WO2013122363A1 - Twin rotary compressor and heat pump having the same - Google Patents

Twin rotary compressor and heat pump having the same Download PDF

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Publication number
WO2013122363A1
WO2013122363A1 PCT/KR2013/001063 KR2013001063W WO2013122363A1 WO 2013122363 A1 WO2013122363 A1 WO 2013122363A1 KR 2013001063 W KR2013001063 W KR 2013001063W WO 2013122363 A1 WO2013122363 A1 WO 2013122363A1
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WO
WIPO (PCT)
Prior art keywords
compression chamber
intermediate plate
refrigerant
channel
injection channel
Prior art date
Application number
PCT/KR2013/001063
Other languages
English (en)
French (fr)
Inventor
Jong Chul Ha
Jin Ung Shin
Bum Dong Sa
Dong Hyuk Lee
Se Seok Seol
Original Assignee
Lg Electronics Inc.
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 Lg Electronics Inc. filed Critical Lg Electronics Inc.
Publication of WO2013122363A1 publication Critical patent/WO2013122363A1/en

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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
    • F04C18/30—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
    • 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
    • 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
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression 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
    • 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

Definitions

  • the present invention relates to a twin rotary compressor and a heat pump having the same, and more particularly, a twin rotary compressor with intermediate plates dividing a plurality of compression chambers, and a heat pump with the twin rotary compressor.
  • heat pumps are apparatuses that include a compressor, an outdoor heat exchanger, an expansion device, and an indoor heat exchanger, and cool or heat an interior.
  • Heat pumps can be operated for cooling under a bad condition with too high exterior air temperature or for heating under a bad condition with too low exterior air temperature, then when a compressors operates under overload, the discharge temperature of the compressor may increase too high and reliability of the heat pumps may reduce.
  • Heat pumps can inject a liquid-state refrigerant overcooled through an exterior heat exchanger or an interior heat exchanger into a compressor to reduce the discharge temperature of a compressor and can inject a gas-state refrigerant at a middle pressure which is separated by an accumulator into a compressor.
  • Patent Document 1 KR 10-2010-0112486 A (2010.10.19)
  • a low-pressure side compression assembly and a high-pressure side compression assembly are connected by a connection pipe and an injection pipe is connected to the connection pipe in rotary 2-stage compressors of the related art, but twin rotary compressors have a problem in that it is difficult to reduce the discharge temperature of a compressor by injecting a refrigerant, because they do not compress refrigerant in several stages and not include a specific connection pipe.
  • An object of the present invention is to provide a twin rotary compressor that can inject a refrigerant with a simple structure with minimum number of parts, and a heat pump with the twin rotary compressor.
  • a twin rotary shaft that sucks and compresses a refrigerant in a first compression chamber and a second compression chamber and then discharges the refrigerant, includes: an intermediate plate disposed between the first compression chamber and the second compression chamber; an intermediate plate connection channel guiding a refrigerant guided to an injection channel to the intermediate plate; and an intermediate plate injection channel through which the refrigerant guided to the intermediate plate connection channel is injected into the first compression chamber and the second compression chamber from the intermediate plate after passing through the intermediate plate.
  • a heat pump includes: a twin rotary compressor including an intermediate plate disposed between a first compression chamber and a second compression chamber, sucking and compressing a refrigerant in the first compression chamber and the second compression chamber, and the discharging the refrigerant; an outdoor heat exchanger condensing or evaporating a refrigerant; an indoor heat exchanger evaporating or condensing a refrigerant; an expansion device expanding a refrigerant between the outdoor heat exchanger and the indoor heat exchanger; and an injection channel through which a refrigerant is injected into the twin rotor compressor, between the outdoor heat exchanger and the indoor heat exchanger, in which the twin rotary compressor includes: an intermediate plate connection channel guiding a refrigerant guided to the injection channel to the intermediate plate; and an intermediate plate injection channel through which a refrigerant guided to the intermediate plate connection channel is injected into the first compression chamber and the second compression chamber after passing through the intermediate plate.
  • the intermediate plate connection channel may include ⁇ a refrigerant pipe disposed through a casing of the twin rotary compressor.
  • the intermediate plate injection channel may include a common channel connected with the intermediate plate connection channel, a first compression chamber injection channel connecting the common channel with the first compression chamber, and a second compression chamber injection channel connecting the common channel with the second compression chamber.
  • the common channel may be formed between the top and the bottom of the intermediate plate.
  • At least one of the first compression chamber injection channel and the second compression chamber injection channel may be formed perpendicularly to the common channel in the intermediate plate.
  • the common channel may have one end formed at the edge of the intermediate plate, between the top and the bottom of the intermediate plate, and the other end positioned inside the intermediate plate.
  • the first compression chamber injection channel may have one end connected with the common channel in the intermediate plate and the other end open to one side of the intermediate plate.
  • the second compression chamber injection channel may have one end connected with the common channel in the intermediate plate and the other end open to the other side of the intermediate plate.
  • the first compression chamber injection channel and the second compression chamber injection channel may be vertically open at the same position in the intermediate plate.
  • the first compression chamber injection channel and the second compression chamber injection channel may allow the refrigerant guided through the common channel to be alternately injected into the first compression chamber and the second compression chamber, in the twin rotary compressor.
  • the first compression chamber injection channel and the second compression chamber injection channel may be formed at position where the first compression chamber injection channel and the second compression chamber injection channel are not blocked by rollers, when the angles of the rollers are an injection setting angle.
  • FIG. 1 is a view showing a heat pump according to an exemplary embodiment of the present invention.
  • FIG. 2 is a cross-sectional view showing a twin rotary compressor for a heat pump according to an exemplary embodiment of the present invention.
  • FIG. 3 is an enlarged cross-sectional view of an intermediate plate of FIG. 2.
  • FIG. 4 is a plan view showing an exemplary embodiment of a compression chamber of a heat pump according to the present invention.
  • FIG. 5 is a plan view showing another exemplary embodiment of a compression chamber of a heat pump according to the present invention.
  • FIG. 1 is a view showing a heat pump according to an exemplary embodiment of the present invention.
  • a heat pump includes a twin rotary compressor 2, an outdoor heat exchanger 4 evaporating or condensing a refrigerant, an indoor heat exchanger 6 evaporating or condensing a refrigerant, an expansion device 8 expanding a refrigerant between the outdoor heat exchanger 4 and the indoor heat exchanger 6, and an injection channel 12 for injecting a refrigerant into the twin rotary compressor 2 between the outdoor heat exchanger 4 and the indoor heat exchanger 6.
  • the twin rotary compressor 2 can compress a refrigerant in two compression chambers with one motor and can independently suck, compress, and discharge a refrigerant with a first compression chamber and a second compression chamber.
  • the twin rotary compressor 2 may be an inverter compressor with variable compression capacity with an input frequency.
  • An accumulator 3 accumulating a liquid-state refrigerant from the refrigerant sucked into the twin rotary compressor 2 may be connected to the twin rotary compressor 2.
  • the twin rotary compressor 2 may be connected with the accumulator 3 by intake pipes 2a and 2b.
  • One or a plurality of intake pipes 2a and 2b may be provided.
  • the outdoor heat exchanger 4 can allow a refrigerant to evaporate or condense by exchanging heat with the exterior air blown by an outdoor fan 5.
  • the outdoor fan 5 is disposed outside with the outdoor heat exchanger 4 and can blow the exterior air into the outdoor heat exchanger 4.
  • the heat pump may be an air conditioner of the heat pump type or a water heater of the heat pump type.
  • an air conditioner of the heat pump type interior air can change the interior temperature by being discharged to the interior after exchanging heat with a refrigerant through the indoor heat exchanger 6.
  • a water heater of the heat pump type a liquid-state thermal medium such as water or antifreeze can be used to heat water after exchanging heat with a refrigerant through the indoor heat exchanger 6.
  • the indoor heat exchanger 6 is composed of a refrigerant tube through which a refrigerant passes and a fin-tube heat exchanger including at least one fin connected to the refrigerant tube, such that the interior air can exchange heat with the refrigerant by coming in contact with the fin-tube heat exchanger.
  • the indoor heat exchanger 6 can condense or evaporate a refrigerant by allowing the refrigerant passing through it to exchange heat with the interior air blown by an indoor fan 7.
  • the indoor heat exchanger 6 may include a first channel through which a refrigerant passes and a second channel through which a liquid-state thermal medium passes and may be a double pipe heat exchanger, a plate type heat exchanger, or a shell-tube type heat exchanger where a refrigerant in the first channel and a liquid-state thermal medium in the second channel exchange heat, with a thermal conductive member therebetween, and in this case, the liquid-state thermal medium can exchange heat with the refrigerant through the thermal conductive member while passing through the second channel.
  • the indoor heat exchanger 6 can be connected with a tank (or hot water tank, not shown) filled with a liquid-state thermal medium by a liquid-state thermal medium circuit channel and the liquid-state thermal medium flowing out of the tank (or hot water tank) can evaporate or condense a refrigerant while passing through the second channel of the indoor heat exchanger 6.
  • the expansion device 8 may include an outdoor expansion device disposed closer to the outdoor heat exchanger 4 than the indoor heat exchanger 6 and the outdoor heat exchanger may be a capillary tube or an electronic expansion valve.
  • the expansion device 8 may further include an indoor expansion device disposed closer to the outdoor heat exchanger 4 than the indoor heat exchanger 6 and the indoor heat exchanger may be a capillary tube or an electronic expansion valve.
  • the injection channel 12 may have one end connected between the outdoor heat exchanger 4 and the indoor heat exchanger 6 and the other end connected to the twin rotary compressor 2.
  • An injection valve 14 controlling the refrigerant passing through the injection channel 12 may be disposed in the injection channel 12.
  • the invention valve 14 may be an expansion valve that expands a refrigerant.
  • the injection channel 12 may be disposed between the outdoor heat exchanger 4 and the expansion device 8, such that it can allow a refrigerant supercooled through the outdoor heat exchanger 4 to be injected into the twin rotary compressor 2 in cooling and a refrigerant supercooled through the indoor heat exchanger 6 to be injected into the twin rotary compressor 2 in heating.
  • the expansion device 8 includes both an outdoor expansion device and an indoor expansion device, the injection channel 12 can be connected between the outdoor expansion device and the indoor expansion device.
  • the heat pump may further include a switching unit 16.
  • the switching unit 16 can allow the refrigerant passing through the indoor heat exchanger 6 to flow to the twin rotary compressor 2 and the refrigerant compressed and discharged from the twin rotary compressor 2 to flow to the outdoor heat exchanger 4, in cooling.
  • the switching unit 16 can allow the refrigerant passing through the outdoor heat exchanger 4 to flow to the twin rotary compressor 2 and the refrigerant compressed and discharged from the twin rotary compressor 2 to flow to the outdoor heat exchanger 4, in heating.
  • one 4-way valve can change the flow direction of the refrigerant and a plurality of shut-off valves can change the direction of the refrigerant.
  • the compressor 2, the outdoor heat exchanger 4, the outdoor fan 5, the expansion device 8, the injection channel 12, and the switching unit 16 may be disposed in an outdoor unit O, and the indoor heat exchanger 6 and the indoor fan 7 may be disposed in an indoor unit I.
  • the expansion device 8 includes an outdoor expansion device and an indoor expansion device
  • the outdoor expansion device may be disposed in the outdoor unit O and the indoor expansion device may be disposed in the indoor unit I.
  • FIG. 2 is a cross-sectional view showing a twin rotary compressor for a heat pump according to an exemplary embodiment of the present invention
  • FIG. 3 is an enlarged cross-sectional view of an intermediate plate of FIG. 2
  • FIG. 4 is a plan view showing an exemplary embodiment of a compression chamber of a heat pump according to the present invention
  • FIG. 5 is a plan view showing another exemplary embodiment of a compression chamber of a heat pump according to the present invention.
  • the twin rotary compressor 2 includes an intermediate plate 26 between a first compression chamber 22 and a second compression chamber 24, sucks and compresses a refrigerant in the first compression chamber 22 and the second compression chamber 24, and then discharges the refrigerant.
  • the twin rotary compressor 2 may include a casing 32, a motor 34 disposed in the casing 32, a first compression assembly 36 including the first compression chamber 22 disposed in the casing 32 and compressing a refrigerant when the motor 34 is driven, and a second compression assembly 38 including the second compression chamber 24 disposed in the casing 32 and compressing a refrigerant when the motor 34 is driven.
  • the casing 32 may form the external appearance of the twin rotary compressor 2.
  • the casing 32 may include a hollow cylindrical shell, a base coupled to the bottom of the shell, and a top cover coupled to the top of the shell, thereby forming a closed space inside.
  • a first intake pipe 40 that guides a refrigerant sucked to the first compression assembly 36 and a second intake pipe 42 that guides a refrigerant sucked to the second compression assembly 38 may be connected to the casing 32.
  • a discharge pipe 44, which guides the refrigerant compressed and discharged from the first compression chamber 22 and the refrigerant compressed and discharged from the second compression chamber to the outside, may be connected to the casing 32.
  • the motor 34 includes a stator 52, a rotor 54, and a rotary shaft 56.
  • the rotary shaft 56 is fixed to the rotor 54 through the center of the rotor 54.
  • the rotor 54 is rotated by interactive electromagnetic force between the stator 52 and the rotor 54 and the rotary shaft 56 fixed to the rotor 54 rotates with the rotor 54.
  • the rotary shaft 56 extends toward the bottom of the casing 32 from the rotor 54 through the centers of the first compression assembly 36, the intermediate plate 26, and the second compression assembly 38.
  • the first compression assembly 36 and the second compression assembly 38 may include cylinders 62 and 72, eccentric parts 64 and 74, and rollers 66 and 76, respectively.
  • the first compression assembly 36 and the second compression assembly 38 may respectively have refrigerant intake ports 61 and 71 through which a refrigerant is sucked into the compression chambers 22 and 24, and refrigerant discharge ports 63 and 73 through which the refrigerant compressed through the compression chambers 22 and 24 is discharged.
  • the first compression assembly 36 and the second compression assembly 38 may further include vanes 67 and 77 disposed in the cylinders 62 and 72 in contact with the rollers 66 and 76, respectively.
  • the first compression assembly 36 may include a first cylinder 62 formed in the first compression chamber 22, a first eccentric part 64 disposed on the rotary shaft 56, and a first roller 66 disposed in the first eccentric part 64 and rolling along the inner side of the first cylinder 62.
  • a first vane 67 keeping in contact with the first roller 66 may be elastically supported by a spring in the first cylinder 62.
  • the first compression assembly 36 may further include a first bearing 68 that composes the first compression chamber 22 together with the first cylinder 62 and supports the rotary shaft 56 to be rotatable.
  • the second compression assembly 38 may include a second cylinder 72 formed in the second compression chamber 24, a second eccentric part 74 disposed on the rotary shaft 56, and a second roller 76 disposed in the second eccentric part 74 and rolling along the inner side of the second cylinder 72.
  • a second vane 77 keeping in contact with the second roller 76 may be elastically supported by a spring in the second cylinder 72.
  • the second compression assembly 38 may further include a second bearing 78 that composes the second compression chamber 24 together with the second cylinder 72 and supports the rotary shaft 56 to be rotatable.
  • the second eccentric part 74 may be arranged with a phase difference of 180° from the first eccentric part 64.
  • the intermediate plate 26 may be disposed between the first cylinder 62 and the second cylinder 72.
  • the intermediate plate 26 may function as a partition dividing the first compression chamber 22 and the second compression chamber 24.
  • the first cylinder 62 may be disposed above the intermediate plate 26, the second cylinder 72 may be disposed under the intermediate plate 26 at a predetermined distance from the first cylinder 62, and the intermediate plate 26 may be disposed horizontally between the first cylinder 62 and the second cylinder 72.
  • One of both sides of the intermediate plate 26 may form the first compression chamber 22 together with the first cylinder 62.
  • the other one of both sides of the intermediate plate 26 may form the second compression chamber 24 together with the second cylinder 72.
  • a hole 27 through which the rotary shaft 56 passes may be formed through the center of the intermediate plate 26.
  • the twin rotary compressor 2 may include an intermediate plate connection channel 90 that guides the refrigerant guided to the injection channel 12 to the intermediate plate 26 and an intermediate plate injection channel 100 through which the refrigerant guided to the intermediate plate connection channel 90 is injected into the first compression chamber 22 and the second compression chamber 24 from the intermediate plate 26 after passing through the intermediate plate 26.
  • the intermediate connection channel 90 may be implemented by a refrigerant pipe through which a refrigerant flows.
  • the intermediate plate connection channel 90 may be implemented by a refrigerant pipe with one end disposed outside the casing 32 and the other end disposed inside and through the casing 32 and the injection channel 12 may include a refrigerant pipe connected to the intermediate plate connection pipe 90 from the outside of the casing 32.
  • the intermediate plate connection channel 90 may be implemented by a refrigerant pipe with both of one end and the other end disposed inside the casing 32 and the injection channel 12 may include a refrigerant pipe connected to the intermediate plate connection pipe 90 inside and through the casing 32.
  • the intermediate plate injection channel 100 may include a common channel 102 to which the intermediate plate connection channel 90 is connected, a first compression chamber injection channel 104 connecting the common channel 102 with the first compression chamber 22, and a second compression chamber injection channel 106 that connects the common channel 102 with the second compression chamber 24.
  • the intermediate plate 26 may be implemented by one plate and the intermediate plate injection channel 100 may be formed by boring one plate.
  • the common channel 102 may be formed in the shape of a groove on one of the top and the bottom of the intermediate plate 26, and the first compression chamber injection channel 104 and the second compression chamber injection channel 106 may be connected to the groove-shaped common channel 102.
  • the intermediate plate 26 may include a first plate which has the upper common channel 102 formed on the bottom in the shape of a groove and on which the first compression chamber injection channel 104 is connected to the groove-shaped upper common channel and a second plate which is combined with the first plate and has a lower common channel formed in the shape of a groove on the top and on which the second compression chamber injection channel 106 is connected to the groove-shaped lower common channel, and the upper common channel and the lower common channel may form the common channel 102.
  • the common channel 102 may be formed between the top and the bottom of the intermediate plate 26.
  • one end 102a may be formed at the edge of the intermediate plate 26, between the top and the bottom of the intermediate plate, and the other end may be positioned inside the intermediate plate 26.
  • the common channel 102 may be formed horizontally between the top and the bottom of the intermediate plate 26.
  • At least one of the first compression chamber injection channel 104 and the second compression chamber injection channel 106 may be formed perpendicularly to the common channel 102 in the intermediate plate 26. At least one of the first compression chamber injection channel 104 and the second compression chamber injection channel 106 may be formed vertically the intermediate plate 26.
  • the first compression chamber injection channel 104 may have one end connected with the common channel 102 in the intermediate plate 26 and the other end open to one side of the intermediate plate 26.
  • the second compression chamber injection channel 106 may have one end connected with the common channel 102 in the intermediate plate 26 and the other end open to the other side of the intermediate plate 26.
  • the first compression chamber injection channel 104 and the second compression chamber injection channel 106 may be vertically open at the same position in the intermediate plate 26 without a phase difference and the refrigerant guided through the common channel 102 may be alternately injected into the first compression chamber 22 and the second compression chamber 24 due to the phase difference of 180° between the first eccentric part 64 and the second eccentric part 74.
  • the first compression chamber injection channel 104 and the second compression chamber injection channel 106 may be formed at positions where they are not blocked by the rollers 66 and 76, when the angles ⁇ of the rollers 66 an d76 are an injection setting angle.
  • the first compression chamber injection channel 104 and the second compression chamber injection channel 106 may be blocked by the rollers 66 and 76, when the angles ⁇ of the rollers 66 and 76 are an injection stop setting angle.
  • the angles ⁇ of the rollers 66 and 76 are rotation angle of the rollers 66 and 76 from the vanes 67 and 77.
  • the injection setting angle may be set such that the angles ⁇ of the rollers 66 and 76 are over 30° and under 180°.
  • the first compression chamber injection channel 104 and the second compression chamber injection channel 106 may be formed at positions where they are blocked by the rollers 66 and 76 when the angles ⁇ of the rollers 66 and 76 are 30° or less, as in (a) of FIG. 4, not blocked by the rollers 66 and 76 when the angles ⁇ are over 30° and under 125°, as in (b) FIG. 4, and blocked by the rollers 66 and 76 when the angels are 125° or more. That is, the injection setting angle may be set such that the angles ⁇ of the rollers 66 and 76 are over 30° and under 125°.
  • the first compression chamber injection channel 104 and the second compression chamber injection channel 106 may be formed at positions where they are blocked by the rollers 66 and 76 when the angles ⁇ of the rollers 66 and 76 are 85° or less, as in (a) of FIG. 5, not blocked by the rollers 66 and 76 when the angles ⁇ are over 85° and under 175°, as in (b) FIG. 5, and blocked by the rollers 66 and 76 when the angels are 175° or more. That is, the injection setting angle may be set such that the angles ⁇ of the rollers 66 and 76 are over 85° and under 175°.
  • the twin rotary compressor 2 may be driven and the outdoor fan 5 and the indoor fan 7 may be rotated.
  • a frequency corresponding to load may be inputted to the twin rotary compressor 2.
  • a refrigerant is sucked into the first compression chamber 22 and the second compression chamber 24, the refrigerant sucked in the first compression chamber 22 is discharged out of the first compression chamber 22 after compressed by the first roller 66, and the refrigerant sucked in the second compression chamber 24 is discharged out of the second compression chamber 24 after compressed by the second roller 76.
  • the refrigerant discharged outside from the first compression chamber 22 and the refrigerant discharged outside from the second compression chamber 24 are discharged out of the twin rotary compressor 2 through the discharge pipe 44.
  • the refrigerant discharged out of the twin rotary compressor 2 flows to the outdoor heat exchanger 4, condenses through the outdoor heat exchanger 4, expands through the expansion device 8, and flows into twin rotary compressor 2.
  • the injection valve 14 may opens, some of the refrigerant supercooled by the outdoor heat exchanger 4 with the injection valve 14 open may flow into the injection line 12 and the other may flow to the expansion device 8.
  • the refrigerant flowing in the injecting line 12 may be guided to the twin rotary compressor 2 through the injection line 12 in a liquid state, may be guided to the intermediate plate 26 through the intermediate plate connection channel 90, and may flow into the intermediate injection channel 100.
  • the refrigerant flowing in the intermediate plate injection channel 100 is distributed to the first compression chamber injection channel 104 and the second compression chamber injection channel 106 after passing through the common channel 102 and then flows into the first compression chamber 22 and the second compression chamber 24.
  • the refrigerant flowing in the first compression chamber 22 through the first compression chamber injection channel 104 decreases the temperature of the refrigerant compressed by the first roller 66 in the first compression chamber 22 by mixing with it, such that the refrigerant discharged out of the first compression chamber 22 decreases in temperature. Further, the refrigerant flowing in the second compression chamber 24 through the second compression chamber injection channel 106 decreases the temperature of the refrigerant compressed by the second roller 76 in the second compression chamber 24 by mixing with it, such that the refrigerant discharged out of the second compression chamber 24 decreases in temperature.
  • the twin rotary compression 2 In cooling, as the refrigerant discharged out of the first compression chamber 22 decreases in temperature and the refrigerant discharged out of the second compression chamber 24 decreases in temperature, the twin rotary compression 2 can keep stability and the cooling performance of the heat pump can be improved by increasing the frequency inputted from the twin rotary compressor 2 higher than that when the injection valve 14 is open. It is preferable to increase the cooling performance of the heat pump by increasing the frequency inputted to the rotary compressor 2 simultaneously with injection of the refrigerant through the intermediate plate 26 with the injection valve 14 open, under the cooling condition that the exterior temperature is a set temperature or more.
  • the twin rotary compressor 2 may be driven and the outdoor fan 5 and the indoor fan 7 may be rotated.
  • a frequency corresponding to load may be inputted to the twin rotary compressor 2.
  • the twin rotary compressor 2 sucks, compresses, and then discharges a refrigerant in heating, like in cooling.
  • the refrigerant discharged out of the twin rotary compressor 2 flows to the indoor heat exchanger 6, condenses through the indoor heat exchanger 6, expands through the expansion device 8, and then flows into twin rotary compressor 2.
  • the injection valve 14 may opens, some of the refrigerant flowing from the indoor heat exchanger 6 with the injection valve open 14 may flow into the injection line 12 and the other may flow to the outdoor heat exchanger 4.
  • the refrigerant guided to the injection line 12 may be guided to the twin rotary compressor 2 through thee injection line 12 in the liquid state, and like in cooling, it is distributed to the first compression chamber injection channel 104 and the second compression chamber injection channel 106 after sequentially passing the intermediate plate connection channel 90 and the common channel 102, and then flows into the first compression chamber 22 and the second compression chamber 24.
  • the refrigerant flowing in the first compression chamber 22 from the first compression chamber injection channel 104 may decrease the temperature of the refrigerant discharged out of the first compression chamber 22, like in cooling, and the refrigerant flowing in the second compression chamber 24 from the second compression chamber injection channel 106 may decrease the temperature of the refrigerant discharged out of the second compression chamber 24.
  • the twin rotary compression 2 In heating, as the refrigerant discharged out of the first compression chamber 22 decreases in temperature and the refrigerant discharged out of the second compression chamber 24 decreases in temperature, the twin rotary compression 2 can keep stability and the heating performance of the heat pump can be improved by increasing the frequency inputted from the twin rotary compressor 2 higher than that when the injection valve 14 is open. It is preferable to increase the cooling performance of the heat pump by increasing the frequency inputted to the rotary compressor 2 simultaneously with injection of the refrigerant through the intermediate plate 26 with the injection valve 14 open, under the heating condition that the exterior temperature is a se temperature or less.

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  • 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)
PCT/KR2013/001063 2012-02-14 2013-02-12 Twin rotary compressor and heat pump having the same WO2013122363A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2012-0014918 2012-02-14
KR1020120014918A KR101891616B1 (ko) 2012-02-14 2012-02-14 트윈 로터리 압축기 및 그를 갖는 히트 펌프

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015135090A (ja) * 2014-01-17 2015-07-27 株式会社富士通ゼネラル ロータリ圧縮機
CN105065273A (zh) * 2015-08-24 2015-11-18 广东美芝制冷设备有限公司 旋转式压缩机和具有其的冷冻循环装置
US10465682B2 (en) 2015-08-24 2019-11-05 Guangdong Meizhi Compressor Co., Ltd. Rotary compressor and refrigeration cycle device having same
DE102019102213A1 (de) 2019-01-29 2020-07-30 Closurelogic Gmbh Flaschenkappe

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102339600B1 (ko) * 2017-05-26 2021-12-15 엘지전자 주식회사 로터리 압축기

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Publication number Priority date Publication date Assignee Title
JPH0650276A (ja) * 1992-07-28 1994-02-22 Daikin Ind Ltd ロータリー圧縮機
JPH07127575A (ja) * 1993-10-29 1995-05-16 Sanyo Electric Co Ltd 密閉型ロータリ圧縮機の冷却装置
JPH07260262A (ja) * 1994-03-17 1995-10-13 Sanyo Electric Co Ltd 冷凍装置
JP2003097477A (ja) * 2001-09-21 2003-04-03 Sanyo Electric Co Ltd 密閉型回転圧縮機
KR20080089174A (ko) * 2007-03-30 2008-10-06 가부시키가이샤 후지쯔 제네랄 인젝션 대응 2단 압축 로터리 압축기 및 히트 펌프 시스템

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0650276A (ja) * 1992-07-28 1994-02-22 Daikin Ind Ltd ロータリー圧縮機
JPH07127575A (ja) * 1993-10-29 1995-05-16 Sanyo Electric Co Ltd 密閉型ロータリ圧縮機の冷却装置
JPH07260262A (ja) * 1994-03-17 1995-10-13 Sanyo Electric Co Ltd 冷凍装置
JP2003097477A (ja) * 2001-09-21 2003-04-03 Sanyo Electric Co Ltd 密閉型回転圧縮機
KR20080089174A (ko) * 2007-03-30 2008-10-06 가부시키가이샤 후지쯔 제네랄 인젝션 대응 2단 압축 로터리 압축기 및 히트 펌프 시스템

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015135090A (ja) * 2014-01-17 2015-07-27 株式会社富士通ゼネラル ロータリ圧縮機
CN105065273A (zh) * 2015-08-24 2015-11-18 广东美芝制冷设备有限公司 旋转式压缩机和具有其的冷冻循环装置
US10465682B2 (en) 2015-08-24 2019-11-05 Guangdong Meizhi Compressor Co., Ltd. Rotary compressor and refrigeration cycle device having same
DE102019102213A1 (de) 2019-01-29 2020-07-30 Closurelogic Gmbh Flaschenkappe
WO2020156616A1 (de) 2019-01-29 2020-08-06 Closurelogic Gmbh Flaschenkappe

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KR101891616B1 (ko) 2018-08-24

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