US20080078191A1 - Rotary compressor and heat pump system - Google Patents

Rotary compressor and heat pump system Download PDF

Info

Publication number
US20080078191A1
US20080078191A1 US11/882,475 US88247507A US2008078191A1 US 20080078191 A1 US20080078191 A1 US 20080078191A1 US 88247507 A US88247507 A US 88247507A US 2008078191 A1 US2008078191 A1 US 2008078191A1
Authority
US
United States
Prior art keywords
compressor
refrigerant
closed container
discharge
peripheral surface
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.)
Abandoned
Application number
US11/882,475
Other languages
English (en)
Inventor
Taku Morishita
Naoya Morozumi
Kenshi Ueda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fujitsu General Ltd
Original Assignee
Fujitsu General Ltd
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 Fujitsu General Ltd filed Critical Fujitsu General Ltd
Assigned to FUJITSU GENERAL LIMITED reassignment FUJITSU GENERAL LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MORISHITA, TAKU, MOROZUMI, NAOYA, UEDA, KENSHI
Publication of US20080078191A1 publication Critical patent/US20080078191A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • 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
    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/19—Temperature
    • 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
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • 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
    • 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
    • F25B2600/2513—Expansion valves
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D29/00—Arrangement or mounting of control or safety devices
    • F25D29/005—Mounting of control devices
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to a rotary compressor used for air conditioners and water heaters. More particularly, it relates to a technique used to control the capacity of a heat pump system and to ensure the reliability of a compressor by exactly detecting the discharge temperature of a refrigerant compressed by a compression section.
  • the compressor used for the refrigeration cycle of a heat pump system has a problem in that if the degree of superheat of the intake refrigerant thereof is too high, the density of intake refrigerant decreases, so that the capacity and efficiency of compressor decreases, and a problem in that the temperature of the whole of the compressor rises, so that the reliability of compressor, especially the durability of motor winding and insulating paper, decreases.
  • the intake refrigerant is not in a superheated state but in a wet state, that is, in a state in which the ratio of liquid is high, the lubricating oil in the compression section is diluted by a liquid refrigerant, resulting in poor lubrication. If the ratio of liquid increases further, the intake refrigerator becomes in a liquid compression state, which presents a problem in that an abnormal rise in pressure leads to damage of compression section.
  • the temperature of intake refrigerant in the compressor does not change regardless of the ratio of liquid. Generally, therefore, the temperature of discharge refrigerant after being compressed is detected, by which the intake state is estimated from the fact that the compression is substantially in an adiabatic process.
  • Patent Document 1 Japanese Patent Application Publication No. 2005-147437
  • Patent Document 2 Japanese Patent Application Publication No. H07-174417
  • a discharge temperature sensor is provided within the compressor, the degree of superheat of intake refrigerant in the compressor is estimated by using the detected discharge refrigerant temperature of compressor as one piece of information, and to make the degree of superheat in a proper state, the throttle amount of an expansion valve, the number of revolutions of the compressor, and the number of revolutions of a fan of a condenser or an evaporator are controlled.
  • the compression section of a general hermetic rotary compressor is arranged in a lower part of a closed container, and therefore the refrigerant discharged from the compression section passes through the surroundings of the motor arranged in an upper part of the closed container and is discharged to the outside of the closed container through the discharge pipe in an upper part.
  • the compressor of this type has both of a cause for the rise in temperature due to absorption of loss heat of motor during the time from when the refrigerant is discharged from the compression section to when it reaches the discharge pipe and a cause for the fall in temperature due to heat release from the compressor to the surroundings thereof, so that the temperature detected in the discharge pipe in the upper part of the compressor differs from the temperature immediately after the discharge from the compression section.
  • the injection refrigerant is generally sucked into the compressor without passing through an accumulator. Therefore, to properly keep the degree of superheat or the dryness in the compressor intake state of the injection refrigerant, it is necessary to more exactly detect the discharge temperature of compressor.
  • a problem to be solved by the present invention is that in a rotary compressor in which a motor and a compression section are contained in a closed container, the temperature of a refrigerant discharged from the compression section can be detected more exactly without being influenced by variable factors existing around the compression section, by which the capacity of a heat pump system is controlled properly, and the reliability of compressor is ensured.
  • the present invention provides a closed rotary compressor of what is called an interior high pressure type, that is, a type in which the compressor has a motor provided in an upper part of a cylindrical closed container and a compression section provided in a lower part thereof, and a refrigerant compressed by the compression section is discharged to the outside through a discharge pipe provided in an upper end part of the closed container after passing through the interior of the closed container, wherein a muffler chamber is provided on the upper side of the compression section to reduce pressure pulsation of refrigerant discharged from the compression section, and to detect the temperature of compressed refrigerant near an upper muffler discharge hole for discharging the refrigerant from the muffler chamber into the closed container, a discharge temperature sensor for detecting the temperature of compressed refrigerant is provided on the outer peripheral surface of the closed container approximately at the height at which the upper muffler discharge hole is positioned.
  • an interior high pressure type that is, a type in which the compressor has a motor provided in an upper part of a
  • an upper muffler cover has a horizontal end plate part, a vertical side plate part, and the upper muffler discharge hole which is provided in the side plate part and is open toward the inner peripheral surface of the closed container; and a discharge temperature sensor for detecting the temperature of compressed refrigerant is provided on the outer peripheral surface of the closed container opposed to the upper muffler discharge hole.
  • the upper muffler cover has a horizontal end plate part, a vertical side plate part, and a cut and raised part which is provided in the end plate part and is open toward the inner peripheral surface of the closed container as an upper muffler discharge hole; and a discharge temperature sensor for detecting the temperature of compressed refrigerant is provided on the outer peripheral surface of the closed container opposed to the upper muffler discharge hole.
  • the upper muffler cover has an upper muffler pipe which is fixed to the upper muffler cover and one end of which is open to an upper muffler chamber and the other end of which is open toward the inner peripheral surface of the closed container as an upper muffler discharge hole; and a discharge temperature sensor for detecting the temperature of compressed refrigerant is provided on the outer peripheral surface of the closed container opposed to the upper muffler discharge hole.
  • the upper muffler cover has a horizontal end plate part, a vertical side plate part, a projecting part provided in the side plate part so as to be close to the inner peripheral surface of the closed container, and an upper muffler discharge hole which is provided in the projecting part and is open toward the inner peripheral surface of the closed container; and a discharge temperature sensor for detecting the temperature of compressed refrigerant is provided on the outer peripheral surface of the closed container opposed to the upper muffler discharge hole.
  • the end plate part of the upper bearing has a bearing end plate discharge passage one end of which is open to the upper muffler chamber and the other end of which is open toward the inner peripheral surface of the closed container as an upper muffler discharge hole; and a discharge temperature sensor for detecting the temperature of compressed refrigerant is provided on the outer peripheral surface of the closed container opposed to the upper muffler discharge hole.
  • the present invention is preferably applied to a rotary compressor in which the number of revolutions is variable.
  • the present invention is preferably applied to a two-stage compression rotary compressor in which the compression section has a low stage side compression section arranged on the lower side, a high stage side compression section arranged on the upper side, a two-stage compression section being formed by connecting the discharge side of the low stage side compression section to the suction side of the high stage side compression section by an intermediate interconnection passage; and the compression section also has a low-pressure suction pipe connected to the suction side of the low stage side compression section, and an intermediate-pressure suction pipe connected to the suction side of the high stage side compression section via the intermediate interconnection passage.
  • the present invention embraces any mode described below as a heat pump system using the rotary compressor in accordance with the present invention.
  • a heat pump system including a refrigeration cycle in which a compressor, a condenser, an expansion mechanism, and an evaporator are connected in succession by a line; and a control unit which detects the temperatures of a plurality of locations of the refrigeration cycle and controls the number of revolutions of the compressor and the throttle amount of the expansion mechanism, wherein the rotary compressor described in any one of claims 1 to 7 is used as the compressor; and based on the temperature detected by a discharge temperature sensor provided on the outer peripheral surface of a closed container of the compressor, the throttle amount of the expansion mechanism and the number of revolutions of the compressor are controlled, and the degree of superheat of a refrigerant sucked into the compressor is kept proper.
  • a heat pump system provided with a gas injection cycle, which includes a basic refrigeration cycle in which a compressor, a condenser, a basic cycle expansion mechanism, and an evaporator are connected in succession by a line; a branch pipe which branches some of a high-pressure refrigerant behind the outlet of the condenser from the basic refrigeration cycle as an injection refrigerant; an injection expansion mechanism which decompresses the injection refrigerant to an intermediate pressure between the pressure of the condenser and the pressure of the evaporator; an internal heat exchanger which heat-exchanges the decompressed injection refrigerant with the branched high-pressure refrigerant of basic refrigeration cycle; an injection line which sucks the injection refrigerant, having been subjected to the heat exchange, during the compression process of the compressor; and a control unit which detects the temperatures of a plurality of locations of the refrigeration cycle and controls the number of revolutions of the compressor, the throttle amount of the basic cycle expansion mechanism, and the throttle amount of the injection expansion mechanism,
  • a heat pump system provided with a gas injection cycle, which includes a basic refrigeration cycle configured by connecting a compressor, a condenser, a first expansion mechanism, an intermediate-pressure gas-liquid separator, a second expansion mechanism, and an evaporator in succession by a line; an injection pipe which branches a gas refrigerant separated by the intermediate-pressure gas-liquid separator from the basic refrigeration cycle as an injection refrigerant and sucks the injection refrigerant during the compression process of the compressor; and a control unit which detects the temperatures of a plurality of locations of the refrigeration cycle and controls the number of revolutions of the compressor, the throttle amount of the first expansion mechanism, and the throttle amount of the second expansion mechanism, wherein the rotary compressor described in claim 8 is used as the compressor, the discharge pipe of the compressor is connected to the condenser, the low-pressure suction pipe of the compressor is connected to the evaporator, and the intermediate-pressure suction pipe of the compressor is connected to the injection line; and based on the temperature detected by a discharge temperature sensor
  • the temperature of refrigerant discharged from the compression section can be detected more exactly without being influenced by variable factors, such as the motor, existing around the compression section.
  • the state of refrigerant sucked into the compressor that is, the degree of superheat or the dryness thereof can be estimated more exactly, and therefore the capacity of heat pump system can be controlled and the reliability of compressor can be ensured at a low cost.
  • the degree of superheat or the dryness of injection refrigerant sucked into the compressor can be kept proper.
  • FIG. 1A is a general sectional view of a rotary compressor in accordance with a first embodiment of the present invention
  • FIG. 1B is a transverse sectional view of a compression section of a rotary compressor in accordance with a first embodiment of the present invention
  • FIG. 1C is a configuration diagram of a refrigeration cycle in accordance with a first embodiment of the present invention.
  • FIG. 2 is a partial sectional view of a lower part of a rotary compressor in accordance with a second embodiment of the present invention
  • FIG. 3A is a perspective view of an upper muffler cover of a rotary compressor in accordance with a third embodiment of the present invention.
  • FIG. 3B is a partial sectional view of a lower part of a rotary compressor in accordance with a third embodiment of the present invention.
  • FIG. 4 is a partial sectional view of a lower part of a rotary compressor in accordance with a fourth embodiment of the present invention.
  • FIG. 5A is a perspective view of an upper muffler cover of a rotary compressor in accordance with a fifth embodiment of the present invention.
  • FIG. 5B is a partial sectional view of a lower part of a rotary compressor in accordance with a fifth embodiment of the present invention.
  • FIG. 6 is a partial sectional view of a lower part of a rotary compressor in accordance with a sixth embodiment of the present invention.
  • FIG. 7A is a general sectional view of a rotary compressor in accordance with a seventh embodiment of the present invention.
  • FIG. 7B is a configuration diagram of a refrigeration cycle in accordance with a seventh embodiment of the present invention.
  • FIG. 8 is a configuration diagram of a refrigeration cycle in accordance with an eighth embodiment of the present invention.
  • FIG. 1A is a general sectional view of a rotary compressor in accordance with the first embodiment of the present invention
  • FIG. 1B is a transverse sectional view of the compression section of the rotary compressor in accordance with the first embodiment of the present invention
  • FIG. 1C is a configuration diagram of a refrigeration cycle in accordance with the first embodiment of the present invention.
  • a rotary compressor 1 is configured so that a cylindrical closed container 2 is arranged in the vertical direction, and a motor 6 and a compression section 3 are provided in an upper part and a lower part of the closed container, respectively.
  • the compression section 3 is a two-cylinder type rotary compressor having a first compression section 3 A and a second compression section 3 B.
  • a discharge pipe 26 for discharging a refrigerant discharged from the compression section 3 into the closed container to the outside of the closed container.
  • a stator 61 of the motor 6 is shrinkage fitted in the closed container 2
  • a rotor 62 of the motor 6 is shrinkage fitted on a shaft 31 that mechanically connects the motor 6 to the compression section 3 .
  • the compression section 3 has a cylinder 32 and a cylindrical piston 33 housed in a cylindrical cylinder bore 321 formed on the inside of the cylinder 32 , and a working chamber 11 for the refrigerant is formed between the inner peripheral surface of the cylinder bore 321 and the outer peripheral surface of the piston 33 .
  • the cylinder 32 is provided with a vane groove 322 extending from the cylinder bore 321 toward the outer periphery of the cylinder 32 , and a flat plate-shaped vane 34 is provided in the vane groove 322 .
  • a spring 38 is provided between the vane 34 and the inner peripheral surface of the closed container 2 so that the tip end of the vane 34 is brought into sliding contact with the outer peripheral surface of the piston 33 by an urging force of the spring 38 , and thereby the working chamber 11 is partitioned into a suction chamber 111 and a compression chamber 112 .
  • the upper first compression section 3 A and the lower compression section 3 B of the compression section 3 have the same basic configuration except that the pistons 33 are out of phase by 180°. Next, referring again to FIG. 1A , the whole of the compressor 1 is explained.
  • the compression section 3 has a first cylinder 32 A corresponding to the first compression section 3 A, a second cylinder 32 B corresponding to the second compression section 3 B, an upper bearing 36 provided on the upper side of the first cylinder 32 A, a lower bearing 37 provided on the lower side of the second cylinder 32 B, and an intermediate partitioning plate 35 provided between the first cylinder 32 A and the second cylinder 32 B, so that the upper and lower sides of the working chambers 11 of the two compression sections 3 A and 3 B are closed by an end plate part 361 of the upper bearing 36 , the intermediate partitioning plate 35 , and an end plate part 371 of the lower bearing.
  • an upper muffler cover 46 and a lower muffler cover 47 are provided, respectively, and an upper muffler chamber 56 and a lower muffler chamber 57 are formed to reduce pressure pulsation of the discharged refrigerant.
  • the upper muffler cover 46 , the upper bearing 36 , the first cylinder 32 A, the intermediate partitioning plate 35 , the second cylinder 32 B, the lower bearing 37 , and the lower muffler cover 47 are fixed integrally with bolts (not shown), and further the outer peripheral part of the upper bearing end plate part 361 is fixed to the closed container 2 by spot welding.
  • the upper bearing 36 and the lower bearing 37 have bearing parts 362 and 372 , respectively.
  • the shaft 31 is rotatably supported.
  • the shaft 31 has two crank parts 311 a and 311 b that are off-center in the 180° different direction, and the two crank parts 311 a and 311 b fit in the pistons 33 in the first compression section 3 A and the second compression section 3 B, respectively.
  • the piston 33 revolves while making sliding contact with the inner wall of the cylinder bore 321 . Accordingly, the vane 34 reciprocates following the revolution of the piston 33 , by which the volumes of the suction chamber 111 and the compression chamber 112 are changed continuously.
  • the suction chamber 111 of the first compression section 3 A is connected to a low-pressure suction pipe 71 via a suction hole 323 A provided in the first cylinder 32 A, and the compression chamber 112 of the first compression section 3 A communicates with the upper muffler chamber 56 via a compression section discharge hole 363 provided in the upper bearing end plate part 361 .
  • the low-pressure suction pipe 71 is connected to the suction hole 323 A via a suction connection pipe 27 , and a check valve 364 is provided in the compression section discharge hole 363 .
  • the suction chamber 111 on the suction side of the second compression section 3 B is connected to a low-pressure suction pipe 71 via a suction hole 323 B provided in the second cylinder 32 B, and the compression chamber 112 of the second compression section 3 B communicates with the lower muffler chamber 57 via a compression section discharge hole 373 provided in the lower bearing end plate part 371 .
  • the low-pressure suction pipe 71 is connected to the suction hole 323 B via a suction connection pipe 27 , and a check valve 374 is provided in the compression section discharge hole 373 .
  • FIG. 1A shows a state in which the check valves 364 and 374 are opened and are in contact with the valve guards 364 a and 374 a , respectively.
  • a muffler chamber communication hole (not shown) that passes through these elements continuously to cause the upper muffler chamber 56 and the lower muffler chamber 57 to communicate with each other is provided.
  • an upper muffler discharge hole 462 that opens to the interior of the closed container 2 is provided, and a discharge temperature sensor 20 is mounted on the outer peripheral surface of the closed container 2 approximately at the height of the upper muffler discharge hole 462 .
  • an accumulator 7 consisting of an independent closed vessel is provided.
  • an accumulator inlet pipe 72 connecting with the low-pressure side of a refrigeration cycle is provided, and at lower parts of the accumulator 7 , the two low-pressure suction pipes 71 that connect the interior of the accumulator 7 to the suction chambers 111 of the first compression section 3 A and the second compression section 3 B are provided.
  • the accumulator 7 is used to prevent a liquid refrigerant from being sucked into the compressor in the case where the liquid refrigerant is mixed in an intake refrigerant in a transient state such as the start time of compressor.
  • the explanation of the internal construction of the accumulator 7 is omitted because the internal construction thereof does not relate directly to the present invention.
  • the suction chamber 111 is located at a position at which it is isolated from the suction hole 323 , and is changed over to the compression chamber 112 as it is, by which the refrigerant is compressed.
  • the refrigerant discharged into the lower muffler chamber 57 reduces the pressure pulsation, which may cause noise, in the lower muffler chamber 57 , and then flows into the upper muffler chamber 56 through the muffler chamber communication hole (not shown), joining to the refrigerant discharged from the first compression section 3 A.
  • the joined refrigerant reduces the pressure pulsation, which may cause noise, in the upper muffler chamber 56 , and then is discharged into the closed container 2 through the upper muffler discharge hole 462 .
  • the refrigerant is introduced into a space above the motor 6 after passing through a notch portion (not shown) of a stator core 612 of the motor 6 , a gap between the stator core 612 and a winding 611 , and a gap between the stator 61 and the rotor 62 , and is discharged to a high-pressure side (condenser side) of the refrigeration cycle through the discharge pipe 26 .
  • the refrigerant compressed in the first compression section 3 A and the second compression section 3 B is discharged into the closed container 2 after passing through the upper muffler chamber 56 , and is discharged to the outside of the closed container 2 through the discharge pipe 26 after passing through the surroundings of the motor 6 .
  • the refrigeration cycle is formed by connecting the compressor 1 , a condenser 91 , a basic cycle expansion mechanism 93 , and an evaporator 92 in succession by using a line 99 .
  • reference symbol Ta denotes a temperature sensor for detecting the refrigerant temperature on the outlet side of the condenser 91
  • Tb denotes a temperature sensor for detecting the refrigerant temperature at an intermediate position in the condenser 91
  • Tc denotes a temperature sensor for detecting the refrigerant temperature at an intermediate position in the evaporator 92
  • Td denotes a sensor for detecting the temperature of intake refrigerant.
  • the high temperature and pressure gas refrigerant discharged from the compressor 1 is heat-exchanged with air in the condenser 91 to release heat, and becomes in a supercooled state.
  • the refrigerant in the supercooled state is decompressed in the basic cycle expansion mechanism 93 and becomes in a low temperature and pressure two-phase state.
  • the refrigerant in the low temperature and pressure two-phase state is heat-exchanged with air in the evaporator 92 to absorb heat and to be gasified, that is, becomes in a state having a degree of superheat, and is sucked into the compressor 1 .
  • the indoor air is cooled, so that the heat pump system serves as a cooler, and in the case where the condenser 91 is arranged in an indoor unit, the indoor air is heated, so that the heat pump system serves as a heater.
  • the heat pump system can be used as a cooling and heating machine.
  • the condenser 91 is heat-exchanged with water for hot-water supply, the heat pump system serves as a water heater.
  • the heat pump system of this embodiment is provided with a control unit 97 for keeping the refrigerant in the refrigeration cycle in a proper state.
  • the control unit 97 sends a signal for detecting at least condenser refrigerant temperature, evaporator refrigerant temperature, and compressor discharge temperature and controlling the throttle amount of the basic cycle expansion mechanism 93 and the number of revolutions of the compressor 1 to keep the refrigerant circulating amount of refrigeration cycle proper with respect to the capacity required in the heat pump system, and further to keep the state of refrigerant in the refrigeration cycle, that is, the degree of supercooling of refrigerant at the outlet of the condenser 91 in the refrigeration cycle and the degree of superheat of refrigerant in the low-pressure suction pipe 71 of the compressor 1 proper.
  • the discharge temperature sensor 20 is mounted on the outer peripheral surface of closed container opposed to a portion in which the refrigerant compressed in the closed container 2 of the compressor 1 comes into contact with the closed container 2 before passing through the surroundings of the motor 6 , by which the refrigerant temperature before heat exchange with the motor 6 , that is, immediately after the discharge from the compression section can be detected almost directly. Therefore, the throttle amount of the basic cycle expansion mechanism 93 and the number of revolutions of the compressor 1 can be controlled based on the detected temperature, and the degree of superheat of refrigerant in the low-pressure suction pipe 71 of the compressor 1 can be kept more proper.
  • FIG. 2 is a partial sectional view of the lower part of a rotary compressor in accordance with the second embodiment of the present invention.
  • the same reference symbols are applied to elements that are the same as those in FIG. 1A showing the first embodiment, and the detailed explanation thereof is omitted.
  • the refrigeration cycle is the same as that in the first embodiment shown in FIG. 1C .
  • the upper muffler cover 46 has an end plate part 463 and a side plate part 464 , and an upper muffler discharge hole 462 is provided in the side plate part 464 so that the refrigerant discharged from the upper muffler chamber 56 is directly sprayed onto the inner peripheral surface of the closed container 2 . Further, the discharge temperature sensor 20 is mounted on the outer peripheral surface of the closed container 2 opposed to the sprayed portion.
  • the difference between the closed container temperature in the portion in which the discharge temperature sensor 20 is mounted and the refrigerant temperature immediately after the discharge from the compression section can be made small as compared with the first embodiment, so that the degree of superheat of intake refrigerant can be kept proper with higher accuracy.
  • FIG. 3A is a perspective view of the upper muffler cover of a rotary compressor in accordance with the third embodiment of the present invention
  • FIG. 3B is a partial sectional view of a lower part of the rotary compressor in accordance with the third embodiment of the present invention.
  • the same reference symbols are applied to elements that are the same as those in FIG. 1A showing the first embodiment, and the detailed explanation thereof is omitted.
  • the refrigeration cycle is the same as that in the first embodiment shown in FIG. 1C .
  • a cut and raised part 465 capable of being pressed simultaneously with the pressing of the whole of the upper muffler cover is provided in the end plate part 463 of the upper muffler cover 46 .
  • the cut and raised part 465 is open toward the inner peripheral surface of the closed container 2 as the upper muffler discharge hole 462 so that the refrigerant discharged from the upper muffler chamber 56 is sprayed directly onto the inner peripheral surface of the closed container 2 .
  • the discharge temperature sensor 20 is mounted on the outer peripheral surface of the closed container 2 opposed to the sprayed portion.
  • the upper muffler discharge hole 462 that is open toward the inner surface of the closed container can be formed without separately fabricating the side plate part 464 of the upper muffler cover 46 as compared with the second embodiment, so that the degree of superheat of intake refrigerant can be kept proper with high accuracy at a lower cost.
  • FIG. 4 is a partial sectional view of the lower part of a rotary compressor in accordance with the fourth embodiment of the present invention.
  • the same reference symbols are applied to elements that are the same as those in FIG. 1A showing the first embodiment, and the detailed explanation thereof is omitted.
  • the refrigeration cycle is the same as that in the first embodiment shown in FIG. 1C .
  • an L-shaped upper muffler pipe 466 one end of which is open to the upper muffler chamber 56 and the other end of which is open toward the inner peripheral surface of the closed container 2 as the upper muffler discharge hole 462 is fixed to the end plate part 463 of the upper muffler cover 46 so that the refrigerant discharged from the upper muffler chamber 56 is sprayed directly onto the inner peripheral surface of the closed container 2 .
  • the discharge temperature sensor 20 is mounted on the outer peripheral surface of the closed container 2 opposed to the sprayed portion.
  • the upper muffler discharge hole 462 can be opened close to the inner peripheral surface of the closed container 2 as compared with the second and third embodiments, so that the degree of superheat of intake refrigerant can be kept proper with still higher accuracy.
  • FIG. 5A is a perspective view of the upper muffler cover of a rotary compressor in accordance with the fifth embodiment of the present invention
  • FIG. 5B is a partial sectional view of the lower part of the rotary compressor in accordance with the fifth embodiment of the present invention.
  • the same reference symbols are applied to elements that are the same as those in FIG. 1A showing the first embodiment, and the detailed explanation thereof is omitted.
  • the refrigeration cycle is the same as that in the first embodiment shown in FIG. 1C .
  • a projecting part 467 that is formed by bringing a part of the side plate part 464 of the upper muffler cover 46 close to the inner peripheral surface of the closed container 2 is provided, and further an opening 468 is provided in this projecting part 467 .
  • the opening 468 in the projecting part is used as the upper muffler discharge hole 462 that is open toward the inner peripheral surface of the closed container 2 so that the refrigerant discharged from the upper muffler chamber 56 is sprayed directly onto the inner peripheral surface of the closed container 2 .
  • the discharge temperature sensor 20 is mounted on the outer peripheral surface of the closed container 2 opposed to the sprayed portion.
  • the upper muffler discharge hole 462 that is open close to the inner peripheral surface of the closed container 2 can be formed without attaching a separate pipe to the upper muffler cover 46 as compared with the fourth embodiment, so that the degree of superheat of intake refrigerant can be kept proper with far higher accuracy at a lower cost.
  • FIG. 6 is a partial sectional view of the lower part of a rotary compressor in accordance with the sixth embodiment of the present invention.
  • the same reference symbols are applied to elements that are the same as those in FIG. 1A showing the first embodiment, and the detailed explanation thereof is omitted.
  • the refrigeration cycle is the same as that in the first embodiment shown in FIG. 1C .
  • a bearing end plate discharge passage 365 one end of which is open to the upper muffler chamber 56 and the other end of which is open toward the inner peripheral surface of the closed container 2 as the upper muffler discharge hole 462 is provided in the end plate part 361 of the upper bearing so that the refrigerant discharged from the upper muffler chamber 56 is sprayed directly onto the inner peripheral surface of the closed container 2 .
  • the discharge temperature sensor 20 is mounted on the outer peripheral surface of the closed container 2 opposed to the sprayed portion.
  • an opening can be provided close to the inner peripheral surface of the closed container 2 without providing the upper muffler discharge hole 462 in the body of the upper muffler cover 46 , so that the degree of superheat of intake refrigerant can be kept proper with high accuracy.
  • the compressor described in the first to sixth embodiments is a two-cylinder type rotary compressor provided with two compression sections.
  • the present invention is not limited to this type, and can be applied to one-cylinder type rotary compressor provided with one compression section.
  • FIG. 7A is a general sectional view of a rotary compressor in accordance with the seventh embodiment of the present invention
  • FIG. 7B is a configuration diagram of a refrigeration cycle in accordance with the seventh embodiment of the present invention.
  • FIG. 7A the same reference symbols are applied to elements that are the same as those in FIG. 1A showing the first embodiment, and the detailed explanation thereof is omitted.
  • the compressor 1 of the seventh embodiment is a rotary compressor provided with two compression sections like the compressor of the first embodiment.
  • points different from the compressor of the first embodiment are explained.
  • the compressor of the first embodiment has two compression sections connected in parallel with respect to the flow of refrigerant.
  • the compressor 1 of the seventh embodiment has two compression sections 3 L and 3 H connected in series with respect to the flow of refrigerant by connecting the discharge side of the low stage side compression section 3 L to the suction side of the high stage side compression section 3 H by using an intermediate interconnection pipe 82 .
  • the suction side of the low stage side compression section 3 L is connected to the accumulator 7 via the low-pressure suction pipe 71 .
  • the low-pressure refrigerant sucked into the low stage side compression section 3 L after passing through the accumulator 7 is compressed to an intermediate pressure in the low stage side compression section 3 L, then being sucked into the high stage side compression section 3 H through the intermediate interconnection pipe 82 , and is compressed from the intermediate pressure to a high pressure in the high stage side compression section 3 H.
  • the compressor 1 has an intermediate-pressure suction pipe 81 , which is connected to an injection line 991 , described later, to suck an intermediate-pressure injection refrigerant, in addition to the low-pressure suction pipe 71 for sucking the low-pressure refrigerant into the low stage side compression section 3 L.
  • the intermediate-pressure suction pipe 81 is connected to the intermediate interconnection pipe 82 that connects the discharge side of the low stage side compression section 3 L to the suction side of the high stage side compression section 3 H. Thereby, the injection refrigerant is sucked into the high stage side compression section 3 H bypassing the low stage side compression section 3 L.
  • the refrigerant compressed in the high stage side compression section 3 H is discharged into the closed container 2 after passing through the upper muffler chamber 56 , and further discharged to the outside of the closed container 2 through the discharge pipe 26 after passing through the surroundings of the motor 6 .
  • the upper muffler discharge hole 462 is open toward the inner peripheral surface of the closed container 2 so that the refrigerant discharged from the upper muffler chamber 56 is sprayed directly toward the inner peripheral surface of the closed container 2 . Further, the discharge temperature sensor 20 is mounted on the outer peripheral surface of the closed container 2 opposed to the sprayed portion.
  • the configuration of the upper muffler cover 46 is the same as that of the fifth embodiment. However, the upper muffler cover 46 may have the same configuration as that of the first to fourth embodiments or the sixth embodiment.
  • the refrigeration cycle in the seventh embodiment has a basic cycle formed by connecting the compressor 1 , the condenser 91 , the basic cycle expansion mechanism 93 , and the evaporator 92 in succession by using the line 99 .
  • This basic cycle is provided with a temperature sensor Te for detecting the temperature of injection refrigerant and a temperature sensor Tf for detecting the refrigerant temperature on the outlet side of an internal heat exchanger 95 in addition to the temperature sensors Ta to Td having been explained with reference to FIG. 1C .
  • Some of the refrigerant is branched from the basic cycle as an injection refrigerant by a branch pipe 96 provided behind the outlet of the condenser 91 , and is further decompressed by an injection expansion mechanism 94 .
  • the decompressed injection refrigerant is heat-exchanged with the branched refrigerant of basic cycle by the internal heat exchanger 95 .
  • the injection refrigerant having enthalpy increased by the heat exchange in the internal heat exchanger 95 is injected into the intermediate-pressure suction pipe 81 through the injection line 991 .
  • the injection refrigerant is not gasified completely and some thereof is used as a liquid by controlling the throttle amount of the injection expansion mechanism 94 , by which the compressor 1 is cooled to improve the compression efficiency of the compressor 1 .
  • the enthalpy of refrigerant in the basic cycle is decreased by the heat exchange in the internal heat exchanger 95 , and further the enthalpy thereof is increased by the evaporator 92 after the refrigerant has been decompressed by the basic cycle expansion mechanism 93 .
  • the refrigerant in the basic cycle is sucked into the low-pressure suction pipe 71 after passing through the accumulator 7 of the compressor 1 .
  • the heat releasing capacity is increased by the increase in refrigerant circulation flow rate in the condenser 91 , and the heat absorbing capacity is increased by the decrease in enthalpy of the refrigerant at the evaporator inlet in the evaporator 92 , by which the capacity as the refrigeration cycle is increased.
  • the indoor air is cooled, so that the heat pump system serves as a cooler, and in the case where the condenser 91 is arranged in an indoor unit, the indoor air is heated, so that the heat pump system serves as a heater.
  • the heat pump system can be used as a cooling and heating machine.
  • the condenser 91 is heat-exchanged with water for hot-water supply, the heat pump system serves as a water heater.
  • the heat pump system of this embodiment is provided with the control unit 97 for keeping the refrigerant in the refrigeration cycle in a proper state.
  • the control unit 97 sends a signal for detecting at least condenser refrigerant temperature, evaporator refrigerant temperature, compressor discharge temperature, and internal heat exchanger outlet temperature of injection refrigerant and controlling the throttle amount of the basic cycle expansion mechanism 93 , the throttle amount of the injection expansion mechanism, and the number of revolutions of the compressor 1 to keep the refrigerant circulating amount of refrigeration cycle proper with respect to the capacity required in the heat pump system, and further to keep the state of refrigerant in the refrigeration cycle, that is, the degree of supercooling of refrigerant at the outlet of the condenser 91 in the refrigeration cycle, the degree of superheat of refrigerant in the low-pressure suction pipe 71 of the compressor 1 , and the dryness or the degree of superheat of refrigerant in the intermediate-pressure suction pipe 81 proper.
  • the discharge temperature sensor 20 is mounted on the outer peripheral surface of the closed container 2 opposed to a portion in which the refrigerant compressed in the closed container 2 of the compressor 1 comes into contact with the closed container 2 before passing through the surroundings of the motor 6 , by which the refrigerant temperature before heat exchange with the motor 6 , that is, immediately after the discharge from the high stage side compression section 3 H can be detected almost directly. Therefore, the throttle amount of the basic cycle expansion mechanism 93 , the throttle amount of the injection expansion mechanism 94 , and the number of revolutions of the compressor 1 can be controlled based on the detected temperature, and the dryness or the degree of superheat of refrigerant sucked into the high stage side compression section 3 H of the compressor 1 can be kept more proper.
  • FIG. 8 is a configuration diagram of a refrigeration cycle in accordance with the eighth embodiment of the present invention.
  • the compressor of this embodiment is the same as that of the seventh embodiment shown in FIG. 7A .
  • the refrigeration cycle in the eighth embodiment has a basic cycle formed by connecting the compressor 1 , the condenser 91 , a first expansion mechanism 931 , an intermediate-pressure gas-liquid separator 98 , a second expansion mechanism 932 , and the evaporator 92 in succession by using the line 99 .
  • reference symbol Tg denotes a temperature sensor for detecting the refrigerant temperature on the downstream side of the first expansion mechanism 931 .
  • the refrigerant having become in a two-phase state by being decompressed to an intermediate pressure by the first expansion mechanism 931 is separated into a gas refrigerant and a liquid refrigerant by the intermediate-pressure gas-liquid separator 98 .
  • the gas refrigerant is injected into the intermediate-pressure suction pipe 81 of the compressor 1 as an injection refrigerant through the injection line 991 .
  • an injection liquid flow control mechanism 942 is opened by a proper amount to mix the liquid refrigerant in some of the injection refrigerant, by which the compressor 1 is cooled to improve the compression efficiency of the compressor 1 .
  • the enthalpy of liquid refrigerant in the intermediate-pressure gas-liquid separator 98 is increased by the evaporator 92 after the liquid refrigerant has been decompressed by the second expansion mechanism 932 . Then, the liquid refrigerant is sucked into the low-pressure suction pipe 71 after passing through the accumulator 7 of the compressor 1 .
  • the heat releasing capacity is increased by the increase in refrigerant circulation flow rate in the condenser 91 , and the heat absorbing capacity is increased by the decrease in enthalpy of the refrigerant at the evaporator inlet in the evaporator 92 , by which the capacity as the refrigeration cycle is increased.
  • the indoor air is cooled, so that the heat pump system serves as a cooler, and in the case where the condenser 91 is arranged in an indoor unit, the indoor air is heated, so that the heat pump system serves as a heater.
  • the heat pump system can be used as a cooling and heating machine.
  • the condenser 91 is heat-exchanged with water for hot-water supply, the heat pump system serves as a water heater.
  • the heat pump system of this embodiment is provided with the control unit 97 for keeping the refrigerant in the refrigeration cycle in a proper state.
  • the control unit 97 sends a signal for detecting at least condenser refrigerant temperature, evaporator refrigerant temperature, compressor discharge temperature, and injection refrigerant temperature and controlling the throttle amount of the first expansion mechanism 931 , the throttle amount of the second expansion mechanism 932 , an injection gas refrigerant flow control mechanism 941 , the injection liquid refrigerant flow control mechanism 942 , and the number of revolutions of the compressor 1 to keep the refrigerant circulating amount of refrigeration cycle proper with respect to the capacity required in the heat pump system, and further to keep the state of refrigerant in the refrigeration cycle, that is, the degree of supercooling of refrigerant at the outlet of the condenser 91 in the refrigeration cycle, the degree of superheat of refrigerant in the low-pressure suction pipe 71 of the compressor 1 , and the dryness or the degree of superheat of refrigerant in the intermediate-pressure suction pipe 81 proper.
  • the compressor 1 is the same as the compressor of the seventh embodiment, and the discharge temperature sensor 20 is mounted on the outer peripheral surface of the closed container 2 opposed to a portion in which the refrigerant before passing through the surroundings of the motor 6 comes into contact with the closed container 2 , by which the refrigerant temperature before heat exchange with the motor 6 , that is, immediately after the discharge from the high stage side compression section 3 H can be detected almost directly.
  • the throttle amount of the first expansion mechanism 931 , the throttle amount of the second expansion mechanism 932 , the injection gas refrigerant flow control mechanism 941 , the injection liquid refrigerant flow control mechanism 942 , and the number of revolutions of the compressor 1 can be controlled based on the detected temperature, and the dryness or the degree of superheat of refrigerant sucked into the high stage side compression section 3 H of the compressor 1 can be kept more proper.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
US11/882,475 2006-09-29 2007-08-02 Rotary compressor and heat pump system Abandoned US20080078191A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2006-266429 2006-09-29
JP2006266429 2006-09-29
JP2007-126573 2007-05-11
JP2007126573A JP2008106738A (ja) 2006-09-29 2007-05-11 ロータリ圧縮機およびヒートポンプシステム

Publications (1)

Publication Number Publication Date
US20080078191A1 true US20080078191A1 (en) 2008-04-03

Family

ID=38969900

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/882,475 Abandoned US20080078191A1 (en) 2006-09-29 2007-08-02 Rotary compressor and heat pump system

Country Status (3)

Country Link
US (1) US20080078191A1 (fr)
EP (1) EP1908958A3 (fr)
JP (1) JP2008106738A (fr)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110223874A1 (en) * 2010-03-12 2011-09-15 Sunrise Micro Devices, Inc. Power efficient communications
US20110314851A1 (en) * 2009-03-19 2011-12-29 Daikin Industries, Ltd. Air conditioner
US20110314852A1 (en) * 2009-03-19 2011-12-29 Daikin Industries, Ltd. Air conditioner
US20110314854A1 (en) * 2009-03-06 2011-12-29 Mitsubishi Electric Corporation Refrigerator
US20120011876A1 (en) * 2009-03-25 2012-01-19 Daikin Industries, Ltd. Discharge muffler and two-stage compressor including the same
US20120240600A1 (en) * 2009-11-18 2012-09-27 Peter Marie Paulus Method of handling a boil off gas stream and an apparatus therefor
US20120260679A1 (en) * 2009-06-17 2012-10-18 Emerson Electric Co. Control of an Expansion Valve Regulating Refrigerant to an Evaporator of a Climate Control System
US20120266624A1 (en) * 2011-04-21 2012-10-25 Denso Corporation Heat pump cycle
US20130055753A1 (en) * 2011-09-07 2013-03-07 Beomchan Kim Air conditioner
US20130104584A1 (en) * 2010-07-07 2013-05-02 Denso Corporation Two-stage pressurising refrigeration cycle device
US20140096561A1 (en) * 2011-06-08 2014-04-10 Toshiba Carrier Corporation Sealed compressor and refrigeration cycle device
US20140109606A1 (en) * 2012-10-23 2014-04-24 Earthlinked Technologies, Inc. Referigerant-to-air device
CN105180510A (zh) * 2015-08-06 2015-12-23 芜湖美智空调设备有限公司 空调装置及其控制方法
US10365021B2 (en) * 2014-01-23 2019-07-30 Samsung Electronics Co., Ltd. Cooling apparatus and compressor
US10675940B2 (en) * 2016-05-10 2020-06-09 Byd Company Limited Heat pump air-conditioning system and electric vehicle
US10843528B2 (en) 2016-05-10 2020-11-24 Byd Company Limited Heat pump air-conditioning system and electric vehicle
CN112689713A (zh) * 2018-08-09 2021-04-20 大金工业株式会社 压缩机和压缩机的制造方法
US11143446B2 (en) 2017-01-30 2021-10-12 Daikin Industries, Ltd. Refrigeration device controlling a temperature of compressor-discharged refrigerant
US11506206B2 (en) 2017-12-22 2022-11-22 Daikin Industries, Ltd. Compressor having casing and temperature detector thereon
US20220397316A1 (en) * 2021-06-11 2022-12-15 Hanon Systems eTXV DIRECT DISCHARGE INJECTION COMPRESSOR

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5321055B2 (ja) * 2008-12-26 2013-10-23 ダイキン工業株式会社 冷凍装置
KR101576459B1 (ko) 2009-02-25 2015-12-10 엘지전자 주식회사 스크롤 압축기 및 이를 적용한 냉동기기
KR101552618B1 (ko) * 2009-02-25 2015-09-11 엘지전자 주식회사 공기 조화기
JP5730335B2 (ja) * 2011-01-31 2015-06-10 三菱電機株式会社 空気調和装置
US9671119B2 (en) * 2011-01-31 2017-06-06 Mitsubishi Electric Corporation Air-conditioning apparatus
JP2015218909A (ja) * 2014-05-14 2015-12-07 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置およびそれを備えた温水生成装置
AU2016225795B2 (en) * 2015-09-11 2020-03-05 Fujitsu General Limited Rotary compressor
JP2018096272A (ja) * 2016-12-13 2018-06-21 ダイキン工業株式会社 ケーシングに固定された圧縮機構を備える圧縮機
JP7478992B2 (ja) * 2018-02-26 2024-05-08 パナソニックＩｐマネジメント株式会社 密閉型圧縮機

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4889471A (en) * 1987-07-10 1989-12-26 Hatachi, Ltd. Mechanism for prevention of burning of bearing portions in a hermetic type scroll compressor
US5203179A (en) * 1992-03-04 1993-04-20 Ecoair Corporation Control system for an air conditioning/refrigeration system
US5752391A (en) * 1996-01-23 1998-05-19 Nippon Soken, Inc. Refrigerating system
US6293123B1 (en) * 1999-07-30 2001-09-25 Denso Corporation Refrigeration cycle device
US6398520B2 (en) * 1999-01-14 2002-06-04 Samsung Electronics Co., Ltd. Discharge muffler of a hermetic rotary compressor
US20060056983A1 (en) * 2002-06-05 2006-03-16 Sanyo Electric Co., Ltd. Internal intermediate pressure multistage compression type rotary compressor, manufacturing method thereof and displacement ratio setting method
US20080193310A1 (en) * 2005-02-23 2008-08-14 Lg Electronics Inc. Capacity Varying Type Rotary Compressor and Refrigeration System Having the Same

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02264189A (ja) * 1989-04-04 1990-10-26 Mitsubishi Electric Corp 横置形回転式圧縮機
JPH02294591A (ja) * 1989-05-10 1990-12-05 Mitsubishi Electric Corp 横置形回転式圧縮機
JPH0544679A (ja) * 1991-08-19 1993-02-23 Mitsubishi Heavy Ind Ltd 密閉型ロータリ圧縮機
US5368446A (en) * 1993-01-22 1994-11-29 Copeland Corporation Scroll compressor having high temperature control
JP2587897B2 (ja) * 1993-05-19 1997-03-05 サンデン株式会社 スクロール型圧縮機
JP3391072B2 (ja) * 1993-12-28 2003-03-31 松下電器産業株式会社 密閉型スクロール圧縮機
JP3813702B2 (ja) * 1996-08-22 2006-08-23 株式会社日本自動車部品総合研究所 蒸気圧縮式冷凍サイクル
EP1746706B1 (fr) * 2001-03-30 2011-07-06 Sanyo Electric Co., Ltd. Moteur à induction synchrone
JP4264208B2 (ja) * 2001-10-26 2009-05-13 三菱重工業株式会社 空気調和装置
JP4219198B2 (ja) * 2003-03-26 2009-02-04 三洋電機株式会社 冷媒サイクル装置
FR2878317B1 (fr) * 2004-11-23 2007-04-20 Frigorie Service Sarl Dispositif d'echange de chaleur pour installation de chauffage geothermique
JP2006177194A (ja) * 2004-12-21 2006-07-06 Sanyo Electric Co Ltd 多気筒回転圧縮機
JP2006177226A (ja) * 2004-12-22 2006-07-06 Hitachi Home & Life Solutions Inc ロータリ圧縮機及びそれを用いる空気調和機
JP4652225B2 (ja) * 2004-12-22 2011-03-16 トヨタ紡織株式会社 コンプレッサ

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4889471A (en) * 1987-07-10 1989-12-26 Hatachi, Ltd. Mechanism for prevention of burning of bearing portions in a hermetic type scroll compressor
US5203179A (en) * 1992-03-04 1993-04-20 Ecoair Corporation Control system for an air conditioning/refrigeration system
US5752391A (en) * 1996-01-23 1998-05-19 Nippon Soken, Inc. Refrigerating system
US6398520B2 (en) * 1999-01-14 2002-06-04 Samsung Electronics Co., Ltd. Discharge muffler of a hermetic rotary compressor
US6293123B1 (en) * 1999-07-30 2001-09-25 Denso Corporation Refrigeration cycle device
US20060056983A1 (en) * 2002-06-05 2006-03-16 Sanyo Electric Co., Ltd. Internal intermediate pressure multistage compression type rotary compressor, manufacturing method thereof and displacement ratio setting method
US20080193310A1 (en) * 2005-02-23 2008-08-14 Lg Electronics Inc. Capacity Varying Type Rotary Compressor and Refrigeration System Having the Same

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110314854A1 (en) * 2009-03-06 2011-12-29 Mitsubishi Electric Corporation Refrigerator
US9046275B2 (en) * 2009-03-19 2015-06-02 Daikin Industries, Ltd. Air conditioner with electromagnetic induction heating unit
US20110314851A1 (en) * 2009-03-19 2011-12-29 Daikin Industries, Ltd. Air conditioner
US20110314852A1 (en) * 2009-03-19 2011-12-29 Daikin Industries, Ltd. Air conditioner
US9074782B2 (en) * 2009-03-19 2015-07-07 Daikin Industries, Ltd. Air conditioner with electromagnetic induction heating unit
US20120011876A1 (en) * 2009-03-25 2012-01-19 Daikin Industries, Ltd. Discharge muffler and two-stage compressor including the same
US9163622B2 (en) * 2009-03-25 2015-10-20 Daikin Industries, Ltd. Discharge muffler and two-stage compressor including the same
US20120260679A1 (en) * 2009-06-17 2012-10-18 Emerson Electric Co. Control of an Expansion Valve Regulating Refrigerant to an Evaporator of a Climate Control System
US9250001B2 (en) * 2009-06-17 2016-02-02 Emerson Electric Co. Control of an expansion valve regulating refrigerant to an evaporator of a climate control system
US20120240600A1 (en) * 2009-11-18 2012-09-27 Peter Marie Paulus Method of handling a boil off gas stream and an apparatus therefor
US20110223874A1 (en) * 2010-03-12 2011-09-15 Sunrise Micro Devices, Inc. Power efficient communications
US20130104584A1 (en) * 2010-07-07 2013-05-02 Denso Corporation Two-stage pressurising refrigeration cycle device
US20120266624A1 (en) * 2011-04-21 2012-10-25 Denso Corporation Heat pump cycle
US8671707B2 (en) * 2011-04-21 2014-03-18 Denso Corporation Heat pump cycle
US20140096561A1 (en) * 2011-06-08 2014-04-10 Toshiba Carrier Corporation Sealed compressor and refrigeration cycle device
US20130055753A1 (en) * 2011-09-07 2013-03-07 Beomchan Kim Air conditioner
US20140109606A1 (en) * 2012-10-23 2014-04-24 Earthlinked Technologies, Inc. Referigerant-to-air device
US10365021B2 (en) * 2014-01-23 2019-07-30 Samsung Electronics Co., Ltd. Cooling apparatus and compressor
CN105180510A (zh) * 2015-08-06 2015-12-23 芜湖美智空调设备有限公司 空调装置及其控制方法
US10675940B2 (en) * 2016-05-10 2020-06-09 Byd Company Limited Heat pump air-conditioning system and electric vehicle
US10843528B2 (en) 2016-05-10 2020-11-24 Byd Company Limited Heat pump air-conditioning system and electric vehicle
US11143446B2 (en) 2017-01-30 2021-10-12 Daikin Industries, Ltd. Refrigeration device controlling a temperature of compressor-discharged refrigerant
US11506206B2 (en) 2017-12-22 2022-11-22 Daikin Industries, Ltd. Compressor having casing and temperature detector thereon
CN112689713A (zh) * 2018-08-09 2021-04-20 大金工业株式会社 压缩机和压缩机的制造方法
EP3835583A4 (fr) * 2018-08-09 2021-09-22 Daikin Industries, Ltd. Compresseur et procédé de fabrication de compresseur
US11261866B2 (en) 2018-08-09 2022-03-01 Daikin Industries, Ltd. Compressor having external temperature sensor and method of manufacturing compressor
US20220397316A1 (en) * 2021-06-11 2022-12-15 Hanon Systems eTXV DIRECT DISCHARGE INJECTION COMPRESSOR
US11885535B2 (en) * 2021-06-11 2024-01-30 Hanon Systems ETXV direct discharge injection compressor

Also Published As

Publication number Publication date
JP2008106738A (ja) 2008-05-08
EP1908958A2 (fr) 2008-04-09
EP1908958A3 (fr) 2010-10-13

Similar Documents

Publication Publication Date Title
US20080078191A1 (en) Rotary compressor and heat pump system
EP1975414B1 (fr) Compresseur rotatif injectable à deux étages et système de pompe à chaleur
US8122735B2 (en) Refrigerating apparatus
US7914267B2 (en) Multistage compressor for a CO2 cycle that includes a rotary compressing mechanism and a scroll compressing mechanism
US7918096B2 (en) Refrigeration system
US8312732B2 (en) Refrigerating apparatus
JP2009127902A (ja) 冷凍装置及び圧縮機
EP2497955A1 (fr) Dispositif de pompe à chaleur, compresseur à deux étages et procédé de fonctionnement du dispositif de pompe à chaleur
CN101153600A (zh) 旋转压缩机和热泵系统
US20100326125A1 (en) Refrigeration system
CN112771322A (zh) 多级压缩系统
JP5321697B2 (ja) インジェクション対応２段圧縮ロータリ圧縮機
CN112752934B (zh) 多级压缩系统
JP7042929B2 (ja) 冷凍サイクル装置
JP6791233B2 (ja) 多段圧縮システム
JP2020094762A (ja) 多段圧縮システム
JP6702401B1 (ja) 多段圧縮システム
WO2020067197A1 (fr) Système de compression à étages multiples

Legal Events

Date Code Title Description
AS Assignment

Owner name: FUJITSU GENERAL LIMITED, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MORISHITA, TAKU;MOROZUMI, NAOYA;UEDA, KENSHI;REEL/FRAME:019706/0261

Effective date: 20070518

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION