WO2008066156A1 - Compresseur à piston de machine frigorigène - Google Patents

Compresseur à piston de machine frigorigène Download PDF

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Publication number
WO2008066156A1
WO2008066156A1 PCT/JP2007/073169 JP2007073169W WO2008066156A1 WO 2008066156 A1 WO2008066156 A1 WO 2008066156A1 JP 2007073169 W JP2007073169 W JP 2007073169W WO 2008066156 A1 WO2008066156 A1 WO 2008066156A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
valve
compression chamber
chamber
reciprocating compressor
Prior art date
Application number
PCT/JP2007/073169
Other languages
English (en)
Japanese (ja)
Inventor
Kiyoshi Terauchi
Original Assignee
Sanden Corporation
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 Sanden Corporation filed Critical Sanden Corporation
Priority to EP07849947A priority Critical patent/EP2088322A4/fr
Priority to US12/516,718 priority patent/US20100068085A1/en
Publication of WO2008066156A1 publication Critical patent/WO2008066156A1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1009—Distribution members
    • F04B27/1018—Cylindrical distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/062—Cooling by injecting a liquid in the gas to be compressed
    • 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
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • 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
    • 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
    • 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
    • F25B2400/23—Separators

Definitions

  • the present invention relates to a reciprocating compressor of a refrigerator, and more particularly, to a compressor suitable for a refrigerator included in an air conditioning system of an automobile.
  • This type of reciprocating compressor includes a cylinder block having a plurality of cylinder bores, a piston that is reciprocally inserted into each cylinder bore of the cylinder block, and forms a compression chamber in the cylinder bore. And a rotatable main shaft that reciprocates each piston within the corresponding cylinder bore. When the main shaft is rotated, the pistons reciprocate sequentially in the corresponding cylinder bores, and the reciprocating motion of such pistons is caused by the suction of refrigerant into the corresponding compression chamber through the compression of the refrigerant in the compression chamber. Then, a series of processes leading to the discharge of the compressed refrigerant from the compression chamber is repeatedly performed (Patent Document 1).
  • Patent Document 1 Japanese Patent Laid-Open No. 2001-027177
  • R134a An alternative chlorofluorocarbon gas called R134a is generally used for an air conditioning system of an automobile, that is, a refrigerant of its refrigerator.
  • R134a a chlorofluorocarbon gas
  • Such alternative chlorofluorocarbons are very high V and have a global warming index (Global
  • the GWP of the alternative chlorofluorocarbon gas is about 1300. Therefore, the refrigerator of Patent Document 1 uses carbon dioxide (GWP) with a low GWP instead of the above-mentioned alternative chlorofluorocarbon as a refrigerant. CO) is used. In recent years, it has also been proposed to use a new alternative refrigerant having a low GPW, and this alternative refrigerant contains a double bond (for example, R1 234YF).
  • the temperature of the refrigerant that is, the discharge temperature of the refrigerant
  • the CO refrigerant The discharge temperature exceeds 150 ° C and the heat load received by the compressor is large.
  • the discharge temperature of this refrigerant is suppressed to the same extent as in the case of R134a.
  • a new alternative refrigerant containing a double bond is easily decomposed at the discharge temperature of the refrigerant because the double bond is likely to be released under high temperature use conditions.
  • An object of the present invention is to provide a reciprocating compressor for a refrigerator that can suppress an increase in refrigerant discharge temperature and at the same time increase the compression efficiency of the refrigerant.
  • a reciprocating compressor of a refrigerator is fitted with a housing having a cylinder bore and a compression chamber formed in the cylinder bore, and in the cylinder bore.
  • This reciprocating piston performs a series of processes including suction of refrigerant into the compression chamber, compression of suction refrigerant in the compression chamber, and discharge of compressed refrigerant from the compression chamber.
  • the introduction device is lower than the temperature of the compressed refrigerant in the compression process, the introduction device having an intermediate refrigerant having a pressure higher than the pressure of the compressed refrigerant in the compression chamber.
  • the intermediate refrigerant into the compression chamber having a degree.
  • the introduction device is formed in the housing and is supplied with an intermediate pressure chamber to which the intermediate refrigerant is supplied from the refrigerant circulation path, a connection passage connecting the intermediate pressure chamber and the compression chamber, and the connection A valve that is provided in the passage and opens and closes the connection passage, and the connection passage is opened in a time zone until the pressure of the compressed refrigerant in the compression process reaches the pressure of the intermediate refrigerant in the intermediate pressure chamber.
  • the valve is opened when the refrigerant is in the compression process in the compression chamber. Since the pressure of the intermediate refrigerant in the intermediate pressure chamber is higher than the pressure of the compressed refrigerant in the compression chamber at the timing when the valve is opened, the intermediate medium is injected into the compression chamber when the valve is opened. At this time, the temperature of the intermediate refrigerant is the compressed refrigerant in the compression chamber in the compression process. The compressed refrigerant in the compression chamber that is lower than the temperature of the refrigerant is cooled by being mixed with the intermediate refrigerant, so that the rise in the temperature of the refrigerant discharged from the compressor is suppressed.
  • Refrigerants containing compounds with double bonds can be used, greatly contributing to the prevention of global warming. Also, when the refrigerant is in the compression process in the compression chamber, if the intermediate refrigerant is injected into the compression chamber, the compression efficiency of the compressed refrigerant can be increased, and the energy efficiency of the refrigerator is greatly improved.
  • the valve described above is a rotary valve that is mechanically coupled to the main shaft and rotates integrally with the main shaft, or a rotary valve that is rotated by a motor independent of the main shaft, or an electromagnetic valve.
  • the compressor can further include a variable capacity mechanism that varies the discharge amount of the compressed refrigerant, and the variable capacity mechanism has a swash plate.
  • FIG. 1 is a diagram showing an outline of a refrigerator.
  • FIG. 2 is a cross-sectional view showing details of the compressor of FIG.
  • FIG. 3 is a view showing a rotary valve of a modified example.
  • FIG. 4 is a view showing an electromagnetic on-off valve.
  • the refrigerator of FIG. 1 is incorporated in an air conditioning system for an automobile and includes a circulation path 2 for the refrigerant.
  • a compressor 4 compresses and discharges the refrigerant, and the discharged refrigerant is supplied to the condenser 6 and circulates in the circulation path 2.
  • the circulation path 2 includes the discharge port of the compressor 4 or the high pressure region 2 from the 4d through the condenser 6 to the first expansion valve 8, and the gas-liquid separator 10 and the second expansion valve from the first expansion valve 8. 12 and evaporator 14
  • FIG. 2 shows details of the compressor 4.
  • the compressor 4 is a variable capacity and reciprocating compressor, and includes a housing 16.
  • the housing 16 has an end plate 18, a center casing 20 and a cylinder head 22 from the left side as viewed in FIG. 2, and the end plate 18, the center casing 20 and the cylinder head. 22 is integrally connected.
  • the center casing 20 defines a crank chamber 24 therein, and the crank chamber 24 is disposed between the end plate 18 and the end wall of the center casing 20, that is, the cylinder block 26.
  • a compression unit 28 is disposed in the center casing 20, and the compression unit 28 will be described in detail below.
  • the cylinder block 26 has a plurality of cylinder bores 30 therein. These cylinder bores 30 are arranged at equal intervals around the axis of the cylinder block 26 and pass through the cylinder block 26. Pistons 32 are slidably fitted in the cylinder bores 30, and these pistons 32 form compression chambers 33 in the corresponding cylinder bores 30.
  • a main shaft 34 is disposed in the crank chamber 24. The main shaft 34 is positioned coaxially with the axis of the cylinder block 26 and has an inner end and an outer end, respectively. The inner end of the main shaft 34 enters the cylinder block 26 and is supported by the cylinder block 26 through a bearing 36 so as to rotate freely.
  • the outer end of the main shaft 34 protrudes outside the housing 16. That is, the main shaft 34 passes through the end plate 18 and is supported by the end plate 18 via the bearing 38 and the seal unit 40.
  • the outer end of the main shaft 34 is connected to an automobile engine via a power transmission path (not shown). Therefore, when the driving force of the engine is transmitted from the engine to the main shaft 34, the main shaft 34 rotates in one direction.
  • a rotor 42 is attached to the main shaft 34, and the rotor 42 is disposed in the crank chamber 24.
  • the rotor 42 rotates integrally with the main shaft 34 and is rotatably supported by the end plate 18 via a thrust bearing 44.
  • a swash plate 46 is disposed in the crank chamber 24, and this swash plate 46 surrounds the main shaft 34.
  • the swash plate 46 and the rotor 42 are connected to each other via a link 48, and the link 48 allows the swash plate 46 to tilt with respect to the main shaft 34 that changes the inclination angle of the swash plate 46.
  • the swash plate 46 supports a swing plate 42 via a radial bearing 50 and a thrust bearing 52, and the rotation of the swing plate 54 is blocked by a rotation prevention mechanism (not shown! /). ! /
  • the swing plate 54 described above is connected to each piston 32 via a piston rod 56. These screw rods 56 have ball joints 57a and 57b at both ends thereof.
  • the ball joint 57a connects the swing plate 54 and the piston rod 56
  • the ball joint 57b connects the piston rod 56 and the piston 32. Therefore, when the main shaft 34 is rotated, the rotation of the main shaft 34 is converted into a reciprocating motion of each piston 32 via the rotor 42, the swash plate 46, the swing plate 54 and the piston rod 56.
  • a valve plate 58 is sandwiched through (not shown).
  • the valve plate 58 has a cylinder bore 30, that is, a suction hole 60 and a discharge hole 62 assigned to each compression chamber 33.
  • a suction chamber 64, a discharge chamber 66, and an intermediate pressure chamber 68 are formed between the valve plate 58 and the cylinder head 22, and these chambers 64, 66, and 68 are independent of each other.
  • the intermediate pressure chamber 68 is disposed in the center of the cylinder head 22, the discharge chamber 66 has an annular shape surrounding the intermediate pressure chamber 68, and the suction chamber 64 has an annular shape surrounding the discharge chamber 66. That is, the intermediate pressure chamber 68, the discharge chamber 66, and the suction chamber 64 form a triple structure!
  • the suction chamber 64 communicates with the suction hole 60 of each compression chamber 33, and is connected to the low pressure region 2 of the circulation path 2 through the suction port 4s described above.
  • the discharge chamber 66 is connected to the suction hole 60 of each compression chamber 33, and is connected to the low pressure region 2 of the circulation path 2 through the suction port 4s described above.
  • the discharge port 4d is formed in the cylinder head 22, respectively.
  • a suction valve 70 is assigned to each of the suction holes 60 described above, and these suction valves 70 can open and close the corresponding suction ports 60. Further, a discharge valve 72 is assigned to each discharge hole 62, and these discharge valves 72 can open and close the corresponding discharge holes 62.
  • the intake valve 70 and the discharge valve 72 are both reed valves.
  • the suction valve 70 is disposed on one end surface of the valve plate 58 on the compression chamber 33 side, while the discharge valve 72 is disposed on the other end surface of the valve plate 58.
  • reference numeral 73 indicates a valve retainer for restricting the opening operation of the discharge valve 72.
  • an introduction port 74 is formed in the cylinder head 22.
  • the introduction port 74 communicates with the intermediate pressure chamber 68 described above, and is connected to the introduction path 76.
  • the introduction path 76 is connected to the gas-liquid separator 10 described above.
  • the intermediate refrigerant in the gas phase is transferred from the gas-liquid separator 10 through the introduction port 74. It is introduced into the intermediate pressure chamber 68.
  • a rotary valve 78 is disposed between the intermediate pressure chamber 68 and the main shaft 34, and the rotary valve 78 has a cylindrical shape and is rotatably supported with respect to the cylinder block 26. That is, a cylinder hole 79 for receiving the rotary valve 78 is formed in the cylinder block 26, and the rotary valve 78 is airtightly fitted in the cylinder hole 79.
  • the rotary valve 78 is positioned coaxially with the main shaft 34 and is integrally coupled to the main shaft 34.
  • the main shaft 34 has a pin 80 protruding from the inner end thereof into the rotary valve 78, and the pin 80 is coupled to the rotary valve 78 via a key 82. Therefore, the rotary valve 78 rotates integrally with the main shaft 34.
  • the outer peripheral surface of the rotary valve 78 is in airtight contact with the inner peripheral surface of the cylinder hole 79.
  • the rotary valve 78 passes through the valve plate 58 in an airtight manner and protrudes into the intermediate pressure chamber 68 and is rotatably supported by the cylinder head 22 via a ring-shaped thrust bearing 84.
  • a valve passage 86 is formed in the rotary valve 78, and the valve passage 86 has a valve port 86 a that opens to the outer peripheral surface of the rotary valve 78 and a communication port 86 b that communicates with the intermediate pressure chamber 68. As apparent from FIG. 2, the valve port 86a is positioned in the vicinity of one end face of the valve plate 58 described above.
  • connection holes 88 are formed in the cylinder block 26, and these connection holes 88 are assigned to the compression chambers 33. More specifically, each connection hole 88 is a radial hole extending from the inner peripheral surface of the cylinder hole 79 toward the corresponding compression chamber 33, and in the vicinity of one end surface of the valve plate 58, the compression chamber 33. And an inner end that opens to the inner peripheral surface of the cylinder hole 79. The outer end of each connection hole 88 is always connected to the corresponding compression chamber 33 regardless of the reciprocation of the binder 32.
  • connection holes 88 are arranged at equal intervals in the circumferential direction of the rotary valve 78, and are intermittently connected to the valve port 86a of the valve passage 86 when the rotary valve 78 is rotated. Is done. That is, the inner end of the connection hole 88 is arranged on a rotation locus drawn by the valve port 86a while the rotary valve 78 is rotating.
  • the valve ports 86a of the valve passage 88 are sequentially connected to the connection holes 88 of the compression chambers 33.
  • the intermediate pressure chamber 68 is sequentially connected to each compression chamber 33 by the rotary valve 78.
  • the rotary valve 78 sequentially opens and closes each connection hole 88,
  • the intermediate refrigerant in the intermediate pressure chamber 68 is distributed to each compression chamber 33. It is a valve arrangement.
  • the distribution timing and distribution period of the intermediate refrigerant from the intermediate pressure chamber 68 to the compression chamber 33 will be apparent from the following description.
  • each piston 32 reciprocates in the corresponding cylinder bore 30 sequentially. Therefore, the refrigerant in the suction chamber 64 is sucked into each compression chamber 33 through the suction valve 70 and the suction hole 60. Thereafter, the sucked refrigerant is compressed in each compression chamber 33, and the compressed refrigerant is discharged from the compression chamber 33 to the discharge chamber 66 through the discharge hole 62 and the discharge valve 72.
  • the discharge chamber 66 is connected to the high pressure area 2 of the circulation path 2.
  • the discharged refrigerant is supplied from the compressor 2 to the condenser 6.
  • the suction chamber 64 is connected to the low pressure region 2 of the circulation path 2
  • the cooling chamber 33 is returned to the compression chamber 33.
  • the medium is sucked from the suction chamber 64.
  • the rotary valve 78 rotates integrally with the main shaft 34, and the valve port 86a of the valve passage 86 of the rotary valve 78 is distributed to the connection hole 88 of the compression chamber 33 in a state where the refrigerant is in the compression process. Connected only for timing and distribution period. That is, the rotary valve 78 is opened at the distribution timing and closed at the end of the distribution period.
  • the distribution timing and the distribution period are set within the time period until the pressure of the refrigerant in the compression process in the compression chamber 33 rises to the pressure of the intermediate refrigerant in the intermediate pressure chamber 68.
  • the intermediate refrigerant in the intermediate pressure chamber 68 is injected into the compression chamber 33 through the rotary valve 78 and the connection 88.
  • a gas-phase intermediate refrigerant is introduced into the intermediate pressure chamber 68 through the introduction path 76 from the gas-liquid separator 10 described above. Therefore, the intermediate refrigerant in the intermediate pressure chamber 68, that is, the intermediate refrigerant injected into the compression chamber 33, has a temperature sufficiently lower than the discharge temperature of the refrigerant discharged from the compressor 4 and the compressor 4 force, etc. The pressure is lower than the discharged discharge pressure.
  • the low-temperature intermediate refrigerant ejected into the compression chamber 33 is mixed with the high-temperature refrigerant in the compression process, so that the compressed refrigerant in the compression chamber 33 is cooled, and thereby discharged from the compressor 4.
  • the temperature rise of the refrigerant is suppressed.
  • the compressor 4 of the present invention is favorable for preventing global warming. It enables the use of a suitable refrigerant, i.e. carbon dioxide or the new refrigerant mentioned above.
  • the compression efficiency of the refrigerant in the compression chamber 33 is increased, and the energy efficiency of the refrigerator is dramatically improved. That is, the multi-effect cycle required for this kind of refrigerator can be easily realized.
  • crank chamber 24 is connected to each of the suction chamber 64 and the discharge chamber 66 via connection passages 96 and 98 indicated by a one-dot chain line in FIG.
  • the valve plate 58 and the cylinder block 26 are passed through.
  • a throttle 100 is disposed in the connection passage 96, while an electromagnetic control valve 102 is disposed in the connection passage 98.
  • This electromagnetic control valve 102 controls the amount of high-pressure refrigerant that should flow from the discharge chamber 66 into the crank chamber 24 to adjust the pressure in the crank chamber 24.
  • the inclination angle of the swash plate 46 described above is determined by the compression reaction force applied from each piston 32 to the front surface of the swash plate 46 and the pressure in the crank chamber 24 applied to the rear surface of the swash plate 46, that is, the back pressure. Therefore, it changes as the pressure in the crank chamber 24 is adjusted. Since the inclination angle of the swash plate 46 determines the stroke of each piston 32, the refrigerant discharge amount from the compressor 4 is variable from the inclination angle of the swash plate 46.
  • connection hole 86 of the compression chamber 33 described above is disposed near the top dead center of the piston 32, even if the stroke of the piston 32 is changed, the distribution timing and distribution period of the rotary valve 78 with respect to each compression chamber 33 are not changed. It does not change. Therefore, the relationship between the pressure of the refrigerant discharged from the compressor 4 and the pressure of the intermediate refrigerant in the intermediate pressure chamber 68 is kept almost constant regardless of the stroke of the piston 32, and the refrigerant is compressed.
  • the power S is used to stably inject the low-temperature intermediate refrigerant into the compression chamber 33.
  • FIG. 3 shows a rotary valve 78 that is rotated independently of the main shaft 34.
  • the rotary valve 78 is connected to the output shaft 92 of the electric motor 90, and the electric motor 90 is attached to the outer surface of the cylinder head 22.
  • the electric motor 90 is a force that rotates the rotary valve 78 in synchronization with the rotation of the main shaft 34.
  • the distribution timing and the distribution period of the rotary valve 78 are adjusted as necessary.
  • FIG. 4 shows an electromagnetic on-off valve 94 used in place of the rotary valve 78.
  • Each solenoid valve 94 It is allocated and arranged in the compression chamber 33 and exhibits the same function as the rotary valve 78 described above.
  • the reciprocating compressor of the present invention may be a fixed capacity type or may be driven by an electric motor instead of the engine.
  • the type of reciprocating motion is not limited to the illustrated swing plate type, but may be a swash plate type or other axial piston type! /.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Sliding Valves (AREA)

Abstract

La présente invention concerne un compresseur à piston de machine frigorigène qui permet d'empêcher toute augmentation de température de réfrigérant déchargé et d'améliorer le rendement de compression du réfrigérant. Le compresseur à piston de machine frigorigène comprend un boîtier (16) avec un alésage de cylindre (30) ; un piston (32) capable d'un mouvement alternatif dans l'alésage de cylindre (30), inséré dans ce même alésage de cylindre (30) ; une chambre de pression intermédiaire (68) disposée à l'intérieur du boîtier (16), dans laquelle un réfrigérant à basse température est dirigé à partir d'un séparateur gaz-liquide (10) de machine frigorigène ; et une soupape rotative (78) disposée entre une chambre de compression (33) et la chambre de pression intermédiaire (68). Ladite soupape rotative (78) pivote conjointement à l'arbre principal (34) du compresseur et, lorsque le réfrigérant se trouve à l'état de compression à l'intérieur de la chambre de compression (33), elle s'ouvre de manière à expulser le réfrigérant à basse température de la chambre de pression intermédiaire (68) à la chambre de compression (33).
PCT/JP2007/073169 2006-12-01 2007-11-30 Compresseur à piston de machine frigorigène WO2008066156A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP07849947A EP2088322A4 (fr) 2006-12-01 2007-11-30 Compresseur à piston de machine frigorigène
US12/516,718 US20100068085A1 (en) 2006-12-01 2007-11-30 Reciprocating Compressor for Refrigerator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006325544A JP5118340B2 (ja) 2006-12-01 2006-12-01 冷凍回路の往復動型圧縮機
JP2006-325544 2006-12-01

Publications (1)

Publication Number Publication Date
WO2008066156A1 true WO2008066156A1 (fr) 2008-06-05

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ID=39467942

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2007/073169 WO2008066156A1 (fr) 2006-12-01 2007-11-30 Compresseur à piston de machine frigorigène

Country Status (5)

Country Link
US (1) US20100068085A1 (fr)
EP (1) EP2088322A4 (fr)
JP (1) JP5118340B2 (fr)
CN (1) CN101535646A (fr)
WO (1) WO2008066156A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010019457A (ja) * 2008-07-09 2010-01-28 Sanden Corp 冷凍回路
JPWO2009157320A1 (ja) * 2008-06-24 2011-12-08 三菱電機株式会社 冷凍サイクル装置及び空気調和装置
KR101216317B1 (ko) * 2008-06-17 2012-12-27 미쓰비시덴키 가부시키가이샤 로터리 압축기
JP5400043B2 (ja) * 2008-06-16 2014-01-29 三菱電機株式会社 スクロール圧縮機
WO2015140882A1 (fr) * 2014-03-17 2015-09-24 三菱電機株式会社 Dispositif de réfrigération

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JP5062160B2 (ja) * 2008-12-19 2012-10-31 株式会社デンソー 冷凍サイクル及び圧縮機
KR101192346B1 (ko) * 2010-04-22 2012-10-18 엘지전자 주식회사 히트 펌프식 급탕장치
KR101155497B1 (ko) 2010-04-23 2012-06-15 엘지전자 주식회사 히트펌프식 급탕장치
JP6367164B2 (ja) * 2015-07-17 2018-08-01 株式会社鷺宮製作所 圧力作動弁及び冷凍サイクル
JP6977651B2 (ja) * 2018-03-30 2021-12-08 株式会社豊田自動織機 ピストン式圧縮機
WO2020049844A1 (fr) * 2018-09-06 2020-03-12 日立ジョンソンコントロールズ空調株式会社 Compresseur et dispositif à cycle frigorifique doté dudit compresseur
CN109958597B (zh) * 2019-03-12 2021-04-23 复盛实业(上海)有限公司 一种空气压缩设备及其热交换系统
CN112443679B (zh) * 2019-06-24 2024-02-13 杭州三花研究院有限公司 热管理系统

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KR101216317B1 (ko) * 2008-06-17 2012-12-27 미쓰비시덴키 가부시키가이샤 로터리 압축기
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JP5118340B2 (ja) 2013-01-16
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CN101535646A (zh) 2009-09-16
EP2088322A1 (fr) 2009-08-12
US20100068085A1 (en) 2010-03-18

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