WO2015177851A1 - Compresseur à spirales - Google Patents

Compresseur à spirales Download PDF

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Publication number
WO2015177851A1
WO2015177851A1 PCT/JP2014/063265 JP2014063265W WO2015177851A1 WO 2015177851 A1 WO2015177851 A1 WO 2015177851A1 JP 2014063265 W JP2014063265 W JP 2014063265W WO 2015177851 A1 WO2015177851 A1 WO 2015177851A1
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WO
WIPO (PCT)
Prior art keywords
oil
scroll
oil supply
orbiting scroll
supply hole
Prior art date
Application number
PCT/JP2014/063265
Other languages
English (en)
Japanese (ja)
Inventor
浩平 達脇
角田　昌之
石園　文彦
哲仁 ▲高▼井
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2014/063265 priority Critical patent/WO2015177851A1/fr
Priority to JP2016520830A priority patent/JPWO2015177851A1/ja
Publication of WO2015177851A1 publication Critical patent/WO2015177851A1/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

Definitions

  • the present invention relates to a scroll compressor used as a component of a refrigeration cycle employed in, for example, an air conditioner or a refrigeration apparatus.
  • the swing scroll and the fixed scroll each have a substantially symmetrical spiral body, and the swing scroll and the fixed scroll are housed in a frame having a refrigerant inlet for sucking refrigerant. ing.
  • the swinging scroll in the frame performs a swinging motion, whereby the refrigerant sucked from the refrigerant suction port is compressed.
  • the oscillating scroll oscillates while sliding on the thrust bearing surface.
  • a thrust plate is disposed between the oscillating scroll and the frame. Has been.
  • Patent Document 1 In such a scroll compressor, in order to reduce the sliding resistance of each sliding part, lubricating oil flows through each sliding part (for example, refer to Patent Document 1).
  • the thrust bearing surface of an orbiting scroll is used for the purpose of improving the slidability between the scrolls of the orbiting scroll and the fixed scroll and reducing the leakage loss of refrigerant by improving the sealing performance during low-speed rotation.
  • An oil supply hole is provided, and the thrust plate is provided with an oil supply hole, and a scroll compressor that secures the required amount of oil supplied to the spiral by intermittently supplying oil from the oil supply hole to the oil supply hole. It is disclosed.
  • Patent Document 1 If the configuration of Patent Document 1 is adopted, a required amount of oil can be secured when the scroll compressor rotates at a low speed. However, the amount of oil supply during high-speed rotation becomes excessive, leading to a decrease in refrigeration capacity and performance as the amount of oil rises.
  • the present invention has been made to solve the above-described problems, and provides a scroll compressor that can supply lubricating oil to a compression mechanism with an appropriate amount of oil supply not only at low speed but also at high speed. It is intended to provide.
  • the scroll compressor according to the present invention is capable of swinging a fixed scroll having a fixed-side spiral body, a swing scroll having a swing-side spiral body combined with the fixed-side spiral body of the fixed scroll, and a lower surface of the swing scroll.
  • a compression chamber is formed between the fixed scroll and the orbiting scroll to suck the working fluid, and includes a supporting thrust plate, an orbiting scroll and a thrust plate.
  • the scroll compressor is provided on a sliding surface that slides with the thrust plate, and includes an oil supply groove that is supplied with lubricating oil. The thrust plate slides with the swing scroll.
  • the oil supply groove is formed so as to communicate with the compression chamber from the surface to be Lubricating oil that has passed through the oil circulation portion when it is positioned on the oil supply hole, and is connected to the oil circulation portion extending from the oil inflow portion to the rotation direction of the orbiting scroll and the other side of the oil circulation portion. Is provided with an oil outflow portion for allowing the oil to flow out to the oil supply hole side.
  • the oil circulation portion extending in the rotation direction of the orbiting scroll is formed between the oil inflow portion and the oil outflow portion in the oil supply groove. Since the movement of the lubricating oil in the circulation section is restricted, the amount of oil rising can be suppressed by preventing the increase in the amount of oil supply at the time of high-speed rotation, while ensuring the required amount of oil supply at the low-speed rotation. In addition, the refrigerating capacity and performance can be improved.
  • FIG. 1 is a longitudinal sectional view showing a cross-sectional configuration example of a scroll compressor according to Embodiment 1 of the present invention.
  • the scroll compressor 1 will be described with reference to FIG.
  • the relationship of the size of each component may be different from the actual one.
  • a scroll compressor 1 in FIG. 1 sucks refrigerant compressed in a refrigeration cycle, compresses it and discharges it as a high-temperature and high-pressure state. It becomes one of the components of the refrigerating cycle used for various industrial machines, such as a container.
  • the scroll compressor 1 includes a sealed container 2, a fixed scroll 3, a swing scroll 4, a frame 5, a thrust plate 6, and the like. Further, the scroll compressor 1 includes a rotation drive unit 10 including a motor and the like housed in the sealed container 2.
  • the scroll compressor 1 is an example of a so-called vertical scroll compressor in which the fixed scroll 3 and the swing scroll 4 are disposed on the upper side in the sealed container 2 and the rotation driving unit 10 is disposed on the lower side.
  • the sealed container 2 forms a sealed space inside, and has a center shell 2a, an upper shell 2b provided at the upper part of the center shell 2a, and a lower shell 2c provided at the lower part of the center shell 2a. ing.
  • a suction pipe 2d for sucking a working fluid such as a refrigerant gas to be compressed is connected to the center shell 2a.
  • a discharge pipe 2e for discharging a working fluid such as a compressed refrigerant gas is connected to the upper shell 2b.
  • the inside of the center shell 2a is a low pressure chamber 2l, and the inside of the upper shell 2b is a high pressure chamber 2h.
  • a frame 5 is fixed to the upper side of the center shell 2a, and a subframe 9 that holds the main shaft 8 is fixed to the lower side.
  • the lower shell 2c is an oil sump for storing lubricating oil.
  • the fixed scroll 3 includes a fixed side base plate 3a and a fixed side spiral body 3b which is a spiral projection provided on one surface of the fixed side base plate 3a.
  • the fixed side base plate 3a is fixed to the upper side of the frame 5 with a bolt or the like, and a discharge port 3c for discharging a working fluid such as a compressed refrigerant gas is formed in the center of the fixed side base plate 3a.
  • a discharge valve 16 is provided on the discharge port 3c to prevent the refrigerant from flowing backward from the high pressure chamber 2h to the discharge port 3c.
  • the orbiting scroll 4 includes an orbiting side base plate 4a and an orbiting side spiral body 4b that is a spiral projection provided on one surface of the orbiting side base plate 4a.
  • the swing side base plate 4a is supported in the frame 5 so as to be swingable. That is, the other surface of the orbiting scroll 4 acts as a thrust bearing surface 4c that slides on the frame 5, and a load generated during operation is supported on the frame 5 via the thrust bearing surface 4c.
  • the swing-side spiral body 4b has substantially the same shape as the fixed-side spiral body 3b, and the swing-side spiral body 4b and the fixed-side spiral body 3b are combined with each other in combination with the fixed-side spiral body 3b. In this state, it is stored in the frame 5.
  • the orbiting scroll 4 has a hollow cylindrical boss 4d at the center of the other surface (the thrust bearing surface 4c side). An eccentric shaft portion 8a provided at the upper end of the main shaft 8 is inserted into the boss portion 4d. Then, the orbiting scroll 4 performs a revolving motion with respect to the fixed scroll 3 when the main shaft 8 rotates.
  • the fixed scroll 3 and the orbiting scroll 4 include a fixed-side spiral body 3b and an orbiting-side spiral body 4b in order to reduce refrigerant leakage from the front end surfaces of the fixed-side spiral body 3b and the swing-side spiral body 4b. Seals 25 and 26 are provided on the front end surfaces, respectively.
  • the frame 5 accommodates the swing scroll 4 and the fixed scroll 3 and is fixed to the upper part of the sealed container 2.
  • the frame 5 is provided with a refrigerant suction port through which the refrigerant sucked from the suction pipe 2d flows.
  • the frame 5 has a main bearing 20 that rotatably supports the upper portion of the main shaft 8.
  • the thrust plate 6 is provided between the frame 5 and the thrust bearing surface 4c of the orbiting scroll 4, and has, for example, an annular shape and a hole into which the boss portion 4d is inserted (see FIG. 2).
  • the thrust plate 6 improves the slidability of the thrust bearing surface 4 c when the orbiting scroll 4 revolves around the frame 5, and the orbiting scroll 4 is axially moved to the frame 5 via the thrust plate 6. It is in a state supported by.
  • the Oldham ring 7 is disposed between the orbiting scroll 4 and the frame 5 and transmits the rotational force of the main shaft 8 to the orbiting scroll 4 while restricting the rotation of the orbiting scroll 4.
  • the Oldham ring 7 has a pair of first Oldham keys 7 a protruding to the side facing the rocking scroll 4 and a pair of second Oldham keys 7 b protruding to the side facing the frame 5.
  • the first Oldham key 7a is fitted on the swing scroll 4 side
  • the second Oldham key 7b is fitted on the frame 5 side.
  • the thrust bearing surface 4c of the orbiting scroll 4 is provided with a first Oldham key groove 4e (see FIG. 3) extending in the radial direction for inserting the first Oldham key 7a.
  • a second Oldham key groove 5a extending in the radial direction for inserting the second Oldham key 7b is formed on the frame 5 side.
  • the first Oldham key groove 4e and the second Oldham key groove 5a are formed to extend in the radial direction, for example, at positions shifted in phase by 90 °.
  • the first Oldham key 7a and the second Oldham key 7b are provided, for example, at positions that are 90 ° out of phase.
  • the first Oldham key 7a is fitted to the first Oldham key groove 4e so as to be movable in the radial direction
  • the second Oldham key 7b is fitted to the second Oldham key groove 5a so as to be movable in the radial direction. Then, the first Oldham key 7a and the second Oldham key 7b advance and retreat in the first Oldham key groove 4e and the second Oldham key groove 5a, respectively, and the rotational force of the rotary drive unit 10 is revolved while restricting the rotational movement of the orbiting scroll 4. Is transmitted to the oscillating scroll 4.
  • the main shaft 8 is rotatably supported by a main bearing 20 provided on the frame 5 in the sealed container 2, and a lower portion of the main shaft 8 is rotatably supported by a sub bearing 21.
  • the sub-bearing 21 is press-fitted and fixed in a bearing housing portion formed in the center portion of the sub-frame 9 provided at the lower part of the sealed container 2.
  • An eccentric shaft portion 8a is attached to the upper end of the main shaft 8 in a state of being eccentric with respect to the main shaft 8.
  • a boss portion 4d of the orbiting scroll 4 is provided on the eccentric shaft portion 8a so as to be capable of revolving.
  • the subframe 9 is provided with a positive displacement oil pump 15.
  • the oil pump 15 sucks the lubricating oil stored in the lower shell 2 c and sends it to each sliding part via an oil supply path 8 b formed inside the main shaft 8.
  • An oil supply chamber 31 that is a space communicating with the oil supply path 8 b is formed between the outer peripheral side of the boss portion 4 d of the rocking scroll 4 and the frame 5, and the oil supply path 31 includes an oil supply path. Lubricating oil supplied from 8b is supplied.
  • the oil supply chamber 31 communicates with the first Oldham key groove 4e of the orbiting scroll 4, and the lubricating oil in the oil supply chamber 31 is supplied to the first Oldham key groove 4e.
  • the main shaft 8 is provided with a first balance weight 13 and a second balance weight 14 for canceling an imbalance caused by the swing scroll 4 swinging.
  • the first balance weight 13 is fixed to the upper portion of the main shaft 8 by shrink fitting, and the second balance weight 14 is fixed to the lower portion of the main shaft 8 integrally with the rotor 12.
  • the rotation drive unit 10 is made of, for example, a motor, and includes a stator 11 fixed to the sealed container 2 and a rotor 12 fixed to the main shaft 8.
  • the stator 11 and the rotor 12 are disposed, for example, below the first balance weight 13.
  • the stator 11 is formed by winding a coil, for example, and is fixed by shrink fitting to the center shell 2a. Electric power is supplied to the stator 11 via a power supply terminal 19 provided in the center shell 2a.
  • the rotor 12 has, for example, a permanent magnet and is shrink-fitted and fixed to the main shaft 8. Then, the energization of the stator 11 is started, so that the rotor 12 and the main shaft 8 are rotated.
  • a working fluid such as refrigerant gas flows into the sealed container 2 through the suction pipe 2d.
  • a part of the working fluid such as the refrigerant gas flows into the compression chamber 30 and the compression process is started.
  • the revolving motion of the orbiting scroll 4 causes the compression chamber 30 to move to the center of the orbiting scroll 4 to reduce its volume, and the refrigerant gas sucked into the compression chamber 30 is compressed.
  • the compressed refrigerant passes through the discharge port 3c of the fixed scroll 3, pushes the discharge valve 16 open, and flows into the high pressure chamber 2h. And it discharges from the airtight container 2 via the discharge pipe 2e.
  • the remaining part of the refrigerant gas cools the rotary drive unit 10 and the lubricating oil through notches (not shown) of the steel plate of the stator 11.
  • the frame 5 supporting the thrust bearing surface 4 c receives a load on the thrust bearing surface 4 c generated by the pressure of the refrigerant gas in the compression chamber 30. Further, the centrifugal force generated in the first balance weight 13 and the second balance weight 14 and the load from the working fluid are received by the main bearing 20 and the sub bearing 21. Further, the low-pressure refrigerant gas in the low-pressure chamber 2l and the high-pressure working fluid in the high-pressure chamber 2h are partitioned by the fixed scroll 3 and the frame 5, and airtightness is maintained.
  • the lubricating oil is supplied to the sliding portion where the parts slide. Specifically, the lubricating oil stored in the lower shell 2 c flows from the lower part of the main shaft 8 to the upper side by the oil pump 15, and is supplied from the upper end of the main shaft 8 between the main shaft 8 and the boss portion 4 d of the orbiting scroll 4. The Then, the lubricating oil flows into the oil supply chamber 31 in the space on the outer peripheral side of the boss portion 4 d while lubricating the sliding portion between the main shaft 8 and the boss portion 4 d of the orbiting scroll 4.
  • the lubricating oil flowing into the compression chamber 30 is mixed with the working fluid in the compression chamber 30.
  • the lubricating oil mixed with the working fluid in the compression chamber 30 adheres to the sliding portions of the fixed-side spiral body 3b and the swing-side spiral body 4b, thereby improving the airtightness of the compression chamber 30 and suppressing wear. .
  • the lubricating oil flows into the compression chamber 30 through the thrust plate 6 and the swing scroll 4 in order to lubricate the lubrication portion between the fixed scroll 3 and the swing scroll 4.
  • the scroll compressor 1 has a structure for supplying an appropriate amount of lubricating oil to the compression chamber 30.
  • FIG. 2 is a plan view showing an example of a thrust plate in the scroll compressor of FIG.
  • an oil supply hole 6a is formed in the thrust plate 6, and the oil supply hole 6a communicates with the compression chamber 30 (see FIG. 1). Therefore, the lubricating oil is supplied to the compression chamber 30 when the lubricating oil is supplied to the oil supply hole 6a.
  • the oil supply hole 6a is provided on the outer peripheral side of the thrust plate 6, and is exposed from the orbiting scroll 4 during a predetermined rotation period when the orbiting scroll 4 revolves. Lubricating oil is directly supplied from the oil supply chamber 31 to the oil supply hole 6 a during the rotation period exposed from the orbiting scroll 4.
  • the rotation period during which the lubricating oil is directly supplied depends on the position where the oil supply hole 6a is formed.
  • the lubricating oil 6d is directly supplied to the oil supply hole 6a as the oil supply hole 6a is formed on the outer peripheral side of the thrust plate 6.
  • the rotation period is longer.
  • the formation position of the oil supply hole 6a can be appropriately set as necessary.
  • FIG. 3 is a plan view showing an example of a thrust bearing surface in the scroll compressor of FIG.
  • an oil supply groove 40 is formed on the thrust bearing surface 4c.
  • the oil supply groove 40 includes an oil inflow portion 41, an oil circulation portion 42, and an oil outflow portion 43.
  • the oil inflow portion 41 is a portion into which the lubricating oil flows, and is connected to the first Oldham key groove 4e on the swing scroll 4 side, for example. Then, the lubricating oil filled in the first Oldham key groove 4e flows into the oil inflow portion 41.
  • the oil circulation part 42 is connected to the oil inflow part 41 on one side, and is formed so as to extend from the oil inflow part 41 toward the rotation direction of the rocking scroll 4 (arrow R direction).
  • the oil circulation part 42 is formed in, for example, an arc shape, and the arc shape has a shape along the rotation trajectory of the rocking scroll 4.
  • the oil outflow portion 43 communicates with the other side of the oil circulation portion 42 and causes the lubricating oil that has passed through the oil circulation portion 42 to flow out into the oil supply hole 6a.
  • the oil outflow part 43 is provided in the front-end
  • the oil supply groove 40 is formed so that the oil outflow portion 43 is positioned on the oil supply hole 6a during a predetermined rotation period while the rocking scroll 4 swings once.
  • the oil outflow portion 43 of the oil supply groove 40 is positioned on the oil supply hole 6a. Accordingly, the lubricating oil can be supplied from the oil supply groove 40 to the oil supply hole 6a.
  • the lubricating oil flowing through the oil circulation portion 42 is inhibited from moving toward the oil outflow portion 43 by the swinging motion of the swing scroll 4. Furthermore, the faster the rotation of the orbiting scroll 4, the more difficult it is for the lubricating oil to flow to the oil outflow portion 43 side. Therefore, depending on the rotational speed of the orbiting scroll 4, even if the oil outflow portion 43 is positioned on the oil supply hole 6a, the rotation period during which the lubricating oil is not supplied to the oil supply hole 6a is reached.
  • the rotation period in which the lubricant is supplied from the oil supply groove 40 to the oil supply hole 6a the rotation period in which the lubricant is not supplied to the oil supply hole 6a, and the lubricant oil
  • the lubricating oil is intermittently supplied to the oil supply hole 6a.
  • whether or not the lubricating oil flows to the oil outflow portion 43 side and is supplied to the oil supply hole 6a during the rotation period in which the lubricating oil is supplied from the oil supply groove 40 to the oil supply hole 6a depends on the rotation of the orbiting scroll 4. Depends on speed.
  • the oil supply groove 40 is formed with the oil circulation portion 42 extending in the rotation direction of the orbiting scroll 4, thereby increasing the amount of oil supplied at high speed rotation while ensuring the required amount of oil supply at low speed rotation. Can be prevented and the amount of oil rising can be suppressed, so that the refrigerating capacity and performance can be improved. That is, when the oil supply hole is provided in the thrust bearing surface 4c of the orbiting scroll 4 and the oil supply hole is provided in the thrust plate 6 as in the prior art, the slidability is improved when the scroll compressor rotates at a low speed. Refrigerant leakage loss due to improved sealing performance can be reduced. However, as the rotational speed increases, the amount of lubrication increases, so the amount of lubrication becomes excessive during high-speed rotation. As a result, the amount of oil rising during high-speed rotation increases, leading to a reduction in refrigeration capacity and performance.
  • the oil supply hole 6a and the oil supply groove 40 are arranged so that their positions overlap each other during a predetermined rotation period of the rotation period in which the orbiting scroll 4 rotates once. Even during the rotating period, the orbit of the orbiting scroll 4 is configured to prevent the oil flow in the oil supply groove 40. Therefore, the lubricating oil is not excessively supplied to the compression mechanism during high-speed rotation, and the amount of oil rising can be suppressed.
  • the lubrication hole 6a is exposed during the rotation period of the orbiting scroll 4, the lubrication oil is supplied from the lubrication hole 6a even during high-speed rotation, so that the lubrication oil is insufficient. It is possible to prevent the occurrence of malfunctions.
  • the oil outflow portion 43 of the oil supply groove 40 is formed so as to be positioned on the oil supply hole 6a during a predetermined rotation period when the swing scroll 4 performs the swinging motion, the oil outflow portion 43 is oiled during the low speed rotation. Since the lubricating oil can be supplied from the supply groove 40 to the oil supply hole 6a, it is possible to prevent the lubricating oil from being insufficient during low-speed rotation.
  • FIG. FIG. 5 is a plan view showing an example of a thrust plate in a scroll compressor according to Embodiment 2 of the present invention
  • FIG. 6 is a plan view showing an example of a thrust bearing surface in the scroll compressor according to Embodiment 2 of the present invention.
  • a second embodiment of the scroll compressor will be described with reference to FIGS. 5 and FIG. 6, parts having the same configuration as in FIG. 2 and FIG.
  • two oil supply holes 6a of the thrust plate 6 and two oil supply grooves 40 of the orbiting scroll 4 are provided.
  • the two oil supply holes 6a and the oil supply groove 40 are formed at positions that are rotationally symmetric, for example.
  • the amount of oil supplied to the compression chamber 30 can be increased.
  • the required amount of oil can be ensured as required when it cannot be ensured. Even in this case, as in the first embodiment, it is possible to suppress an increase in the amount of oil rising and a decrease in performance due to excessive lubricating oil being supplied during high-speed rotation.
  • the embodiment of the present invention is not limited to the above embodiment.
  • the oil supply groove 40 of the orbiting scroll 4 is formed in an arc shape. It suffices if it extends toward).
  • the oil circulation part 42 may be, for example, a linear shape or an ellipse as long as the lubricating oil flow from the oil inflow part 41 to the oil outflow part 43 in the oil supply groove 40 is obstructed by the rotation trajectory of the orbiting scroll 4. Any shape such as a shape or a polygonal shape may be used.
  • the case where two oil supply grooves 40 and oil supply holes 6a are provided is illustrated, but three or more oil supply grooves 40 and oil supply holes 6a may be provided.
  • FIG. 3 illustrates the case where the oil supply groove 40 communicates with the first Oldham key groove 4e, and the lubricating oil is supplied to the oil supply groove 40 via the first Oldham key groove 4e.
  • the shape is not limited to this.
  • the oil supply groove 40 and the first Oldham key groove 4e are formed independently, and the lubricant oil is directly supplied from the oil supply chamber 31 to the oil supply groove 40 without passing through the first Oldham key groove 4e. May be.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

Selon l'invention, une plaque de poussée comporte un trou d'alimentation en huile conduisant à une chambre de compression à partir d'une surface de la plaque de poussée, cette surface coulissant sur une spirale en orbite. La spirale en orbite comporte une rainure d'alimentation en huile comprenant : une partie orifice d'entrée d'huile dans laquelle s'écoule de l'huile lubrifiante ; une partie écoulement d'huile pourvue d'un côté conduisant à la partie orifice d'entrée d'huile et s'étendant dans le sens de rotation de la spirale en orbite à partir de la partie orifice d'entrée d'huile ; et une partie orifice de sortie d'huile conduisant à l'autre côté de la partie écoulement d'huile et permettant l'écoulement de l'huile lubrifiante ayant traversé la partie écoulement d'huile vers le côté trou d'alimentation en huile lorsque la partie orifice de sortie d'huile se situe sur le trou d'alimentation en huile.
PCT/JP2014/063265 2014-05-19 2014-05-19 Compresseur à spirales WO2015177851A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2014/063265 WO2015177851A1 (fr) 2014-05-19 2014-05-19 Compresseur à spirales
JP2016520830A JPWO2015177851A1 (ja) 2014-05-19 2014-05-19 スクロール圧縮機

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/063265 WO2015177851A1 (fr) 2014-05-19 2014-05-19 Compresseur à spirales

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WO2015177851A1 true WO2015177851A1 (fr) 2015-11-26

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017149707A1 (fr) * 2016-03-02 2017-09-08 三菱電機株式会社 Machine à fluide à volutes et dispositif à cycle de réfrigération
WO2019207784A1 (fr) * 2018-04-27 2019-10-31 三菱電機株式会社 Compresseur à spirales et dispositif à cycle frigorifique
JPWO2021149180A1 (fr) * 2020-01-22 2021-07-29

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5993982A (ja) * 1982-11-19 1984-05-30 Hitachi Ltd スクロ−ル流体機械
JPS62267588A (ja) * 1986-05-15 1987-11-20 Mitsubishi Electric Corp スクロ−ル圧縮機
JPS6415479A (en) * 1987-07-08 1989-01-19 Mitsubishi Electric Corp Scroll compressor
JPH04112984A (ja) * 1990-09-03 1992-04-14 Zexel Corp スクロール流体機械

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5993982A (ja) * 1982-11-19 1984-05-30 Hitachi Ltd スクロ−ル流体機械
JPS62267588A (ja) * 1986-05-15 1987-11-20 Mitsubishi Electric Corp スクロ−ル圧縮機
JPS6415479A (en) * 1987-07-08 1989-01-19 Mitsubishi Electric Corp Scroll compressor
JPH04112984A (ja) * 1990-09-03 1992-04-14 Zexel Corp スクロール流体機械

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017149707A1 (fr) * 2016-03-02 2017-09-08 三菱電機株式会社 Machine à fluide à volutes et dispositif à cycle de réfrigération
JPWO2017149707A1 (ja) * 2016-03-02 2018-09-20 三菱電機株式会社 スクロール流体機械および冷凍サイクル装置
WO2019207784A1 (fr) * 2018-04-27 2019-10-31 三菱電機株式会社 Compresseur à spirales et dispositif à cycle frigorifique
CN112041561A (zh) * 2018-04-27 2020-12-04 三菱电机株式会社 涡旋压缩机以及制冷循环装置
JPWO2019207784A1 (ja) * 2018-04-27 2021-02-12 三菱電機株式会社 スクロール圧縮機及び冷凍サイクル装置
JPWO2021149180A1 (fr) * 2020-01-22 2021-07-29
WO2021149180A1 (fr) * 2020-01-22 2021-07-29 三菱電機株式会社 Compresseur
GB2605715A (en) * 2020-01-22 2022-10-12 Mitsubishi Electric Corp Compressor
GB2605715B (en) * 2020-01-22 2023-10-11 Mitsubishi Electric Corp Compressor
JP7399193B2 (ja) 2020-01-22 2023-12-15 三菱電機株式会社 圧縮機
US11953005B2 (en) 2020-01-22 2024-04-09 Mitsubishi Electric Corporation Compressor having orbiting scroll supply hole to lubricate thrust surface

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