-08 2017-03-22 上海益科汽车科技有限公司 一种滑片式空气压缩机总成

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6195997U (fr) * 1984-11-30 1986-06-20
JPS62265487A (ja) * 1986-05-09 1987-11-18 Mitsubishi Electric Corp スクロ−ル圧縮機
JPH0533784A (ja) * 1991-07-31 1993-02-09 Kubota Corp スクロール圧縮機
JP2005201114A (ja) * 2004-01-14 2005-07-28 Toyota Industries Corp 圧縮機
WO2014002456A1 (fr) * 2012-06-26 2014-01-03 パナソニック株式会社 Compresseur rotatif
JP2016094824A (ja) * 2014-11-12 2016-05-26 パナソニックＩｐマネジメント株式会社 圧縮機
JP2017075538A (ja) * 2015-10-13 2017-04-20 三菱重工業株式会社 ロータリ圧縮機、ロータリ圧縮機の製造方法

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021076072A (ja) * 2019-11-11 2021-05-20 パナソニックＩｐマネジメント株式会社 スクロール圧縮機
JP7345135B2 (ja) 2019-11-11 2023-09-15 パナソニックＩｐマネジメント株式会社 スクロール圧縮機

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US20210156381A1 (en) 2021-05-27
JPWO2019044349A1 (ja) 2020-10-01

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