WO2016199281A1 - スクロール圧縮機及び冷凍サイクル装置 - Google Patents
スクロール圧縮機及び冷凍サイクル装置 Download PDFInfo
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- WO2016199281A1 WO2016199281A1 PCT/JP2015/066929 JP2015066929W WO2016199281A1 WO 2016199281 A1 WO2016199281 A1 WO 2016199281A1 JP 2015066929 W JP2015066929 W JP 2015066929W WO 2016199281 A1 WO2016199281 A1 WO 2016199281A1
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- refrigerant
- scroll
- injection
- scroll compressor
- shell
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C18/023—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 both members are moving
- F04C18/0238—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 both members are moving with symmetrical double wraps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C18/0284—Details of the wrap tips
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C18/063—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 with coaxially-mounted members having continuously-changing circumferential spacing between them
- F04C18/07—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 with coaxially-mounted members having continuously-changing circumferential spacing between them having crankshaft-and-connecting-rod type drive
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/005—Axial sealings for working fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/006—Cooling of compressor or motor
- F25B31/008—Cooling of compressor or motor by injecting a liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
Definitions
- the present invention mainly relates to a scroll compressor and a refrigeration cycle apparatus mounted on a refrigerator, an air conditioner, and a water heater.
- Carbon dioxide and the like are candidate refrigerants that have a lower GWP than HFC refrigerants.
- Carbon dioxide is a refrigerant having a high operating pressure and a high discharge temperature due to its physical properties.
- a tip seal member is disposed on the front end face of each of the scrolls of the fixed scroll and the swing scroll as a seal portion for sealing an axial gap between adjacent compression chambers.
- the tip seal member is arranged on the tip surface of the spiral body as described above, when carbon dioxide is used, the following problems occur. That is, when carbon dioxide is used, the pressure in the compression chamber increases as described above, and thus the pressure difference between the pressure inside the injection port and the pressure in the compression chamber during injection stop is large. Further, when the tip seal member on the swing scroll side passes over the injection port during the eccentric orbiting motion of the swing scroll, the pressure seal causes the tip seal member to enter the injection port and break the tip seal member. It was.
- the present invention has been made to solve the above-described problems, and provides a scroll compressor and a refrigeration cycle apparatus capable of improving the reliability by preventing breakage of a chip seal member. .
- a scroll compressor according to the present invention is provided in each of a shell, a fixed scroll and an orbiting scroll disposed in the shell, and a fixed scroll and an orbiting scroll, and is engaged with each other to form a plurality of compression chambers.
- An injection port that is provided through the base plate and introduces a refrigerant having an intermediate pressure between the suction pressure and the discharge pressure from the outside into the compression chamber, and the refrigerant is a single carbon dioxide or a mixed refrigerant containing carbon dioxide.
- the diameter ⁇ inj of the injection port and the width TIP of the tip seal member in the direction orthogonal to the spiral direction are ⁇ inj ⁇ 0 .95 ⁇ TIP relationship.
- a refrigeration cycle apparatus includes a scroll compressor, a radiator, a decompression device, and an evaporator, which are sequentially connected to circulate a refrigerant, a radiator, An intermediate injection circuit that branches from the decompression device and is connected to the injection port of the scroll compressor, and a flow rate adjustment valve that adjusts the flow rate of the intermediate injection circuit, and injects liquid refrigerant from the intermediate injection circuit It leads to.
- the tip seal member can be prevented from being damaged and the reliability can be improved.
- a possible scroll compressor and refrigeration cycle apparatus can be obtained.
- FIG. 1 It is a schematic sectional drawing of the scroll compressor which concerns on Embodiment 1 of this invention. It is the top view which looked at the combined structure of the fixed scroll and rocking scroll of the scroll compressor concerning Embodiment 1 of this invention from the rocking scroll side to the axial direction. It is a circuit block diagram which shows the refrigerant circuit of the refrigerating-cycle apparatus provided with the scroll compressor which concerns on Embodiment 1 of this invention. It is a compression process figure of the scroll compressor of FIG. In the scroll compressor which concerns on Embodiment 1 of this invention, it is a compression chamber sectional drawing when not performing intermediate injection.
- Embodiment 1 FIG. The first embodiment will be described below with reference to the drawings.
- the same reference numerals denote the same or corresponding parts, and are common to the whole text of the embodiments described below.
- the form of the component represented by the whole specification is an illustration to the last, Comprising: It does not limit to the form described in the specification.
- the level of temperature, pressure, etc. is not particularly determined in relation to absolute values, but is relatively determined in terms of the state, operation, etc. of the system, apparatus, etc.
- FIG. 1 is a schematic cross-sectional view of a scroll compressor according to Embodiment 1 of the present invention.
- FIG. 1 shows an example of a so-called high pressure shell type hermetic scroll compressor.
- FIG. 2 is a plan view of the combined structure of the fixed scroll and the orbiting scroll of the scroll compressor according to Embodiment 1 of the present invention as viewed in the axial direction from the orbiting scroll side.
- the fixed scroll 1 is indicated by a solid line
- the swing scroll 2 is indicated by a dotted line.
- This scroll compressor 100 has a function of sucking in refrigerant, compressing it, and discharging it in a high temperature and high pressure state.
- the scroll compressor 100 is configured such that a compression mechanism 35, a drive mechanism 36, and other components are housed in a shell 8 that is a sealed container constituting an outer shell. As shown in FIG. 1, in the shell 8, the compression mechanism part 35 is arrange
- the frame 3 and the subframe 19 are arranged so as to face each other with the drive mechanism 36 interposed therebetween.
- the frame 3 is disposed on the upper side of the drive mechanism unit 36 and is positioned between the drive mechanism unit 36 and the compression mechanism unit 35, and the subframe 19 is positioned on the lower side of the drive mechanism unit 36.
- the frame 3 and the subframe 19 are fixed to the inner peripheral surface of the shell 8 by shrink fitting, welding, or the like.
- a bearing 3 b is provided at the center of the frame 3, and a sub-bearing 19 a is provided at the center of the subframe 19.
- the crankshaft 4 is rotatably supported by the bearing portion 3b and the auxiliary bearing 19a.
- the shell 8 is connected to a suction pipe 5 for sucking the refrigerant, a discharge pipe 13 for discharging the refrigerant, and an injection pipe 15 for injecting the refrigerant into the compression chamber 9.
- the compression mechanism 35 has a function of compressing the refrigerant sucked from the suction pipe 5 and discharging it to the high-pressure space 14 formed above the shell 8. This high-pressure refrigerant is discharged from the discharge pipe 13 to the outside of the scroll compressor 100.
- the drive mechanism unit 36 functions to drive the orbiting scroll 2 constituting the compression mechanism unit 35 in order to compress the refrigerant by the compression mechanism unit 35. That is, the driving mechanism 36 drives the orbiting scroll 2 via the crankshaft 4 so that the compression mechanism 35 compresses the refrigerant.
- the compression mechanism unit 35 includes a fixed scroll 1 and a swing scroll 2. As shown in FIG. 1, the orbiting scroll 2 is arranged on the lower side, and the fixed scroll 1 is arranged on the upper side.
- the fixed scroll 1 is composed of a first base plate 1c and a first spiral body 1b which is a spiral projection standing on one surface of the first base plate 1c.
- the orbiting scroll 2 includes a second base plate 2c and a second spiral body 2b which is a spiral projection standing on one surface of the second base plate 2c.
- the fixed scroll 1 and the swing scroll 2 are mounted in the shell 8 in a state where the first spiral body 1b and the second spiral body 2b are engaged with each other.
- the first spiral body 1b and the second spiral body 2b are formed in accordance with an involute curve, and the first spiral body 1b and the second spiral body 2b are engaged with each other and combined.
- a plurality of compression chambers 9 are formed between the spiral body 2b.
- the fixed scroll 1 is fixed in the shell 8 through the frame 3.
- a discharge port 1 a that discharges the compressed refrigerant to a high pressure is formed at the center of the fixed scroll 1.
- a leaf spring valve 11 is disposed at the outlet opening of the discharge port 1a so as to cover the outlet opening and prevent reverse flow of the refrigerant.
- a valve presser 10 that restricts the lift amount of the valve 11 is provided on one end side of the valve 11. That is, when the refrigerant is compressed to a predetermined pressure in the compression chamber 9, the valve 11 is lifted against the elastic force, and the compressed refrigerant is discharged from the discharge port 1a into the high-pressure space 14, and the discharge pipe 13 is discharged. It is discharged to the outside of the scroll compressor 100 through.
- an injection port 16 is formed in the first base plate 1c of the fixed scroll 1 at a position not communicating with the low pressure space (suction pressure space).
- the injection port 16 is for injecting liquid refrigerant of intermediate pressure (pressure between suction pressure and discharge pressure) into the compression chamber 9 from the outside of the shell 8 into the compression chamber 9 in which refrigerant in the course of compression exists.
- One injection port 16 is provided in each of the pair of symmetrical compression chambers 9 with the centers of the first spiral body 1b and the second spiral body 2b interposed therebetween, and the pressures in the pair of symmetrical compression chambers 9 are equal to each other. It is comprised so that it may become.
- the fixed scroll 1 is formed with an injection distribution flow path 15a that branches the injection refrigerant supplied from the injection pipe 15 into two and flows into two injection ports 16.
- FIG. 1 shows an example in which the injection distribution flow path 15 a is configured by holes formed in the fixed scroll 1, it may be formed by piping independent from the fixed scroll 1. In short, any configuration may be used as long as it has a pipe that guides the injection refrigerant from the outside of the shell 8 to the injection port 16 located in the shell 8, the outflow side of the pipe branches in two directions, and communicates with each injection port 16. .
- the orbiting scroll 2 performs an eccentric turning motion without rotating with respect to the fixed scroll 1.
- a hollow cylindrical concave bearing 2d that receives a driving force is formed at a substantially central portion of a surface (hereinafter referred to as a thrust surface) opposite to the surface on which the second spiral body 2b of the orbiting scroll 2 is formed. ing.
- An eccentric pin portion 4a (described later) provided at the upper end of the crankshaft 4 is fitted (engaged) with the concave bearing 2d.
- tip seal members 17a and 17c are arranged along the spiral direction as shown by black portions in FIG. 2 at the respective leading ends of the first spiral body 1b and the second spiral body 2b of the fixed scroll 1 and the swing scroll 2.
- a chip seal member 17b is inserted.
- the chip seal member 17a and the chip seal member 17b can advance and retreat in the axial direction (in the vertical direction in FIGS. 1 and 5) in the groove 18a (see FIG. 5 described later) and the groove 18b for housing them.
- the tip seal member 17a comes into sliding contact with the surface (tooth bottom surface) of the second base plate 2c of the orbiting scroll 2, and the tip seal member 17b. Is in sliding contact with the surface (tooth bottom surface) of the first base plate 1 c of the fixed scroll 1 to seal the axial gap between the adjacent compression chambers 9.
- the drive mechanism 36 is rotatably disposed on the stator 7, the inner peripheral surface side of the stator 7, and is accommodated in the vertical direction in the shell 8 and the shell 8, and is a rotating shaft. And at least a crankshaft 4.
- the stator 7 has a function of rotating the rotor 6 when energized.
- the outer peripheral surface of the stator 7 is fixedly supported on the shell 8 by shrink fitting or the like.
- the rotor 6 has a function of rotating and driving the crankshaft 4 when the stator 7 is energized.
- the rotor 6 is fixed to the outer periphery of the crankshaft 4, has a permanent magnet inside, and is held with a slight gap from the stator 7.
- the crankshaft 4 has an eccentric pin portion 4a formed at the upper end thereof, and the eccentric pin portion 4a is fitted to the concave bearing 2d of the orbiting scroll 2, and the orbiting scroll 2 is eccentrically swung by the rotation of the crankshaft 4. It is supposed to let you.
- An oil pump 21 is fixed to the lower side of the crankshaft 4.
- the oil pump 21 is a positive displacement pump and functions to supply refrigerating machine oil held in the oil reservoir 12 to the concave bearing 2d and the bearing portion 3b through an oil circuit 22 provided in the crankshaft 4 as the crankshaft 4 rotates. Has come to fulfill.
- an Oldham ring 20 is disposed in the shell 8 for preventing the rotational movement of the orbiting scroll 2 during the eccentric turning motion.
- the Oldham ring 20 is disposed between the fixed scroll 1 and the orbiting scroll 2, and functions to prevent the rotation movement of the orbiting scroll 2 and to enable the revolution movement.
- FIG. 1 The compressed refrigerant gas is discharged from the discharge port 1 a provided in the fixed scroll 1 against the valve presser 10 and discharged from the discharge pipe 13 to the outside of the shell 8.
- FIG. 3 is a circuit configuration diagram showing a refrigerant circuit of the refrigeration cycle apparatus including the scroll compressor according to Embodiment 1 of the present invention.
- the refrigeration cycle apparatus of FIG. 3 includes a scroll compressor 100, a radiator 51, an expansion valve 52 as a pressure reducing device, and an evaporator 53, which are connected in series by a pipe so that the refrigerant circulates. Main circuit. Further, an intermediate injection circuit 54 that branches from between the radiator 51 and the expansion valve 52 and is connected to the injection pipe 15 of the scroll compressor 100 is provided.
- the intermediate injection circuit 54 is provided with an expansion valve 55 as a flow rate adjusting valve and an electromagnetic valve 56 as an on-off valve that opens and closes the intermediate injection circuit 54.
- the expansion valve 55 and the electromagnetic valve 56 are controlled by a control device (not shown), and the flow rate injected into the compression chamber 9 can be adjusted by the control of the expansion valve 55.
- the refrigeration cycle apparatus is filled with carbon dioxide (CO 2 ) as a refrigerant. Note that a mixed refrigerant containing carbon dioxide may be used as the refrigerant.
- the refrigerant discharged from the scroll compressor 100 flows into the radiator 51, dissipates heat by exchanging heat with the air passing through the radiator 51, and flows out of the radiator 51.
- the refrigerant that has flowed out of the radiator 51 flows into the evaporator 53 after the expansion coefficient and flow rate are controlled by the expansion valve 52.
- the low-pressure two-phase refrigerant flowing into the evaporator 53 exchanges heat with the air passing through the evaporator 53, returns to the inside of the scroll compressor 100 from the suction pipe 5, and is sucked into the compression chamber 9 again.
- suction temperature the difference between the temperature of the refrigerant sucked into the scroll compressor 100 (hereinafter referred to as suction temperature) and the discharge temperature is large
- suction temperature the pressure difference between the high pressure and the low pressure is large
- high compression ratio operation the pressure difference between the high pressure and the low pressure is large
- the refrigerant discharged from the discharge pipe 13 becomes high temperature. Therefore, the discharge temperature is lowered by injecting the liquid refrigerant taken out from the outlet of the radiator 51 into the compression chamber 9.
- the expansion rate and the flow rate are controlled by the expansion valve 52 and the electromagnetic valve 56, and the pressure is reduced to the intermediate pressure.
- the intermediate-pressure liquid refrigerant enters the scroll compressor 100 from the injection pipe 15.
- the liquid refrigerant that has entered the scroll compressor 100 is injected into the compression chamber 9 through the injection distribution channel 15 a formed in the fixed scroll 1 and into the compression chamber 9, and the gas that is being compressed in the compression chamber 9. Cool the refrigerant.
- the injection of the intermediate-pressure liquid refrigerant may be referred to as intermediate injection.
- FIG. 4 is a compression process diagram of the scroll compressor of FIG. 1 and shows the compression process of the compression chamber every 60 °.
- the operation of the compression mechanism unit 35 of the scroll compressor 100 will be briefly described with reference to FIGS. 4 and 1.
- FIG. 4A shows a state where the suction of the compression chamber 9 formed by the fixed scroll 1 and the orbiting scroll 2 is completed and a pair of outermost chambers (portions indicated by dots in FIG. 4) is formed. (The closing completion angle is 0 °).
- the closing completion angle is 0 °.
- the operation of the compression mechanism unit 35 will be described by paying attention to the compression chamber 9a which is the outermost chamber in FIG.
- the orbiting scroll 2 is revolving, and the first spiral body 1b and the second spiral body 2b are moving on the injection port 16.
- the orbiting scroll 2 is further swung, and the injection port 16 communicates with the compression chamber 9a. Thereby, intermediate injection is performed from the injection port 16 to the compression chamber 9a, and the inside of the compression chamber 9a is cooled.
- the orbiting scroll 2 is further swung, and the compression chamber 9a and the injection port 16 continue to communicate with each other to cool the inside of the compression chamber 9a by intermediate injection.
- FIG. 4 (f) the orbiting scroll 2 is further swung, and the compression chamber 9a and the injection port 16 continue to communicate with each other to cool the compression chamber 9a by intermediate injection. Moreover, in FIG.4 (f), the compression chamber 9a and the innermost chamber 9b connected to the discharge port 1a inside are connected. For this reason, the injection port 16 opened to the compression chamber 9a communicates with the discharge port 1a. Therefore, in FIG. 4F, the intermediate injection is continuously performed while the injection port 16 communicates with the discharge port 1a.
- the liquid refrigerant passes through the injection port 16, but the injection is stopped in other than the high compression ratio operation, so the liquid refrigerant does not pass through the injection port 16, It is a space.
- carbon dioxide is used as the refrigerant, and the operating pressure is three to four times higher than that of the HFC refrigerant. Therefore, the pressure difference between the pressure in the injection port 16 and the pressure in the compression chamber 9 is large. Become. In order to prevent damage to the chip seal member 17b due to deformation of the chip seal member 17b due to such differential pressure, the following measures are taken.
- FIG. 5 is a cross-sectional view of the compression chamber when intermediate injection is not performed in the scroll compressor according to Embodiment 1 of the present invention.
- FIG. 6 shows a ratio of the injection port diameter ⁇ inj to the tip seal width TIP and the deflection amount ⁇ [ It is a graph which shows the actual machine test result which calculated
- FIG. 5 shows a state in which the tip seal member 17b on the swing scroll 2 side is lifted by the differential pressure and pressed to the fixed scroll 1 side. As shown in the enlarged view on the right side of FIG. 5, when the tip seal member 17 b on the swing scroll 2 side passes over the injection port 16, the tip seal member 17 b is bent into the injection port 16 due to the differential pressure. Deform.
- FIG. 7 is a Ph diagram (refrigerant pressure [Mpa] and enthalpy [kJ / kg] when carbon dioxide is used as the refrigerant in the refrigeration cycle apparatus including the scroll compressor according to Embodiment 1 of the present invention. ] Is a diagram showing the relationship between the Since carbon dioxide has a high critical point of 31 ° C. and a critical pressure of about 7.5 MPa, it has a very high pressure and a transcritical cycle without a condensation phenomenon in which the high pressure side becomes a supercritical refrigerant.
- FIG. 8 is a diagram illustrating a result of measuring the compressor input using the refrigerant temperature at the radiator outlet as a parameter in the refrigeration cycle apparatus including the scroll compressor according to Embodiment 1 of the present invention.
- the horizontal axis represents the refrigerant temperature at the radiator outlet (heat radiator outlet temperature) [° C.]
- the vertical axis represents the compressor input [W]. From FIG. 8, it can be seen that the compressor input has increased since the radiator outlet temperature has exceeded 30 ° C. This reason will be described in comparison with a case where a conventional HFC refrigerant is used as the refrigerant.
- liquid refrigerant is injected using an intermediate injection mechanism, and the inside of the compression chamber 9 is utilized using latent heat when the liquid refrigerant undergoes a phase transition from a liquid phase state to a gas phase state.
- the gas refrigerant was cooling.
- latent heat since latent heat is used, the gas refrigerant can be efficiently cooled.
- the opening temperature of the expansion valve 52 it is desirable to control the opening temperature of the expansion valve 52 to control the radiator outlet temperature to 30 ° C. or lower.
- the outlet refrigerant of the radiator 51 that is, the refrigerant used for injection can be converted into a liquid refrigerant, and the gas refrigerant in the compression chamber 9 can be efficiently cooled.
- the lower limit value of the radiator outlet temperature varies depending on the heat medium that cools the refrigerant by the heat radiator 51, and is the outside air (ambient) temperature when the heat medium is air. Further, when the heat medium is water, the temperature is over 0 ° C.
- FIG. 9 is a diagram showing a boost curve in the compression chamber of the scroll compressor according to Embodiment 1 of the present invention.
- the horizontal axis indicates the compression chamber volume, and the vertical axis indicates the pressure.
- FIG. 9 shows a boosting curve when intermediate injection is not performed and a boosting curve when intermediate injection is performed.
- the discharge temperature is high, the intermediate injection is performed to lower the discharge temperature as described above. Since intermediate pressure refrigerant flows into the compression chamber 9 in the intermediate injection, the boosting curve with intermediate injection swells to the upper right in the figure as compared to the boosting curve without intermediate injection.
- the injection port 16 and the discharge port 1a communicate with each other. Prevention is possible.
- the tip seal member 17b is damaged. Can be prevented, and the reliability of the scroll compressor 100 can be ensured.
- injection port 16 communicates with the discharge port 1a provided at the center of the fixed scroll 1 in the compression process, over-compression can be prevented.
- FIG. The scroll compressor 100 according to the first embodiment is a so-called high pressure shell type scroll compressor in which the pressure in the internal space of the shell 8 is high.
- the second embodiment is a so-called low pressure shell type scroll compressor in which the pressure in the internal space of the shell 8 is low.
- the effect acquired is the same as that of a high pressure shell type scroll compressor.
- a specific configuration in the case of the low-pressure shell type will be described.
- FIG. 10 is a schematic cross-sectional view of a scroll compressor according to Embodiment 2 of the present invention.
- the second embodiment will be described focusing on the differences from the first embodiment.
- the refrigerant gas discharged from the discharge port 1 a is directly guided to the discharge pipe 13 without being supplied to the internal space of the shell 8. Therefore, the internal space of the shell 8 is reduced in pressure by the suction pressure refrigerant flowing from the suction pipe 5.
- the injection pipe 15 can be prevented from being damaged by making the injection pipe 15 a flexible structure that suppresses elongation due to thermal expansion.
- the number of times of bending of the injection pipe 15 is not limited to two, and the same effect can be obtained if it is bent once or more.
- the injection pipe 15 has an L-shape, and a convex portion is provided on the back surface of the fixed scroll 1 (the upper surface of the fixed scroll 1 in FIG. 10). What is necessary is just to make it the structure which inserts the edge part inside the shell 8 of the injection piping 15 into this.
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Abstract
Description
本実施の形態1を以下、図面を用いて説明する。ここで、以下の各図面において、同一の符号を付したものは、同一又はこれに相当するものであり、以下に記載する実施の形態の全文において共通することとする。そして、明細書全文に表わされている構成要素の形態は、あくまでも例示であって、明細書に記載された形態に限定するものではない。また、温度、圧力等の高低については、特に絶対的な値との関係で高低等が定まっているものではなく、システム、装置等における状態、動作等において相対的に定まるものとする。
シェル8に設けられた図示省略の電源端子に通電されると、ステータ7とロータ6とにトルクが発生し、クランクシャフト4が回転する。クランクシャフト4の回転により、揺動スクロール2がオルダムリング20により自転を規制されて偏心旋回運動する。吸入管5からシェル8内に吸入された冷媒は、固定スクロール1の第1渦巻体1bと揺動スクロール2の第2渦巻体2b間に形成された複数の圧縮室9のうち外周部の圧縮室9に取り込まれる。
図3の冷凍サイクル装置は、スクロール圧縮機100と、放熱器51と、減圧装置としての膨張弁52と、蒸発器53とを備え、これらが順次配管で接続されて冷媒が循環するように構成された主回路を備えている。また、放熱器51と膨張弁52との間から分岐し、スクロール圧縮機100のインジェクション配管15に接続される中間インジェクション回路54を備えている。中間インジェクション回路54には流量調整弁としての膨張弁55と中間インジェクション回路54を開閉する開閉弁としての電磁弁56とが設けられている。膨張弁55及び電磁弁56は図示しない制御装置によって制御され、膨張弁55の制御により、圧縮室9にインジェクションする流量を調整可能となっている。冷凍サイクル装置には、冷媒として二酸化炭素(CO2)が充填されている。なお、冷媒としては、二酸化炭素を含む混合冷媒を用いても良い。
スクロール圧縮機100から吐出された冷媒は放熱器51に流入し、放熱器51を通過する空気と熱交換して放熱し、放熱器51から流出する。放熱器51を流出した冷媒は、膨張弁52で絞り膨張率と流量を制御された後、蒸発器53に流入する。蒸発器53に流入した低圧二相冷媒は、蒸発器53を通過する空気と熱交換した後、吸入管5からスクロール圧縮機100の内部へと戻り、再び圧縮室9に吸い込まれる。
図4(a)は、固定スクロール1と揺動スクロール2によって形成される圧縮室9の吸入が完了し、一対の最外室(図4においてドットで示した部分)が形成されたところを示している(閉じ込み完了角度0°)。ここでは、図4(a)において最外室となっている圧縮室9aに着目して圧縮機構部35の動作を説明する。
図5には、揺動スクロール2側のチップシール部材17bが、差圧によって浮上して固定スクロール1側に押し付けられた状態を示している。そして、図5の右側の拡大図に示すように、揺動スクロール2側のチップシール部材17bがインジェクションポート16上を通過する際、その差圧によりチップシール部材17bがインジェクションポート16内に撓むように変形する。
図8より、放熱器出口温度が30℃を超えたあたりから、圧縮機入力が増加していることがわかる。この理由について、冷媒として従来のHFC冷媒を用いた場合と比較して説明する。
吐出温度が高い場合、中間インジェクションを行って吐出温度を下げることは上述の通りである。そして、中間インジェクションでは中間圧冷媒を圧縮室9に流入させるため、中間インジェクション有りの昇圧曲線は、中間インジェクション無しの昇圧曲線と比較して図右上に膨れる。インジェクション冷媒の圧力(中間圧)が必要以上に高い場合、圧縮室9内の圧力が、目標の吐出圧力よりも高くなる過圧縮部が生じて損失となる。この損失が生じると圧縮機の入力が高くなり、COPが低下する。このため、過圧縮を防止することが望まれ、本実施の形態1では図4(f)で説明したように、インジェクションポート16と吐出ポート1aとが連通する構成としたことで、過圧縮の防止を可能としている。
上記実施の形態1のスクロール圧縮機100は、シェル8の内部空間の圧力が高圧である、いわゆる高圧シェル型のスクロール圧縮機であった。これに対し、本実施の形態2では、シェル8の内部空間の圧力が低圧である、いわゆる低圧シェル型のスクロール圧縮機としたものである。このように低圧シェル型のスクロール圧縮機としても、得られる効果は高圧シェル型のスクロール圧縮機と同様である。以下、低圧シェル型とした場合の特有の構成について説明する。
本実施の形態2のスクロール圧縮機100では吐出ポート1aから吐出された冷媒ガスが、シェル8の内部空間に供給されることなく、直接吐出管13に導かれるようになっている。よって、シェル8の内部空間は吸入管5から流入した吸入圧冷媒によって低圧になっている。
Claims (8)
- シェルと、
前記シェル内に配置された固定スクロール及び揺動スクロールと、
前記固定スクロール及び前記揺動スクロールのそれぞれに設けられ、相互に噛み合わされて複数の圧縮室を形成する渦巻体と、
前記揺動スクロールを偏心旋回運動させるクランクシャフトと、
前記揺動スクロールの前記渦巻体の先端部に渦巻方向に沿って挿入され、前記固定スクロールの台板と摺接するチップシール部材と、
前記固定スクロールの前記台板に貫通して設けられ、前記シェルの外部から前記圧縮室内に吸入圧と吐出圧との間の中間圧の冷媒を導入するインジェクションポートとを備え、
前記冷媒は二酸化炭素単体又は二酸化炭素を含む混合冷媒であり、
前記インジェクションポートの径φinjと前記渦巻方向に対して直交する方向の前記チップシール部材の幅TIPとが、φinj≦0.95×TIPの関係を有するスクロール圧縮機。 - 前記インジェクションポートは、前記固定スクロールの中央部に設けられた吐出ポートに圧縮過程で連通する請求項1記載のスクロール圧縮機。
- 前記スクロール圧縮機は低圧シェル型である請求項1又は請求項2記載のスクロール圧縮機。
- 前記インジェクションポートに接続され、外部から前記冷媒を前記インジェクションポートに導くインジェクション配管を備え、前記インジェクション配管において前記シェル内に位置する部分は、前記クランクシャフトの軸方向と前記軸方向に対して垂直な方向とに1回以上、曲げられている請求項3記載のスクロール圧縮機。
- 前記複数の圧縮室は、前記渦巻体の中心に対して対称な一対の圧縮室を有しており、前記インジェクションポートは、前記一対の圧縮室のそれぞれに1個以上且つ同数であることを特徴とする請求項1~請求項4の何れか一項に記載のスクロール圧縮機。
- 前記インジェクションポートに接続され、前記シェルの外部から前記冷媒を前記インジェクションポートに導くインジェクション配管の流出側が2方向に分岐し、前記インジェクションポートにそれぞれ連通する請求項5記載のスクロール圧縮機。
- 請求項1~請求項6の何れか一項に記載のスクロール圧縮機と、放熱器と、減圧装置と、蒸発器とを備え、これらが順次接続されて冷媒が循環するように構成された主回路と、
前記放熱器と前記減圧装置との間から分岐し、前記インジェクションポートに接続される中間インジェクション回路と、
前記中間インジェクション回路の流量を調整する流量調整弁とを備え、
液状態の前記冷媒を前記中間インジェクション回路から前記インジェクションポートに導く冷凍サイクル装置。 - 前記放熱器の出口の冷媒温度が30℃以下、0℃超に制御される請求項7記載の冷凍サイクル装置。
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PCT/JP2015/066929 WO2016199281A1 (ja) | 2015-06-11 | 2015-06-11 | スクロール圧縮機及び冷凍サイクル装置 |
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WO2018225155A1 (ja) * | 2017-06-06 | 2018-12-13 | 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 |
JPWO2018225155A1 (ja) * | 2017-06-06 | 2019-12-26 | 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 |
CN110691911A (zh) * | 2017-06-06 | 2020-01-14 | 三菱电机株式会社 | 涡旋压缩机及制冷循环装置 |
US11248604B2 (en) | 2017-06-06 | 2022-02-15 | Mitsubishi Electric Corporation | Scroll compressor and refrigeration cycle apparatus |
WO2020255243A1 (ja) * | 2019-06-18 | 2020-12-24 | 三菱電機株式会社 | 圧縮機 |
JPWO2020255243A1 (ja) * | 2019-06-18 | 2021-11-25 | 三菱電機株式会社 | 圧縮機 |
Also Published As
Publication number | Publication date |
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JPWO2016199281A1 (ja) | 2017-12-07 |
CN107614878B (zh) | 2019-12-24 |
CN107614878A (zh) | 2018-01-19 |
EP3309399B1 (en) | 2022-07-27 |
EP3309399A1 (en) | 2018-04-18 |
EP3309399A4 (en) | 2019-03-13 |
US20180128270A1 (en) | 2018-05-10 |
US10578103B2 (en) | 2020-03-03 |
JP6366834B2 (ja) | 2018-08-01 |
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