CN101156029A - Refrigerant system with variable speed compressor in tandem compressor application - Google Patents

Refrigerant system with variable speed compressor in tandem compressor application Download PDF

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Publication number
CN101156029A
CN101156029A CNA2006800111652A CN200680011165A CN101156029A CN 101156029 A CN101156029 A CN 101156029A CN A2006800111652 A CNA2006800111652 A CN A2006800111652A CN 200680011165 A CN200680011165 A CN 200680011165A CN 101156029 A CN101156029 A CN 101156029A
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CN
China
Prior art keywords
compressor
compressors
refrigeration system
variable speed
speed drive
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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.)
Pending
Application number
CNA2006800111652A
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Chinese (zh)
Inventor
A·利夫森
M·F·塔拉斯
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Carrier Corp
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Carrier Corp
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Publication of CN101156029A publication Critical patent/CN101156029A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/026—Compressor control by controlling unloaders
    • F25B2600/0261—Compressor control by controlling unloaders external to the compressor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

A refrigerant system is provided with tandem compressors. As is known, tandem compressors operate in parallel to provide a refrigerant system designer with the ability to achieve a stepped capacity control of the refrigerant system. At least one of the tandem compressors is provided with a variable speed drive. Further, at least one of the tandem compressors may be provided with the economizer and/or unloader functions. System configurations with multiple compression stages and multiple injection ports are disclosed. In this manner, the stepless capacity control can be achieved.

Description

Refrigeration system with the speed changeable compressor in the tandem compressor applications
Technical field
The present invention relates to a kind of variable speed machine that is used for drive installation to the compressor of refrigeration system with tandem compressor.
Background technology
In many air conditionings and heat pump applications, all adopt refrigeration system to cool off and/or the heating environment air.The cooling or the heating load of environment become with ambient conditions, and the variation of and/or humidity level temperature required with the building occupant changes.
In some refrigeration system, adopt single compressor to come compressed refrigerant and the indoor and outdoor heat exchanger of mobile cold-producing medium in closure by circulating and connecting.Yet in many cases, hope can change capacity or the cooling that refrigeration system provides or add heat.Therefore, known refrigeration system is provided with tandem compressor.Tandem compressor comes down at least two compressors of parallel running, wherein interconnects these compressors through shared sucking pump and/or discharge manifold.For example, the controller that is used for double compressor system activates two compressors or one of them compressor.These two compressors have different size, and distinct capacity (capacity) level is provided during partial load run.Refrigeration system with tandem compressor is not to have single capacitance grade, but has several discrete capacitance grades.
In the prior art, control device is by sequencing, thereby activates tandem compressor alternatively.Yet the volume controlled that is provided by tandem compressor increases or reduces by big discrete step.Wish can the improvement system control capacity so that can be between these discrete steps the change capacity, thereby the accurate external loading demand of the broad range of match ambient conditions as well.
Adopt variable speed drive to drive that the compressor of variable-ratio is a common practise in the refrigeration system.By with higher speed or than the driven at low speed compressor, the amount of compressed cold-producing medium of unit interval changes, therefore can the regulating system capacity.
In comprising the refrigeration system of tandem compressor, also do not adopt variable speed drive, wherein, drive the tandem compressor of selected quantity by variable speed drive in order to change the power system capacity that control is conditioned temperature and humidity grade in the space.
Summary of the invention
In disclosed embodiment of the present invention, at least one compressor in having the refrigeration system of tandem compressor variable speed is set.By this compressor of selective use, can be implemented in the capacity regulating between the discrete step that tandem compressor operation provides.
Control device identification expectation cooling capacity, then, realize this expected capacity by following steps: at first, in the most effective and reliable mode, the activation tandem compressor is with accurately near desired volume.Then, increment changes the speed of this at least one compressor with variable-ratio function.Monitor this capacity then.When the required grade of final realization, then move this at least one compressor with this new speed.If this capacity still needs to regulate, this speed of incremental adjustments once more then, and the condition that produces of monitoring once more.
In the disclosed embodiment, one of them tandem compressor is provided with variable speed drive, and another tandem compressor does not have.In other embodiments, two compressors all are provided with variable speed drive.
The disclosed embodiments are attached to legend with economizer cycle and emptier circulation with variable speed drive.
By following explanation and accompanying drawing, can best understanding these and other features of the present invention, be description of drawings below.
Description of drawings
Fig. 1 illustrates the refrigeration system of first embodiment.
Figure 1A illustrates other possible circuit diagrams.
Figure 1B illustrates other possible circuit diagrams.
Fig. 1 C illustrates other possible circuit diagrams.
Fig. 2 illustrates the refrigeration system of second embodiment.
The volume controlled that is provided by prior art is provided Fig. 3.
Fig. 4 illustrates by volume controlled provided by the invention.
Fig. 5 is the flow chart according to control algolithm of the present invention.
The specific embodiment
Refrigeration system 20 shown in Figure 1.Compressor 22 is provided with variable speed drive 24.Second compressor 26 is not provided with variable speed drive, and it moves in conjunction with compressor 22.As shown in the figure, shut-off valve 28 makes compressor 26 be isolated from discharge manifold, and the control device that is used for system only need should determine compressor 22 just can realize to constant volume.As everyone knows, compressor 22 and 26 transmits cold-producing medium to common discharge line 30, and this common discharge line causes condenser 32.Though this system 20 should be understood that as air-conditioning system the present invention can also be applied to heat pump and cooler.
As everyone knows, these two compressors 22 and 26 preferably are provided with distinct capacity, so that can realize the change of total levels of capacity by operation one or two in compressor 22 and 26.In this case, select greater or lesser compressor whether to be provided with variable speed drive by the judgement of system designer.This selection will be decided according to many factors, include, but is not limited to application demand, cost, running efficiency of system or the like.Expansion gear 34 is arranged on the downstream of condenser 32, and evaporimeter 36 is arranged on the downstream of expansion gear 34.Common suction line 38 causes discrete absorption line 39, so that cold-producing medium is turned back to compressor 22 and 26.
As shown in the figure, in the schematic diagram of Fig. 1, has energy-saving device circuit.Economizer heat exchanger 40 receives branched-refrigerant from the line 42 by economizer expansion device 44.As everyone knows, by branched-refrigerant is passed through expansion gear 44, its pressure and temperature can reduce.Therefore, in economizer heat exchanger 40, this branched-refrigerant is the cold-producing medium in the cooling liquid main line 45 again, and wherein this main liquid line is also by economizer heat exchanger 40.Economizer function is a general knowledge known in this field, and the capacity and/or the efficient that can increase refrigeration system 20.
As shown in the figure, at least one compressor, be depicted as compressor 22 here, this branched-refrigerant warp 46 turns back to intermediate compression point 48.Flow through economizer heat exchanger 40 though the cold-producing medium in the branch line 42 is depicted as the edge direction identical with the cold-producing medium of main liquid line 45, should be understood that, in a preferred embodiment, in fact two fluids can be in the opposite direction fluidic structures.
In bypass line 50 was also contained in, it made a part from the cold-producing medium of the intermediate compression point in the compressor 22 48 turn back to absorb line 39.When hope has the unloading operation, Open valve 52, simultaneously preferred (but not necessarily) closes expansion gear 44.In this way, will turn back to absorption line 39, therefore offloading functions will be provided by compressor 22 part refrigerant compressed.
Should be understood that, this energy-saving compressor 22 have more than an injection port 48 with more than a relevant economizer heat exchanger 40.And well-known, this economizer heat exchanger arrangement can be flashed jar next substituting.And, can adopt multi-stage compression system, substitute single energy-saving compressor.In this compound compressor system, can utilize variable speed drive that one or more levels are provided.
As shown in the figure, motor 200 is connected to fan, and this fan is used to agitate air to pass through condenser 32 and evaporimeter 36 tops.One of them motor 200 or other motor 200 can be provided with variable speed drive 202.Those skilled in the art will appreciate that when variable-ratio control fan or for example during the miscellaneous part of secondary circuit pump, wish to be provided with the motor that is connected to refrigeration system.
Figure 1A illustrates another circuit Figure 100, wherein substitutes for example compressor 22 of one of them compressor by two compressor stages 104 and 106.Though two compressor stages 104 shown in the figure and 106 all are connected to variable speed drive 102, also can only have a level to be connected thereto.As shown in the figure, the loop line 108 that begins from economizer heat exchanger extends between two levels simply, rather than extends in the discharge chambe in one of them grade.
Figure 1B illustrates another embodiment 110, and three compressor stages 112,114 and 116 are wherein arranged.Variable speed drive 118 control is two levels 114 and 116 wherein.Each level is connected to unloader valve 120 as shown in the figure.Two independent economizer heat exchanger 122 selectivity transmit refrigerant through lines 124 and get back to point between the compressor stage.Well known to those skilled in the artly be to require to select a plurality of compressor stages a plurality of compressor stages and the particular location thereof of variable-ratio operation (and with), a plurality of unloader valve and a plurality of economizer heat exchanger according to designer's wish and concrete application scenario.
Fig. 1 C illustrates another embodiment 130, wherein provides first order compressor by a pair of a pair of tandem compressor 134 and 136 that advances to be fed to second compressor stage 138.As shown in the figure, intermediate pressure refrigerant return line 140 is extended between these levels.Variable speed drive 132 only is connected to compressor 134.Certainly, many other legends all fall within the scope of the present invention, and include, but is not limited to the tandem and the speed changeable compressor of variable number.
Fig. 2 illustrates another different embodiment 60, wherein substitutes two tandem compressors by one group of four compressor.As shown in the figure, compressor 64 is provided with variable speed drive 62.Shut-off valve 66 is arranged on the takeoff line of three compressors 64,68 and 70, isolates these compressors when they are stopped by system's control with box lunch.Common discharge manifold 72 causes condenser 74, expansion gear 76 and evaporimeter 78.The control device that is used for refrigeration system 60 is used for variable-ratio this two compressors 64 that move, and these two compressors 68 and 70 are issued to expected capacity at fixed speed.
The control device that is used for each refrigeration system 20 and 60 can be discerned required cooling capacity, and operation tandem compressor and/or energy-saving appliance, and moves unloader functions as required.Therefore, as shown in Figure 3, be attached to Fig. 1 legend and do not have the prior art systems of variable speed drive that at least three volume controlled level A, B and A+B can be provided.In fact, legend shown in Figure 1 can have even be more multistage, because the operation of unloader valve and economizer function can provide additional capacity steps.Yet in order to understand remaining content of the present invention, the simplified illustration of Fig. 3 can be satisfied the demand.The some numerical value that exist prior art systems not provide between numerical value A, B and A+B can be provided.The too simple version of this system that Here it is is certainly understood good basis of the present invention but this can not provide.The embodiment of Fig. 2 can also obtain many other grades of volume controlled.
Fig. 3 and 4 is too simple versions of Fig. 1 embodiment, and capacitance grade can be provided.As mentioned above, by operation unloader valve and economizer function, can realize additional capacity steps.Yet the compressor (for example, compressor 26) that the control device of this system can move less than compressor 22 provides grade A.Can move another compressor 22 grade B is provided, wherein compressor 26 be stopped.By moving two compressors 22 and 26, can realize grade A+B.In each grade,, can realize the inclined-plane R that the A of class, B or A+B are above therein by increasing the drive motors speed of compressor 22.On the other hand, by reducing this speed, reverse situation can take place, promptly begin to move down the inclined-plane from these numerical value.Usually make based on required amount of cooling water, efficient and reliability consideration with the handover decisions that moves to different operational modes in compressor speed adjustment.For example, the operation compressor can be dangerous under specific speed, because the lubrication deficiency between the compressor part.On the other hand, and switch to the energy-saving appliance operational mode and compare, the efficient of operation compressor is lower under fair speed relatively.
Fig. 5 illustrates and utilizes standard variable speed machine well known in the art control how typically to realize these inclined-planes.Inclined-plane R shown in Figure 4 is a simple version too.In fact, this control procedure is carried out in incremental steps usually, the operation of monitoring refrigerant circulation after increment changes then.Therefore, have a plurality of steps along each inclined-plane R and change, rather than infinite a plurality of variation is arranged as shown in Figure 4.Yet Fig. 4 has set forth the process how the present invention provides the capacity of variation really well.
Notice, can be in conjunction with also being that for example fan or pump are used the variable-ratio tandem compressor with the other system parts of variable-ratio operation.
Though disclose the preferred embodiments of the present invention, those skilled in the art will appreciate that some modification also falls within the scope of the present invention.For this reason, following claim should limit true scope of the present invention and content.

Claims (20)

1. refrigeration system comprises:
At least two tandem compressors of parallel running, wherein at least one compressor has variable speed drive, is used to change the speed of described at least one compressor;
Be arranged on the condenser in downstream of described compressor and the evaporimeter that is arranged on described condenser downstream; And
The control device that is used for the described speed of described at least one compressor of selectively changing.
2. refrigeration system according to claim 1, economizer heat exchanger wherein is set in the middle of described condenser and described evaporimeter, described economizer heat exchanger selectivity receives branched-refrigerant, cross the main flow of refrigerant of described economizer heat exchanger with cool stream again, and described branched-refrigerant turns back at least one compressor, and described control device operationally changes the speed of described at least one compressor, changes with the volume controlled between the grade that is provided at the described economizer heat exchanger of operation and the grade of not moving described economizer heat exchanger.
3. refrigeration system according to claim 2 wherein is provided with a plurality of Centronics ports, and wherein said branched-refrigerant turns back to described at least one described compressor through described Centronics port.
4. refrigeration system according to claim 1, wherein at least one described tandem compressor is provided by compound compressor.
5. refrigeration system according to claim 1, wherein said control device change the described speed of described at least one compressor in incremental steps.
6. refrigeration system according to claim 1, at least one in wherein said at least two compressors is provided with unloader functions.
7. refrigeration system according to claim 1, at least one in wherein said at least two compressors is not provided with variable speed drive.
8. refrigeration system according to claim 1, wherein said at least two compressors are to have more than two, and at least two described compressors are provided with variable speed drive.
9. refrigeration system according to claim 1, the fan or the pump that wherein are connected to miscellaneous part except that compressor also are provided with variable speed drive.
10. refrigeration system according to claim 1, wherein said at least two compressors have different capabilities.
11. a method of controlling refrigeration system may further comprise the steps:
(1) provides at least two tandem compressors of parallel running, wherein at least one compressor has variable speed drive, be used to change the speed of described at least one compressor, condenser that is positioned at described compressor downstream and the evaporimeter that is positioned at described condenser downstream are provided, and provide control device, the described speed that is used for described at least one compressor of selectively changing is to realize the variation grades of volume controlled; And
(2) determine desired volume, and move one of them or another of described at least two compressors or two, and the speed that changes described at least one compressor, to realize described definite expected capacity.
12. method according to claim 11 wherein utilizes refrigeration system that economizer function is provided, and the expected capacity of performing step 2 if desired, the described economizer function of selective activation then is to provide additional capacity or to increase operational efficiency.
13. method according to claim 12, wherein the cold-producing medium from corresponding economizer heat exchanger turns back to a plurality of ports that are associated with described at least two tandem compressors.
14. method according to claim 11, at least one in wherein said at least two compressors provided by compound compressor.
15. method according to claim 11, wherein said control device change the described speed of described at least one compressor in incremental steps.
16. method according to claim 11 wherein provides unloader functions, to unload at least one in described at least two compressors, with the expected capacity of performing step 2.
17. method according to claim 11, at least one in wherein said at least two compressors is not provided with variable speed drive.
18. method according to claim 11, wherein said at least two compressors are to have more than two, and at least two described compressors are provided with variable speed drive, and described control device changes the speed of the compressor of described at least two variable speed drive.
19. method according to claim 11, wherein said at least two compressors are provided with different capabilities.
20. method according to claim 11, at least one fan or the pump that wherein are connected to another parts in the described refrigeration system are provided with variable speed drive.
CNA2006800111652A 2005-04-07 2006-02-14 Refrigerant system with variable speed compressor in tandem compressor application Pending CN101156029A (en)

Applications Claiming Priority (2)

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US11/101,347 2005-04-07
US11/101,347 US20060225445A1 (en) 2005-04-07 2005-04-07 Refrigerant system with variable speed compressor in tandem compressor application

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CN101156029A true CN101156029A (en) 2008-04-02

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EP (1) EP1866576A4 (en)
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CA (1) CA2598706A1 (en)
WO (1) WO2006110209A2 (en)

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* Cited by examiner, † Cited by third party
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US7793509B2 (en) * 2004-04-12 2010-09-14 Johnson Controls Technology Company System and method for capacity control in a multiple compressor chiller system
US7628027B2 (en) * 2005-07-19 2009-12-08 Hussmann Corporation Refrigeration system with mechanical subcooling
US20070187086A1 (en) * 2006-02-14 2007-08-16 Anatoly Nikolayevich Ivanov Device for cutting slot-shaped seats in wells by hydro-sandblasting method
US9746218B2 (en) * 2006-10-26 2017-08-29 Johnson Controls Technology Company Economized refrigeration system
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DE102007003464B4 (en) * 2007-01-24 2012-10-18 Technotrans Ag Cooling device for printing machines
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WO2008130412A1 (en) * 2007-04-23 2008-10-30 Carrier Corporation Co2 refrigerant system with booster circuit
JP2010525294A (en) * 2007-04-24 2010-07-22 キャリア コーポレイション Refrigerant vapor compression system with two-line economizer circuit
CN101809378B (en) * 2007-09-24 2014-06-25 开利公司 Refrigerant system with bypass line and dedicated economized flow compression chamber
US20110094259A1 (en) * 2007-10-10 2011-04-28 Alexander Lifson Multi-stage refrigerant system with different compressor types
US20110214439A1 (en) * 2007-10-10 2011-09-08 Alexander Lifson Tandem compressor of different types
US20090217679A1 (en) * 2008-02-28 2009-09-03 Optidyn Inc. Refrigeration cooling system control
US20090241595A1 (en) * 2008-03-27 2009-10-01 Praxair Technology, Inc. Distillation method and apparatus
US20110030397A1 (en) * 2008-06-13 2011-02-10 Taras Michael F Start-up procedure for refrigerant systems having microchemical consensor and reheat cycle
US20110079032A1 (en) * 2008-07-09 2011-04-07 Taras Michael F Heat pump with microchannel heat exchangers as both outdoor and reheat exchangers
US8192171B2 (en) * 2009-01-15 2012-06-05 Ingersoll-Rand Company Compressor system
WO2010084552A2 (en) * 2009-01-20 2010-07-29 Panasonic Corporation Refrigeration cycle apparatus
JP5608991B2 (en) * 2009-03-12 2014-10-22 ダイキン工業株式会社 Refrigeration apparatus and operation method thereof
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WO2010135407A2 (en) 2009-05-19 2010-11-25 Carrier Corporation Variable speed compressor
US8011191B2 (en) 2009-09-30 2011-09-06 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
US8011201B2 (en) * 2009-09-30 2011-09-06 Thermo Fisher Scientific (Asheville) Llc Refrigeration system mounted within a deck
US10544801B2 (en) 2009-10-21 2020-01-28 Carrier Corporation Centrifugal compressor part load control algorithm for improved performance
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US9845981B2 (en) 2011-04-19 2017-12-19 Liebert Corporation Load estimator for control of vapor compression cooling system with pumped refrigerant economization
US9316424B2 (en) 2011-04-19 2016-04-19 Liebert Corporation Multi-stage cooling system with tandem compressors and optimized control of sensible cooling and dehumidification
FR2977656B1 (en) * 2011-07-06 2015-07-17 Electricite De France THERMAL EXCHANGE SYSTEM AND METHOD FOR CONTROLLING THERMAL POWER DEVELOPED BY SUCH THERMAL EXCHANGE SYSTEM
US20140151015A1 (en) * 2011-07-26 2014-06-05 Carrier Corporation Termperature Control Logic For Refrigeration System
US8925346B2 (en) 2012-02-07 2015-01-06 Thermo Fisher Scientific (Asheville) Llc High performance freezer having cylindrical cabinet
DE102013200473A1 (en) * 2013-01-15 2014-07-17 Krones Ag Method and device for cooling a fermentation and / or storage tank
US9599118B2 (en) 2013-04-04 2017-03-21 Trane International Inc. System and method for controlling a system that includes fixed speed and variable speed compressors
JP6276004B2 (en) * 2013-11-19 2018-02-07 株式会社Ｎｔｔファシリティーズ refrigerator
US9759468B2 (en) * 2014-03-21 2017-09-12 Lennox Industries Inc. System for controlling operation of an HVAC system having tandem compressors
US10119738B2 (en) 2014-09-26 2018-11-06 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
WO2016182135A1 (en) * 2015-05-11 2016-11-17 Lg Electronics Inc. Refrigerator and control method thereof
US10871314B2 (en) 2016-07-08 2020-12-22 Climate Master, Inc. Heat pump and water heater
US10866002B2 (en) 2016-11-09 2020-12-15 Climate Master, Inc. Hybrid heat pump with improved dehumidification
US10856449B2 (en) * 2016-12-02 2020-12-01 Dell Products L.P. Dynamic cooling system
US10566881B2 (en) 2017-01-27 2020-02-18 Franklin Electric Co., Inc. Motor drive system including removable bypass circuit and/or cooling features
US10495365B2 (en) 2017-03-21 2019-12-03 Lennox Industries Inc. Method and apparatus for balanced fluid distribution in tandem-compressor systems
US10655897B2 (en) 2017-03-21 2020-05-19 Lennox Industries Inc. Method and apparatus for common pressure and oil equalization in multi-compressor systems
US10731901B2 (en) 2017-03-21 2020-08-04 Lennox Industries Inc. Method and apparatus for balanced fluid distribution in multi-compressor systems
US10465937B2 (en) * 2017-08-08 2019-11-05 Lennox Industries Inc. Hybrid tandem compressor system and method of use
US10935260B2 (en) 2017-12-12 2021-03-02 Climate Master, Inc. Heat pump with dehumidification
EP3781883A1 (en) * 2018-04-16 2021-02-24 Carrier Corporation Dual compressor heat pump
US11397034B2 (en) 2018-06-27 2022-07-26 Carrier Corporation Unloading system for variable speed compressor
US11592215B2 (en) 2018-08-29 2023-02-28 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
CA3081986A1 (en) 2019-07-15 2021-01-15 Climate Master, Inc. Air conditioning system with capacity control and controlled hot water generation
CN110356283B (en) * 2019-07-31 2022-07-08 重庆长安汽车股份有限公司 Thermal management system of vehicle power battery
US11131491B1 (en) 2020-08-07 2021-09-28 Emerson Climate Technologies, Inc. Systems and methods for multi-stage operation of a compressor
US11994135B2 (en) * 2021-06-14 2024-05-28 Air Products And Chemicals, Inc. Method and apparatus for compressing a gas feed with a variable flow rate
US11906188B2 (en) * 2022-03-11 2024-02-20 Johnson Controls Tyco IP Holdings LLP Energy efficient heat pump systems and methods

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2246244A (en) * 1940-06-19 1941-06-17 York Ice Machinery Corp Refrigeration
US3250931A (en) * 1962-12-31 1966-05-10 James A Hardman Piston-ported volume displacement means accommodating multiple, work effecting components
US4951475A (en) * 1979-07-31 1990-08-28 Altech Controls Corp. Method and apparatus for controlling capacity of a multiple-stage cooling system
US5265434A (en) * 1979-07-31 1993-11-30 Alsenz Richard H Method and apparatus for controlling capacity of a multiple-stage cooling system
US4947655A (en) * 1984-01-11 1990-08-14 Copeland Corporation Refrigeration system
US4748820A (en) * 1984-01-11 1988-06-07 Copeland Corporation Refrigeration system
US4787211A (en) * 1984-07-30 1988-11-29 Copeland Corporation Refrigeration system
US4895005A (en) * 1988-12-29 1990-01-23 York International Corporation Motor terminal box mounted solid state starter
US5927088A (en) * 1996-02-27 1999-07-27 Shaw; David N. Boosted air source heat pump
DE19620105A1 (en) * 1996-04-23 1997-10-30 Bruno Pfurtscheller Operation of refrigerating plant
JP3680619B2 (en) * 1999-03-10 2005-08-10 株式会社日立製作所 Refrigeration equipment
JP3629587B2 (en) * 2000-02-14 2005-03-16 株式会社日立製作所 Air conditioner, outdoor unit and refrigeration system
US6516622B1 (en) * 2000-06-13 2003-02-11 Belair Technologies, Llc Method and apparatus for variable frequency controlled compressor and fan
DE10118444A1 (en) * 2001-04-12 2002-10-17 Linde Ag Compressor set and method for regulating a compressor set
US6434960B1 (en) * 2001-07-02 2002-08-20 Carrier Corporation Variable speed drive chiller system
JP2003129956A (en) * 2001-10-22 2003-05-08 Toyota Industries Corp Variable displacement compressor, air conditioner provided with the same, and capacity control method in the same
US6659726B2 (en) * 2001-12-31 2003-12-09 Carrier Corporation Variable speed control of multiple motors
KR100471442B1 (en) * 2002-07-03 2005-03-08 엘지전자 주식회사 Control Method of air-conditioner using multi-compressors
JP4214021B2 (en) * 2003-08-20 2009-01-28 ヤンマー株式会社 Engine heat pump
US6883341B1 (en) * 2003-11-10 2005-04-26 Carrier Corporation Compressor with unloader valve between economizer line and evaporator inlet
US6928828B1 (en) * 2004-01-22 2005-08-16 Carrier Corporation Tandem compressors with economized operation
US7096681B2 (en) * 2004-02-27 2006-08-29 York International Corporation System and method for variable speed operation of a screw compressor
US6973797B2 (en) * 2004-05-10 2005-12-13 York International Corporation Capacity control for economizer refrigeration systems

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103038146A (en) * 2010-07-09 2013-04-10 德国基依埃制冷股份有限公司 Refrigeration system for cooling a container
CN103038146B (en) * 2010-07-09 2015-01-07 德国基依埃制冷股份有限公司 Refrigeration system for cooling a container
CN103884125A (en) * 2011-04-19 2014-06-25 力博特公司 Cooling system
CN103884125B (en) * 2011-04-19 2016-05-25 力博特公司 Cooling system
CN103635763A (en) * 2011-05-16 2014-03-12 开利公司 Multi-compressor refrigeration system
CN104819607A (en) * 2015-05-12 2015-08-05 广东美的暖通设备有限公司 Refrigerating system, refrigerant control method and device and air conditioner
CN104819607B (en) * 2015-05-12 2017-04-12 广东美的暖通设备有限公司 Refrigerating system, refrigerant control method and device and air conditioner

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