EP1396640B1 - Compresseur à vis - Google Patents

Compresseur à vis Download PDF

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Publication number
EP1396640B1
EP1396640B1 EP03018778A EP03018778A EP1396640B1 EP 1396640 B1 EP1396640 B1 EP 1396640B1 EP 03018778 A EP03018778 A EP 03018778A EP 03018778 A EP03018778 A EP 03018778A EP 1396640 B1 EP1396640 B1 EP 1396640B1
Authority
EP
European Patent Office
Prior art keywords
inlet
compressor according
channel
screw compressor
screw
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03018778A
Other languages
German (de)
English (en)
Other versions
EP1396640A3 (fr
EP1396640A2 (fr
Inventor
Stephan Rölke
Klaus Hossner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority to SI200330459T priority Critical patent/SI1396640T1/sl
Publication of EP1396640A2 publication Critical patent/EP1396640A2/fr
Publication of EP1396640A3 publication Critical patent/EP1396640A3/fr
Application granted granted Critical
Publication of EP1396640B1 publication Critical patent/EP1396640B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0035—Equalization of pressure pulses
    • 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 invention relates to a screw compressor comprising two screw rotors arranged in screw rotor bores in a compressor housing, which compress a refrigerant entering at a refrigerant inlet and let it out at a refrigerant outlet, and an inlet arranged in the compressor casing for the inlet coming from a subcooling circuit via a line system to the inlet Refrigerant, wherein the inlet is arranged such that it opens into compaction spaces enclosed by the screw and screw rotor bores.
  • the invention is therefore based on the object to provide a screw compressor in which the occurring at the inlet pressure oscillations or pulsations propagate to the least possible extent on the piping system of the subcooling outside the compressor housing.
  • the damper channel is arranged in the compressor housing.
  • the compressor housing from a plurality of housing sections and to provide the damper channel in one housing section, while the screw rotor bores are arranged in another housing section.
  • the damper channel is formed in a housing section receiving the screw rotor bores, which thus forms an integral unit which additionally reduces a transmission of the pressure oscillations.
  • the damper channel can be formed as a side arm of the line system and therefore can not be constantly flowed through.
  • an inlet passage extending through the compressor housing is provided as part of the conduit system leading from an external connection to the compressor housing connected to the piping system of the subcooling circuit to the inlet, the damper passage in is arranged in the inlet channel.
  • the realization of the damper channel in the compressor housing can also be done in a variety of ways.
  • a particularly advantageous embodiment provides that the damper channel is arranged in a usable part in the compressor housing.
  • This part could include both the inlet channel and the damper channel. It is particularly favorable, however, if the insertable into the compressor housing part can be inserted into the inlet channel in the compressor housing.
  • the insertable part comprises a damper tube and a holder, with which the damper tube is fixable in the compressor housing.
  • a particularly convenient fixation of the damper tube and the holder in the inlet channel provides for a positive fixation of the holder in the inlet channel.
  • a particularly favorable embodiment provides that the compressor housing comprises a control slide, and that the inlet is arranged in the control slide and is displaceable therewith.
  • connection between the inlet to the inlet channel a variety of solutions are conceivable.
  • a structurally advantageous solution provides that the inlet is connected in the control slide over a variable-length portion of the inlet channel with the outer terminal.
  • variable-length portion of the inlet channel is formed telescopically.
  • variable-length portion of the inlet channel provides that the variable-length portion of the inlet channel is formed by an insertable into a receiving channel connecting pipe.
  • the damper channel has a length which corresponds to approximately one quarter of the wavelength of the pressure swing to be damped or an odd multiple of the same.
  • the wavelength of the pressure oscillations to be damped can be determined from a fundamental frequency of the pressure oscillations, whereby the fundamental frequency of the pressure oscillations results from the product of the rotational speed of the screw rotors and the number of screw combs of the same.
  • the damper channel opens with a second orifice opening in a lying between this and the inlet second volume, so that there is a so-called open end at the second orifice.
  • the first volume lying between the first orifice and the outer connection is located in the compressor housing.
  • the first volume preferably lies in an inlet channel section of the inlet channel guided through the compressor housing.
  • the second volume also extends in the intake passage section receiving the damper passage.
  • an expansion volume is assigned in connection for the subcooling circuit.
  • This expansion volume may also be provided in the inlet channel and in the compressor housing.
  • a particularly advantageous solution provides that the line system is connected to an oil drain, which ensures that oil, especially near the damper channel collecting oil is removed from the line system.
  • a particularly favorable solution provides that the oil discharge empties into the first volume.
  • the oil drainage is possible, in particular in the region of the first volume to avoid oil accumulation and thus to maintain the effect of the damper channel.
  • a first embodiment of a screw compressor according to the invention shown in Fig. 1 comprises a designated as a whole with / 10 compressor housing, on which a suction port 12 and a pressure port 14 are provided, wherein sucked at the suction port 12 refrigerant and at the pressure port 14 compressed refrigerant is discharged.
  • the compressed refrigerant discharged at the pressure port 14 is first supplied to a condenser 16 and passes from the condenser 16 into a buffer 18 for liquid refrigerant. After the buffer 18, the liquefied refrigerant flows through a check valve 20 and a branch 22, from which a cooling circuit 24 on to an expansion valve 26, and an evaporator 28 leads, and then back from the evaporator 28 to the suction port 12th
  • a subcooling circuit 30 is provided to the cooling circuit 24, which branches off from the cooling circuit 24 at the branch 22 and an expansion valve 32, through which a portion of the mass flow of the first compressed by the screw compressor refrigerant from the cooling circuit 24 expands and a subcooler 34 is supplied , the subcooler 34 flows through and is then fed to a provided on the compressor housing 10 port 40 for the subcooling circuit 30.
  • the refrigerant circulating in the cooling circuit 24 also flows through the subcooler 34 between the branch 22 and the expansion valve 26 and undergoes further subcooling in the subcooler 34 before its expansion in the expansion valve 26, which results in the cooling capacity with the additional subcooling circuit 30 in the cooling circuit 24 and improves the coefficient of performance, with only a slight increase in the power requirement of the screw compressor.
  • a first embodiment of a screw compressor according to the invention comprises, as shown in detail in FIGS. 2 and 3, in the compressor housing 10 provided fferenarearbohronne 48, in which intermeshing screw rotors 50 are rotatably arranged, wherein the fferenoccupationrbohronne 48 from a suction-side refrigerant inlet 52 to a pressure-side Refrigerant outlet 54 extend and the intermeshing screw rotor 50 suck the refrigerant in the region of the refrigerant inlet 52, in the course of the way to the refrigerant outlet 54 compress and deliver as a compressed refrigerant at the refrigerant outlet 54.
  • a recess 56 is provided in the compressor housing 10, in which a control slide 58 is movable in a direction 60 which is parallel to a rotation axis 62 of the screw rotor 50.
  • the control slide 58 forms, with a slider wall 64 facing the screw rotors 50, a wall side of the screw rotor bores 48 which, by being displaceable in the direction 60, makes it possible to control the compression achievable by the screw rotors 50.
  • the entire slide wall 64 extends along the screw rotor 50, and creates the possibility that the screw rotor 50th contribute to the compression of the refrigerant over its entire length in the direction of its axis of rotation 62, while in the position shown in Fig.
  • the control slide 58 is actuatable by means of an adjusting device 70, which can be configured, for example, as described in the European patent application 1 072 796.
  • the adjusting device 70 may also be designed differently and, for example, be controlled externally continuously.
  • an inlet 80 is provided for to be sucked from the subcooling circuit 30 via a line system 78 refrigerant in the form of a slide wall 64 passing through hole, wherein an opening into the compression chamber 72 inlet opening 82 is always so that above this always an opposite to the refrigerant inlet 52 and the refrigerant outlet 54 closed compression chamber 72 is or the inlet port 82 is closed by a screw comb 84 x .
  • the inlet port 82 is such that it opens into the first of the screw combs 84 opposite the refrigerant inlet 82 closed compression chamber 72.
  • the inlet 80 is in communication with a in the direction 60 in the control slide 58 extending central receiving channel 90, which has on one side an opening 92, through which projects into this held on the compressor housing 10 connecting pipe 94, wherein between the central receiving channel 90 and the connecting tube 94, a seal 96 is provided and the Connecting tube 94 has a length such that it protrudes sealed in each position of the control slide 58 by the seal 96 in the central receiving channel 90 without hindering the displacement of the control slide 58 between the intended positions for control.
  • the connecting tube 94 is connected to a housing channel 98 running in the compressor housing 10, which is led to the connection 40 on the compressor housing 10.
  • a portion of the conduit system 78 forming inlet channel 100 between the port 40 and the inlet 80 in the compressor housing 10 is thus formed by the housing channel 98, extending in the connecting pipe 94 and the central channel 102 receiving channel 90 in the control slide 58, from which the inlet 80 branches off , wherein the connecting tube 94 and the receiving channel 90 form a variable-length portion 104 of the inlet channel 100.
  • inlet channel 100 In order to dampen such pressure oscillations or pulsations, is in the inlet channel 100, preferably in a directly to the outer terminal 40, formed by a connecting flange 112 and a pipe connection 114, subsequent inlet channel section 116 of the inlet channel 100, in particular of the housing channel 98, a damper channel 120 is provided, which extends in a damper tube 122 which is inserted into the inlet channel section 116.
  • the damper channel 120 in the damper tube 122 extends from a first orifice 124 to a second orifice 126 having a preferably uniform cross-section, wherein the orifices 124 and 126 have cross-sectional areas which are smaller than the cross-sectional areas of the inlet duct 116 surrounding the damper tube 122 that at both mouth openings 124 and 126, starting from the damper channel 120, there is a jump in the cross-section to a larger cross-sectional area by a factor of at least 1.5.
  • the damper tube 122 has a smaller cross-section than the inlet channel section 116 and is held in the inlet channel section 116 with a retainer 130.
  • the holder 130 is formed as a retaining ring, which is provided with an external thread 127 which engages in an internal thread 128 of the inlet channel section 116, so that a positive connection between the holder 130 and the compressor housing 10 can be produced.
  • the holder 130 and the damper tube 122 divide the inlet channel section 116 into two volumes lying outside of the damper tube 122, namely a first volume 132 and a second volume 134.
  • the first volume 132 is located between the port 40 and the first orifice 124, wherein the first volume may extend around the damper tube 122 as far as the holder 130.
  • the second volume 134 is located between the second orifice 126 and the inlet 80, wherein the second volume 134 may still extend around the damper tube 122 up to the holder 130.
  • the length of the damper channel 120 in the damper tube 122 is now dimensioned so that it corresponds to the order of a quarter or an integer multiple of a quarter, the wavelength of forming a fundamental frequency pressure oscillation or pulsation in the refrigerant, so that in particular by the combination of the damper channel 120 with the first volume 132 and the second volume 134, the pressure oscillations or pulsations are attenuated.
  • the damper channel 120 is effective regardless of whether he subcooling circuit 30 is effective or not.
  • the inlet channel 100 is provided with an oil discharge 136, as shown in FIG 4, in the inlet channel 100 in the region of the inlet channel section 116, preferably in the first volume 132 thereof, and on the other hand with the suction port 12, preferably with the suction end of the cooling circuit 24, connected is.
  • the oil discharge 136 also includes a valve 138, which can be actuated at intervals, for example when the subcooling circuit 30 is inactive, in order to discharge collecting oil in the inlet channel 100, in particular in the first volume 132 thereof, at these intervals.
  • the oil discharge 136 does not necessarily work even with effective subcooling circuit 30, since with effective subcooling circuit 30 usually due to the refrigerant flowing through the inlet channel 100 there collecting oil is supplied to the compression chambers 72.
  • an expansion volume 142 is provided, which creates the possibility, still from the compressor housing 10 out in the section 140 of the piping system propagating pressure oscillations or pulsations to further attenuate and thus further reduce their impact on the piping system.
  • the second embodiment is formed in the same manner as the first embodiment, so that reference is made to the comments on this full content.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Supercharger (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Compressor (AREA)

Claims (25)

  1. Compresseur à vis comportant
    deux rotors à vis (50) disposés dans un boîtier de compresseur (10) dans des alésages de rotor à vis (48), lesquels rotors compriment un fluide frigorigène entrant par un orifice d'admission de fluide frigorigène (52) et le laissent sortir par un orifice d'évacuation de fluide frigorigène (54), et un orifice d'admission (80) prévu dans le boîtier de compresseur (10) pour le fluide frigorigène provenant d'un circuit de surrefroidissement (30), guidé dans le système de conduite (78) en direction de l'orifice d'admission (80), l'orifice d'admission (80) étant disposé de telle sorte qu'il débouche dans les espaces de compression (72) entourés par les rotors à vis (50) et les alésages de rotor à vis (48),
    caractérisé en ce qu'un canal amortisseur (120) réduisant les vibrations de pression ou les pulsations associé au système de conduite (78) est monté en amont de l'orifice d'admission, canal dans lequel se situe le fluide frigorigène provenant du circuit de surrefroidissement (30).
  2. Compresseur à vis selon la revendication 1, caractérisé en ce que le canal amortisseur (120) est disposé dans le boîtier de compresseur (10).
  3. Compresseur à vis selon la revendication 2, caractérisé en ce que le canal amortisseur (120) est moulé dans une section de boîtier recevant les alésages de rotor à vis (48).
  4. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il est prévu un canal d'admission (100) s'étendant à travers le boîtier de compresseur (10) comme partie du système de conduite (78), lequel mène d'un raccord (40) extérieur au boîtier de compresseur (10), relié au circuit de surrefroidissement (30), à l'orifice d'admission (80), et en ce que le canal amortisseur (120) est disposé dans le canal d'admission (100).
  5. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal amortisseur (120) est disposé dans une partie (122) pouvant être insérée dans le boîtier de compresseur (10).
  6. Compresseur à vis selon la revendication 5, caractérisé en ce que la partie (122) pouvant être insérée dans le boîtier de compresseur (10) peut être insérée dans le canal d'admission (100) dans le boîtier de compresseur (10).
  7. Compresseur à vis selon la revendication 5 ou 6, caractérisé en ce que la partie pouvant être insérée comporte un tube amortisseur (122) et un support (130), avec lequel le tube amortisseur (122) peut être fixé dans le boîtier de compresseur (10).
  8. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que le boîtier de compresseur (10) comporte un robinet de réglage (58), et en ce que l'orifice d'admission (80) est disposé dans le robinet de réglage (58) et est mobile avec celui-ci.
  9. Compresseur à vis selon la revendication 8, caractérisé en ce que l'orifice d'admission (80) dans le robinet de réglage (58) est relié par une section à longueur variable (104) du canal d'admission (100) au raccord extérieur (40).
  10. Compresseur à vis selon la revendication 9, caractérisé en ce que la section à longueur variable (104) du canal d'admission (100) est conçue de façon télescopique.
  11. Compresseur à vis selon la revendication 9 ou 10, caractérisé en ce que la section à longueur variable (104) du canal d'admission (100) est formée par un tube de raccordement (94) pouvant être introduit dans un canal de réception (90).
  12. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal amortisseur (120) comprend une longueur qui correspond approximativement à un quart de la longueur d'onde des vibrations de pression destinées à être amorties ou à un multiple impair de celui-ci.
  13. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal amortisseur (120) débouche avec une première embouchure (124) dans un premier volume (132) situé entre le raccord extérieur (40) et la première embouchure (124).
  14. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal amortisseur (120) débouche avec une seconde embouchure (126) dans un second volume (134) situé entre celle-ci et l'orifice d'admission (80).
  15. Compresseur à vis selon l'une quelconque des revendications 13 ou 14, caractérisé en ce qu'un saut de superficie de section est présent au passage d'une des embouchures (124, 126) dans le volume (132, 134) respectif.
  16. Compresseur à vis selon la revendication 15, caractérisé en ce que le saut de superficie de section est au moins un facteur 1,5.
  17. Compresseur à vis selon l'une quelconque des revendications 13 à 16, caractérisé en ce que le premier volume (132) situé entre la première embouchure (124) et le raccord extérieur (40) se situe dans le boîtier de compresseur (10).
  18. Compresseur à vis selon la revendication 17, caractérisé en ce que le premier volume (132) se situe dans une section de canal d'admission (116).
  19. Compresseur à vis selon l'une quelconque des revendications 14 à 18, caractérisé en ce que le second volume (134) situé entre la seconde embouchure (126) et l'orifice d'admission (80) se situe dans le boîtier de compresseur (10).
  20. Compresseur à vis selon la revendication 19, caractérisé en ce que le second volume (134) se situe dans la section de canal d'admission (116).
  21. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un volume de détente (142) est associé au raccord extérieur (40).
  22. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que le système de conduite (78) est relié à une évacuation d'huile (136).
  23. Compresseur à vis selon la revendication 22, caractérisé en ce que l'évacuation d'huile (136) débouche dans le canal d'admission (100).
  24. Compresseur à vis selon la revendication 23, caractérisé en ce que l'évacuation d'huile (136) débouche dans la section de canal d'admission (116) recevant le canal amortisseur (120).
  25. Compresseur à vis selon la revendication 24, caractérisé en ce que l'évacuation d'huile (136) débouche dans le premier volume (132).
EP03018778A 2002-09-03 2003-08-28 Compresseur à vis Expired - Lifetime EP1396640B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
SI200330459T SI1396640T1 (sl) 2002-09-03 2003-08-28 Vijacni kompresor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10242139 2002-09-03
DE10242139A DE10242139A1 (de) 2002-09-03 2002-09-03 Schraubenverdichter

Publications (3)

Publication Number Publication Date
EP1396640A2 EP1396640A2 (fr) 2004-03-10
EP1396640A3 EP1396640A3 (fr) 2004-11-17
EP1396640B1 true EP1396640B1 (fr) 2006-07-26

Family

ID=31502532

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03018778A Expired - Lifetime EP1396640B1 (fr) 2002-09-03 2003-08-28 Compresseur à vis

Country Status (10)

Country Link
US (1) US6898948B2 (fr)
EP (1) EP1396640B1 (fr)
CN (1) CN1312402C (fr)
AT (1) ATE334311T1 (fr)
CY (1) CY1105723T1 (fr)
DE (2) DE10242139A1 (fr)
DK (1) DK1396640T3 (fr)
ES (1) ES2269886T3 (fr)
PT (1) PT1396640E (fr)
SI (1) SI1396640T1 (fr)

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EP1567770B1 (fr) 2002-12-03 2017-01-18 BITZER Kühlmaschinenbau GmbH Compresseur a vis
DE10258145A1 (de) * 2002-12-03 2004-06-24 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
DE102006044821B4 (de) * 2006-09-14 2015-09-24 Halla Visteon Climate Control Corporation Kältemittelverdichter mit Schalldämpfer für Klimaanlagen
WO2009045187A1 (fr) * 2007-10-01 2009-04-09 Carrier Corporation Amortisseur de pulsation pour compresseur à vis
US8459963B2 (en) * 2007-10-10 2013-06-11 Carrier Corporation Screw compressor pulsation damper
US20090210301A1 (en) * 2008-02-14 2009-08-20 Microsoft Corporation Generating customized content based on context data
CN103512259B (zh) * 2013-03-21 2016-04-20 广东美芝制冷设备有限公司 热泵系统、制冷系统
DE102015006129A1 (de) * 2015-05-09 2016-11-10 Man Diesel & Turbo Se Schraubenmaschine
US9920763B2 (en) * 2015-09-17 2018-03-20 Ingersoll-Rand Company Contact cooled rotary airend injection spray insert
CN208089547U (zh) * 2017-09-30 2018-11-13 江森自控空调冷冻设备(无锡)有限公司 一种滑阀
EP3742080B1 (fr) * 2019-05-21 2021-11-03 Carrier Corporation Appareil de réfrigération
CN113513474B (zh) * 2020-04-09 2023-02-21 江森自控空调冷冻设备(无锡)有限公司 螺杆压缩机、制冷系统和制冷系统的控制方法
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SE382663B (sv) * 1974-04-11 1976-02-09 Stal Refrigeration Ab Sett att fora in mellantryckgas i en skruvkylkompressor jemte skruvkompressor for genomforande av settet.
US4220197A (en) * 1979-01-02 1980-09-02 Dunham-Bush, Inc. High speed variable delivery helical screw compressor/expander automotive air conditioning and waste heat energy _recovery system
US4545742A (en) * 1982-09-30 1985-10-08 Dunham-Bush, Inc. Vertical axis hermetic helical screw rotary compressor with discharge gas oil mist eliminator and dual transfer tube manifold for supplying liquid refrigerant and refrigerant vapor to the compression area
US4478054A (en) * 1983-07-12 1984-10-23 Dunham-Bush, Inc. Helical screw rotary compressor for air conditioning system having improved oil management
DE19757829A1 (de) * 1997-12-24 1999-07-01 Bitzer Kuehlmaschinenbau Gmbh Kältemittelkompressor
DE19925744A1 (de) * 1999-06-05 2000-12-07 Mannesmann Vdo Ag Elektrisch angetriebenes Kompressionskältesystem mit überkritischem Prozeßverlauf
DE19935041A1 (de) 1999-07-26 2001-02-08 Bitzer Kuehlmaschinenbau Gmbh Schraubenverdichter

Also Published As

Publication number Publication date
EP1396640A3 (fr) 2004-11-17
DE10242139A1 (de) 2004-03-18
US20040040332A1 (en) 2004-03-04
ES2269886T3 (es) 2007-04-01
PT1396640E (pt) 2006-10-31
ATE334311T1 (de) 2006-08-15
DK1396640T3 (da) 2006-11-20
SI1396640T1 (sl) 2006-12-31
EP1396640A2 (fr) 2004-03-10
DE50304341D1 (de) 2006-09-07
CN1492150A (zh) 2004-04-28
CN1312402C (zh) 2007-04-25
CY1105723T1 (el) 2010-12-22
US6898948B2 (en) 2005-05-31

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