EP1865274A1 - Dampfkompressions-Kühlschaltung und Fahrzeugklimaanlagensystem mit der Kühlschaltung - Google Patents

Dampfkompressions-Kühlschaltung und Fahrzeugklimaanlagensystem mit der Kühlschaltung Download PDF

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Publication number
EP1865274A1
EP1865274A1 EP07010829A EP07010829A EP1865274A1 EP 1865274 A1 EP1865274 A1 EP 1865274A1 EP 07010829 A EP07010829 A EP 07010829A EP 07010829 A EP07010829 A EP 07010829A EP 1865274 A1 EP1865274 A1 EP 1865274A1
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EP
European Patent Office
Prior art keywords
low
stage compression
refrigerant
refrigeration circuit
intercooler
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP07010829A
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English (en)
French (fr)
Inventor
Kenichi Suzuki
Masato Tsuboi
Yuuichi Matsumoto
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Sanden Corp
Original Assignee
Sanden Corp
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Filing date
Publication date
Application filed by Sanden Corp filed Critical Sanden Corp
Publication of EP1865274A1 publication Critical patent/EP1865274A1/de
Withdrawn legal-status Critical Current

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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
    • 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
    • F04B25/00—Multi-stage pumps
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/04—Multi-stage pumps having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • 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
    • 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
    • F04B27/12—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 having plural sets of cylinders or pistons
    • 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
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element

Definitions

  • the present invention relates to a vapor-compression refrigeration circuit and an automotive air-conditioning system using the refrigeration circuit.
  • a vapor-compression refrigeration circuit is used, for example, in an air-conditioning system for a motor vehicle and has a circulation passage for circulating a refrigerant therethrough.
  • a circulation passage for circulating a refrigerant therethrough.
  • a compressor In the circulation passage are generally inserted a compressor, a heat radiator (condenser or gas cooler), a pressure reducer (expansion valve), and an evaporator in the mentioned order as viewed in the flowing direction of the refrigerant.
  • a compound compressor and an intercooler may be used, as disclosed in Unexamined Japanese Patent Publication No. H05-164041 .
  • the compound compressor has a low-stage compression section and a high-stage compression section connected in series with each other.
  • the intercooler is inserted in a refrigerant passage connecting between the discharge port of the low-stage compression section and the suction port of the high-stage compression section.
  • the refrigerant discharged from the low-stage compression section is cooled by the intercooler, and the refrigerant thus cooled by the intercooler is further compressed by the high-stage compression section, whereby the motive power consumed by the compressor as a whole is presumably reduced.
  • the compound compressor is not suited for operation at high rotating speeds. Accordingly, the compressor is not suited to be supplied with motive power from an automotive engine because the rotational speed of the automotive engine varies significantly.
  • the mountability of the refrigeration circuit onto a vehicle is low, because the refrigeration circuit requires an increased number of component parts as well as complicated piping.
  • An object of the present invention is to provide a vapor-compression refrigeration circuit provided with a compound compressor capable of stable and quiet operation even at high rotational speeds and also with an intercooler simplified in construction, and an automotive air-conditioning system using the refrigeration circuit.
  • the present invention provides a vapor-compression refrigeration circuit comprising: a compound compressor having a low-stage compression section and a high-stage compression section connected in series with each other and each adapted to perform a process of sucking in a refrigerant, a process of compressing the refrigerant, and a process of discharging the refrigerant; and an intercooler inserted in a refrigerant passage connecting between the low-stage compression section and the high-stage compression section, for cooling the refrigerant discharged from the low-stage compression section and then allowing the refrigerant to be sucked into the high-stage compression section.
  • the compound compressor includes: a swash plate; a cylinder bore and a piston constituting the low-stage compression section; a cylinder bore and a piston constituting the high-stage compression section; and conversion means for converting rotation of the swash plate to reciprocating motions of the pistons of the low- and high-stage compression sections.
  • rotation of the swash plate is converted to reciprocating motions of the pistons of the low- and high-stage compression sections. Accordingly, during the operation of the compressor, torque fluctuation is small, thus reducing vibration and noise. Also, since vibration can be reduced, the compressor is suited for operation at high rotational speeds.
  • the intercooler is combined integrally with the compound compressor.
  • the intercooler is combined integrally with the compound compressor, whereby the refrigeration circuit is simplified in construction.
  • each of the low- and high-stage compression sections has a suction port and a discharge port, both opening in the housing of the compound compressor
  • the intercooler includes a pipe member having opposite ends connected to the discharge port of the low-stage compression section and the suction port of the high-stage compression section, respectively, and an outer surface spaced from the housing of the compound compressor.
  • the pipe member of the intercooler is set apart from the outer surface of the housing of the compound compressor, whereby the refrigerant flowing through the pipe member is efficiently cooled.
  • the.intercooler has surface irregularities formed on one or both of the inner and outer peripheral surfaces of the pipe member.
  • the intercooler has surface irregularities formed on one or both of the inner and outer peripheral surfaces of the pipe member and thus has an increased surface area.
  • the refrigerant can therefore be efficiently cooled through the intercooler, and as a result, the refrigeration circuit has an improved coefficient of performance, despite its simple construction.
  • the intercooler is combined integrally with a heat radiator.
  • the intercooler since the intercooler is combined integrally with the radiator, the refrigerant can be efficiently cooled by the intercooler, so that the refrigeration circuit has a significantly high coefficient of performance.
  • the intercooler has an inlet connected to the discharge port of the low-stage compression section and an outlet connected to the suction port of the high-stage compression section, and a first pipe connecting between the inlet of the intercooler and the discharge port of the low-stage compression section and a second pipe connecting between the inlet of the heat radiator and the discharge port of the high-stage compression section are integrally formed into a one-piece body.
  • the first pipe connecting between the inlet of the intercooler and the discharge port of the low-stage compression section and the second pipe connecting between the inlet of the radiator and the discharge port of the high-stage compression section are integrally formed as a one-piece body.
  • the number of pipes used is reduced, making it possible to simplify the construction of the refrigeration circuit.
  • the vapor-compression refrigeration circuit further comprises an internal heat exchanger having a high-temperature section inserted in a refrigerant passage extending between the outlet of the radiator and the inlet of a pressure reducer, and a low-temperature section inserted in a refrigerant passage extending between the outlet of an evaporator and the inlet of the low-stage compression section of the compound compressor.
  • the enthalpy of the refrigerant at the inlet of the evaporator is reduced.
  • the amount of change of the enthalpy in the evaporator increases, making it possible to further increase the coefficient of performance of the refrigeration circuit.
  • the refrigerant used is CO 2 .
  • the preferred refrigeration circuit uses CO 2 as the refrigerant and thus is environmentally friendly. Where CO 2 is used as the refrigerant, the refrigerant pressure in the high-pressure side of the refrigeration circuit is considerably high. However, since the refrigeration circuit is provided with the compound compressor and the intercooler, increase in the motive power needed to drive the compressor is restrained, ensuring a sufficiently high coefficient of performance.
  • An automotive air-conditioning system is provided with any one of the aforementioned vapor-compression refrigeration circuits.
  • the automotive air-conditioning system equipped with any one of the aforementioned refrigeration circuits, vibration and noise can be reduced, and therefore, the ride comfort of the vehicle improves. Also, since the compound compressor used in the air-conditioning system is suited for operation at high rotational speeds, the motive force of the engine can be transmitted to the compressor by using simple mechanical equipment. Further, the intercooler or the piping of the refrigeration circuit is simple in construction, and therefore, it is easy to mount the air-conditioning system onto a vehicle.
  • FIG. 1 schematically shows a refrigeration circuit of an automotive air-conditioning system according to one embodiment of the present invention.
  • the refrigeration circuit is of a vapor compression type and is used to cool or dehumidify the air supplied to a passenger compartment 2.
  • the refrigeration circuit has a circulation passage 4, and CO 2 refrigerant (R-744), which is a natural refrigerant and which contains a small amount of lubricating oil as a refrigerating machine oil, is circulated through the circulation passage 4.
  • the circulation passage 4 extends from an engine compartment 6 into a front part of the passenger compartment 2 through a partition wall 8.
  • the front part of the passenger compartment 2 is partitioned by an instrument panel 10 and serves as a machinery compartment 12.
  • a compressor 14 In the circulation passage 4, a compressor 14, a heat radiator (gas cooler) 16, a high-temperature section 18a of an internal heat exchanger 18, a pressure reducer (expansion valve) 20, an evaporator 22, an accumulator (gas-liquid separator) 24 and a low-temperature section 18b of the internal heat exchanger 18 are inserted in the mentioned order as viewed in the flowing direction of the refrigerant.
  • the refrigeration circuit operates in the manner described below.
  • the compressor 14 is driven by motive power transmitted from an engine 26 via a belt to suck in the low-temperature, low-pressure refrigerant of gas phase from the low-temperature section 18b of the internal heat exchanger 18. Then, the compressor 14 compresses the refrigerant into a high-temperature, high-pressure supercritical state and discharges the compressed refrigerant to the radiator 16. Namely, the compressor 14 successively performs the process of sucking in the refrigerant, the process of compressing the refrigerant, and the process of discharging the refrigerant.
  • the refrigerant is circulated through the circulation passage 4 to successively pass through the radiator 16, the high-temperature section 18a of the internal heat exchanger 18, the pressure reducer 20, the evaporator 22, the accumulator 24, and the low-temperature section 18b of the internal heat exchanger 18.
  • a fan 28 is arranged near the radiator 16.
  • the refrigerant When passing through the radiator 16, the refrigerant is cooled by the air flow produced by the fan 28 or produced as the vehicle runs, so that the temperature of the refrigerant lowers.
  • the temperature thereof When the refrigerant passes through the high-temperature section 18a of the internal heat exchanger 18 thereafter, the temperature thereof further lowers because the refrigerant is cooled due to heat exchange with the refrigerant passing through the low-temperature section 18b of the internal heat exchanger 18.
  • the high-pressure, supercritical or liquid-phase refrigerant cooled in this manner then passes through the pressure reducer 20, where the refrigerant is allowed to expand, causing a drop in both the pressure and temperature of the refrigerant. Consequently, the refrigerant turns into a low-temperature, low-pressure gas-liquid mixture state (two-phase state).
  • a blower 30 is arranged close to the evaporator 22.
  • the liquid-phase component contained therein evaporates while removing heat from the ambient air, whereby the air flow produced by the blower 30 and flowing around the evaporator 22 is cooled.
  • the cooled air flows into the passenger compartment 2, so that the passenger compartment 2 is cooled or dehumidified.
  • the low-temperature, low-pressure refrigerant of which part of the liquid-phase component has evaporated in the evaporator 22, then passes through the accumulator 24, where the remaining liquid-phase component is substantially totally removed. Subsequently, the low-temperature, low-pressure refrigerant in the gas phase passes through the low-temperature section 18b of the internal heat exchanger 18, in which the refrigerant is superheated due to heat exchange with the refrigerant passing through the high-temperature section 18a of the internal heat exchanger 18. The superheated refrigerant is sucked into the compressor 14, and the aforementioned cycle is repeated thereafter.
  • the compressor 14 is a compound compressor having a low-stage compression section 34 and a high-stage compression section 36 connected in series with each other with an intercooler 32 therebetween.
  • the compressor 14 has a basic construction similar to a variable-displacement swash plate compressor, as shown in FIG. 2.
  • the compressor 14 has a cylinder block 40 having a cylindrical shape, and seven cylinder bores 42, for example, are formed in the cylinder block 40.
  • the cylinder bores 42 are arranged around the axis of the cylinder block 40 concentrically therewith and penetrate through the cylinder block 40 in its axial direction.
  • the cylinder block 40 is fitted into one end portion of a cylindrical casing 44.
  • a crank chamber 46 is defined inside the casing 44 and between the cylinder block 40 and the other end wall of the casing 44.
  • An end portion of a piston 48 received in each cylinder bore 42 projects into the crank chamber 46.
  • a drive shaft 50 extends through the crank chamber 46 parallel with the pistons 48 and is rotatably supported by radial bearings and thrust bearings.
  • the drive shaft 50 penetrates through the other end wall of the casing 44, and a driven unit of an electromagnetic clutch 52 is fixed on the outer end portion of the drive shaft 50.
  • a drive unit, with which the driven unit is coupled by electromagnetic force, is rotatably supported on the casing 44 by a radial bearing.
  • the drive unit has a pulley 54, and a belt is passed around the pulley 54 and the output shaft of the engine 26.
  • a base rotor 56 is securely fixed on a portion of the drive shaft 50 extending through the crank chamber 46 and is coupled through a hinge 58 to the boss 60.
  • the drive shaft 50 penetrates through the boss 60, and the swash plate 62, which is annular in shape, is securely fitted on the boss 60. Accordingly, the swash plate 62 is rotatable together with the drive shaft 50 and is also tiltable with respect to the drive shaft 50.
  • the outer peripheral portion of the swash plate 62 is positioned in recesses formed at the projecting end portions of the individual pistons 48, and a pair of semispherical shoes 64 are arranged in each of the recesses.
  • Each pair of shoes 64 hold the swash plate 62 from opposite sides thereof, as viewed in the thickness direction of the swash plate 62, so that the individual pistons 48 are coupled to the swash plate 62 by the shoes 64. Consequently, rotation of the drive shaft 50 is converted to reciprocating motions of the pistons 48 through the base rotor 56, the hinge 58, the boss 60, the swash plate 62, and the shoes 64.
  • a cylinder head 66 which constitutes the housing of the compressor 14 together with the casing 44, is airtightly fixed to the one end of the casing 44 with a valve plate 68 and a gasket interposed between the cylinder head 66 and the cylinder block 40.
  • the valve plate 68 has regions closing the respective cylinder bores 42, and a suction hole 70 and a discharge hole 72 are formed through each region.
  • Each suction hole 70 is opened and closed by a suction reed valve arranged on the same side as the cylinder bore 42, and each discharge hole 72 is opened and closed by a discharge reed valve 74 arranged on the same side as the cylinder head 66.
  • the cylinder head 66 has a low-stage suction chamber 78, a low-stage discharge chamber 80, a high-stage suction chamber 82 and a high-stage discharge chamber 84 defined therein in an airtight fashion with respect to one another.
  • four cylinder bores 42a out of the seven cylinder bores 42, communicate with the low-stage suction chamber 78 and the low-stage discharge chamber 80 through the suction holes 70 and the discharge holes 72, respectively.
  • the remaining three cylinder bores 42b communicate with the high-stage suction chamber 82 and the high-stage discharge chamber 84 through the suction holes 70 and the discharge holes 72, respectively.
  • the cylinder head 66 has a low-stage suction port 86, a low-stage discharge port 88, a high-stage suction port 90 and a high-stage discharge port 92, all opening in the outer surface thereof.
  • the low-stage suction port 86, the low-stage discharge port 88, the high-stage suction port 90 and the high-stage discharge port 92 communicate respectively with the low-stage suction chamber 78, the low-stage discharge chamber 80, the high-stage suction chamber 82, and the high-stage discharge chamber 84.
  • the low-stage suction port 86 is connected with the outlet of the low-temperature section 18b of the internal heat exchanger 18.
  • the high-stage discharge port 92 is connected to the inlet of the radiator 16. Accordingly, the low-stage suction port 86 functions as the suction port of the compressor 14, and the high-stage discharge port 92 functions as the discharge port of the compressor 14.
  • the low-stage discharge port 88 and the high-stage suction port 90 are connected, for example, by brazing, with the respective opposite ends of a heat exchange pipe 94 serving as the intercooler 32, as shown in FIG. 4.
  • the heat exchange pipe 94 has a plurality of collar-shaped fins 96 securely brazed to the outer peripheral surface of an intermediate portion thereof.
  • the heat exchange pipe 94 is spaced from the outer surface of the cylinder head 66, except for the opposite ends thereof.
  • the refrigerant delivered from the low-temperature section 18b of the internal heat exchanger 18 flows into the low-stage suction chamber 78 through the low-stage suction port 86 and then is sucked into the cylinder bores 42a through the respective suction holes 70.
  • the state of the refrigerant in the low-stage suction chamber 78 is indicated at point A in the Mollier diagram of FIG. 5.
  • the refrigerant sucked into the respective cylinder bores 42a is compressed and then discharged into the low-stage discharge chamber 80 through the respective discharge holes 72.
  • the state of the refrigerant in the low-stage discharge chamber 80 is indicated at point B in FIG. 5.
  • the refrigerant in the low-stage discharge chamber 80 then flows into the intercooler 32 through the low-stage discharge port 88. While passing through the intercooler 32, the refrigerant is cooled due heat exchange with the air (external medium) surrounding the intercooler 32. The refrigerant thus cooled in the intercooler 32 flows into the high-stage suction chamber 82 through the high-stage suction port 90. The state of the refrigerant in the high-stage suction chamber 82 is indicated at point C in FIG. 5.
  • the refrigerant in the high-stage suction chamber 82 is introduced into the cylinder bores 42b through the respective suction holes 70, then compressed and discharged into the high-stage discharge chamber 84 through the respective discharge holes 72.
  • the state of the refrigerant in the high-stage discharge chamber 84 is indicated at point D in FIG. 5.
  • the refrigerant in the high-stage discharge chamber 84 is then delivered from the compressor 14 through the high-stage discharge port 92 and flows to the inlet of the radiator 16.
  • the four pistons 48a and their associated cylinder bores 42a constitute the low-stage compression section 34
  • the three pistons 48b and their associated cylinder bores 42b constitute the high-stage compression section 36.
  • intercooler 32 is combined integrally with the compressor 14, and thus the refrigeration circuit is simplified in construction.
  • the heat exchange pipe 94 of the intercooler 32 is, except for its opposite ends, set apart from the outer surface of the compressor housing, namely, the casing 44 and the cylinder head 66, whereby the refrigerant flowing through the intercooler 32 is efficiently cooled.
  • the heat exchange pipe 94 of the intercooler 32 has the fins 96 attached to its outer surface and has an increased surface area. Accordingly, the refrigeration circuit can cool the refrigerant efficiently through the heat exchange pipe 94 and has a high coefficient of performance, despite its simple construction.
  • the refrigerant to be used is not limited to CO 2 .
  • CO 2 is preferred.
  • the refrigerant pressure in the high-pressure side of the refrigeration circuit is considerably high.
  • the aforementioned refrigeration circuit is provided with the compressor 14 and the intercooler 32, increase in the motive power needed to drive the compressor 14 is restrained, thus ensuring a sufficiently high coefficient of performance.
  • the refrigeration circuit of the foregoing embodiment includes the internal heat exchanger 18, but the internal heat exchanger 18 may be omitted.
  • the internal heat exchanger 18 it is possible to lower the enthalpy of the refrigerant at the inlet of the evaporator 22. As a consequence, the amount of change of the enthalpy in the evaporator 22 increases, making it possible to further increase the coefficient of performance.
  • rotation of the swash plate 62 is converted to reciprocating motions of the pistons 48 by means of the shoes 64.
  • the shoes 64 may be replaced by a wobble plate, which moves from side to side as the swash plate rotates, and connecting rods connecting the outer peripheral portion of the wobble plate and the respective pistons.
  • the compressor may be a wobble plate compressor.
  • a fixed-displacement compressor or an electrically-driven compressor may be used.
  • the heat exchange pipe 94 is used as the intercooler 32.
  • a low fin tube shown in FIG. 6 may be used.
  • the low fin tube has a helical ridge 98 formed on an outer peripheral surface thereof by rolling and has an increased surface area because of its ridge 98.
  • an internally grooved pipe shown in FIG. 7 may also be used.
  • the internally grooved pipe has a plurality of grooves 100 cut in an inner peripheral surface thereof and thus has an increased surface area.
  • heat exchange pipe 94 may be replaced by a flat pipe shown in FIG. 8.
  • the flat pipe has a plurality of internal passages 102, thereby increasing the internal surface area that contacts with the refrigerant.
  • grooves as surface irregularities may be cut in the inner peripheral surface of the heat exchange pipe 94 with fins, or conversely, fins may be attached to the outer surface of the internally grooved pipe or flat pipe.
  • the intercooler 32 is joined integrally to the compressor 14.
  • an intercooler 104 may be combined integrally with the radiator 16.
  • FIGS. 10A, 10B and 10C show the radiator 16 and the intercooler 104.
  • the intercooler 104 is attached, for example, to a lower part of the radiator 16.
  • the intercooler 104 can also be efficiently cooled by the air flow produced by the fan 28 or produced as the vehicle runs. As a result, the coefficient of performance of the refrigeration circuit significantly increases.
  • a discharge pipe 106 shown in FIG. 11 is used to connect between the inlet of the radiator 16 and the high-stage discharge port 92 and between the inlet of the intercooler 104 and the low-stage discharge port 88.
  • the discharge pipe 106 has two internal passages separated from each other by a partition wall 108.
  • a first pipe connecting between the inlet of the intercooler 104 and the low-stage discharge port 88 and a second pipe connecting between the inlet of the radiator 16 and the high-stage discharge port 92 are integrally formed into a one-piece body.
  • the use of the single discharge pipe 106 does not entail the situation where the refrigerant flowing from the low-stage discharge port 88 to the intercooler 104 is heated by the refrigerant flowing from the high-stage discharge port 92 to the radiator 16, or the situation where the refrigerant flowing from the high-stage discharge port 92 to the radiator 16 is cooled by the refrigerant flowing from the low-stage discharge port 88 to the intercooler 104.
  • the vapor-compression refrigeration circuit of the present invention is applicable not only to automotive air-conditioning system but to refrigerator-freezer and the like.
  • the ride comfort of the vehicle improves because vibration and noise of the compressor 14 can be reduced.
  • the motive force of the engine 26 can be transmitted to the compressor 14 by using simple mechanical equipment.
  • the intercooler 32 or the discharge pipe 106 of the refrigeration circuit is simple in construction, which makes it easier to mount the air-conditioning system onto a vehicle.

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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)
EP07010829A 2006-06-06 2007-05-31 Dampfkompressions-Kühlschaltung und Fahrzeugklimaanlagensystem mit der Kühlschaltung Withdrawn EP1865274A1 (de)

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JP2006157306A JP2007327355A (ja) 2006-06-06 2006-06-06 蒸気圧縮式冷凍回路及び当該回路を用いた車両用空調システム

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Publication number Priority date Publication date Assignee Title
DE102012003567A1 (de) * 2012-02-27 2013-08-29 Gea Bock Gmbh Kälteanlage
CN106885392A (zh) * 2017-02-28 2017-06-23 重庆长安汽车股份有限公司 一种混合动力车用中冷热泵联合系统及其制冷制热方法

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KR102188240B1 (ko) * 2019-01-04 2020-12-08 (주)테크니컬코리아 왕복동식 압축기
CN111102759A (zh) * 2019-12-18 2020-05-05 南京久鼎精机冷冻设备有限公司 一种节能型co2双机双级制冷多联机系统

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EP1462739A2 (de) * 2003-03-27 2004-09-29 Sanyo Electric Co., Ltd. Gerät mit Kältemittelkreislauf
US20050279127A1 (en) * 2004-06-18 2005-12-22 Tao Jia Integrated heat exchanger for use in a refrigeration system

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US4516913A (en) * 1977-11-30 1985-05-14 Techniques Girodin Multistage drum compressor
US4802826A (en) * 1982-06-25 1989-02-07 Rix Industries Sealed, self-contained, liquid-cooled, gas compressor
US20030059316A1 (en) * 2000-01-11 2003-03-27 Kazuo Murakami Multistage type piston compressor
EP1462740A2 (de) * 2003-03-24 2004-09-29 Sanyo Electric Co., Ltd. Kältegerät
EP1462739A2 (de) * 2003-03-27 2004-09-29 Sanyo Electric Co., Ltd. Gerät mit Kältemittelkreislauf
US20050279127A1 (en) * 2004-06-18 2005-12-22 Tao Jia Integrated heat exchanger for use in a refrigeration system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012003567A1 (de) * 2012-02-27 2013-08-29 Gea Bock Gmbh Kälteanlage
CN106885392A (zh) * 2017-02-28 2017-06-23 重庆长安汽车股份有限公司 一种混合动力车用中冷热泵联合系统及其制冷制热方法
CN106885392B (zh) * 2017-02-28 2019-04-09 重庆长安汽车股份有限公司 一种混合动力车用中冷热泵联合系统及其制冷制热方法

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