US20090288432A1 - Tandem compressors with pulse width modulation suction valve - Google Patents

Tandem compressors with pulse width modulation suction valve Download PDF

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Publication number
US20090288432A1
US20090288432A1 US12/307,631 US30763109A US2009288432A1 US 20090288432 A1 US20090288432 A1 US 20090288432A1 US 30763109 A US30763109 A US 30763109A US 2009288432 A1 US2009288432 A1 US 2009288432A1
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United States
Prior art keywords
refrigerant
compressors
set forth
refrigerant system
compressor
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US12/307,631
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English (en)
Inventor
Alexander Lifson
Michael F. Taras
Mark A. Lifson
George M. Taras
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Carrier Corp
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Carrier Corp
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Assigned to CARRIER CORPORATION reassignment CARRIER CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LIFSON, ALEXANDER, LIFSON, MARK, TARAS, GEORGE M., TARAS, MICHAEL F.
Publication of US20090288432A1 publication Critical patent/US20090288432A1/en
Abandoned legal-status Critical Current

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    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
    • 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
    • F25B2600/025—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
    • F25B2600/25—Control of valves
    • F25B2600/2521—On-off valves controlled by pulse signals

Definitions

  • This application relates to a refrigerant system incorporating tandem compressors and pulse width modulation control on a suction line leading to at least one of the tandem compressors.
  • Refrigerant HVAC&R systems typically include a compressor delivering a compressed refrigerant from a compressor discharge port to a condenser, and then passing the refrigerant from the condenser to an expansion device, an evaporator, and finally back to the compressor suction port throughout a closed-loop circuit.
  • the thermal load demand on the refrigerant system may vary and generally depends on indoor and outdoor operational environments, thermal load generation in a conditioned space and fresh air circulation requirements. At times, there may be a need for a higher system cooling capacity, and hence higher flow of refrigerant circulating throughout the refrigerant system is required. At other times, a lower cooling capacity, and consequently lower refrigerant flow, may be adequate to maintain the conditioned space within the comfort zone.
  • some refrigerant systems utilize tandem compressors to provide unloading capability by switching off one of the tandem compressors to match the system capacity to the thermal load in the conditioned space.
  • two or more compressors may simultaneously deliver a compressed refrigerant to a downstream heat exchanger, such as a condenser.
  • individual discharge lines communicate with the discharge ports of the tandem compressors. These discharge lines are then merged into a single discharge manifold connected to a condenser.
  • individual suction lines communicate with the suction ports of the tandem compressors. These suction lines emerge from a single suction manifold connected to a line extending from the evaporator exit.
  • tandem compressor systems are known, wherein separate condensers are associated with each of the compressors, while the compressors are still connected to the same evaporator.
  • tandem compressor systems may be connected to separate evaporators, while still communicating to the same condenser. The last two configurations are typically utilized when either condensers or evaporators are associated with separate indoor or outdoor environments that may have different operational characteristics.
  • tandem compressor arrangements may include pressure and oil equalization lines to prevent oil pumpout from compressors and improve reliability.
  • One method of providing finer control over the capacity of a refrigerant system is the use of pulse width modulation controls for a refrigerant system compressor.
  • a suction pulse width modulation valve is cycled at a predetermined rate between on and off positions to prevent and then allow the flow of refrigerant to the compressor. Since the valve is cycled between open and closed positions, the throttling or any other losses are practically eliminated. In this manner, the amount of refrigerant compressed by the compressor can be finely tailored to a desired capacity, while maintaining efficient system operation.
  • pulse width modulation controls are known in refrigerant systems, they have not been incorporated into tandem compressor systems.
  • two or more tandem compressors are operated in a refrigerant system.
  • a suction line leading to at least one of two compressors is provided with a suction valve having a pulse width modulation control.
  • the provided capacity of that compressor can be finely tailored to thermal load demands in an environment to be conditioned.
  • only one of the compressors is provided with such a suction valve controlled by pulse width modulation.
  • the suction pulse width modulation valve is provided on a manifold leading to each of the compressors.
  • the compressors may deliver refrigerant to separate condensers, while still connected to a single evaporator, or may receive refrigerant from separate evaporators, while still communicating compressed refrigerant to a single condenser.
  • the tandem compressor refrigerant system may be provided with an economizer cycle and/or a bypass feature to achieve even more flexible control over supplied capacity.
  • FIG. 1 shows a first schematic refrigerant system.
  • FIG. 2 shows a second schematic
  • FIG. 3 shows a third schematic.
  • FIG. 4 shows a fourth schematic.
  • FIG. 5 shows a capacity chart for the FIG. 1 schematic.
  • FIG. 6 shows a fifth schematic.
  • FIG. 7 shows a sixth schematic.
  • FIG. 1 shows a refrigerant system 20 having two compressors 22 and 24 operating in tandem to compress refrigerant and deliver the refrigerant to a common discharge manifold 28 .
  • a single condenser 30 receives refrigerant from the common discharge manifold 28 and delivers that refrigerant to an expansion device 32 .
  • An evaporator 34 is positioned downstream of the expansion device 32 . Refrigerant from the evaporator 34 passes into a common suction manifold 26 and back to the compressors 22 and 24 .
  • a control 38 for the system operates to drive one or both of the compressors 22 and 24 to provide a desired capacity for the refrigerant system 20 .
  • the compressors 22 and 24 can be of the same size, or can be of different sizes.
  • the control and operation of a tandem compressor refrigerant system are, as known in the art, and thus no further description is deemed necessary.
  • What is inventive is the provision of a suction valve 36 having pulse width modulation control by the control 38 , or by a dedicated controller.
  • the control 38 cycles the valve 36 at a predetermined rate between an open (normally fully open position) and closed position (normally either fully closed or nearly closed position) to control the flow of refrigerant to the compressors 22 and 24 .
  • the amount of refrigerant delivered to the compressors 22 and 24 can be finely tailored to achieve precise capacity values, no matter how many compressors are operated at a particular moment of time.
  • the pulse width modulation valve 36 Since the pulse width modulation valve 36 is cycled from an open to closed position, there are minimal throttling or other losses that are associated with the valve 36 .
  • the cycling rate and time interval for the valve 36 to stay in an open position are determined by the capacity to be delivered to a conditioned environment, reliability requirements, allowable comfort zone parameter variations and refrigerant system thermal inertia. While two tandem compressors are shown, refrigerant systems are known with three, four or even higher number of tandem compressors. The present invention thus provides a very powerful and efficient means of achieving a precisely tailored refrigerant system capacity from a tandem compressor configuration, while minimizing temperature and humidity variation in the conditioned space, improving occupant's comfort and reducing power consumption.
  • FIG. 2 shows another embodiment 220 , wherein the tandem compressors 122 and 124 again deliver refrigerant to a common discharge manifold 28 and a downstream condenser 30 .
  • This system configuration is distinct in that the refrigerant branches to two separate expansion devices 132 , and two separate evaporators 134 A and 134 B.
  • Such an arrangement is typically provided when the evaporators are serving different conditioned/refrigerated zones and having different operational characteristics.
  • there is no common suction manifold delivering refrigerant to each of the compressors 122 and 124 .
  • only one of the compressors has a suction pulse width modulated valve 136 , mounted on its suction line leading to that compressor, which is controlled by a pulse width modulation control 138 .
  • the control 138 can be a separate control or integrated into a system control for the refrigerant system 220 .
  • the compressor 122 would be operated, as it is able to provide precise refrigerant flow control by its associated pulse width modulation suction valve 136 .
  • FIG. 3 shows yet another embodiment 221 , wherein each of the compressors 22 and 24 deliver refrigerant to separate condensers 230 and 232 , while still receiving refrigerant from the same evaporator 34 .
  • Such an arrangement would be typically used when the condensers reject heat into different environments (such as, for instance, indoors and outdoors) and have different operational characteristics.
  • the condensers 230 and 232 deliver refrigerant to individual expansion devices 233 , and the refrigerant flows are then combined before returning to the evaporator 34 , and the common suction manifold 26 .
  • a pulse width modulation valve 36 is mounted on the suction line leading to the tandem compressors 22 and 24 and controls refrigerant flow through the refrigerant system 221 , no matter how many compressors are in operation. Similar to the FIG. 2 embodiment, the pulse width modulation valve 36 can be associated with only one of the compressors 22 or 24 and control the refrigerant flow through that particular compressor and an associated condenser, if desired (see further explanation below). Once again, this embodiment can be extended to any number of tandem compressors.
  • FIG. 4 shows a refrigerant system 222 .
  • This system is somewhat similar to the FIG. 1 system; however, the pulse width modulation valve 136 is positioned downstream of the common suction manifold 26 , and on a suction line delivering refrigerant only to the compressor 122 .
  • the pulse width modulation valve 136 is positioned downstream of the common suction manifold 26 , and on a suction line delivering refrigerant only to the compressor 122 .
  • the compressor 122 is capable of providing precise control to the capacity provided by the refrigerant system 222 . Any number of tandem compressors may have the associated pulse width modulated valves in this
  • FIG. 5 A tailored refrigerant system capacity achieved by a pulse width modulation valve of FIG. 1 is illustrated in FIG. 5 .
  • FIG. 5 A tailored refrigerant system capacity achieved by a pulse width modulation valve of FIG. 1 is illustrated in FIG. 5 .
  • two tandem compressors operate together with pulse width modulation valve fully open.
  • the pulse width modulation valve will cycle between open and closed positions. As more capacity reduction is required, the valve would stay in a closed position for longer periods of time than in an open position.
  • the pulse width modulation valve cycle is altered once again to be most of the time in an open position.
  • FIG. 5 illustrates adjustments in the pulse width modulation valve position for schematic shown in FIG. 1 , it can be applied in a similar fashion to other embodiments of this invention as shown in other Figures.
  • FIG. 6 shows enhancement features that can be incorporated into any of the above schematics, in a system 300 .
  • the tandem compressors 302 and 304 are similar to the above embodiments, and the compressor 302 has an associated pulse width modulation valve 303 with a pulse width modulation control 305 . However, even more flexibility in capacity control is provided in this arrangement.
  • a condenser 306 receives refrigerant from the tandem compressors 302 and 304 , and delivers it to a liquid line.
  • a portion of refrigerant is tapped from the liquid line downstream of the condenser 306 , and the tapped refrigerant passes through an economizer expansion device 310 , where it is expanded to a lower pressure and temperature, and into an economizer heat exchanger 312 for the heat transfer interaction with the refrigerant circulating through the main circuit.
  • the refrigerant passing through a tap line 308 subcools the refrigerant in a liquid line 314 flowing into the main expansion device (not shown). This provides a greater thermal potential for the refrigerant entering an evaporator (also, not shown) and consequently enhances refrigerant system cooling capacity and/or efficiency.
  • the use of an economizer cycle is known in the art.
  • the flow from the tap line 308 and the liquid line 314 are shown passing through the economizer heat exchanger 312 in the same direction, this is for illustration simplicity only. In practice, they are preferably flowing in a counterflow arrangement.
  • the refrigerant from the tap line 308 is then flown through a return line 316 , having a shutoff valve 318 , and a vapor injection line 320 .
  • the vapor injection line 320 would inject the returned refrigerant from the line 316 to an intermediate compression point in the economized compressor 302 .
  • the shutoff valve 318 may not be need, if the economizer expansion device 310 is equipped with a shutoff capability.
  • a return line 330 can also return refrigerant to the second compressor 304 , if the compressor 304 is of an economized type as well. It should be noted that the compressors 302 and 304 may not necessarily share the same economizer branch components such as economizer heat exchanger 312 and economizer expansion device 310 .
  • a bypass valve 322 may be opened to selectively bypass at least a portion of partially compressed refrigerant back from the compressor 302 , through the vapor injection line 320 , and a bypass line 324 to a suction line.
  • a bypass function is utilized in a non-economized mode of operation.
  • the compressor 304 may be also equipped with a bypass function. Again, the use of the bypass for compressor unloading is as known in the art.
  • the addition of the bypass and/or economizer function into a tandem compressor system having at least one compressor provided with a pulse width modulation control allows for even more flexible control over the provided capacity.
  • the pulse width modulation technique offers precision control for refrigerant system operation within the economizer stage (when an economizer circuit is engaged) and bypass stage (when the bypass function is activated).
  • superior accuracy control is provided in the conditioned space and efficiency boost in the refrigerant system operation is achieved.
  • more than a single tandem compressor can be equipped with economizer and bypass features (whether or not sharing the economizer branch components such an economizer heat exchanger and economizer expansion device) and associated with the pulse width modulation control.
  • the economizer and bypass function do not need to be combined with each other.
  • only an economizer feature or only a bypass feature can be associated with a particular compressor.
  • each compressor shown in the above Figures can represent a bank of compressors connected together in tandem and providing a nested arrangement.
  • any compressor can be equipped with a pulse width modulated valve.
  • a two-level nested tandem compressor system incorporating two compressor banks 422 and 424 and suction modulation valves 436 , is shown in FIG. 7 .
  • the pulse width modulation valve can be associated with any compressor in the system or with any compressor type, such as a scroll compressor, a rotary compressor, a reciprocating compressor, a screw compressor, etc.
  • the described refrigerant systems can be of a single circuit configuration or can be a part of a multi-circuit arrangement. In multi-circuit configurations, only a single circuit may be equipped with tandem compressors having a suction pulse width modulation valve or multiple circuits may have tandem compressors and an associated suction pulse width modulation valve.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
US12/307,631 2006-08-08 2006-08-08 Tandem compressors with pulse width modulation suction valve Abandoned US20090288432A1 (en)

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PCT/US2006/030884 WO2008018867A1 (en) 2006-08-08 2006-08-08 Tandem compressors with pulse width modulation suction valve

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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100011792A1 (en) * 2006-11-07 2010-01-21 Alexander Lifson Refrigerant system with pulse width modulation control in combination with expansion device control
US20130074534A1 (en) * 2011-09-23 2013-03-28 Lennox Industries Inc. Multi-staged water manifold system for a water source heat pump
US20130098087A1 (en) * 2011-04-19 2013-04-25 Liebert Corporation Cooling system with tandem compressors and electronic expansion valve control
US20130098085A1 (en) * 2011-04-19 2013-04-25 Liebert Corporation High efficiency cooling system
CN103925752A (zh) * 2013-01-10 2014-07-16 海瑞弗机房设备(北京)有限公司 制冷装置和制冷方法
US20140331694A1 (en) * 2013-05-08 2014-11-13 Carrier Corporation Movement of electronic expansion valve
US20150168042A1 (en) * 2013-12-17 2015-06-18 Lennox Industries Inc. Compressor operation management in air conditioners
US20150330688A1 (en) * 2014-05-16 2015-11-19 Lennox Industries Inc. Compressor operation management in air conditioners
US20150330651A1 (en) * 2014-05-15 2015-11-19 Lennox lndustries Inc. Accommodating cssh for tandem compressor transitions
JP2016057005A (ja) * 2014-09-10 2016-04-21 矢崎エナジーシステム株式会社 吸収式冷凍システム
US9845981B2 (en) 2011-04-19 2017-12-19 Liebert Corporation Load estimator for control of vapor compression cooling system with pumped refrigerant economization
US9951984B2 (en) 2013-05-21 2018-04-24 Carrier Corporation Tandem compressor refrigeration system and a method of using the same
US20180135914A1 (en) * 2015-06-18 2018-05-17 Lg Chem, Ltd. Heat recovery apparatus
US10352604B2 (en) * 2016-12-06 2019-07-16 Heatcraft Refrigeration Products Llc System for controlling a refrigeration system with a parallel compressor
US11112050B2 (en) 2011-09-26 2021-09-07 Lennox Industries Inc. Multi-staged water manifold system for a water source heat pump
US11644141B2 (en) 2011-09-26 2023-05-09 Lennox Industries Inc. Controller, method of operating a water source heat pump and a water source heat pump

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BR102015023711A2 (pt) * 2015-09-15 2017-03-21 Whirlpool Sa sistema de refrigeração de múltipla evaporação
CN110296565A (zh) * 2019-07-19 2019-10-01 西安交通大学 一种双蒸发温度制冷系统及其控制方法

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US6206652B1 (en) * 1998-08-25 2001-03-27 Copeland Corporation Compressor capacity modulation
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Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100011792A1 (en) * 2006-11-07 2010-01-21 Alexander Lifson Refrigerant system with pulse width modulation control in combination with expansion device control
US20130098087A1 (en) * 2011-04-19 2013-04-25 Liebert Corporation Cooling system with tandem compressors and electronic expansion valve control
US20130098085A1 (en) * 2011-04-19 2013-04-25 Liebert Corporation High efficiency cooling system
US9980413B2 (en) 2011-04-19 2018-05-22 Liebert Corporation High efficiency cooling system
US8881541B2 (en) * 2011-04-19 2014-11-11 Liebert Corporation Cooling system with tandem compressors and electronic expansion valve control
US9845981B2 (en) 2011-04-19 2017-12-19 Liebert Corporation Load estimator for control of vapor compression cooling system with pumped refrigerant economization
US9038404B2 (en) * 2011-04-19 2015-05-26 Liebert Corporation High efficiency cooling system
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
US10378800B2 (en) * 2011-09-23 2019-08-13 Lennox Industries Inc. Multi-staged water manifold system for a water source heat pump
US20130074534A1 (en) * 2011-09-23 2013-03-28 Lennox Industries Inc. Multi-staged water manifold system for a water source heat pump
US11644141B2 (en) 2011-09-26 2023-05-09 Lennox Industries Inc. Controller, method of operating a water source heat pump and a water source heat pump
US11112050B2 (en) 2011-09-26 2021-09-07 Lennox Industries Inc. Multi-staged water manifold system for a water source heat pump
US11162627B2 (en) * 2011-09-26 2021-11-02 Lennox Industries Inc. Controller, method of operating a water source heat pump and a water source heat pump
CN103925752A (zh) * 2013-01-10 2014-07-16 海瑞弗机房设备(北京)有限公司 制冷装置和制冷方法
US10077929B2 (en) * 2013-05-08 2018-09-18 Carrier Corporation Movement of electronic expansion valve
US20140331694A1 (en) * 2013-05-08 2014-11-13 Carrier Corporation Movement of electronic expansion valve
US9951984B2 (en) 2013-05-21 2018-04-24 Carrier Corporation Tandem compressor refrigeration system and a method of using the same
US9989286B2 (en) * 2013-12-17 2018-06-05 Lennox Industries Inc. Compressor operation management in air conditioners
US20150168042A1 (en) * 2013-12-17 2015-06-18 Lennox Industries Inc. Compressor operation management in air conditioners
US10247460B2 (en) * 2014-05-15 2019-04-02 Lennox Industries Inc. Accommodating CSSH for tandem compressor transitions
US20150330651A1 (en) * 2014-05-15 2015-11-19 Lennox lndustries Inc. Accommodating cssh for tandem compressor transitions
US20150330688A1 (en) * 2014-05-16 2015-11-19 Lennox Industries Inc. Compressor operation management in air conditioners
US9897361B2 (en) * 2014-05-16 2018-02-20 Lennox Industries Inc. Compressor operation management in air conditioners
US9482454B2 (en) * 2014-05-16 2016-11-01 Lennox Industries Inc. Compressor operation management in air conditioners
US20170010032A1 (en) * 2014-05-16 2017-01-12 Lennox Industries Inc. Compressor Operation Management In Air Conditioners
JP2016057005A (ja) * 2014-09-10 2016-04-21 矢崎エナジーシステム株式会社 吸収式冷凍システム
US10591219B2 (en) * 2015-06-18 2020-03-17 Lg Chem, Ltd. Heat recovery apparatus
US20180135914A1 (en) * 2015-06-18 2018-05-17 Lg Chem, Ltd. Heat recovery apparatus
US10352604B2 (en) * 2016-12-06 2019-07-16 Heatcraft Refrigeration Products Llc System for controlling a refrigeration system with a parallel compressor

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WO2008018867A1 (en) 2008-02-14
CN101506595A (zh) 2009-08-12
EP2049848A1 (de) 2009-04-22
EP2049848A4 (de) 2012-02-15

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