EP1710435A1 - Compresseur de réfrigérant - Google Patents

Compresseur de réfrigérant Download PDF

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Publication number
EP1710435A1
EP1710435A1 EP06005929A EP06005929A EP1710435A1 EP 1710435 A1 EP1710435 A1 EP 1710435A1 EP 06005929 A EP06005929 A EP 06005929A EP 06005929 A EP06005929 A EP 06005929A EP 1710435 A1 EP1710435 A1 EP 1710435A1
Authority
EP
European Patent Office
Prior art keywords
switching
refrigerant compressor
compressor according
valve
cylinder
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.)
Granted
Application number
EP06005929A
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German (de)
English (en)
Other versions
EP1710435B1 (fr
EP1710435B2 (fr
Inventor
Wolfgang SANDKÖTTER
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
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Application filed by Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority to PL06005929T priority Critical patent/PL1710435T3/pl
Priority to SI200630009T priority patent/SI1710435T1/sl
Publication of EP1710435A1 publication Critical patent/EP1710435A1/fr
Publication of EP1710435B1 publication Critical patent/EP1710435B1/fr
Application granted granted Critical
Publication of EP1710435B2 publication Critical patent/EP1710435B2/fr
Active 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/053—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/067—Control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/24—Control not provided for in a single group of groups F04B27/02 - F04B27/22
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/06—Valve parameters
    • F04B2201/0601—Opening times
    • F04B2201/06011—Opening times of the inlet valve only
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow valves
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2521—On-off valves controlled by pulse signals

Definitions

  • the invention relates to a refrigerant compressor for refrigeration systems comprising at least one cylinder unit, which has a cylinder housing and a piston oscillatingly movable in the cylinder housing, a cylinder head, with an inlet chamber through which an inlet flow of the at least one cylinder unit passes and with one of an outlet flow of the at least one cylinder unit Outlet chamber, and a switching valve for interrupting the inlet flow.
  • Such refrigerant compressors are known from the prior art, in these consists with the switching valve, the ability to permanently disable one or more cylinder units or permanently switch on.
  • the invention is therefore based on the object to improve a refrigerant compressor of the generic type such that it can be operated in any part load ranges.
  • a control is provided for driving the switching valve, which operates the switching valve in consecutive, each an opening interval and a closing interval of the switching valve comprehensive switching intervals for operation of the refrigerant compressor in a lower part load range, which are shorter than a shortest period of time after which a temperature of an evaporator in the working refrigeration system has increased by about 10% at an interruption of the intake flow.
  • the advantage of the solution according to the invention is the fact that this opens up the possibility to operate a refrigerant compressor, in particular a reciprocating compressor in a lower part load range at any part load, as by the ratio of the opening intervals and the closing intervals within each switching interval of the mass flow to be compressed continuously and is arbitrarily adjustable.
  • time periods are selected for the switching intervals, which are sufficiently short, so that due to the inertia of the reaction of the refrigeration system according to the invention to the switching intervals only insignificant temperature fluctuations in the evaporator of the refrigerators arise that do not affect a precise control of the temperature.
  • a controller for driving the switching valve is provided, which for the operation of the refrigerant compressor in a lower part-load range Operating the switching valve in successive, one opening interval and a closing interval of the switching valve comprehensive switching intervals that are shorter than about 10 seconds.
  • the switching intervals are longer than approximately 0.02 seconds.
  • the switching intervals are longer than 0.05 seconds, and it is particularly favorable if the switching intervals are longer than 0.1 seconds.
  • the switching intervals correspond to a switching frequency which is smaller by more than a factor of 5 than a natural frequency of the switching valve.
  • a particularly expedient solution provides that the controller operates in the lower part-load range all cylinder units of the refrigerant compressor in the switching intervals.
  • duration of the switching intervals a wide variety of possible solutions are conceivable.
  • a variant which is particularly favorable for reasons of simplicity provides that the control operates with time-constant switching intervals.
  • controller varies the switching intervals according to a drive speed of the refrigerant compressor.
  • the switching valve so that it acts directly, for example magnetically controlled, on the inlet flow.
  • the switching valve is a servo valve.
  • the servo valve comprises a valve body which can be actuated by a pressure associated with the pressure in the outlet chamber.
  • valve body In order to ensure that the valve body does not automatically assume the end position brought about by the pressure in the outlet chamber, it is preferably provided that the valve body is acted upon by an elastic force store acting in the opposite direction to the action of the pressure on the valve body.
  • valve body is coupled to a pressure which is acted upon by the pressure in the outlet chamber and is guided in a switching cylinder housing, which then actuates the valve body.
  • the switching piston and the switching cylinder housing enclose a switching cylinder chamber and when the pressure in the switching cylinder chamber is controllable.
  • valve body and the switching piston form a unit which is guided in the switching cylinder housing.
  • Such a control valve is formed, for example, as a fast-reacting, electrically actuated solenoid valve or similarly constructed valve.
  • control valve opens or closes a connection channel between the control cylinder chamber and the outlet, so that in a simple way there is the possibility to pressurize the control piston with under pressure in the outlet chamber medium.
  • the natural frequency of the unit consisting of switching piston, valve body and elastic energy storage at least equal to the natural frequency of the switching valve.
  • Such a high natural frequency of the switching valve can be achieved in particular when the switching piston is made of a lightweight construction material.
  • Such a lightweight material may for example be a light metal or a plastic, for example, a fiber-reinforced plastic.
  • control piston provides that this is designed as a hollow body, so that also by a high natural frequency of the unit of control piston, valve body and elastic energy storage device can be achieved.
  • An exemplary embodiment of a refrigeration system according to the invention designated as a whole by 10, comprises a refrigerant compressor 12, from whose high-pressure connection 14 a line 16 leads to a condenser designated as a whole by 18, in which the compressed refrigerant condenses due to heat dissipation.
  • liquid refrigerant flows in a line 20 to a collector 22, in which the liquid refrigerant collects and from which this then flows via a line 28 to an expansion valve 30 for an evaporator 32.
  • the vaporized refrigerant flows via a line 34 to a low pressure port 36 of the refrigerant compressor 12th
  • the refrigerant compressor 12 is designed as a reciprocating compressor and comprises a compressor housing 40, in which two cylinder banks 42a and 42b arranged in a V-shape are provided, each of which comprises at least one, in particular two or more cylinder units 44.
  • Each of these cylinder units 44 is formed from a cylinder housing 46, in which a piston 48 is oscillated by the fact that the piston 48 is driven by a connecting rod 50, which in turn sits on an eccentric 52 of an eccentric shaft 54 which is driven for example by an electric motor 55 is.
  • the cylinder housing 46 of each of the cylinder units 44 is closed by a valve plate 56 on which a cylinder head 58 is disposed.
  • valve plate 56 covers not only a cylinder housing 46 of a cylinder bank 42, but all cylinder housing 46 of the respective cylinder bank 42 and in the same way, the cylinder head 58 also engages over all the cylinder housing 46 of the respective cylinder bank 42nd
  • the compressor housing 40 further comprises an inlet channel 60 communicating with the low-pressure connection 36, which is integrated, for example, in the compressor housing 40.
  • each cylinder bank 42 is associated with a switching valve 70, designated as a whole, which serves to convey an inlet flow 74 that passes from the inlet channel 60 into the respective cylinder head 58 and into an inlet chamber 72 thereof through the valve plate 56 of refrigerant to break.
  • a switching valve 70 designated as a whole, which serves to convey an inlet flow 74 that passes from the inlet channel 60 into the respective cylinder head 58 and into an inlet chamber 72 thereof through the valve plate 56 of refrigerant to break.
  • the inlet flow 74 has the possibility, via an inlet opening 76 provided in the valve plate 56 and an inlet valve 78 provided on the valve plate 56, into a cylinder chamber bounded by the respective piston 48 and the respective cylinder housing 46 and the valve plate 56 80 to be compressed therein by the oscillating movement of the piston 48, so that via an outlet opening 82 and an outlet valve 84, an outlet stream 86 exits the cylinder chamber 80 and enters an outlet chamber 88 of the cylinder head 58.
  • the switching valve 70 is formed as a servo valve, which is integrated in the cylinder head 58 and has a valve body 90, with which an opening provided in the valve plate 56 Eihströmö réelle 92 of the inlet chamber 72 is closed.
  • the valve body 90 is further arranged on a switching piston 94, which is guided in a switching cylinder housing 96, so that the switching piston 94 is movable in the direction of the valve plate 56 by pressure present in a switching cylinder chamber 98 to close the inflow opening 92 in the same.
  • the force acting on the switching piston 94 by the high pressure in the switching cylinder chamber 98 counteracts the force of an elastic force accumulator 120 which is supported on the switching cylinder housing 96 on the one hand and on the other hand acts on the switching piston 94 such that it moves away from the valve plate 56 and thus moves the valve body 90 into a position releasing the inlet opening 92.
  • the switching piston 94 is provided with a pressure relief passage 122 which leads from an opening facing the switching cylinder chamber 98 to an outlet opening 124 shown in FIG. 4, which closes the valve body 90 and the closing position 92 in the inlet opening 92 Switching piston 94 opens into the inlet chamber 72.
  • the pressure relief passage 124 thereby causes the pressure in the switching cylinder chamber 98 to rapidly collapse when the connection between the high-pressure passage 116 and the pressure feed passage 118 is interrupted, thus releasing the switching piston 94, together with the valve body 90, into the inlet opening 92 under the action of the elastic force accumulator 120 , move in Fig. 3 shown position.
  • the switching valve 70 can be controlled by a controller 130 shown in FIG. 1 such that it closes and opens the switching valve 70 in continuously successive switching intervals SI, wherein each of the switching intervals SI has an opening interval O, in which the valve body 90 is in its releasing position Passage of the inlet stream 74 through the inlet opening 92 allows, and a closing interval S, in which the valve body 90, as shown in Fig. 4, in its closing position, the flow of the inlet stream 74 through the inlet opening 92 blocked.
  • the duration of the opening interval O and the closing interval S relative to each other can now be set variably in all partial load ranges, so that either the opening interval O is greater than the closing interval or vice versa.
  • the opening interval O may substantially extend over the entire duration of the switching interval SI, while the closing interval S is arbitrarily small, or vice versa, the closing interval S may extend substantially over the entire duration of the switching interval SI, so that the opening interval O becomes arbitrarily small.
  • the system is provided with a reaction inertia, so that when the extraction of refrigerant from the evaporator 32 is interrupted, the temperature T of the evaporator 32 does not rise immediately but, as shown in FIG. 6, requires a time Z to increase by one value D to rise.
  • the switching interval SI is set to be shorter than the time Z that elapses until the temperature T of the evaporator 32 rises from a temperature T A of the evaporator 32 by a value D of about 10% better about 5%, when there is a sudden interruption in the extraction of refrigerant from the evaporator 32 and the supply of high pressure medium at the high pressure port 14.
  • the durations of the switching intervals SI are shorter than about 10 seconds, more preferably less than about 2 seconds.
  • the switching intervals are longer than about 0.02 second, more preferably longer than 0.05 second, and preferably longer than 0.1 second.
  • a preferred operating range provides switching intervals SI whose duration is between 0.1 and 10 seconds.
  • the switching pistons 94 together with the valve body 90 and the elastic force accumulators 120 have a natural frequency higher than the frequency corresponding to the maximum switching intervals SI, so that the switching pistons 94 are able to realize the opening intervals O and the closing intervals S substantially instantaneously within the switching intervals SI.
  • the natural frequencies of the systems of switching piston 94, valve body 90 and elastic energy storage device 120 by a factor of at least 5 or even better at least 10 higher than the switching intervals SI corresponding frequencies.
  • the switching pistons 94 are made of a lightweight construction material, for example light metal or plastic, in order to move small masses.
  • the switching pistons 94 ' are designed as hollow bodies in order to achieve the lowest possible mass and thus the highest possible natural frequency.
  • the solution according to the invention provides, for example, such a switching valve 70 per cylinder bank, so that there is the possibility of correspondingly switching off the inlet flow for all cylinder units 44 of a cylinder bank 42.
  • the controller 130 controls all cylinder units 44 at the same switching intervals, at least in a lower part-load range, that is, in a range between about 1% and about 30% of the maximum mass flow.
  • the controller 130 is now able to control the switching valve 70 in an operation of the refrigerant compressor 12 in the full load range such that the valve body 90 is constantly in the inlet opening 92 releasing position, so that the inlet flow 74 to all cylinder units 44 of the respective cylinder bank 42nd can flow.
  • valve body 90 is constantly in its position closing the inflow opening 92. In this case, essentially no mass flow of refrigerant is compressed. Only the mass flow flowing through the pressure channel 116 and the pressure supply channel 118 and the pressure relief channel 122 is compressed.
  • the controller 130 is capable of continuously adjusting any partial load by variably setting the duration of the opening interval O and the duration of the closing interval S which add to the period of the switching interval SI in the desired ratio.
  • the switching interval SI can be the same in all partial load ranges.
  • the variation of the switching interval SI occurs so that at low speed of the electric motor, the switching intervals SI are long and at high speed of the electric motor, the switching intervals are shorter.
  • the advantage of the solution according to the invention is the fact that in the reciprocating compressor, the power consumption is proportional to the mass flow and thus with a reduction of the mass flow through successive opening intervals O and closing intervals S in the partial load range, the possibility to reduce the power consumption of the reciprocating compressor.
  • the solution according to the invention makes it possible to configure the start-up process of the refrigerant compressor 12 by controlling the mass flow rate in such a way that the risks from boiling-out refrigerant are minimized.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP06005929.2A 2005-04-05 2006-03-23 Compresseur de réfrigérant Active EP1710435B2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PL06005929T PL1710435T3 (pl) 2005-04-05 2006-03-23 Sprężarka czynnika chłodniczego
SI200630009T SI1710435T1 (sl) 2005-04-05 2006-03-23 Kompresor za hladivo

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005016433A DE102005016433A1 (de) 2005-04-05 2005-04-05 Kältemittelverdichter

Publications (3)

Publication Number Publication Date
EP1710435A1 true EP1710435A1 (fr) 2006-10-11
EP1710435B1 EP1710435B1 (fr) 2007-08-22
EP1710435B2 EP1710435B2 (fr) 2023-06-07

Family

ID=36371025

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06005929.2A Active EP1710435B2 (fr) 2005-04-05 2006-03-23 Compresseur de réfrigérant

Country Status (10)

Country Link
US (1) US20060218959A1 (fr)
EP (1) EP1710435B2 (fr)
CN (1) CN100523671C (fr)
AT (1) ATE371111T1 (fr)
DE (2) DE102005016433A1 (fr)
DK (1) DK1710435T3 (fr)
ES (1) ES2290930T5 (fr)
PL (1) PL1710435T3 (fr)
PT (1) PT1710435E (fr)
SI (1) SI1710435T1 (fr)

Cited By (7)

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Publication number Priority date Publication date Assignee Title
US7654098B2 (en) 1995-06-07 2010-02-02 Emerson Climate Technologies, Inc. Cooling system with variable capacity control
US8157538B2 (en) 2007-07-23 2012-04-17 Emerson Climate Technologies, Inc. Capacity modulation system for compressor and method
US8308455B2 (en) 2009-01-27 2012-11-13 Emerson Climate Technologies, Inc. Unloader system and method for a compressor
USRE44636E1 (en) 1997-09-29 2013-12-10 Emerson Climate Technologies, Inc. Compressor capacity modulation
WO2014124898A1 (fr) * 2013-02-13 2014-08-21 Kriwan Industrie-Elektronik Gmbh Procédé pour régler un compresseur pourvu d'un moteur d'un système de refroidissement et un compresseur d'un système de refroidissement
WO2021160672A1 (fr) * 2020-02-14 2021-08-19 Bitzer Kühlmaschinenbau Gmbh Compresseur de fluide de refroidissement
EP4116586A1 (fr) * 2021-07-08 2023-01-11 BITZER Kühlmaschinenbau GmbH Ensemble compresseur de fluide frigorigène

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WO2010019582A2 (fr) * 2008-08-12 2010-02-18 Carrier Corporation Soupape à impulsion spécialisée pour cylindre de compresseur
WO2011011221A2 (fr) 2009-07-20 2011-01-27 Carrier Corporation Soupape de décompression à coupure d'aspiration pour commande de capacité de compresseur
US10378533B2 (en) * 2011-12-06 2019-08-13 Bitzer Us, Inc. Control for compressor unloading system
WO2014023694A2 (fr) 2012-08-06 2014-02-13 Kriwan Industrie-Elektronik Gmbh Procédé de réglage d'un compresseur d'une installation frigorifique et installation frigorifique
DE102012107183B4 (de) 2012-08-06 2016-08-04 Kriwan Industrie-Elektronik Gmbh Verfahren zur Regelung eines Verdichters einer Kälteanlage sowie eine Kälteanlage
US10514026B2 (en) 2013-02-08 2019-12-24 Hitachi Industrial Equipment Systems Co., Ltd. Fluid compression system and control device therefor
ITMI20130583A1 (it) * 2013-04-11 2014-10-12 Frascold S P A Compressore per un impianto frigorifero e impianto frigorifero comprendente detto compressore
JP5984784B2 (ja) * 2013-11-19 2016-09-06 三菱電機株式会社 温冷水空調システム
CN108072201B (zh) 2016-11-11 2022-02-01 开利公司 热泵系统及其启动控制方法
EP4077943B1 (fr) * 2019-12-17 2024-06-05 Officine Mario Dorin S.p.A Compresseur alternatif polycylindrique
DE102020118740A1 (de) * 2020-07-15 2022-01-20 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichter

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US5540061A (en) * 1992-01-09 1996-07-30 Hitachi, Ltd. Refrigerator
US20010011463A1 (en) * 1999-04-22 2001-08-09 Volker Pollrich Refrigerant compressor apparatus

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US5540061A (en) * 1992-01-09 1996-07-30 Hitachi, Ltd. Refrigerator
DE4212162A1 (de) * 1992-04-10 1993-10-14 Ilka Maschinenfabrik Halle Gmb Einrichtung zur Kühlung des Elektromotors eines halbhermetischen Kältemittelverdichters
US20010011463A1 (en) * 1999-04-22 2001-08-09 Volker Pollrich Refrigerant compressor apparatus

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7654098B2 (en) 1995-06-07 2010-02-02 Emerson Climate Technologies, Inc. Cooling system with variable capacity control
USRE44636E1 (en) 1997-09-29 2013-12-10 Emerson Climate Technologies, Inc. Compressor capacity modulation
US8157538B2 (en) 2007-07-23 2012-04-17 Emerson Climate Technologies, Inc. Capacity modulation system for compressor and method
US8807961B2 (en) 2007-07-23 2014-08-19 Emerson Climate Technologies, Inc. Capacity modulation system for compressor and method
US8308455B2 (en) 2009-01-27 2012-11-13 Emerson Climate Technologies, Inc. Unloader system and method for a compressor
EP2391826A4 (fr) * 2009-01-27 2015-08-12 Emerson Climate Technologies Système bipasse de démarrage et procédé pour un compresseur
WO2014124898A1 (fr) * 2013-02-13 2014-08-21 Kriwan Industrie-Elektronik Gmbh Procédé pour régler un compresseur pourvu d'un moteur d'un système de refroidissement et un compresseur d'un système de refroidissement
US9982928B2 (en) 2013-02-13 2018-05-29 Kriwan Industrie-Elektronik Gmbh Method for controlling a compressor of a refrigeration system comprising a motor, and a compressor of a refrigeration system
WO2021160672A1 (fr) * 2020-02-14 2021-08-19 Bitzer Kühlmaschinenbau Gmbh Compresseur de fluide de refroidissement
EP4116586A1 (fr) * 2021-07-08 2023-01-11 BITZER Kühlmaschinenbau GmbH Ensemble compresseur de fluide frigorigène

Also Published As

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PL1710435T3 (pl) 2008-01-31
DE102005016433A1 (de) 2006-10-12
DE502006000063D1 (de) 2007-10-04
SI1710435T1 (sl) 2008-02-29
DK1710435T3 (da) 2008-01-28
US20060218959A1 (en) 2006-10-05
PT1710435E (pt) 2007-09-24
ES2290930T3 (es) 2008-02-16
EP1710435B1 (fr) 2007-08-22
CN100523671C (zh) 2009-08-05
CN1847757A (zh) 2006-10-18
EP1710435B2 (fr) 2023-06-07
ATE371111T1 (de) 2007-09-15
ES2290930T5 (es) 2023-11-20

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