EP3080457B1 - Verdichter - Google Patents

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Publication number
EP3080457B1
EP3080457B1 EP14824368.6A EP14824368A EP3080457B1 EP 3080457 B1 EP3080457 B1 EP 3080457B1 EP 14824368 A EP14824368 A EP 14824368A EP 3080457 B1 EP3080457 B1 EP 3080457B1
Authority
EP
European Patent Office
Prior art keywords
compressor
slide
rod
screw
axial direction
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.)
Revoked
Application number
EP14824368.6A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3080457A1 (de
Inventor
Dieter Mosemann
Ottomar Neuwirth
Dmytro Zaytsev
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.)
GEA Refrigeration Germany GmbH
Original Assignee
GEA Refrigeration Germany GmbH
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=52292851&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP3080457(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by GEA Refrigeration Germany GmbH filed Critical GEA Refrigeration Germany GmbH
Publication of EP3080457A1 publication Critical patent/EP3080457A1/de
Application granted granted Critical
Publication of EP3080457B1 publication Critical patent/EP3080457B1/de
Revoked legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C28/125—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 with sliding valves controlled by the use of fluid other than the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/811—Actuator for control, e.g. pneumatic, hydraulic, electric

Definitions

  • the present invention relates to a screw compressor according to the preamble of claim 1.
  • screw compressors are used in many applications because their construction is robust and the efficiency that can be achieved is high.
  • speed-controlled screw compressors i.e. screw compressors that have two intermeshing screw rotors for compressing a medium to be compressed, preferably refrigerant, the speed of which is regulated, and also screw compressors that have a fixed speed.
  • a speed-controlled screw compressor with a slide for regulating a so-called internal volume ratio (also called Vi) is from the DE 199 16 983 A1 known.
  • the internal volume ratio is the ratio of tooth gap volumes of the intermeshing screw rotors at the beginning and the end of compaction.
  • the internal volume ratio of the compressor is influenced with the help of the so-called Vi slide.
  • Speed-controlled, semi-hermetic compact screw compressors with a Vi slide for stepped control of the internal volume ratio are from the DE 10 2011 051 730 A1 known.
  • the Vi slide can be positioned in one of two possible positions, the inner one in one of the positions
  • Volume ratio is greater than in the other of the positions.
  • Compressor according to the DE 10 2011 051 730 A1 cannot be optimally adapted to any operating conditions. This means that compressor operation that is favorable in terms of energy is only possible to a limited extent. Furthermore, slide movement errors can occur, which can result in an energetically unfavorable operation as well as an increased susceptibility to failure.
  • a compressor which has a slide which is used to regulate the delivery rate of the compressor while at the same time influencing the volume ratio of the compressor.
  • a screw compressor which has at least one screw rotor which is arranged rotatably about an axis of rotation arranged in the axial direction.
  • the at least one screw rotor is arranged in a compression chamber which is designed to be fluid-tight at least in sections towards the surroundings and opens into a high-pressure volume (26).
  • the compressor also has a Vi slide for influencing a volume ratio of the compressor, the Vi slide at least partially forming a section of the fluid-tight delimitation of the compression space and being arranged such that it can be displaced in position in the axial direction.
  • the Vi slide is infinitely adjustable and the compressor has a device for detecting the slide position of the Vi slide.
  • the Vi slide can be moved continuously and the screw compressor has a device for detecting the position of the Vi slide results in an energetically favorable mode of operation with low susceptibility to failure.
  • a possible embodiment of a compressor according to the invention more precisely a screw compressor 10 according to the invention, which is also referred to below as compressor 10 for short, is shown.
  • the compressor 10 has a housing 12 and an electric motor 14 arranged in the housing 12. Furthermore, the compressor 10 has a drive shaft 16 and a compression device 18 with a first and a second intermeshing screw rotor 20 and 22.
  • the screw rotors 20, 22 are driven in rotation directly via the drive shaft 16 (in alternative embodiments indirectly, for example via a gear arrangement).
  • a compressor according to the invention can also have only one screw rotor or also three or more screw rotors.
  • the first screw rotor 20 is arranged so as to be rotatable about a first axis of rotation arranged in the axial direction.
  • the second screw rotor 22 is arranged to be rotatable about a second axis of rotation which extends parallel to the first axis of rotation.
  • Both the first and the second helical rotor 20, 22 are arranged in a compression space 24 which is at least partially fluid-tight towards the environment and opens into a high-pressure volume 26.
  • the compressor 10 also has a Vi slide 28 which, with the delimitation surfaces 30, at least partially forms a section of the fluid-tight delimitation of the compression space 24.
  • the Vi slide 28 is arranged to be positionally displaceable in the axial direction. Furthermore, the Vi slide 28 can be moved continuously.
  • the compressor 10 also has a device 32 for detecting the slide position of the Vi slide, in particular the axial position of the Vi slide 28.
  • the device 32 for detecting the position of the Vi slide has a rod-shaped feeler element or a rod 34 which at a first end 36 engages in a recess formed on the Vi slide 28 in the form of a groove 38.
  • the groove 38 has an increasing depth in the axial direction, so that an unambiguous determination of the axial position of the Vi slide 28 is possible.
  • the spring-loaded rod 34 is in operative engagement at a second end 40 with a position sensor 41, so that the position of the Vi slide 28 can be determined.
  • an elastic element in the form of a spring (compression spring) 40 or is loaded or acted upon in the corresponding direction.
  • the compressor 10 also has an adjusting device 42 for adjusting the position of the Vi slide 28.
  • the position of the Vi slide 28 is adjusted hydraulically.
  • the compressor 10 has a cylindrical recess or chamber 44 in which a piston 46 connected to the Vi slide 28 is arranged so as to be axially displaceable.
  • the piston 46 is sealed against a chamber wall 47 by means of a seal 48 and divides the chamber 44 into two partial volumes, namely a first partial volume 50 and a second partial volume 52, which are separated from each other by the piston 46 provided with the seal 48.
  • the pressure in the first partial volume 50 can be increased and / or the pressure in the second partial volume 52 can be decreased.
  • the pressure in the first partial volume 50 is reduced and / or in the second partial volume 52 increased.
  • a first valve 54 and a second valve 56 are available, by means of which the first sub-volume 50 and the second sub-volume 52 can be pressurized with hydraulic fluid or can also be correspondingly relaxed.
  • the two valves 54, 56 are designed as solenoid valves, with electrically or electro-mechanically actuated valves also being conceivable in alternative embodiments.
  • the compressor 10 has a regulating device (not shown in the figures), by means of which the optimal position of the Vi slide 28 for the prevailing operating condition is regulated.
  • Vi slide 28 is actuated via a pneumatic device or a mechanical device, for example with or against the bias of an elastic element.
  • the compressor 10 in order to enable the optimal internal volume ratio Vi and thus an energetically favorable compressor operation under any operating conditions within the application limits of the compressor 10, the compressor 10 is designed with a stepless Vi control, the Vi slide 28 being continuously adjustable and is equipped with a slide position sensor.
  • Fig. 2 shows an embodiment of a compressor 10 according to the invention.
  • an inclined groove 38 is arranged in the Vi slide 28.
  • a spring-loaded rod 34 pushes with a first end into the groove 28.
  • a second end of the rod 34 is connected to a slide position sensor 41.
  • the Vi slide 28 can be adjusted hydraulically, for example.
  • solenoid valves 54, 56 for increasing Vi and for decreasing Vi are arranged on the compressor 10.
  • the respective valve 54, 56 is activated by the control or regulation (for example by a pulse / pause signal) until the required position of the Vi slide 28 is reported by the slide position sensor 41 to the control or regulation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP14824368.6A 2013-12-12 2014-12-12 Verdichter Revoked EP3080457B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013020534.4A DE102013020534A1 (de) 2013-12-12 2013-12-12 Verdichter
PCT/EP2014/003343 WO2015086159A1 (de) 2013-12-12 2014-12-12 Verdichter

Publications (2)

Publication Number Publication Date
EP3080457A1 EP3080457A1 (de) 2016-10-19
EP3080457B1 true EP3080457B1 (de) 2021-07-14

Family

ID=52292851

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14824368.6A Revoked EP3080457B1 (de) 2013-12-12 2014-12-12 Verdichter

Country Status (6)

Country Link
US (1) US20160319814A1 (da)
EP (1) EP3080457B1 (da)
CN (1) CN105793572A (da)
DE (1) DE102013020534A1 (da)
DK (1) DK3080457T3 (da)
WO (1) WO2015086159A1 (da)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105626520B (zh) * 2016-04-01 2017-07-28 福建雪人股份有限公司 一种可调节内容积比的半封闭式的螺杆压缩机
DE102020115442A1 (de) 2020-06-10 2021-12-16 Bitzer Kühlmaschinenbau Gmbh Schraubenexpander und Anlage zur Gewinnung elektrischer Energie aus Wärme mit einem Schraubenexpander

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4351160A (en) 1980-06-16 1982-09-28 Borg-Warner Corporation Capacity control systems for screw compressor based water chillers
DE3422573A1 (de) * 1982-09-10 1985-12-19 Frick Co., Waynesboro, Pa. Mikroprozessor-regelung des verdichtungsverhaeltnisses bei vollast in einem schrauben-rotationskompressor entsprechend dem antriebsmotorstrom
DE3528058A1 (de) 1985-04-05 1986-10-16 Frick Co., Waynesboro, Pa. Schrauben-rotationsverdichter
US20030007873A1 (en) 2001-02-15 2003-01-09 Toshiro Hattori Screw compressor equipment for accommodating low compression ratio and pressure variation and the operation method thereof
US20050013702A1 (en) * 2003-07-16 2005-01-20 Bitzer Kuehlmaschinenbau Gmbh Screw compressor
EP1553300A1 (en) 2002-10-16 2005-07-13 Daikin Industries, Ltd. Variable inner volume ratio-type inverter screw compressor

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GB1171291A (en) * 1965-10-12 1969-11-19 Svenska Rotor Maskiner Ab Screw Rotor Machines
DE2658928A1 (de) * 1976-12-24 1978-07-06 Beringer Hydraulik Gmbh Hydraulische steuerung
US4388048A (en) * 1981-03-10 1983-06-14 Dunham Bush, Inc. Stepping type unloading system for helical screw rotary compressor
DD244386A1 (de) * 1985-12-18 1987-04-01 Kuehlautomat Veb Vorrichtung zur positionsanzeige des regelschlittens an schraubenverdichtern
DD286203A5 (de) * 1989-07-14 1991-01-17 Veb Kuehlautomat,De Vorrichtung zur positionsanzeige des regelschlittens an schraubenverdichtern
US5135374A (en) * 1990-06-30 1992-08-04 Kabushiki Kaisha Kobe Seiko Sho Oil flooded screw compressor with thrust compensation control
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DE19521922A1 (de) * 1995-06-09 1996-12-12 Kuehlautomat Berlin Gmbh Kab Leistungsregelung von Schraubenverdichtern
EP0902188B1 (en) * 1997-09-10 2003-05-28 KABUSHIKI KAISHA KOBE SEIKO SHO also known as Kobe Steel Ltd. Screw compressor
DE19916983A1 (de) 1999-04-15 2000-10-19 Grasso Gmbh Refrigeration Tech Schraubenverdichter mit Drehzahlregelung
CN2667205Y (zh) * 2003-12-19 2004-12-29 泰豪科技股份有限公司 螺杆压缩机输气量调节滑阀位置信号检测装置
CN101821479A (zh) * 2007-10-10 2010-09-01 开利公司 螺杆压缩机的滑阀系统
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DE102011051730A1 (de) 2011-07-11 2013-01-17 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
JP2013036403A (ja) * 2011-08-09 2013-02-21 Daikin Industries Ltd スクリュー圧縮機
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Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4351160A (en) 1980-06-16 1982-09-28 Borg-Warner Corporation Capacity control systems for screw compressor based water chillers
DE3422573A1 (de) * 1982-09-10 1985-12-19 Frick Co., Waynesboro, Pa. Mikroprozessor-regelung des verdichtungsverhaeltnisses bei vollast in einem schrauben-rotationskompressor entsprechend dem antriebsmotorstrom
DE3528058A1 (de) 1985-04-05 1986-10-16 Frick Co., Waynesboro, Pa. Schrauben-rotationsverdichter
US20030007873A1 (en) 2001-02-15 2003-01-09 Toshiro Hattori Screw compressor equipment for accommodating low compression ratio and pressure variation and the operation method thereof
EP1553300A1 (en) 2002-10-16 2005-07-13 Daikin Industries, Ltd. Variable inner volume ratio-type inverter screw compressor
US20050013702A1 (en) * 2003-07-16 2005-01-20 Bitzer Kuehlmaschinenbau Gmbh Screw compressor
DE10333400A1 (de) 2003-07-16 2005-02-10 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter

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Title
TEWES N.: "Vergleichende Betrachtung verschiedener Verfahren zur Veranderung des eingebauten Volumenverhaltnisses von Schraubenkompressoren", VDI BERICH, no. 1135, 1 January 1994 (1994-01-01), pages 237 - 248, XP055912460

Also Published As

Publication number Publication date
EP3080457A1 (de) 2016-10-19
WO2015086159A1 (de) 2015-06-18
DE102013020534A1 (de) 2015-06-18
US20160319814A1 (en) 2016-11-03
DK3080457T3 (da) 2021-10-18
CN105793572A (zh) 2016-07-20

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