EP2644892A2 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

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Publication number
EP2644892A2
EP2644892A2 EP13161233.5A EP13161233A EP2644892A2 EP 2644892 A2 EP2644892 A2 EP 2644892A2 EP 13161233 A EP13161233 A EP 13161233A EP 2644892 A2 EP2644892 A2 EP 2644892A2
Authority
EP
European Patent Office
Prior art keywords
chamber
spool valve
pressure
refrigerant
suction
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.)
Granted
Application number
EP13161233.5A
Other languages
English (en)
French (fr)
Other versions
EP2644892B1 (de
EP2644892A3 (de
Inventor
Kazuo Murakami
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP2644892A2 publication Critical patent/EP2644892A2/de
Publication of EP2644892A3 publication Critical patent/EP2644892A3/de
Application granted granted Critical
Publication of EP2644892B1 publication Critical patent/EP2644892B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • F04C29/0014—Injection of a fluid in the working chamber for sealing, cooling and lubricating with control systems for the injection of the fluid
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring
    • 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
    • F04C2270/18—Pressure
    • 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

Definitions

  • the present invention relates to a scroll compressor.
  • Japanese Unexamined Patent Application Publication No. 11-107968 discloses a scroll compressor that is provided with an injection pipe for injection of refrigerant gas into the compression chamber.
  • the injection pipe is connected to a refrigerant gas supply passage connected to a separator and provided with a three-way solenoid valve.
  • the valve opens the injection passage, so that the refrigeration cycle of the scroll compressor is operated at high efficiency with the help of the injection of refrigerant.
  • low load operation such as cooling operation, the valve closes the injection passage to cause the refrigerant to be flown from the refrigerant gas supply passage into the suction passage, so that the refrigeration cycle of the scroll compressor is operated at high efficiency also during the low load operation.
  • Japanese Unexamined Patent Application Publication No. 2008-303858 discloses another scroll compressor in which a cylindrical chamber communicating with an injection passage is provided.
  • a piston is slidingly movable in the cylindrical chamber to define a first space and a second space therein.
  • the first space is in communication with a high pressure space, while the second space is in communication with a low pressure space.
  • the piston is moved depending on the pressure difference between the first and second spaces, so that the injection passage is connected to or disconnected from the compression chamber, thereby allowing increased operating efficiency of the scroll compressor.
  • the compressor disclosed in the publication No. 11-107968 in which the three-way valve is provided in the refrigerant gas supply passage outside the compressor increases the entire size of the cycle.
  • the compressor also requires an electric signal line to operate the valve and hence increases the entire size of the cycle further, resulting in an increased cost.
  • the compressor disclosed in the publication No. 2008-303858 in which the cylindrical chamber and its related piston for the injection are incorporated in the fixed scroll, on the other hand, allows compact configuration, but the operating efficiency of the compressor during heating operation tends to be reduced as compared to the case of cooling operation if the compressor is used in both cooling and heating.
  • the injection should preferably be performed during heating operation to increase the refrigerant flow rate.
  • the injection may not necessarily be controlled appropriately with the switching between the cooling and the heating operations of the compressor.
  • the present invention is directed to providing a scroll compressor having a selector device that allows the injection to be controlled appropriately with the switching between the cooling and the heating operations of the compressor.
  • a scroll compressor in accordance with an aspect of the present invention, includes a housing having therein a suction chamber and a discharge chamber, a fixed scroll fixed in the housing, a movable scroll disposed in the housing in engagement with the fixed scroll to form therebetween a compression chamber into which low pressure refrigerant is introduced from the suction chamber and from which high pressure refrigerant is discharged into the discharge chamber, the movable scroll orbiting relative to the fixed scroll to vary the volume of the compression chamber, and an injection passage through which medium-pressure refrigerant is introduced into the compression chamber.
  • the scroll compressor further includes a selector device connecting the compression chamber to the injection passage or disconnecting the compression chamber from the injection passage with the change of the pressure or the temperature of the refrigerant in the suction chamber.
  • the electric scroll compressor of the first embodiment designated generally by 1 has a housing 10 formed of a cylindrical front housing 11 having an opening at the rear end on the left side in Fig. 1 and a rear housing 12 fastened by plural bolts 13 to the rear end of the front housing 11 to close the opening with a seal (not shown) interposed therebetween.
  • the front housing 11 has an inlet port 15 at a position adjacent to the front end thereof for connection to an external refrigerant circuit.
  • the front housing 11 accommodates a drive shaft 18 extending in longitudinal direction of the front housing 11, a stator 20 fixed to the inner surface of the front housing 11, and a rotor 22 fixed on the drive shaft 18 inside the stator 20.
  • the drive shaft 18 is rotatably supported at one end thereof by a bearing 16 mounted in the front housing 11 and at the other end thereof by a bearing 25 mounted in the middle of a shaft support 24 that is provided in the front housing 11.
  • the front housing 11 accommodates a fixed scroll 26 on the side of the shaft support 24 facing the rear housing 12 and a movable scroll 28 between the fixed scroll 26 and the shaft support 24.
  • the movable scroll 28 is disposed in engagement with the fixed scroll 26 to form therebetween plural compression chambers 30, 30A, 30B.
  • plural rings 32 are fixed on the side of the shaft support 24 facing the rear housing 12, and plural pins 33 (only one being shown) to be guided in the respective rings 32 are fixed on the side of the movable scroll 28 facing the shaft support 24.
  • the movable scroll 28 has in the center thereof on the side facing the shaft support 24 a bearing 34 that is connected to a bush 35 in which a cylindrical eccentric pin 36 formed at the end of the drive shaft 18 is inserted.
  • Such configuration allows the movable scroll 28 to orbit relative to the fixed scroll 26 thereby to vary the volume of the compression chambers 30, 30A, 30B for compression of refrigerant gas.
  • a suction chamber 38 for admitting low-pressure refrigerant gas is formed in the region forward of the shaft support 24.
  • Refrigerant gas in the suction chamber 38 is introduced into a compression chamber 30 through a suction port 40 that is formed in the inner surface of the front housing 11 at a position adjacent to the fixed scroll 26 in communication with the compression chamber 30.
  • the fixed scroll 26 and the rear housing 12 cooperate to form therebetween a discharge chamber 44 for admitting high-pressure refrigerant gas.
  • the discharge chamber 44 is communicable with the compression chamber 30A through a discharge port 42 that is formed through the fixed scroll 26 at the center thereof.
  • the fixed scroll 26 is provided with a reed valve 46 to close and open the discharge port 42.
  • the opening of the reed valve 46 is restricted by a retainer 48 disposed on the rear side of the reed valve 46.
  • the rear housing 12 has an outlet port 50 formed therethrough in communication with the discharge chamber 44.
  • the rear housing 12 is provided with an injection passage 52 of a round cross section that extends through the wall of the rear housing 12 and the discharge chamber 44 and to the fixed scroll 26.
  • the injection passage 52 is connected to the compression chamber 30B through a selector device 60.
  • the selector device 60 includes a suction pressure passage 62, a cylindrical chamber 64, a spool valve 66 and an outside air chamber 68.
  • the suction pressure passage 62 is in communication at one end thereof with the suction port 40 and at the other end thereof with the cylindrical chamber 64. That is, the cylindrical chamber 64 is in communication through the suction pressure passage 62 with the suction chamber 38.
  • the injection passage 52 is connected to the cylindrical chamber 64 at a position in the periphery thereof.
  • the cylindrical chamber 64 is in communication with the outside air chamber 68.
  • the outside air chamber 68 is disposed on the side of the cylindrical chamber 64 opposite from the suction pressure passage 62.
  • the outside air chamber 68 has a communication port 68A (see Fig.
  • the cylindrical chamber 64 is in communication through the outside air chamber 68 with the outside air.
  • the cylindrical chamber 64 is communicable with a connecting passage 52A which is formed in the fixed scroll 26 and has a round cross section with a diameter that is substantially equal to the diameter of the injection passage 52.
  • the connecting passage 52A is communicable at one end thereof with the cylindrical chamber 64 and at the other end thereof with the compression chamber 30B.
  • the connecting passage 52A is disposed on the side of the cylindrical chamber 64 opposite from the injection passage 52.
  • the connecting passage 52A and the injection passage 52 are arranged linearly and coaxially.
  • the cylindrical chamber 64 accommodates the cylindrical spool valve 66.
  • the spool valve 66 is slidingly movable in the cylindrical chamber 64.
  • the suction pressure passage 62 is in communication with the cylindrical chamber 64 so that the pressure in the suction chamber 38 is applied to one end of the spool valve 66.
  • the outside air chamber 68 is in communication with the cylindrical chamber 64 so that the outside air pressure in the outside air chamber 68 is applied to the other end of the spool valve 66.
  • the spool valve 66 has a diameter that is slightly smaller than the diameter of the cylindrical chamber 64.
  • the spool valve 66 can block fluid flow from the suction port 40 or the suction chamber 38, the outside air chamber 68, the injection passage 52, and the connecting passage 52A or the compression chamber 30B.
  • the spool valve 66 has a communication hole 66A extending therethrough perpendicularly to the direction of the sliding movement of the spool valve 66.
  • the communication hole 66A has a diameter that is substantially equal to the diameters of the injection passage 52 and the connecting passage 52A.
  • the communication hole 66A connects between the injection passage 52 and the connecting passage 52A when the spool valve 66 is positioned at the end of the cylindrical chamber 64 adjacent to the suction pressure passage 62 (see Fig. 5 ).
  • the spool valve 66 has an annular groove 66B formed in the periphery thereof adjacent to the outside air chamber 68.
  • the annular groove 66B receives an O ring 67 that prevents the outside air in the outside air chamber 68 from flowing through the cylindrical chamber 64 into the suction pressure passage 62 and also prevents refrigerant gas in the suction pressure passage 62 from flowing through the cylindrical chamber 64 into the outside air chamber 68.
  • the cylindrical chamber 64 accommodates a coil spring 69 or an urging member on the side of the spool valve 66 facing the outside air chamber 68.
  • the coil spring 69 urges the spool valve 66 toward one end of the cylindrical chamber 64, that is, toward the suction pressure passage 62 so that the compression chamber 30B is connected to the injection passage 52.
  • the cylindrical chamber 64 has two projections 64A at positions that are radially outside the coil spring 69. The projections 64A restrict the sliding movement of the spool valve 66 toward the outside air chamber 68 in the cylindrical chamber 64.
  • the above-described scroll compressor 1 forms part of the cooling and heating circuit of a vehicular air conditioner through which refrigerant circulates.
  • the circuit further includes a four-way valve 70 with four ports 82, 83, 87 and 88, a first heat exchanger 71, an expansion valve 72, a receiver 73, a second heat exchanger 74, a blower 75, and an expansion valve 76.
  • the outlet port 50 (see Fig. 1 ) of the scroll compressor 1 is connected through a tube 81 to the first port 82 of the valve 70.
  • the second port 83 of the valve 70 is connected through a tube 84 to the first heat exchanger 71,
  • the first heat exchanger 71 for heat exchange with the outside air is connected through a tube to the expansion valve 72 that is in turn connected to the receiver 73.
  • the receiver 73 is connected through a tube 85 to the expansion valve 76 that is in turn connected to the second heat exchanger 74.
  • the second heat exchanger 74 provides heat exchange with the air inside a passenger compartment of the vehicle with the help of the blower 75 disposed adjacent to the second heat exchanger 74.
  • the second heat exchanger 74 is connected through a tube 86 to the third port 87 of the valve 70.
  • the fourth port 88 of the valve 70 is connected through a tube 89 to the inlet port 15 (see Fig. 1 ) of the scroll compressor 1.
  • the valve 70 is operated between a first position in which the first port 82 is connected to the second port 83 and the third port 87 is connected to the fourth port 88 as shown in Fig. 4A and a second position in which the first port 82 is connected to the third port 87 and the second port 83 is connected to the fourth port 88 as shown in Fig. 4B .
  • the receiver 73 is connected to a refrigerant gas supply passage 90 that is in turn connected to the injection passage 52 of the scroll compressor 1.
  • the refrigerant gas supply passage 90 is provided with a check valve (not shown).
  • the scroll compressor 1 of the present embodiment During the cooling operation of the scroll compressor 1 of the air conditioner, refrigerant is circulated through the cooling and heating circuit so that the second heat exchanger 74 functions as an evaporator.
  • the first heat exchanger 71 functions as a condenser to release the heat of refrigerant to the outside air.
  • the first port 82 is connected to the second port 83 while the third port 87 is connected to the fourth port 88, as shown in Fig. 4A .
  • the drive shaft 18 is rotated with the rotor 22, so that the movable scroll 28 connected through the bush 35 and the bearing 34 to the eccentric pin 36 of the drive shaft 18 is driven to make an orbital motion with respect to the fixed scroll 26.
  • refrigerant is introduced from the inlet port 15 into the suction chamber 38 and then through the suction port 40 into the compression chamber 30.
  • the volume of the compression chambers 30, 30A, 30B trapping the refrigerant is reduced thereby to compress the refrigerant.
  • the compressed refrigerant is discharged out of the compression chamber 30A through the discharge port 42 into the discharge chamber 44, and then discharged through the outlet port 50 into the tube 81 of the cooling and heating circuit.
  • the selector device 60 is in the state shown in Fig. 3 .
  • the cylindrical chamber 64 is supplied with suction refrigerant, or refrigerant of suction pressure, from the suction port 40 through the suction pressure passage 62.
  • the cylindrical chamber 64 is also supplied with the outside air from the communication port 68A through the outside air chamber 68.
  • the pressure of suction refrigerant is applied to the spool valve 66 from the left side as seen in Fig. 3 , while the urging force of the coil spring 69 and the outside air pressure are applied to the spool valve 66 from the right side.
  • the force due to the pressure of suction refrigerant is larger than the sum of the urging force of the coil spring 69 and the force due to the outside air pressure. Accordingly, the spool valve 66 is moved rightward as seen in Fig. 3 , or toward the outside air chamber 68 in the cylindrical chamber 64 until the spool valve 66 is brought into contact with the projections 64A, so that the injection passage 52 is disconnected from the communication hole 66A of the spool valve 66 and hence from the connecting passage 52A and the compression chamber 30B.
  • refrigerant of a medium pressure supplied from the receiver 73 through the refrigerant gas supply passage 90 to the injection passage 52 is not introduced into the compression chamber 30B.
  • the second heat exchanger 74 functions as a condenser, so that the passenger compartment is heated.
  • the first heat exchanger 71 then functions as evaporator to release the heat of refrigerant to the outside air.
  • the selector device 60 is in the state shown in Fig. 5 . Since the suction refrigerant has a low temperature and pressure during the heating operation, the sum of the urging force of the coil spring 69 and the outside air pressure is larger than the pressure of suction refrigerant.
  • the spool valve 66 is moved leftward, as seen in Fig.
  • the scroll compressor 1 of the present embodiment offers the following advantages.
  • Figs. 6 , 7 and 8 show the second embodiment of the scroll compressor according to the present invention.
  • the second embodiment differs from the first embodiment in the structure of the selector device.
  • same reference numerals are used for the common elements or components in the first and second embodiments, and the description of such elements or components of the second embodiment will be omitted.
  • the selector device designated generally by 100 includes a suction pressure passage 162, a discharge pressure passage 144, a first cylindrical chamber 164 and a second cylindrical chamber 102.
  • the suction pressure passage 162 is in communication at one end thereof with the suction port 40 and at the other end thereof with the first cylindrical chamber 164.
  • the first cylindrical chamber 164 is in communication through the suction pressure passage 162 and the suction port 40 with the suction chamber 38 ( Fig. 1 ).
  • the discharge pressure passage 144 is connected at one end thereof to the discharge chamber 44 and at the other end thereof to the first cylindrical chamber 164 at a position in the periphery thereof.
  • the first cylindrical chamber 164 is in communication with the outside air chamber 68.
  • the outside air chamber 68 is disposed on the side of the first cylindrical chamber 164 that is opposite from the suction pressure passage 162.
  • the outside air chamber 68 has the communication port 68A (see Fig. 7 ) that is in communication with the outside air.
  • the first cylindrical chamber 164 is in communication through the outside air chamber 68 with the outside air.
  • the first cylindrical chamber 164 is in communication also with a connecting passage 152A which is of a round cross section having a diameter that is substantially equal to the diameter of the discharge pressure passage 144.
  • the connecting passage 152A is in communication at one end thereof with the first cylindrical chamber 164 and at the other end thereof with the second cylindrical chamber 102.
  • the connecting passage 152A is disposed on the side of the first cylindrical chamber 164 that is opposite from the discharge pressure passage 144.
  • the connecting passage 152A and the discharge pressure passage 144 are arranged linearly and coaxially.
  • the injection passage 152 is connected to the second cylindrical chamber 102 at a position in the periphery thereof,
  • the second cylindrical chamber 102 is also in communication with a connecting passage 152B.
  • the connecting passage 152B is in communication at one end thereof with the second cylindrical chamber 102 and at the other end thereof with the compression chamber 30B.
  • the connecting passage 152B is disposed on the side of the second cylindrical chamber 102 that is opposite from the connecting passage 152A.
  • the connecting passage 152A and the connecting passage 152B are arranged linearly and coaxially.
  • the first cylindrical chamber 164 accommodates a cylindrical first spool valve 166.
  • the first spool valve 166 is slidingly movable in the first cylindrical chamber 164.
  • the suction pressure passage 162 is in communication with the first cylindrical chamber 164 so that the pressure in the suction chamber 38 is applied to one end of the first spool valve 166.
  • the outside air chamber 68 is in communication with the first cylindrical chamber 164 so that the outside air pressure in the outside air chamber 68 is applied to the other end of the first spool valve 166.
  • the first spool valve 166 has a diameter that is slightly smaller than the diameter of the first cylindrical chamber 164.
  • the first spool valve 166 can block fluid flow from the suction port 40 or the suction chamber 38, the outside air chamber 68, the discharge pressure passage 144, and the connecting passage 152A or the second cylindrical chamber 102.
  • the first spool valve 166 has in the periphery thereof a first communication passage 166A in the form of an annular groove.
  • the first communication passage 166A connects between the discharge pressure passage 144 and the connecting passage 152A when the first spool valve 166 is moved toward the outside air chamber 68 and brought into contact with the projections 164A (see Fig. 7 ).
  • the first spool valve 166 has an annular groove 166B formed in the periphery thereof adjacent to the outside air chamber 68 to receive the O ring 67.
  • the first cylindrical chamber 164 accommodates the coil spring 69 that urges the first spool valve 166 toward one end of the first cylindrical chamber 164, that is, toward the suction pressure passage 162 so that the suction chamber 38 is connected to the second cylindrical chamber 102.
  • the first spool valve 166 has a second communication passage 166C formed therethrough in the form of an L shape. One end of the second communication passage 166C is opened to the suction pressure passage 162, while the other end of the second communication passage 166C is opened to the connecting passage 152A.
  • the second communication passage 166C is connected to the connecting passage 152A when the first spool valve 166 is positioned at the end of the first cylindrical chamber 164, as shown in Fig. 8 .
  • the second cylindrical chamber 102 accommodates a cylindrical second spool valve 104.
  • the second spool valve 104 is slidingly movable in the second cylindrical chamber 102.
  • the first cylindrical chamber 164 is connected to the second cylindrical chamber 102 so that the pressure in the suction chamber 38 or in the discharge chamber 44 is applied to one end of the second spool valve 104.
  • the compression chamber 30B is in communication with the second cylindrical chamber 102 so that the pressure in the compression chamber 30B is applied to the other end of the second spool valve 104.
  • the second spool valve 104 has a diameter that is slightly smaller than the diameter of the second cylindrical chamber 102. In the second cylindrical chamber 102, the second spool valve 104 can block fluid flow from the connecting passage 152A or the first cylindrical chamber 164, the injection passage 152, and the connecting passage 152B or the compression chamber 30B.
  • the scroll compressor 1 equipped with the above-described selector device 100 forms a part of the cooling and heating circuit of the vehicular air conditioner shown in Figs. 4A and 4B , as in the case of the first embodiment.
  • the first cylindrical chamber 164 is supplied with suction refrigerant, or refrigerant of suction pressure, from the suction port 40 through the suction pressure passage 162.
  • the first cylindrical chamber 164 is also supplied with the outside air from the communication port 68A through the outside air chamber 68.
  • the pressure of suction refrigerant is applied to the first spool valve 166 from the left side as seen in Fig. 7 , while the urging force of the coil spring 69 and the outside air pressure are applied to the first spool valve 166 from the right side.
  • the pressure of suction refrigerant is larger than the sum of the urging force of the coil spring 69 and the outside air pressure.
  • the first spool valve 166 is moved rightward toward the outside air chamber 68 in the first cylindrical chamber 164, so that the discharge pressure passage 144 is connected to the connecting passage 152A through the first communication passage 166A of the first spool valve 166. Then high pressure refrigerant in the discharge chamber 44 is introduced through the discharge pressure passage 144 into second cylindrical chamber 102.
  • the pressure of refrigerant in the discharge chamber 44 is applied to the side of the second spool valve 104 facing the connecting passage 152A, while the pressure of refrigerant in the compression chamber 30B and the injection passage 152 is applied to the side of the second spool valve 104 facing the connecting passage 152B. Since the pressure of refrigerant in the discharge chamber 44 is larger than the pressure of refrigerant in the compression chamber 30B and the injection passage 152, the second spool valve 104 is moved downward as seen in Fig. 7 in the second cylindrical chamber 102, so that the injection passage 152 is disconnected from the connecting passage 152B and hence from the compression chamber 30B by the second spool valve 104. Thus, while the vehicle passenger compartment is being cooled, refrigerant of a medium pressure that is supplied from the receiver 73 through the refrigerant gas supply passage 90 to the injection passage 152 is not introduced into the compression chamber 30B.
  • the selector device 100 is in the state shown in Fig. 8 . Since the suction refrigerant has a low temperature and pressure during the heating operation, the sum of the urging force of the coil spring 69 and the outside air pressure is larger than the pressure of suction refrigerant.
  • the first spool valve 166 is moved leftward as seen in Fig. 8 or toward the suction pressure passage 162 in the first cylindrical chamber 164, so that the first communication passage 166A of the first spool valve 166 is disconnected from the discharge pressure passage 144 and the connecting passage 152A and, therefore, the discharge pressure passage 144 is disconnected from the connecting passage 152A by the first spool valve 166, as shown in Fig. 8 .
  • the second communication passage 166C is connected to the suction pressure passage 162 and the connecting passage 152A and also to the second cylindrical chamber 102.
  • the pressure of refrigerant in the suction chamber 38 is applied to the side of the second spool valve 104 facing the connecting passage 152A, while the pressure of refrigerant in the compression chamber 30B and the injection passage 152 is applied to the side of the second spool valve 104 facing the connecting passage 152B. Since the pressure of refrigerant in the suction chamber 38 is smaller than the pressure of refrigerant in the compression chamber 30B and the injection passage 152, the second spool valve 104 is moved upward as seen in Fig.
  • the second embodiment offers the following advantages.
  • Figs. 9 and 10 show the third embodiment of the scroll compressor according to the present invention.
  • the third embodiment differs from the second embodiment in the structure of the second spool valve of the selector device.
  • same reference numerals are used for the common elements or components in the second and third embodiments, and the description of such elements or components of the third embodiment will be omitted.
  • the selector device designated generally by 110 includes a second spool valve 106 accommodated in the second cylindrical chamber 102.
  • the second spool valve 106 has two cylindrical portions of different diameters, namely a small-diameter portion on the side facing the connecting passage 152A and a large-diameter portion on the side facing the connecting passage 152B.
  • the diameter of the small-diameter portion of the second spool valve 106 is larger than the diameter of the connecting passage 152A.
  • the following will describe the operation of the selector device 110.
  • the selector device 110 is in the state shown in Fig. 9 .
  • the pressure of suction refrigerant is applied to the first spool valve 166 from the left side as seen in Fig. 9 , while the urging force of the coil spring 69 and the outside air pressure are applied to the first spool valve 166 from the right side. Since the suction refrigerant has a high temperature and pressure during the cooling operation, the first spool valve 166 is moved rightward or toward the outside air chamber 68 in the first cylindrical chamber 164.
  • the discharge pressure passage 144 is connected to the connecting passage 152A through the first communication passage 166A of the first spool valve 166.
  • High pressure refrigerant in the discharge chamber 44 is introduced through the discharge pressure passage 144 into the second cylindrical chamber 102.
  • the pressure of refrigerant in the discharge chamber 44 is applied to the side of the second spool valve 106 facing the connecting passage 152A, while the pressure of refrigerant in the compression chamber 30B is applied to the side of the second spool valve 106 facing the connecting passage 152B.
  • the second spool valve 106 Since the pressure in the discharge chamber 44 is larger than the pressure of refrigerant in the compression chamber 30B, the second spool valve 106 is moved downward, or toward the connecting passage 152B in the second cylindrical chamber 102, so that the injection passage 152 is disconnected from the connecting passage 152B and hence from the compression chamber 30B by the second spool valve 106.
  • refrigerant of a medium pressure supplied from the receiver 73 through the refrigerant gas supply passage 90 to the injection passage 152 is not introduced into the compression chamber 30B.
  • the pressure in the discharge chamber 44 is supplied to the injection passage 152 and also to the check valve provided in the refrigerant gas supply passage 90.
  • the selector device 110 is in the state shown in Fig. 10 .
  • the first spool valve 166 is moved leftward as seen in Fig. 10 , or toward the suction pressure passage 162 in the first cylindrical chamber 164, so that the discharge pressure passage 144 is disconnected from the connecting passage 152A by the first spool valve 166.
  • the suction pressure passage 162 is connected to the second cylindrical chamber 102 through the second communication passage 166C of the first spool valve 166.
  • the refrigerant in the injection passage 152 which has substantially the same pressure as the refrigerant in the discharge chamber 44 is flown through the second cylindrical chamber 102 and the suction pressure passage 162 into the suction chamber 38 of lower pressure, so that the refrigerant present in the injection passage 152 and the refrigerant applied to the upper surface of the second spool valve 106 have substantially the same pressure as the refrigerant in the suction chamber 38.
  • the pressure of refrigerant in the compression chamber 30B is applied to the lower surface of the second spool valve 106.
  • the second spool valve 106 Since the pressure of refrigerant in the compression chamber 30B is larger than the pressure of refrigerant in the suction chamber 38, the second spool valve 106 is moved upward in the second cylindrical chamber 102, so that the injection passage 152 is connected to the connecting passage 152B and hence to the compression chamber 30B.
  • refrigerant of a medium pressure supplied from the receiver 73 through the refrigerant gas supply passage 90 to the injection passage 152 is introduced into the compression chamber 30B.
  • the third embodiment offers the advantages similar to those of the second embodiment and also offers the following advantage.
  • Figs. 11 , 12 and 13 show the fourth embodiment of the scroll compressor according to the present invention.
  • the fourth embodiment differs from the first embodiment in the structure of the selector device.
  • same reference numerals are used for the common elements or components in the first and fourth embodiments, and the description of such elements or components of the fourth embodiment will be omitted.
  • the selector device designated generally by 121 includes a bimetal strip 124, a connecting member 126, a cylindrical spool valve 266 and the aforementioned cylindrical chamber 64.
  • the spool valve 266 is slidingly movable in the cylindrical chamber 64 with a variation of the temperature in the suction chamber 38.
  • the compression chamber 30B is connected to or disconnected from the injection passage 52 with the movement of the spool valve 266.
  • the selector device 121 further includes a bracket 122 projecting from the movable scroll 28 into the suction port 40 to support one end of the bimetal strip 124.
  • the other end of the bimetal strip 124 is connected to one end of the connecting member 126.
  • the other end of the connecting member 126 is connected to the spool valve 266.
  • the bimetal strip 124 is connected through the connecting member 126 to the spool valve 266.
  • the bimetal strip 124 is composed of two metal plates 124A, 124B joined together and having different coefficients of thermal expansion.
  • the bimetal strip 124 is disposed such that the metal plate 124B of a lower coefficient of thermal expansion is located closer to the suction pressure passage 62 than the other metal plate 123A (see Fig. 12 ).
  • the bimetal strip 124 is formed such that there is little difference in length between the two metal plates 124A, 124B and no deformation occurs in the bimetal strip 124 when the bimetal strip 124 is exposed to the temperature of refrigerant in the suction chamber 38 during the cooling operation.
  • the connecting member 126 is made of a metal having an elasticity and a low coefficient of thermal expansion.
  • the spool valve 266 has no annular groove such as 66B and no O ring such as 67 and also that no coil spring such as 69 is provided in the cylindrical chamber 64 and no outside air chamber such as 68 is provided (see Figs. 3 , 12 and 13 ).
  • the selector device 121 During the cooling operation of the compressor 1, the selector device 121 is in the state shown in Fig. 12 .
  • the cylindrical chamber 64 is supplied with suction refrigerant from the suction port 40 through the suction pressure passage 62.
  • suction refrigerant has a higher temperature, as compared to the case of heating operation, there is little difference in length between the metal plates 124A, 124B due to thermal expansion and no deformation occurs in the bimetal strip 124.
  • the connecting member 126 connected to the bimetal strip 124 positions the spool valve 266 in contact with the projections 64A in the cylindrical chamber 64.
  • the communication hole 266A of the spool valve 266 is disconnected from the injection passage 52 and the connecting passage 52A, so that the injection passage 52 is disconnected from the compression chamber 30B by the spool valve 266.
  • refrigerant of a medium pressure supplied from the receiver 73 through the refrigerant gas supply passage 90 to the injection passage 52 is not introduced into the compression chamber 30B.
  • the selector device 121 is in the state shown in Fig. 13 .
  • the cylindrical chamber 64 is supplied with suction refrigerant from the suction port 40 through the suction pressure passage 62.
  • suction refrigerant has a lower temperature, as compared to the case of cooling operation, there occurs a noticeable difference in length between the metal plates 124A, 124B due to thermal expansion; which causes deformation of the bimetal strip 124, so that the end of the bimetal strip 124 connected to the connecting member 126 is moved away from the suction pressure passage 62 and, therefore, the spool valve 266 connected to the connecting member 126 is moved leftward in the cylindrical chamber 64 as seen in Fig. 13 .
  • the fourth embodiment offers the following advantages.
  • Figs. 14 and 15 show the fifth embodiment of the scroll compressor according to the present invention.
  • the fifth embodiment differs from the fourth embodiment in the structure of the selector device.
  • same reference numerals are used for the common elements or components in the fourth and fifth embodiments, and the description of such elements or components of the fifth embodiment will be omitted.
  • the selector device designated generally by 130 includes a cylindrical temperature-sensing member 131, an extendable member 132, a connecting member 133 and the aforementioned cylindrical chamber 64 and cylindrical spool valve 266.
  • the selector device 130 includes no bracket such as 122 and no bimetal strip such as 124 as in the fourth embodiment.
  • the temperature-sensing member 131 is provided in the suction port 40 so as to close the opening of the suction pressure passage 62, serving to detect the variation of refrigerant temperature in the suction chamber 38.
  • the temperature-sensing member 131 is made of a metal plate having a high thermal conductivity such as a stainless steel plate or copper plate.
  • the interior of the temperature-sensing member 131 is in communication with the interior of the extendable member 132 that is provided in the suction pressure passage 62.
  • the temperature-sensing member 131 and the extendable member 132 are filled with a thermally expandable medium that is expandable and shrinkable with the variation of its temperature.
  • the extendable member 132 is connected to one end of the connecting member 133.
  • the other end of the connecting member 133 is connected to the spool valve 266.
  • the extendable member 132 is connected through the connecting member 133 to the spool valve 266.
  • the selector device 130 During the cooling operation of the compressor 1, the selector device 130 is in the state shown in Fig. 14 .
  • the temperature-sensing member 131 is exposed to the suction refrigerant in the suction port 40.
  • the thermally expandable medium exposed through the temperature-sensing member 131 to such suction refrigerant is expanded thereby to extend the extendable member 132.
  • the spool valve 266 connected through the connecting member 133 to the extendable member 132 is moved rightward as seen in Fig.
  • the selector device 130 is in the state shown in Fig. 15 .
  • the temperature-sensing member 131 is exposed to the suction refrigerant in the suction port 40.
  • the thermally expandable medium exposed through the temperature-sensing member 131 to such suction refrigerant is shrunk thereby to retract the extendable member 132.
  • the spool valve 266 connected through the connecting member 133 to the extendable member 132 is moved leftward as seen in Fig.
  • the fifth embodiment offers the following advantages.
  • the injection passages 52, 152 may be connected to the compression chamber 30 other than the compression chamber 30B. Plural injection passages such as 52, 152 may be provided for injection of medium-pressure refrigerant into the plural compression chambers 30.
  • the urging member may be provided not only by the coil spring 69 but also by any other elastic member such as leaf spring.
  • the urging member such as 69 disposed not only on the side of the spool valve 66 facing the outside air chamber 68 but also on the side of the spool valve 66 facing the suction pressure passage 62 may urge the spool valve 66 toward the suction pressure passage 62.
  • the length or shape of the connecting passage 152A may be changed. Locating the first cylindrical chamber 164 on the side of the second cylindrical chamber 102 closer to the suction port 40, the distance between the compression chamber 30 and the discharge chamber 44 can be reduced further.
  • the first and second spool valves 166, 104 in the second embodiment are applicable to the fourth and fifth embodiments.
  • the discharge pressure supplied to the check valve in the refrigerant gas supply passage 90 may be used to operate the four-way valve 70 in switching between the cooling and the heating operations.
  • the bimetal strip 124 may be replaced by a shape-memory alloy or any other suitable means that allows the spool valve 266 to be moved with the variation of suction refrigerant temperature.
  • a scroll compressor includes a housing having therein a suction chamber and a discharge chamber, a fixed scroll fixed in the housing, a movable scroll disposed in the housing in engagement with the fixed scroll to form therebetween a compression chamber into which low pressure refrigerant is introduced from the suction chamber and from which high pressure refrigerant is discharged into the discharge chamber, the movable scroll orbiting relative to the fixed scroll to vary the volume of the compression chamber, and an injection passage through which medium-pressure refrigerant is introduced into the compression chamber.
  • the scroll compressor further includes a selector device connecting the compression chamber to the injection passage or disconnecting the compression chamber from the injection passage with the change of the pressure or the temperature of the refrigerant in the suction chamber.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP13161233.5A 2012-03-30 2013-03-27 Spiralverdichter Not-in-force EP2644892B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2012080299A JP5817623B2 (ja) 2012-03-30 2012-03-30 スクロール型圧縮機

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EP2644892A2 true EP2644892A2 (de) 2013-10-02
EP2644892A3 EP2644892A3 (de) 2016-03-02
EP2644892B1 EP2644892B1 (de) 2017-05-10

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Cited By (2)

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EP3805564A1 (de) * 2019-10-10 2021-04-14 LG Electronics Inc. Motorbetriebener verdichter
CN114174681A (zh) * 2019-08-27 2022-03-11 翰昂汽车零部件有限公司 涡旋式压缩机

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Publication number Priority date Publication date Assignee Title
JP6631381B2 (ja) * 2016-04-19 2020-01-15 株式会社デンソー 圧縮機
WO2018150540A1 (ja) * 2017-02-17 2018-08-23 三菱電機株式会社 スクロール圧縮機
KR101926044B1 (ko) 2017-08-11 2018-12-06 한국에너지기술연구원 단일 스테이지 압축기 및 이를 이용한 에너지 시스템

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JPH11107968A (ja) 1997-10-06 1999-04-20 Matsushita Electric Ind Co Ltd 圧縮機のインジェクション装置
JP2008303858A (ja) 2007-06-11 2008-12-18 Daikin Ind Ltd スクロール圧縮機

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JPH10259788A (ja) * 1997-03-18 1998-09-29 Nippon Soken Inc 冷凍サイクル用圧縮機
US7771178B2 (en) * 2006-12-22 2010-08-10 Emerson Climate Technologies, Inc. Vapor injection system for a scroll compressor
KR100916229B1 (ko) * 2008-01-31 2009-09-08 엘지전자 주식회사 스크롤 압축기의 모드 전환장치

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Publication number Priority date Publication date Assignee Title
JPH11107968A (ja) 1997-10-06 1999-04-20 Matsushita Electric Ind Co Ltd 圧縮機のインジェクション装置
JP2008303858A (ja) 2007-06-11 2008-12-18 Daikin Ind Ltd スクロール圧縮機

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114174681A (zh) * 2019-08-27 2022-03-11 翰昂汽车零部件有限公司 涡旋式压缩机
CN114174681B (zh) * 2019-08-27 2023-09-29 翰昂汽车零部件有限公司 涡旋式压缩机
US11891994B2 (en) 2019-08-27 2024-02-06 Hanon Systems Scroll compressor
EP3805564A1 (de) * 2019-10-10 2021-04-14 LG Electronics Inc. Motorbetriebener verdichter

Also Published As

Publication number Publication date
JP5817623B2 (ja) 2015-11-18
EP2644892B1 (de) 2017-05-10
EP2644892A3 (de) 2016-03-02
JP2013209923A (ja) 2013-10-10

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