US20060218959A1 - Refrigerant compressor - Google Patents

Refrigerant compressor Download PDF

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Publication number
US20060218959A1
US20060218959A1 US11/393,215 US39321506A US2006218959A1 US 20060218959 A1 US20060218959 A1 US 20060218959A1 US 39321506 A US39321506 A US 39321506A US 2006218959 A1 US2006218959 A1 US 2006218959A1
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United States
Prior art keywords
switching
refrigerant compressor
valve
compressor according
cylinder
Prior art date
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Abandoned
Application number
US11/393,215
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English (en)
Inventor
Wolfgang Sandkoetter
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
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Filing date
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Application filed by Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Assigned to BITZER KUEHLMASCHINENBAU GMBH reassignment BITZER KUEHLMASCHINENBAU GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SANDKOETTER, WOLFGANG
Publication of US20060218959A1 publication Critical patent/US20060218959A1/en
Abandoned 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 refrigerating systems comprising at least one cylinder unit, which has a cylinder housing and a piston which can move in an oscillating manner in the cylinder housing, a cylinder head, with an inlet chamber, flowed through by an inlet flow of the at least one cylinder unit, and with an outlet chamber, passed through by an outlet flow of the at least one cylinder unit, and also a switching valve for interrupting the inlet flow.
  • Refrigerant compressors of this type are known from the prior art; with these, the switching valve provides the possibility of permanently switching off or permanently switching on one or more cylinder units.
  • This object is achieved in the case of a refrigerant compressor of the type described at the beginning by providing a control for activating the switching valve which, for operating the refrigerant compressor in a lower part-load range, operates the switching valve in successive switching intervals, respectively comprising an opening interval and a closing interval of the switching valve, which are shorter than a shortest time period after which a temperature of an evaporator in the operating refrigerating system has risen by approximately 10% during an interruption of the inlet flow.
  • the advantage of the solution according to the invention can be seen in that it opens up the possibility of operating in particular a reciprocating piston compressor in a lower part-load range with any desired part load, since the mass flow to be compressed can be set steplessly and as desired by the ratio of the opening intervals and the closing intervals within each switching interval.
  • time periods that are adequately short are chosen for the switching intervals, so that, on account of the inertia of the reaction of the refrigerating system according to the invention to the switching intervals, only insubstantial temperature fluctuations that do not impair precise regulation of the temperature occur in the evaporator of the refrigerating systems.
  • a further exemplary embodiment of a refrigerant compressor of the type described at the beginning provides a control for activating the switching valve which, for operating the refrigerant compressor in a lower part-load range, operates the switching valve in successive switching intervals, respectively comprising an opening interval and a closing interval of the switching valve, which are shorter than approximately 10 seconds.
  • Limiting the duration of the switching intervals in such a manner likewise creates the possibility in a way according to the invention of operating the refrigerant compressor in a lower part-load range with a part load that can be set as desired, without pressure fluctuations which impair the quality of the regulation of the refrigerating system occurring in said system.
  • the switching intervals are longer than approximately 0.02 seconds.
  • the switching intervals are longer than 0.05 seconds and particularly advantageous if the switching intervals are longer than 0.1 seconds.
  • the switching valve It is particularly advantageous for switching the switching valve if the switching intervals correspond to a switching frequency which is less than an inherent or natural frequency of the switching valve.
  • the switching intervals correspond to a switching frequency which is less than an inherent or natural frequency of the switching valve by a factor of 5.
  • a particularly suitable solution provides that, in the lower part-load range, the control operates all the cylinder units of the refrigerant compressor in the switching intervals.
  • time duration of the switching intervals a wide variety of solution possibilities are conceivable.
  • a variant that is particularly advantageous for reasons of simplicity provides that the control operates with switching intervals that are of a constant time.
  • Another advantageous solution provides that the control varies the switching intervals on the basis of a rotational drive speed of the refrigerant compressor.
  • 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 accumulator acting counter to the effect of the pressure on the valve body.
  • valve body is coupled to a switching piston which can be acted upon by a pressure associated with the pressure in the outlet chamber and is guided in a switching cylinder housing, and which then actuates the valve body.
  • the switching piston and the switching cylinder housing enclose a switching cylinder chamber and if 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.
  • a servo valve of this type comprises a control valve which can be activated by the control.
  • a control valve of this type is formed for example as a rapidly responding, electrically activatable solenoid valve or similarly constructed valve.
  • control valve opens or closes a connecting channel between the control cylinder chamber and the outlet chamber, so that, in a simple manner, there is the possibility of acting upon the switching piston with medium under the pressure in the outlet chamber.
  • the inherent frequency of the unit comprising the switching piston, valve body and elastic force accumulator corresponds at least to the inherent frequency of the switching valve.
  • a high inherent frequency of this type of the switching valve can be achieved in particular if the switching piston is produced from a lightweight structural material.
  • a lightweight structural material of this type may be, for example, a lightweight metal or else a plastics material, for example also a fiber-reinforced plastics material.
  • a further advantageous form of the switching piston provides that it is formed as a hollow body, so that a high inherent frequency of the unit comprising the switching piston, valve body and elastic force accumulator can also be achieved in this way.
  • FIG. 1 shows a diagrammatic representation of a refrigerating system according to the invention
  • FIG. 2 shows a cross-section along line 2 - 2 through a refrigerant compressor of the refrigerating system according to the invention
  • FIG. 3 shows a section through a switching valve integrated into a cylinder head in the open position of a valve body of the switching valve
  • FIG. 4 shows a section similar to FIG. 3 in a closed position of the valve body of the switching valve
  • FIG. 5 shows a diagrammatic representation of a switching interval comprising an opening interval and a closing interval
  • FIG. 6 shows a diagrammatic representation of a behavior of the temperature of the evaporator in the refrigerating system when the compression of refrigerant is interrupted
  • FIG. 7 shows a section similar to FIG. 3 through a second exemplary embodiment of a refrigerant compressor according to the invention.
  • FIG. 8 shows a section similar to FIG. 4 through the second exemplary embodiment of a refrigerant compressor according to the invention.
  • An exemplary embodiment of a refrigerating system according to the invention designated as a whole by 10 , comprises a refrigerant compressor 12 , from the high-pressure connection 14 of which a line 16 leads to a condenser, designated as a whole by 18 , in which the compressed refrigerant is condensed by removal of heat.
  • liquid refrigerant flows in a line 20 to a collector 22 , in which the liquid refrigerant collects and from which the latter then flows via a line 28 to an expansion valve 30 for an evaporator 32 .
  • the evaporated refrigerant flows via a line 34 to a low-pressure connection 36 of the refrigerant compressor 12 .
  • the refrigerant compressor 12 is formed as a reciprocating piston compressor and comprises a compressor housing 40 , in which two banks of cylinders 42 a and 42 b , disposed in relation to each other in a V-shaped manner, are provided, each of which comprises at least one, in particular two or more, cylinder units 44 .
  • Each of the cylinder units 44 is formed by a cylinder housing 46 , in which a piston 48 can be moved in an oscillating manner by the piston 48 being able to be driven by a connecting rod 50 , which for its part is mounted on an eccentric 52 of an eccentric shaft 54 , which is driven for example by an electric motor 55 .
  • the cylinder housing 46 of each of the cylinder units 44 is closed off by a valve plate 56 , on which a cylinder head 58 is disposed.
  • valve plate 56 preferably covers not only one cylinder housing 46 of a bank of cylinders 42 , but all the cylinder housings 46 of the respective bank of cylinders 42 , and in the same way the cylinder head 58 likewise reaches over all the cylinder housings 46 of the respective bank of cylinders 42 .
  • the compressor housing 40 also comprises an inlet channel 60 , which is in connection with the low-pressure connection 36 and is, for example, integrated in the compressor housing 40 .
  • a switching valve which is designated as a whole by 70 and serves the purpose of interrupting an inlet flow 74 of refrigerant passing from the inlet channel 60 through the valve plate 56 into the respective cylinder head 58 , to be precise into an inlet chamber 72 of the same, is associated with each bank of cylinders 42 .
  • the inlet flow 74 has the possibility of entering 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 80 , delimited by the respective piston 48 and the respective cylinder housing 46 as well as the valve plate 56 , in order to be compressed in said chamber by the oscillating movement of the piston 48 , so that an outlet flow 86 leaves the cylinder chamber 80 via an outlet opening 82 and an outlet valve 84 and enters into 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 inflow opening 92 , provided in the valve plate 56 , of the inlet chamber 72 can be closed.
  • the valve body 90 is also disposed on a switching piston 94 , which is guided in a switching cylinder housing 96 , so that the switching piston 94 can be moved in the direction of the valve plate 56 by pressure prevailing in a switching cylinder chamber 98 , to close the inflow opening 92 in said valve plate.
  • a switching cylinder unit 100 which is formed by the switching cylinder housing 96 , the switching piston 94 and the switching cylinder chamber 98 and is integrated in the cylinder head 58 , is in this case controllable by means of a control valve 110 , which comprises an electromagnetically movable control piston 112 , with which a control valve seat 114 can be closed, the control piston 112 and the control valve seat 114 being provided for the purpose of interrupting or clearing a connection between a pressure channel 116 , leading to the outlet chamber 88 , and a pressure feed channel 118 , leading to the switching cylinder chamber 98 , for the switching cylinder 100 .
  • a control valve 110 which comprises an electromagnetically movable control piston 112 , with which a control valve seat 114 can be closed, the control piston 112 and the control valve seat 114 being provided for the purpose of interrupting or clearing a connection between a pressure channel 116 , leading to the outlet chamber 88 , and a pressure feed channel 118 , leading to the switching cylinder chamber
  • the switching cylinder chamber 98 is under the high pressure prevailing in the outlet chamber 88 and, consequently, the switching piston 94 moves in the direction of the valve plate 56 and presses the valve body 90 against the latter, in order to close the inflow opening 92 in the valve plate 56 .
  • the force acting on the switching piston 94 as a result of the high pressure in the switching cylinder chamber 98 opposes the force of an elastic force accumulator 120 , which on the one hand is supported on the switching cylinder housing 96 and on the other hand acts on the switching piston 94 in such a way that the latter moves away from the valve plate 56 , and consequently moves the valve body 90 into a position clearing the inflow opening 92 .
  • the switching piston 94 is provided with a pressure relieving channel 122 , which leads from an opening facing the switching cylinder chamber 98 to an outlet opening 124 , which is represented in FIG. 4 and, in the position of the valve body 90 and of the switching piston 94 that closes the inflow opening 92 , opens out into the inlet chamber 72 .
  • the pressure relieving channel 124 has the effect in this case that, when there is an interruption of the connection between the high-pressure channel 116 and the pressure feed channel 118 , the pressure in the switching cylinder chamber 98 rapidly collapses, and consequently the switching piston 94 together with the valve body 90 move under the action of the elastic force accumulator 120 into a position clearing the inflow opening 92 , represented in FIG. 3 .
  • the switching valve 70 can be activated by a control 130 , represented in FIG. 1 , in such a way that it closes and opens the switching valve 70 in continuously successive switching intervals SI, each of the switching intervals SI having an opening interval O, in which the valve body 90 in its clearing position allows the inlet flow 74 to pass through the inflow opening 92 , and a closing interval S, in which the valve body 90 , as represented in FIG. 4 , in its closing position blocks the flowing of the inlet flow 74 through the inflow opening 92 .
  • the time period of the opening interval O and of the closing interval S can then be set variably in relation to each other in all part-load ranges, so that either the opening interval O is greater than the closing interval or vice versa.
  • the opening interval O may extend substantially over the entire duration of the switching interval SI, while the closing interval S becomes as small as desired, or, conversely, the closing interval S may extend substantially over the entire duration of the switching interval SI, so that the opening interval O is as small as desired.
  • the system is provided with a reaction inertia, so that, when there is an interruption of the suction removal of refrigerant from the evaporator 32 , the temperature T of the evaporator 32 does not rise immediately but instead, as represented in FIG. 6 , requires a time period Z to rise by a value D.
  • the switching interval SI is chosen such that it is shorter than the time period Z that elapses before the temperature T of the evaporator 32 has risen from a temperature T A of the evaporator 32 by a value D of approximately 10%, even better approximately 5%, when there is a sudden interruption in the suction removal of refrigerant from the evaporator 32 and the feeding of medium under high pressure takes place at the high-pressure connection 14 .
  • the time periods of the switching intervals SI usually lie around time periods which are shorter than approximately 10 seconds, even better shorter than approximately 2 seconds.
  • the switching intervals are longer than approximately 0.02 seconds, even better longer than 0.05 seconds and preferably longer than 0.1 seconds.
  • a preferred operating range provides switching intervals SI of a duration that lies between 0.1 and 10 seconds.
  • the switching pistons 94 together with the valve bodies 90 and the elastic force accumulators 120 altogether have an inherent frequency which is higher than the frequency corresponding to the maximum switching intervals SI, so that the switching pistons 94 are capable of realizing the opening intervals O and the closing intervals S substantially without delay within the switching intervals SI.
  • the inherent frequencies of the systems comprising the switching piston 94 , valve body 90 and elastic force accumulator 120 are preferably higher than the frequencies corresponding to the switching intervals SI by a factor of at least 5 or even better at least 10.
  • the switching pistons 94 are made of a lightweight structural material, for example lightweight metal or plastics material, in order that small masses have to be moved.
  • the switching pistons 94 ′ are formed as hollow bodies, in order to achieve a mass that is as small as possible, and consequently an inherent frequency that is as high as possible.
  • the solution according to the invention provides, for example, a switching valve 70 of this type for each bank of cylinders, so that there is the possibility of correspondingly switching off the inlet flow for all the cylinder units 44 of a bank of cylinders 42 .
  • a switching valve 70 of this type in such a way that it controls the inlet flow 74 to all the cylinder units 44 of the entire refrigerant compressor.
  • control 130 controls all the cylinder units 44 with the same switching intervals.
  • the control 130 is then capable when the refrigerant compressor 12 is operated in the full-load range of activating the switching valve 70 in such a way that the valve body 90 is constantly in the position clearing the inflow opening 92 , so that the inlet flow 74 can flow to all the cylinder units 44 of the respective bank of cylinders 42 .
  • control 130 is capable of continuously setting any desired part load, to be precise in such a way that the time period of the opening interval O and the time period of the closing interval S, which add together to give the time period of the switching interval SI, are set variably in the desired ratio.
  • the switching interval SI may be equal in all part-load ranges.
  • the variation of the switching interval SI takes place in such a way that, at low rotational speed of the electric motor, the switching intervals SI are long and at high rotational speed of the electric motor the switching intervals are shorter.
  • the advantage of the solution according to the invention can be seen in that, in the case of the reciprocating piston compressor, the power consumption is proportional to the mass throughput, and consequently, when there is a reduction in the mass throughput through successive opening intervals O and closing intervals S in the part-load range, there is the possibility of also reducing the power consumption of the reciprocating piston compressor.
  • the solution according to the invention provides the possibility of controlling the mass throughput to implement the starting process of the refrigerant compressor 12 in such a way as to minimize the risks of boiling-out refrigerant.

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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)
US11/393,215 2005-04-05 2006-03-30 Refrigerant compressor Abandoned US20060218959A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005016433A DE102005016433A1 (de) 2005-04-05 2005-04-05 Kältemittelverdichter
DE102005016433.1 2005-04-05

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US20060218959A1 true US20060218959A1 (en) 2006-10-05

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

Cited By (12)

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US20090028723A1 (en) * 2007-07-23 2009-01-29 Wallis Frank S Capacity modulation system for compressor and method
US7654098B2 (en) 1995-06-07 2010-02-02 Emerson Climate Technologies, Inc. Cooling system with variable capacity control
US20100189581A1 (en) * 2009-01-27 2010-07-29 Wallis Frank S Unloader system and method for a compressor
WO2011011221A2 (en) 2009-07-20 2011-01-27 Carrier Corporation Suction cutoff unloader valve for compressor capacity control
US20130139535A1 (en) * 2011-12-06 2013-06-06 Terry Nares Control for Compressor Unloading System
USRE44636E1 (en) 1997-09-29 2013-12-10 Emerson Climate Technologies, Inc. Compressor capacity modulation
RU2528791C2 (ru) * 2008-08-12 2014-09-20 Кэрие Корпорейшн Выделенный импульсный клапан для цилиндра компрессора
WO2014167542A1 (en) 2013-04-11 2014-10-16 Frascold S.P.A. Compressor for a refrigerating plant and refrigerating plant comprising said compressor
US20150316304A1 (en) * 2013-02-13 2015-11-05 Kriwan Industrie-Elektronik Gmbh Method for controlling a compressor of a refrigeration system comprising a motor, and a compressor of a refrigeration system
EP2955377A4 (en) * 2013-02-08 2017-02-15 Hitachi Industrial Equipment Systems Co., Ltd. Fluid compression system and control device therefor
WO2021124087A1 (en) * 2019-12-17 2021-06-24 Officine Mario Dorin S.P.A. Multi-cylinder reciprocating compressor
US11137170B2 (en) 2016-11-11 2021-10-05 Carrier Corporation Heat pump system and start up control method thereof

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Publication number Priority date Publication date Assignee Title
DE102012107183B4 (de) 2012-08-06 2016-08-04 Kriwan Industrie-Elektronik Gmbh Verfahren zur Regelung eines Verdichters einer Kälteanlage sowie eine Kälteanlage
EP2904336A2 (de) 2012-08-06 2015-08-12 Kriwan Industrie-Elektronik GmbH Verfahren zur regelung eines verdichters einer kälteanlage sowie eine kälteanlage
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
DE102020103975A1 (de) 2020-02-14 2021-08-19 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichter
DE102020118740A1 (de) * 2020-07-15 2022-01-20 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichter
DE102021117724A1 (de) * 2021-07-08 2023-01-12 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichterverbund

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ATE371111T1 (de) 2007-09-15
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