US20040184922A1 - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
US20040184922A1
US20040184922A1 US10/736,839 US73683903A US2004184922A1 US 20040184922 A1 US20040184922 A1 US 20040184922A1 US 73683903 A US73683903 A US 73683903A US 2004184922 A1 US2004184922 A1 US 2004184922A1
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Prior art keywords
compression
compression chamber
sub
rotary compressor
path
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Abandoned
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US10/736,839
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English (en)
Inventor
Sung-Hea Cho
Seung-Kap Lee
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Samsung Electronics Co Ltd
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Samsung Electronics Co Ltd
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Publication of US20040184922A1 publication Critical patent/US20040184922A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24C—DOMESTIC STOVES OR RANGES ; DETAILS OF DOMESTIC STOVES OR RANGES, OF GENERAL APPLICATION
    • F24C15/00—Details
    • F24C15/20—Removing cooking fumes
    • F24C15/2021—Arrangement or mounting of control or safety 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
    • 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
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/0001—Control or safety arrangements for ventilation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F7/00—Ventilation
    • F24F7/007—Ventilation with forced flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature

Definitions

  • the present invention relates, in general, to rotary compressors and, more particularly, to a variable capacity rotary compressor which has two compression chambers so as to alternately perform a refrigerant compression stroke and an idle stroke in the two compression chambers in accordance with a change in a rotating direction of a rotating shaft.
  • a rotary compressor is used as a refrigerant compression unit in a refrigerant circulation circuit of a refrigerating system, such as an air conditioner, a heater, or a refrigerator which controls a temperature of air in a desired space.
  • a refrigerant circulation circuit the rotary compressor sucks, compresses and discharges the refrigerant.
  • a refrigerant compression capacity of the rotary compressor may be controlled in accordance with a change in conditions of a target space.
  • the rotary compressors are provided such that the refrigerant compression capacity thereof is controllable, are so-called “variable capacity rotary compressors”. Particularly in a case of multiunit air conditioners each having several indoor units operated in conjunction with one outdoor unit, use of the variable capacity compressors is necessary.
  • the variable capacity of the rotary compressors is accomplished by use of electronic elements, such as inverter motors or blushless direct current (BLDC) motors, in compressors.
  • the electronic elements electronically control a capacity of the rotary compressors.
  • variable capacity rotary compressors having the inverter motors or the BLDC motors are problematic in that to use control circuit boards to control an operation of the inverter motors or the BLDC motors is necessary, thus increasing a production cost of the variable capacity rotary compressors due to the control circuit boards being expensive. Further, due to electric power consumption of the control circuit boards, the power consumption of the variable capacity rotary compressors is undesirably increased.
  • the inventors of the present invention proposed a rotary compressor, the refrigerant compression capacity of which is varied as desired between two stages by use of a mechanical mechanism.
  • variable capacity rotary compressor of which a refrigerant compression capacity is varied as desired between four stages by use of a mechanical mechanism.
  • a rotary compressor having a rotating shaft comprising first and second eccentric parts; a reversible motor to rotate the rotating shaft in a first direction or a second direction; a first cylinder comprising a first compression chamber in which a refrigerant compression stroke or an idle stroke is performed in accordance with a rotating direction of the first eccentric part of the rotating shaft; a first intake port to suck a refrigerant into the first compression chamber; and a first exhaust port to discharge the refrigerant from the first compression chamber after the refrigerant is compressed; a second cylinder comprising a second compression chamber in which the refrigerant compression stroke or the idle stroke is performed in accordance with the rotating direction of the second eccentric part of the rotating shaft, such that first and second compression chambers alternately perform the compression stroke and the idle stroke; a second intake port to suck the refrigerant into the second compression chamber; and a second exhaust port to discharge the refrigerant from the second compression
  • the first sub-path is a first sub-path pipe provided to allow the predetermined point of the first compression chamber to communicate with the first intake port, or a first sub-path groove provided in the first cylinder to allow the predetermined point of the first compression chamber to communicate with the first intake port.
  • the rotary compressor further comprises a second sub-path which allows a predetermined point of the second compression chamber to communicate with the second intake port so as to control a compression capacity of the second compression chamber, an opening ratio of the second sub-path being controlled by the path control unit.
  • the second sub-path is a second sub-path pipe provided to allow the predetermined point of the second compression chamber to communicate with the second intake port, or a second sub-path groove provided in the second cylinder to allow the predetermined point of the second compression chamber to communicate with the second intake port.
  • the path control unit includes first and second path control units which control opening ratios of the first and second sub-paths, respectively.
  • the first and second compression chambers have different compression capacities.
  • a rotary compressor having a rotating shaft; a reversible motor to rotate the rotating shaft in a first direction or a second direction; first and second compression chambers in which a refrigerant compression stroke and an idle stroke are alternately performed in accordance with a rotating direction of the rotating shaft; a first sub-path which allows a predetermined point of the first compression chamber to communicate with a refrigerant intake side of the first compression chamber so as to control a compression capacity of the first compression chamber; a second sub-path which allows a predetermined point of the second compression chamber to communicate with a refrigerant intake side of the second compression chamber so as to control a compression capacity of the second compression chamber; and a path control unit to control opening ratios of the first and second sub-paths.
  • a capacity ratio of the first and second compression chambers in a range of about is 2.1:1 to 1.9:1.
  • the predetermined point of the first compression chamber is determined such that a compression capacity of the first compression chamber, in a state that the first sub-path is opened by the path control unit, is reduced by about 20% to 30%, in comparison with the compression capacity of the first compression chamber in a state that the first sub-path is closed.
  • the predetermined point of the second compression chamber is determined such that a compression capacity of the second compression chamber, in a state that the second sub-path is opened by the path control unit, is reduced by about 40% to 60%, in comparison with the compression capacity of the second compression chamber in a state that the second sub-path is closed.
  • FIG. 1 is a longitudinal sectional view of a variable capacity rotary compressor, according to a first embodiment of the present invention
  • FIG. 2 is a perspective view of a compression unit of the rotary compressor of FIG. 1;
  • FIG. 3 is an exploded perspective view of the compression unit of FIG. 2;
  • FIGS. 4 and 5 are latitudinal sectional views taken along the line I-I showing and operation of the rotary compressor of FIG. 1;
  • FIGS. 6 and 7 are latitudinal sectional views taken along the line II-II showing an operation of the rotary compressor of FIG. 1;
  • FIG. 8 is a latitudinal sectional view of a variable capacity rotary compressor, according to a second embodiment of the present invention.
  • FIG. 1 is a longitudinal sectioned view of a variable capacity rotary compressor, according to a first embodiment of the present invention.
  • FIG. 2 is a perspective view of a compression unit of the rotary compressor of FIG. 1.
  • FIG. 3 is an exploded perspective view of the compression unit of FIG. 2.
  • the variable capacity rotary compressor 1 includes a hermetic casing 100 , with a drive unit 200 and a compression unit 300 installed in the hermetic casing 100 .
  • the drive unit 200 generates a rotating force when an electric current is applied to the drive unit 200 .
  • the compression unit 300 is coupled to the drive unit 200 through a rotating shaft 21 so as to compress refrigerant by the rotating force of the drive unit 200 .
  • the drive unit 200 includes the rotating shaft 21 having first and second eccentric parts 21 a and 21 b.
  • the drive unit 200 also includes a rotor 22 and a stator 23 .
  • the rotor 22 is a cylindrical body fitted over an upper portion of the rotating shaft 21 to electromagnetically rotate in cooperation with the stator 23 .
  • the stator 23 is fixed to an inner surface of the hermetic casing 100 while surrounding the rotor 22 , with an annular gap defined between the rotor 22 and the stator 23 .
  • the stator 23 is wound with a coil that is connected to an external electric power source, so that the stator 23 produces a magnetic field to electromagnetically rotate the rotor 22 .
  • the rotor 22 and the stator 23 comprise a reversible drive motor that is rotatable in either a clockwise direction or a counter clockwise direction.
  • the compression unit 300 includes first and second cylinders 31 and 32 .
  • the first cylinder 31 defines therein a first compression chamber 31 a which receives the first eccentric part 21 a of the rotating shaft 21 therein so as to perform a compression stroke during a forward rotation of the rotating shaft 21 , and an idle stroke during a reverse rotation of the rotating shaft 21 .
  • the second cylinder 32 defines therein a second compression chamber 32 a which receives the second eccentric part 21 b of the rotating shaft 21 therein and has a compression capacity smaller than that of the first compression chamber 31 a (about a half of the compression capacity of that of the first compression chamber 31 a ).
  • the second compression chamber 32 a performs an idle stroke during the forward rotation of the rotating shaft 21 , and a compression stroke during the reverse rotation of the rotating shaft 21 .
  • the first and second compression chambers 31 a and 32 a thus alternately perform the compression and idle strokes.
  • a first roller piston 33 is fitted over the first eccentric part 21 a of the rotating shaft 21 in the first compression chamber 31 a, a predetermined first gap defined between the first roller piston 33 and the first eccentric part 21 a to be eccentric to a side.
  • a second roller piston 34 is fitted over the second eccentric part 21 b of the rotating shaft 21 in the second compression chamber 32 a, a predetermined second gap defined between the second roller piston 34 and the second eccentric part 21 b to be eccentric to another side.
  • a first cam bush 35 having an eccentric shape is fitted in the first eccentric gap between the first eccentric part 21 a and the first roller piston 33 in the first compression chamber 31 a.
  • a second cam bush 36 having an eccentric shape is fitted in the second eccentric gap between the second eccentric part 21 b and the second roller piston 34 in the second compression chamber 32 a.
  • An upper flange 37 hermetically seals an upper end of the first compression chamber 31 a while supporting an intermediate portion of the rotating shaft 21 .
  • An intermediate plate 38 is provided between the first and second cylinders 31 and 32 so as to hermetically seal both a lower end of the first compression chamber 31 a and an upper end of the second compression chamber 32 a.
  • a lower flange 39 hermetically seals a lower end of the second compression chamber 32 a while supporting a lower end of the rotating shaft 21 .
  • the first cam bush 35 causes an eccentric rotation of the first roller piston 33 to allow the compression stroke to be performed in the first compression chamber 31 a.
  • the first cam bush 35 causes a concentric rotation of the first roller piston 33 to allow the idle stroke to be performed in the first compression chamber 31 a.
  • the second cam bush 36 causes a concentric rotation of the second roller piston 34 during the forward rotation of the rotating shaft 21 to allow the idle stroke to be performed in the second compression chamber 32 a.
  • the second cam bush 36 causes an eccentric rotation of the second roller piston 34 to allow the compression stroke to be performed in the second compression chamber 32 a.
  • the first cylinder 31 has a first intake port 31 b, a first exhaust port 31 c, and a first sub-path groove 31 d.
  • the first intake port 31 b sucks the refrigerant into the first compression chamber 31 a, while the first exhaust port 31 c discharges the refrigerant from the first compression chamber 31 a after the refrigerant is compressed.
  • the first sub-path groove 31 d forms a first sub-path, which allows the first intake port 31 b to communicate with a point “A” of the first compression chamber 31 a, so as to control a capacity of the first compression chamber 31 a.
  • the second cylinder 32 has a second intake port 32 b, a second exhaust port 32 c, and a second sub-path groove 32 d.
  • the second intake port 32 b sucks the refrigerant into the second compression chamber 32 a, while the second exhaust port 32 c discharges the refrigerant from the second compression chamber 32 a after the refrigerant is compressed.
  • the second sub-path groove 32 d forms a second sub-path which allows the second intake port 32 b to communicate with a point “B” of the second compression chamber 32 a so as to control a capacity of the second compression chamber 32 a.
  • the variable capacity rotary compressor has a path control unit driven by a solenoid unit to control opening ratios of the first and second sub-path grooves 31 d and 32 d.
  • the path control unit is fabricated as two separate units, first and second path control units 40 a and 40 b which separately control the opening ratios of the first and second sub-path grooves 31 d and 32 d.
  • the first path control unit 40 a controls the opening ratio of the first sub-path groove 31 d
  • the second path control unit 40 b controls the opening ratio of the second sub-path groove 32 d.
  • the path control unit may be a single unit that controls the opening ratios of both of the first and second sub-path grooves 31 d and 32 d.
  • a capacity ratio of the first, second, third and fourth stages of the variable capacity rotary compressor 1 may be set to, for example, 4:3:2:1, and to accomplish the capacity ratio of 4:3:2:1 of the four stages, the first and second compression chambers 31 a and 31 b have a capacity ratio of 2:1.
  • the capacity ratio of the first, second, third and fourth stages of the variable capacity rotary compressor 1 and the capacity ratio of the first and second compression chambers 31 a and 32 a may change from the above-mentioned ratios if the variable capacity rotary compressor 1 varies in a refrigerant compression capacity thereof between the four stages.
  • the capacity ratio of the first, second, third and fourth stages of the variable capacity rotary compressor 1 is set to 4:3:2:1, as described above, the capacity ratio of the first and second compression chambers 31 a and 31 b may be set in a range of about 2.1:1 to 1.9:1, in consideration of machining allowances and other conditions of the variable capacity rotary compressor 1 .
  • the point “A” in the first compression chamber 31 a is determined as follows.
  • the point “A” in the first compression chamber 31 a is determined such that when the first sub-path groove 31 d is opened under the control of the first path control unit 40 a, a variable capacity of the first compression chamber 31 a is reduced by 25%, compared with a capacity of the first compression chamber 31 a in a state that the first sub-path groove 31 d is closed.
  • a capacity reduction ratio of the first compression chamber 31 a may change from the above-mentioned ratio, if the changed capacity reduction ratio of the first compression chamber 31 a allows the rotary compressor to vary in a capacity thereof between the first to fourth stages.
  • the capacity ratio of the first, second, third and fourth stages of the variable capacity rotary compressor 1 is set to 4:3:2:1, as described above, the point “A” in the first compression chamber 31 a may be determined such that the variable capacity of the first compression chamber 31 a, in a state that the first sub-path groove 31 d is opened, is reduced in a range of about 20% to 30%, compared with the capacity of the first compression chamber 31 a in the state that the first sub-path groove 31 d is closed.
  • the point “B” in the second compression chamber 32 a is determined as follows.
  • the point “B” in the second compression chamber 32 a is determined such that when the second sub-path groove 32 d is opened under the control of the second path control unit 40 b, a variable capacity of the second compression chamber 32 a is reduced by 50% compared with the capacity of the second compression chamber 32 a in a state that the second sub-path groove 32 d is closed.
  • a capacity reduction ratio of the second compression chamber 32 a may change from the above-mentioned ratio, if the changed capacity reduction ratio of the second compression chamber 32 a allows the rotary compressor to vary in a capacity thereof between the first to fourth stages.
  • the capacity ratio of the first, second, third and fourth stages of the variable capacity rotary compressor 1 is set to 4:3:2:1, as described above, the point “B” in the second compression chamber 32 a may be determined such that the variable capacity of the second compression chamber 32 a, in a state that the second sub-path groove 32 d, is opened is reduced in a range of about 40% to 60%, in comparison with the capacity of the second compression chamber 32 a in the state that the second sub-path groove 32 d is closed.
  • variable capacity rotary compressor having the above-mentioned construction
  • variable capacity rotary compressor 1 is used as a refrigerant compression unit in a refrigerant circulation circuit of a refrigerating system, such as an air conditioner, a heater, or a refrigerator that controls a temperature of air in a target space.
  • a refrigerating system such as an air conditioner, a heater, or a refrigerator that controls a temperature of air in a target space.
  • the refrigerant compression capacity of the rotary compressor is required to change in accordance with the present temperature of the space.
  • variable capacity rotary compressor 1 is operated as follows in the first to fourth stage modes wherein the rotary compressor achieves different compression capacities, and stage numbers of the variable capacity rotary compressor 1 in the following description are designated in order of a scale of the capacities from a largest capacity to a smallest capacity.
  • a first stage mode the reversible motor of the drive unit 200 rotates the rotating shaft 21 in a forward direction, as shown in FIG. 4, so that the first roller piston 33 eccentrically rotates by an operation of both the first eccentric part 21 a of the rotating shaft 21 and the first cam bush 35 .
  • the first roller piston 33 in the first stage mode performs a compression stroke in the first compression chamber 31 a
  • the second roller piston 34 in the first stage mode concentrically rotates to perform an idle stroke in the second compression chamber 32 a.
  • the first path control unit 40 a closes the first sub-path groove 31 d, and the variable capacity rotary compressor 1 achieves a largest refrigerant compression capacity in the first stage mode.
  • the reversible motor of the drive unit 200 rotates the rotating shaft 21 in the forward direction, as shown in FIG. 5, so that the first roller piston 33 eccentrically rotates by the operation of both the first eccentric part 21 a of the rotating shaft 21 and the first cam bush 35 .
  • the first roller piston 33 performs the compression stroke in the first compression chamber 31 a, while the second roller piston 34 concentrically rotates to perform the idle stroke in the second compression chamber 32 a, in a same manner as that described for the first stage mode.
  • the first path control unit 40 a opens the first sub-path groove 31 d, so that an effective refrigerant compression stroke performed by the first roller piston 33 in the first compression chamber 31 a starts at the point “A” of the first compression chamber 31 a.
  • the variable capacity rotary compressor 1 in the second stage mode achieves a compression capacity equal to 75% of the capacity expected in the first stage mode.
  • the reversible motor of the drive unit 200 rotates the rotating shaft 21 in a reverse direction, as shown in FIG. 6, so that the first roller piston 33 concentrically rotates to perform the idle stroke in the first compression chamber 31 a.
  • the second roller piston 34 eccentrically rotates by an operation of both the second eccentric part 21 b of the rotating shaft 21 and the second cam bush 36 .
  • the second roller piston 34 performs the compression stroke in the second compression chamber 32 a.
  • the second path control unit 40 b in the third stage mode closes the second sub-path groove 32 d, so that the variable capacity rotary compressor 1 in the third stage mode achieves the compression capacity which is equal to 50% of the capacity expected in the first stage mode, and which is equal to 75% of the capacity expected in the second stage mode.
  • the reversible motor of the drive unit 200 rotates the rotating shaft 21 in the reverse direction, as shown in FIG. 7, so that the first roller piston 33 concentrically rotates to perform the idle stroke in the first compression chamber 31 a, while the second roller piston 34 eccentrically rotates by the operation of both the second eccentric part 21 b of the rotating shaft 21 and the second cam bush 36 .
  • the second roller piston 34 performs the compression stroke in the second compression chamber 32 a, in a same manner as that described for the third stage mode.
  • the second path control unit 40 b opens the second sub-path groove 32 d, so that the effective refrigerant compression stroke performed by the second roller piston 34 in the second compression chamber 32 a starts at the point “B” of the second compression chamber 32 a.
  • the variable capacity rotary compressor 1 in the fourth stage mode achieves a compression capacity that is equal to 25% of the capacity expected in the first stage mode, that is equal to 33% of the capacity expected in the second stage mode, and that is equal to 50% of the capacity expected in the third stage mode.
  • variable capacity rotary compressor 1 varies in the refrigerant compression capacity thereof between the four stages such that the first to fourth stages have a capacity ratio of 4:3:2:1.
  • the capacity ratio of the first, second, third and fourth stages of the variable capacity rotary compressor 1 is not limited to the above-mentioned ratio, but may be set to any other ratio without affecting an operation of the present invention.
  • FIG. 8 is a latitudinal sectioned view of a variable capacity rotary compressor 2 , according to a second embodiment of the present invention.
  • the second embodiment alters a construction of the first and second sub-paths and the first and second path control units provided in the variable capacity rotary compressor 2 to control a refrigerant compression capacities of the first and second compression chambers 31 a and 32 a.
  • the first and second sub-paths are, respectively, formed by a first sub-path pipe 51 a which allows the first compression chamber 31 a to communicate with the first intake port 31 b, and a second sub-path pipe 51 b which allows the second compression chamber 32 a to communicate with the second intake port 32 b.
  • the first and second path control units 50 a and 50 b are provided in the variable capacity rotary compressor 2 .
  • variable capacity rotary compressor which varies in the refrigerant compression capacity thereof as desired between four stages such that first to fourth stages by use of a mechanical mechanism, so that the variable capacity rotary compressor 2 may be used in a refrigerating system, such as an air conditioner (particularly, a multiunit air conditioner), a heater, or a refrigerator required to be equipped with a variable capacity compressor.
  • a refrigerating system such as an air conditioner (particularly, a multiunit air conditioner), a heater, or a refrigerator required to be equipped with a variable capacity compressor.
  • variable capacity rotary compressor does not need an expensive control circuit board which must be used in conventional electronically controlled variable capacity compressors to control an operation of an inverter motor or a BLDC motor.
  • the variable capacity rotary compressor reduces a production cost of the variable capacity rotary compressors.
  • variable capacity rotary compressor may reduce power consumption compared with the conventional electronically controlled variable capacity compressors.
  • the rotary compressor of the present invention may be provided with only one of the first and second sub-paths. In such a case, the capacity of the rotary compressor is varied between three stages, that is, first to third stages.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US10/736,839 2003-03-22 2003-12-17 Rotary compressor Abandoned US20040184922A1 (en)

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Application Number Priority Date Filing Date Title
KR1020030017994A KR20040086892A (ko) 2003-03-22 2003-03-22 로터리압축기
KR2003-17994 2003-03-22

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JP (1) JP2004286015A (zh)
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CN (1) CN1532421A (zh)

Cited By (7)

* Cited by examiner, † Cited by third party
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US20060140802A1 (en) * 2004-12-13 2006-06-29 Sanyo Electric Co., Ltd. Multicylindrical rotary compressor, compression system, and freezing device using the compression system
US20080120985A1 (en) * 2006-11-27 2008-05-29 Samsung Electronics Co. Rotary compressor, control method thereof, and air conditioner using the same
US20090277215A1 (en) * 2008-05-12 2009-11-12 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Two-stage screw compressor and refrigerating device
CN105257539A (zh) * 2015-11-02 2016-01-20 广东美芝制冷设备有限公司 多缸旋转式压缩机和具有其的制冷系统
US9546659B2 (en) 2011-03-10 2017-01-17 Panasonic Intellectual Property Management Co., Ltd. Rotary compressor
US11067077B2 (en) * 2016-06-29 2021-07-20 Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai Rotating cylinder enthalpy-adding piston compressor and air conditioning system having same
US11614086B2 (en) * 2016-12-30 2023-03-28 Aspen Compressor, Llc Flywheel assisted rotary compressors

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100715772B1 (ko) * 2004-10-06 2007-05-08 엘지전자 주식회사 선회베인 압축기의 용량 가변장치
KR100664294B1 (ko) * 2005-01-28 2007-01-04 엘지전자 주식회사 로터리 압축기의 용량 가변 장치 및 이를 적용한 에어콘
KR100645820B1 (ko) * 2005-09-16 2006-11-23 엘지전자 주식회사 인버터형 선회베인 압축기
CN105782038B (zh) * 2014-12-25 2018-04-17 珠海格力节能环保制冷技术研究中心有限公司 旋转压缩机组件及具有其的空调器
JP6446542B2 (ja) * 2016-02-02 2018-12-26 クワントン メイヂー コンプレッサー カンパニー リミテッド 可変容量型圧縮機及びこれを備える冷凍装置
CN109387000B (zh) * 2018-10-19 2019-12-10 珠海格力电器股份有限公司 一种压缩机的无级能量调节装置、调节方法以及制冷系统
CN111794972A (zh) * 2020-07-27 2020-10-20 广东美芝制冷设备有限公司 气缸组件、压缩机和制冷设备

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US20060140802A1 (en) * 2004-12-13 2006-06-29 Sanyo Electric Co., Ltd. Multicylindrical rotary compressor, compression system, and freezing device using the compression system
US7566204B2 (en) * 2004-12-13 2009-07-28 Sanyo Electric Co., Ltd. Multicylindrical rotary compressor, compression system, and freezing device using the compression system
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US20090277215A1 (en) * 2008-05-12 2009-11-12 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Two-stage screw compressor and refrigerating device
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CN105257539A (zh) * 2015-11-02 2016-01-20 广东美芝制冷设备有限公司 多缸旋转式压缩机和具有其的制冷系统
US11067077B2 (en) * 2016-06-29 2021-07-20 Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai Rotating cylinder enthalpy-adding piston compressor and air conditioning system having same
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