WO2021240605A1 - Compresseur à vis unique à deux étages et dispositif de réfrigération et de climatisation - Google Patents

Compresseur à vis unique à deux étages et dispositif de réfrigération et de climatisation Download PDF

Info

Publication number
WO2021240605A1
WO2021240605A1 PCT/JP2020/020556 JP2020020556W WO2021240605A1 WO 2021240605 A1 WO2021240605 A1 WO 2021240605A1 JP 2020020556 W JP2020020556 W JP 2020020556W WO 2021240605 A1 WO2021240605 A1 WO 2021240605A1
Authority
WO
WIPO (PCT)
Prior art keywords
compression chamber
compression
rotor
refrigerant
injection port
Prior art date
Application number
PCT/JP2020/020556
Other languages
English (en)
Japanese (ja)
Inventor
慎 栗田
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2020/020556 priority Critical patent/WO2021240605A1/fr
Publication of WO2021240605A1 publication Critical patent/WO2021240605A1/fr

Links

Images

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
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing

Definitions

  • the present disclosure relates to a two-stage single-screw compressor for refrigerating and air-conditioning, and a refrigerating and air-conditioning device equipped with a two-stage single-screw compressor.
  • a single screw compressor having a configuration in which a screw rotor and a gate rotor are housed in a casing is known.
  • the low-temperature low-pressure gas refrigerant sucked into the single-screw compressor is compressed in the compression chamber, becomes a high-temperature and high-pressure gas refrigerant, and is discharged from the single-screw compressor. If the compression process of the refrigerant in the compression chamber is continued during the operation of the single screw compressor, the temperature of the refrigerant in the compression chamber rises. Therefore, the temperature of the inner peripheral surface of the screw rotor and the casing also rises, and the screw rotor and the casing thermally expand.
  • a two-stage single screw compressor is known as a type of single screw compressor.
  • the two-stage single-screw compressor compresses the refrigerant to a high compression ratio with a multi-stage compression unit.
  • the first-stage compression section compresses the refrigerant from the suction pressure to the intermediate pressure
  • the second-stage compression section compresses the refrigerant from the intermediate pressure to the discharge pressure.
  • a twin gate rotor method is a method in which two gate rotors are fitted to a screw rotor.
  • twin gate rotor type compression unit two gate rotors are arranged at symmetrical positions across the rotation axis of the screw rotor, and two compression chambers are formed at symmetrical positions across the rotation axis of the screw rotor.
  • the monogate rotor method is a method in which one gate rotor is fitted to a screw rotor.
  • one compression chamber is formed according to the position of the gate rotor.
  • the first-stage screw rotor and the second-stage screw rotor are provided in series with the rotating shaft.
  • the internal pressure differs between the side where the gate rotor is provided across the rotating shaft and the side where the gate rotor is not provided.
  • the space on the side where the gate rotor is not provided is the atmosphere of the intermediate pressure refrigerant gas discharged from the compression section of the first stage, and the internal pressure of the space on the side where the gate rotor is provided forms a compression chamber. This is because the discharge pressure has risen. Therefore, in the second stage compression section, the differential pressure between the intermediate pressure and the discharge pressure acts on the rotary shaft, and the gas load due to the differential pressure may cause the rotary shaft to bend to the side where the gate rotor is not provided. ..
  • the deformation of the rotating shaft in the second stage compression portion may become more remarkable. Since the screw rotor of the first-stage compression part and the screw rotor of the second-stage compression part are provided in series with the rotation shaft, the deformation of the rotation shaft that occurs in the second-stage compression part is the compression of the first stage. It also affects the department. That is, when the rotation axis is deformed, the internal spaces of the two compression chambers of the first-stage compression section become non-uniform, and the transition of the internal pressures of the two compression chambers becomes different. There is a possibility that a load will be applied in the radial direction.
  • Patent Document 1 when the configuration of the compressor described in Patent Document 1 is adopted for the first-stage compression unit, the injection mechanism of Patent Document 1 is not configured to execute the injection process in consideration of the deformation of the rotating shaft. Deformation of the rotating shaft cannot be suppressed.
  • the present disclosure has been made against the background of the above-mentioned problems, and is a two-stage single-screw compressor with improved reliability by suppressing deformation of the rotating shaft and reducing the load on the bearing of the rotating shaft. And a refrigerating air conditioner equipped with a two-stage single screw compressor.
  • the two-stage single screw compressor includes a first compression unit that compresses the refrigerant, a second compression unit that further compresses the refrigerant compressed by the first compression unit, the first compression unit, and the first compression unit.
  • a two-stage single-screw compressor having the first compression portion, the first screw rotor attached to the rotating shaft and having a spiral groove formed therein, so as to be fitted with the spiral groove of the first screw rotor.
  • a first compression chamber is formed by the spiral groove of the first gate rotor and the first screw rotor, and the spiral groove of the second gate rotor and the first screw rotor is arranged so as to face each other with a shaft interposed therebetween.
  • a second compression chamber is formed by the above, and at least one first injection port that opens into the first compression chamber and injects the refrigerant, and at least one that opens into the second compression chamber and injects the refrigerant.
  • a second injection port is formed, and the second compression portion is provided so as to be fitted to the spiral groove of the second screw rotor and the second screw rotor which is attached to the rotating shaft and has a spiral groove formed therein.
  • a third compression chamber is formed by the third gate rotor and the spiral groove of the second screw rotor, and the second compression chamber and the third compression chamber are formed. It is formed inside the casing on the same side with respect to the rotation axis, and the total opening area of the first injection port is larger than the total opening area of the second injection port.
  • the total opening area of the second injection port of the second compression chamber formed on the same side as the side where the third compression chamber of the second compression portion is formed with respect to the rotation shaft is the rotation shaft.
  • it is larger than the total opening area of the first injection port of the first compression chamber formed on the side different from the side where the third compression chamber is formed. That is, the amount of the refrigerant injected into the first compression chamber is larger than the amount of the refrigerant injected into the second compression chamber. Therefore, it is possible to cancel the load on the rotating shaft from the radial direction from the second compression chamber to the first compression chamber, which is generated in the first compression portion due to the deformation of the rotating shaft generated in the second compression portion. can. As a result, deformation of the rotating shaft is suppressed, the load on the bearing of the rotating shaft is reduced, the life of the bearing can be shortened, and the reliability of the two-stage single screw compressor can be improved. .
  • FIG. 1 is a refrigerant circuit diagram of a refrigerating and air-conditioning apparatus provided with a single-screw compressor according to an embodiment of the present disclosure.
  • a refrigerant circuit 200 is formed in the refrigerating and air-conditioning device 100.
  • the refrigerant circuit 200 has a configuration in which a single screw compressor 10, an evaporator 201, a liquid reservoir (not shown), an expansion valve 202, a condenser 203, and the like are connected by a refrigerant pipe to form a closed loop.
  • the single screw compressor 10 compresses and discharges the refrigerant, and is a two-stage single screw compressor as described later.
  • the refrigerant discharged from the single screw compressor 10 is condensed by the condenser 203, depressurized by the expansion valve 202, and evaporated by the evaporator 201.
  • R410 refrigerant which is a high-pressure refrigerant, is used.
  • An injection tube 204 is provided between the expansion valve 202 and the condenser 203.
  • the injection pipe 204 branches from the pipe connecting the expansion valve 202 and the condenser 203, and is connected to the single screw compressor 10.
  • the liquid refrigerant is injected into the single screw compressor 10 via the injection pipe 204.
  • FIG. 2 is a schematic cross-sectional view of the single screw compressor according to the embodiment of the present disclosure.
  • the single screw compressor 10 of the first embodiment has a cylindrical casing 11.
  • the single screw compressor 10 has a compression unit 20 housed in a casing 11, an electric motor 50, and a rotating shaft 60.
  • the rotating shaft 60 is provided on the central shaft portion of the casing 11, and one end thereof is supported by a bearing (not shown).
  • a motor rotor 51 of the motor 50 is provided at one end of the rotating shaft 60.
  • the motor rotor 51 is rotated by the drive of the electric motor 50, and the rotation shaft 60 is rotated by the rotation of the motor rotor 51.
  • the electric motor 50 can have a variable speed by using an inverter (not shown).
  • the compression unit 20 is divided into a first compression unit 20A and a second compression unit 20B inside the casing 11. That is, the single screw compressor 10 is a two-stage single screw compressor.
  • the rotating shaft 60 inserts the first compression unit 20A and the second compression unit 20B.
  • the first compression unit 20A is the first stage in the two-stage single screw compressor, and is on the lower stage side.
  • the second compression unit 20B is the second stage in the two-stage single screw compressor, and is on the higher stage side.
  • the first compression unit 20A is configured by a twin gate rotor system
  • the second compression unit 20B is configured by a monogate rotor system.
  • FIG. 3 is a cross-sectional view of the first compression portion of the single screw compressor according to the embodiment of the present disclosure.
  • FIG. 3 cuts the single screw compressor 10 at the position of lines AA of FIG. 2 and is shown from the left side of FIG.
  • the first compression unit 20A will be described with reference to FIGS. 2 and 3.
  • the first compression unit 20A includes a first screw rotor 30, a first gate rotor 31, and a second gate rotor 32.
  • the first screw rotor 30, the first gate rotor 31, and the second gate rotor 32 are provided inside a cylindrical cylinder 205 (see FIG. 5) provided in the casing 11.
  • the first gate rotor 31 and the second gate rotor 32 are fitted to the first screw rotor 30.
  • the first screw rotor 30 is attached to the rotating shaft 60.
  • a screw groove 30A which is a plurality of spiral grooves, is formed on the outer peripheral surface of the first screw rotor 30.
  • the first gate rotor 31 and the screw groove 30A mesh with each other, and the first compression chamber 33 is formed in the space between the inner wall of the casing 11.
  • the second gate rotor 32 and the screw groove 30A mesh with each other, and the second compression chamber 34 is formed in the space between the inner wall of the casing 11.
  • the first screw rotor 30 rotates with the rotation of the rotary shaft 60, the volume of the first compression chamber 33 is reduced, the working refrigerant is compressed, and the first screw rotor 30 rotates with the rotation of the rotary shaft 60. 2
  • the volume of the compression chamber 34 is reduced, and the working refrigerant is compressed.
  • the first slide valve 35 adjusts the internal volume ratio of the first compression chamber 33.
  • the second slide valve 36 adjusts the internal volume ratio of the second compression chamber 34.
  • the first slide valve 35 and the second slide valve 36 are configured to be driven along the rotation shaft 60 by a slide mechanism (not shown). In FIG. 2, the first slide valve 35 and the second slide valve 36 are omitted.
  • FIG. 4 is a cross-sectional view of a second compression portion of the single screw compressor according to the embodiment of the present disclosure.
  • FIG. 4 cuts the single screw compressor 10 at the position of line BB in FIG. 2 and is shown from the left side of FIG.
  • the second compression unit 20B will be described with reference to FIGS. 2 and 4.
  • the second compression unit 20B has a second screw rotor 40 and a third gate rotor 41.
  • a third gate rotor 41 is fitted to the second screw rotor 40.
  • a screw groove 40A which is a plurality of spiral grooves, is formed on the outer peripheral surface of the second screw rotor 40.
  • the third gate rotor 41 and the screw groove 40A mesh with each other, and the third compression chamber 43 is formed in the space between the inner wall of the casing 11.
  • the second screw rotor 40 rotates, the volume of the third compression chamber 43 is reduced, and the working refrigerant is compressed.
  • the third slide valve 44 adjusts the internal volume ratio of the third compression chamber 43.
  • the third slide valve 44 is configured to be driven along the rotation shaft 60 by a slide mechanism (not shown). In FIG. 2, the third slide valve 44 is omitted.
  • the first gate rotor 31 is arranged below the rotating shaft 60
  • the second gate rotor 32 is arranged above the rotating shaft 60
  • the third gate rotor 41 is arranged above the rotating shaft 60. It is located above 60. That is, inside the casing 11, the third gate rotor 41 is arranged on the side where the second gate rotor 32 is arranged with respect to the rotating shaft 60.
  • the third compression chamber 43 is formed on the same side as the side on which the second compression chamber 34 is formed with respect to the rotating shaft 60.
  • the first compression chamber 33 and the second compression chamber 34 are formed so as to face each other at positions symmetrical with each other by 180 degrees with the rotation axis 60 interposed therebetween. Therefore, since the first compression chamber 33 and the second compression chamber 34 face each other at a position of 180 degrees with respect to the rotation shaft 60, there is an advantage that the gas load of the refrigerant acting in the radial direction with respect to the rotation shaft 60 can be reduced. be.
  • FIG. 5 is a diagram conceptually showing the injection port of the single screw compressor according to the embodiment of the present disclosure.
  • FIG. 5A shows a second injection port 38 that opens into the second compression chamber 34.
  • FIG. 5B shows a first injection port 37 that opens into the first compression chamber 33.
  • the injection pipe 204 shown in FIG. 1 is connected to the side surface of the casing 11.
  • a second refrigerant passage 207 communicating the injection pipe 204 and the second compression chamber 34 is formed in the cylinder 205.
  • the end of the second refrigerant passage 207 is the second injection port 38.
  • a first refrigerant passage 206 communicating the injection pipe 204 and the first compression chamber 33 is formed in the cylinder 205 described above.
  • the end of the first refrigerant passage 206 is the first injection port 37.
  • the first injection port 37 is formed so that the cross-sectional shape cut along the plane orthogonal to the flow direction of the refrigerant in the first refrigerant passage 206 is circular. Further, the second injection port 38 is formed so that the cross-sectional shape cut along the plane orthogonal to the flow direction of the refrigerant in the second refrigerant passage 207 is circular. Then, as shown in FIGS. 5A and 5B, the diameter ⁇ D1 of the second injection port 38 is smaller than the diameter ⁇ D2 of the first injection port 37.
  • the electric motor 50 for driving the single screw compressor 10 is activated by receiving a signal from an inverter (not shown).
  • the drive of the single screw compressor 10 is started by starting the electric motor 50, the operating refrigerant circulating in the refrigerant circuit 200 is sucked into the first compression chamber 33 and the second compression chamber 34 of the first compression unit 20A.
  • the suction of the operating refrigerant into the first compression chamber 33 and the second compression chamber 34 is completed at the same timing, and the refrigerant having substantially the same mass is sucked into the first compression chamber 33 and the second compression chamber 34.
  • the volumes of the first compression chamber 33 and the second compression chamber 34 are reduced by the rotation of the first screw rotor 30 due to the rotation of the rotating shaft 60, and the internal pressure is increased.
  • the timing at which the operating refrigerant is discharged from the first compression chamber 33 is adjusted by changing the axial position of the first screw rotor 30 of the first slide valve 35.
  • the timing at which the operating refrigerant is discharged from the second compression chamber 34 is adjusted by changing the axial position of the first screw rotor 30 of the second slide valve 36.
  • the liquid refrigerant guided from the injection pipe 204 passes through the first injection port 37 and the second injection port 38, and the first compression chamber 33 and the second are used. It is injected into the compression chamber 34.
  • the diameter of the second injection port 38 opened in the second compression chamber 34 is larger than the diameter of the first injection port 37 opened in the first compression chamber 33.
  • the amount of the liquid refrigerant injected into the second compression chamber 34 is larger than the amount of the refrigerant injected into the first compression chamber 33. That is, when the liquid refrigerant is injected, the second compression chamber 34 acts to allow more liquid refrigerant to flow in than the first compression chamber 33.
  • the operating refrigerant discharged from the first compression chamber 33 and the second compression chamber 34 is sucked into the third compression chamber 43 of the second compression unit 20B.
  • the operating refrigerant sucked into the third compression chamber 43 is further compressed in the third compression chamber 43, discharged to the refrigerant circuit 200 shown in FIG. 1, and circulates in the refrigerant circuit 200.
  • FIG. 6 is a diagram showing pressure transitions between the first compression chamber and the second compression chamber of the first compression portion of the single screw compressor of the comparative example.
  • FIG. 7 is a diagram showing pressure transitions between the first compression chamber and the second compression chamber of the first compression portion of the single screw compressor according to the embodiment of the present disclosure.
  • the horizontal axis is the volume of the compression chamber, and the vertical axis is the pressure in the compression chamber.
  • the second compression section 20B of the single screw compressor 10 is a monogate rotor system, and an intermediate pressure operating refrigerant is sucked into the third compression chamber 43 from the first compression section 20A.
  • the lower side of the rotating shaft 60 of the second compression unit 20B is a refrigerant atmosphere with an intermediate pressure. Therefore, a pressure difference is generated between the upper side and the lower side of the rotary shaft 60, and the load of the gas refrigerant due to this differential pressure, that is, the gas load is applied in the radial direction from the upper side of the rotary shaft 60. As a result, the rotating shaft 60 bends downward and deforms.
  • a refrigerant having a high saturation pressure for example, R410A
  • the rotating shaft 60 is also deformed in the first compression portion 20A on the lower stage side due to the gas load acting on the rotating shaft 60 from the radial direction in the second compression portion 20B on the higher stage side.
  • first compression unit 20A two first compression chambers 33 and a second compression chamber 34 are formed in the vertical direction with the rotation shaft 60 interposed therebetween.
  • the gap between the first screw rotor 30 and the casing 11 in the first compression chamber 33 above the rotary shaft 60 is expanded, and the second compression chamber below the rotary shaft 60 is expanded.
  • the gap between the first screw rotor 30 and the casing 11 in 34 is reduced. Since the internal leakage of the refrigerant increases in the first compression chamber 33 in which the gap is expanded as in the second compression chamber 34 in which the gap is reduced, the internal pressure of the first compression chamber 33 is higher than the internal pressure of the second compression chamber 34.
  • the inflow amount of the liquid refrigerant flowing into the first compression chamber 33 and the second compression chamber 34 is the same.
  • the internal pressure of the second compression chamber 34 in which the gap is expanded is higher than the internal pressure of the first compression chamber 33 in which the gap is reduced. It will change with pressure. That is, as shown in FIG. 5, the acupressure diagram of the second compression chamber 34 in which the above-mentioned gap is expanded has a shape bulging more than the acupressure diagram of the first compression chamber 33 in which the above-mentioned gap is reduced. Will be shown.
  • the gas load applied in the radial direction from above to the rotary shaft 60 is maintained, the rotary shaft 60 remains deformed downward, and the bearing of the rotary shaft 60 may deteriorate.
  • the diameter of the first injection port 37 is set to be larger than the diameter of the second injection port 38. Therefore, according to the present embodiment, the inflow amount of the liquid refrigerant flowing into the first compression chamber 33 below the rotary shaft 60 is the inflow amount of the liquid refrigerant flowing into the second compression chamber 34 above the rotary shaft 60. Can be larger than. Therefore, since the density in the first compression chamber 33 rises as compared with the second compression chamber 34 and the pressure rises, the transition of the internal pressure in the first compression chamber 33 is brought closer to the transition of the internal pressure in the second compression chamber 34. Can be done. That is, as shown in FIG.
  • the acupressure diagram of the first compression chamber 33 can be brought closer to the acupressure diagram of the second compression chamber 34.
  • the gas load on the rotating shaft 60 from the radial direction from the second compression chamber 34 to the first compression chamber 33 is cancelled. Therefore, the downward deformation of the rotating shaft 60 is suppressed, the load on the bearing is reduced, and the life of the bearing can be shortened. That is, according to the present embodiment, the reliability of the two-stage single screw compressor can be improved.
  • one first injection port 37 is formed in the first compression chamber 33, and one second injection port 38 is formed in the second compression chamber 34, but the number of injection ports is limited to this. is not it.
  • a plurality of injection ports may be formed in both or one of the first compression chamber 33 and the second compression chamber 34.
  • the total opening area of the injection ports formed in the first compression chamber 33 that is, the total opening area is set to be larger than the total opening area of the injection ports formed in the second compression chamber 34.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Un compresseur à vis unique à deux étages comprend : une seconde unité de compression pour comprimer davantage un fluide frigorigène comprimé par une première unité de compression ; et un arbre rotatif inséré dans la première unité de compression et la seconde unité de compression, et pourvu d'un premier rotor à vis et d'un second rotor à vis. Dans la première unité de compression, une première chambre de compression est formée par une structure hélicoïdale d'un premier rotor femelle et du premier rotor à vis, et une deuxième chambre de compression est formée par une structure hélicoïdale d'un deuxième rotor femelle et du premier rotor à vis. Le premier rotor femelle et le deuxième rotor femelle sont disposés l'un en face de l'autre, l'arbre rotatif se trouvant entre les deux. Un premier orifice d'injection et un second orifice d'injection, à travers lesquels un fluide frigorigène est injecté, sont formés respectivement dans la première chambre de compression et la deuxième chambre de compression. Dans la seconde unité de compression, une troisième chambre de compression est formée par une structure hélicoïdale d'un troisième rotor femelle et du second rotor à vis. La deuxième chambre de compression et la troisième chambre de compression sont formées sur le même côté par rapport à l'arbre rotatif. La zone d'ouverture totale du premier orifice d'injection est plus grande que la zone d'ouverture totale du second orifice d'injection.
PCT/JP2020/020556 2020-05-25 2020-05-25 Compresseur à vis unique à deux étages et dispositif de réfrigération et de climatisation WO2021240605A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2020/020556 WO2021240605A1 (fr) 2020-05-25 2020-05-25 Compresseur à vis unique à deux étages et dispositif de réfrigération et de climatisation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2020/020556 WO2021240605A1 (fr) 2020-05-25 2020-05-25 Compresseur à vis unique à deux étages et dispositif de réfrigération et de climatisation

Publications (1)

Publication Number Publication Date
WO2021240605A1 true WO2021240605A1 (fr) 2021-12-02

Family

ID=78723232

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2020/020556 WO2021240605A1 (fr) 2020-05-25 2020-05-25 Compresseur à vis unique à deux étages et dispositif de réfrigération et de climatisation

Country Status (1)

Country Link
WO (1) WO2021240605A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010255600A (ja) * 2009-04-28 2010-11-11 Mitsubishi Electric Corp 二段スクリュー圧縮機
JP2011190777A (ja) * 2010-03-16 2011-09-29 Mitsubishi Electric Corp シングルスクリュー圧縮機及びこのシングルスクリュー圧縮機を搭載した冷凍サイクル装置
WO2016189648A1 (fr) * 2015-05-26 2016-12-01 三菱電機株式会社 Compresseur à vis et dispositif à cycle de réfrigération comprenant un compresseur à vis

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010255600A (ja) * 2009-04-28 2010-11-11 Mitsubishi Electric Corp 二段スクリュー圧縮機
JP2011190777A (ja) * 2010-03-16 2011-09-29 Mitsubishi Electric Corp シングルスクリュー圧縮機及びこのシングルスクリュー圧縮機を搭載した冷凍サイクル装置
WO2016189648A1 (fr) * 2015-05-26 2016-12-01 三菱電機株式会社 Compresseur à vis et dispositif à cycle de réfrigération comprenant un compresseur à vis

Similar Documents

Publication Publication Date Title
US6273691B1 (en) Scroll gas compressor having asymmetric bypass holes
US7563080B2 (en) Rotary compressor
EP2634432B1 (fr) Compresseur à vis
US20090007590A1 (en) Refrigeration System
US11732710B2 (en) Screw compressor, and refrigeration device
KR100725893B1 (ko) 스크롤형 유체기계
JPWO2011148453A1 (ja) 二段回転式圧縮機及びヒートポンプ装置
US11841020B2 (en) Variable volume ratio screw compressor
US11136982B2 (en) Screw compressor
JP5338314B2 (ja) 圧縮機および冷凍装置
US7556485B2 (en) Rotary compressor with reduced refrigeration gas leaks during compression while preventing seizure
JP2012127565A (ja) 冷凍サイクル装置
WO2021240605A1 (fr) Compresseur à vis unique à deux étages et dispositif de réfrigération et de climatisation
KR102126815B1 (ko) 냉동 장치
KR101953616B1 (ko) 열 펌프 내부에 사용하기 위한 냉매 스크롤 압축기
JPH07180917A (ja) スクリュ式冷凍機
US12012963B2 (en) Scroll compressor with economizer injection
JP6259309B2 (ja) スクリュー流体機械及び冷凍サイクル装置
JP5727348B2 (ja) 気体圧縮機
CN107642487B (zh) 用于涡旋压缩机的扇形台阶
US7607900B2 (en) Multi-cylinder reciprocating compressor
CN111868384B (zh) 多级压缩机
WO2023182457A1 (fr) Compresseur à vis et congélateur
JP2015028313A (ja) アキシャルベーン型圧縮機
CN213066668U (zh) 供热、通风、空气调节和制冷系统及用于该系统的压缩机

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 20937737

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 20937737

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP