US20110094248A1 - Refrigerant System and Method of Operating the Same - Google Patents

Refrigerant System and Method of Operating the Same Download PDF

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Publication number
US20110094248A1
US20110094248A1 US12/997,938 US99793807A US2011094248A1 US 20110094248 A1 US20110094248 A1 US 20110094248A1 US 99793807 A US99793807 A US 99793807A US 2011094248 A1 US2011094248 A1 US 2011094248A1
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United States
Prior art keywords
refrigerant
economizer
refrigerant circuit
bypass
circuit
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Abandoned
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US12/997,938
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English (en)
Inventor
Michael F. Taras
Alexander Lifson
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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, TARAS, MICHAEL F.
Publication of US20110094248A1 publication Critical patent/US20110094248A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • 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
    • F25B2600/026—Compressor control by controlling unloaders
    • F25B2600/0261—Compressor control by controlling unloaders external to the 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass 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

  • This disclosure relates to refrigerant systems. More particularly, this disclosure relates to refrigerant systems having economizer circuits and methods of operating such refrigerant systems.
  • refrigerant systems are utilized to control the temperature and humidity of air in various environments to be conditioned.
  • refrigerant systems include a refrigerant that is compressed in a compressor and delivered to a heat rejection heat exchanger.
  • the heat rejection heat exchanger is a condenser for subcritical applications and a gas cooler for transcritical applications, for simplicity, it will be referred to as a condenser throughout the disclosure.
  • the condenser heat is exchanged between outside ambient air (or other cooling media) and the refrigerant.
  • the refrigerant passes to an expansion device, in which the refrigerant is expanded to a lower pressure and temperature, and is then passed through an evaporator.
  • the evaporator In the evaporator, heat is exchanged between the refrigerant and the indoor air, which is delivered into the environment to be conditioned.
  • the evaporator cools the air that is being supplied to the conditioned environment.
  • moisture is also taken out of the air. In this manner, the humidity level of the air can also be controlled.
  • Enhancement of system efficiency is one of the foremost concerns in the air conditioning and refrigeration industry.
  • One of the options available to the refrigerant system designer to increase system efficiency is a so-called economizer cycle.
  • the economizer circuit When the economizer circuit is activated, at least a portion of the refrigerant flowing from the condenser is tapped and passed through an economizer expansion device and then to an economizer heat exchanger. This tapped refrigerant cools a main refrigerant flow that also passes through the economizer heat exchanger.
  • the tapped refrigerant leaves the economizer heat exchanger usually in a vapor state and is injected back into the compressor at an intermediate compression point.
  • the main refrigerant is additionally cooled after passing through the economizer heat exchanger and then flown through a main expansion device and to the evaporator.
  • This main refrigerant flow will provide a higher capacity and/or efficiency, due to extra cooling obtained in the economizer heat exchanger.
  • An economizer circuit thus provides enhanced system performance characteristics.
  • the economizer flow can be tapped from the main refrigerant flow downstream (instead of upstream) of the economizer heat exchanger.
  • a flash tank essentially representing a 100% effective economizer heat exchanger, may be utilized instead to provide similar functionality.
  • many refrigerant systems may be equipped with the unloading features.
  • one of such unloading options available for economized refrigerant systems is a bypass unloading, when at least a portion of partially compressed refrigerant is bypassed from an intermediate compression point to the compressor suction.
  • many current economized refrigerant systems, and especially the systems incorporating unloading functionality require extra refrigerant cycle and control hardware, which add to the cost and complexity of the refrigerant systems utilizing such circuits.
  • the cost and complexity of prior art economized refrigerant systems make it difficult and expensive to retrofit existing refrigerant systems with economizer circuits.
  • the present disclosure provides a refrigerant system.
  • the refrigerant system comprises a compressor having a suction port and an intermediate port, a main refrigerant circuit, an economizer refrigerant circuit, a bypass refrigerant circuit, and a refrigerant flow control device.
  • the refrigerant flow control device has at least two positions, with a first position providing fluid communication between the economizer refrigerant circuit and at least one of the suction compressor port and the intermediate compressor port, during an economized mode of operation. A second position provides fluid communication between the intermediate port and the suction port through the bypass refrigerant circuit, during a bypass mode of operation.
  • the refrigerant flow control device may have a third position, at least partially isolating the economizer refrigerant circuit and the bypass refrigerant circuit from the main refrigerant circuit, during a normal mode of operation.
  • the compressor may be a single compression device, or a pair of compressors connected in sequence, so that the discharge port of the first compression stage is connected to a suction port of the second compression stage. In the latter case, the intermediate compressor port is a point on the refrigerant line connecting the two compression stages.
  • the present disclosure also provides a method for operating a refrigerant system.
  • the method comprises: selectively controlling a single refrigerant flow control device to provide the refrigerant flow through the economizer circuit, during an economized mode of operation of the refrigerant system, and to provide the refrigerant flow through the bypass circuit, during a bypass mode of operation of the refrigerant system.
  • the method may include an additional step of controlling the same refrigerant flow control device to provide the refrigerant flow through the main refrigeration circuit, and not through the economizer refrigerant circuit or bypass refrigerant circuit, during a normal mode of operation of the refrigerant system.
  • FIG. 1 shows a schematic drawing of a refrigerant system according to the present disclosure
  • FIG. 2 shows a schematic drawing of a second embodiment of a refrigerant system according to the present disclosure.
  • Refrigerant system 10 has a refrigerant flow control device 12 which is in communication with a controller 14 .
  • Controller 14 may be a main controller for refrigerant system 10 , or a separate auxiliary controller.
  • flow control device 12 is a three-way valve and is controlled by controller 14 to selectively place a main refrigeration circuit 16 in fluid communication with an economizer refrigerant circuit 18 or a bypass refrigerant circuit 20 .
  • Flow control device 12 may have an additional position to isolate main refrigerant circuit 16 from economizer refrigerant circuit 18 and bypass refrigerant circuit 20 .
  • Refrigerant flow control device 12 may regulate the flow of a refrigerant (not shown) through economizer refrigerant circuit 18 and/or bypass refrigerant circuit 20 , with either modulated or pulsed methods of control. Flow control device 12 may also mix refrigerant flows from the economizer refrigerant circuit 18 and the bypass refrigerant circuit 20 in various proportions in a single refrigerant stream.
  • refrigerant system 10 advantageously has a single refrigerant flow control device 12 to provide at least two modes of operation for the refrigerant system 10 : an economized mode of operation and an unloaded mode of operation, unlike currently available refrigerant systems that require at least two refrigerant flow control devices.
  • refrigerant flow control device 12 only occupies a single output (not shown) of controller 14 , unlike the two or more outputs required by conventional refrigerant systems having more than one refrigerant flow control device.
  • the refrigerant system 10 of the present disclosure is less complex and less expensive to implement.
  • the present disclosure due to the use of a single refrigerant flow control device 12 , allows existing refrigerant systems to be more easily retrofitted with economizer refrigerant circuit 18 and bypass refrigerant circuit 20 than currently available equipment.
  • Main refrigeration circuit 16 includes a compressor 22 , a condenser 24 , a main expansion device 26 , and an evaporator 28 in serial fluid communication with one another.
  • controller 14 controls flow control device 12 to a first position (not shown) such that refrigerant from main refrigeration circuit 16 is isolated from both economizer refrigerant circuit 18 and bypass refrigerant circuit 20 .
  • compressor 22 drives refrigerant through discharge refrigerant line 30 to condenser 24 , from condenser 24 through liquid refrigerant line 32 to main expansion device 26 , from main expansion device 26 to evaporator 28 , and from evaporator 28 through suction refrigerant line 36 and back to compressor 22 .
  • Condenser 24 is in a heat exchange relationship with outside air 38
  • evaporator 28 is in a heat exchange relationship with a fluid to be conditioned 40 , such as air delivered to a climate-controlled space.
  • other cooling media such as, for example, circulating water or a glycol solution
  • refrigerant flow control device 12 may have an optional position to provide a refrigerant flow through main refrigeration circuit 16 , and to isolate this main refrigerant circuit 16 from economizer refrigerant circuit 18 and bypass refrigerant circuit 20 , during a normal mode of operation of the refrigerant system 10 .
  • refrigerant system 10 comprises performance-enhancing economizer refrigerant circuit 18 .
  • Economizer refrigerant circuit 18 includes an economizer expansion device 42 and an economizer heat exchanger 44 .
  • economizer expansion device 42 is in fluid communication with a liquid refrigerant line 32 of main refrigerant circuit 16 via a tap refrigerant line 46 .
  • economizer heat exchanger 44 is in serial fluid communication with expansion device 42 , which is in turn in serial fluid communication with refrigerant flow control device 12 , via an economizer refrigerant line 50 .
  • flow control device 12 is also fluidly connected to an intermediate compressor port 56 via an intermediate pressure refrigerant line 58 .
  • Flow control device 12 can be controlled to a second position by controller 14 to place economizer refrigerant circuit 18 in fluid communication with main refrigerant circuit 16 , so that at least a portion of refrigerant in main refrigerant circuit 16 flows through economizer refrigerant circuit 18 , and into intermediate port 56 and/or suction port 54 of the compressor 22 .
  • the refrigerant flows through a tap refrigerant line 46 , economizer expansion device 42 , economizer heat exchanger 44 , economizer refrigerant line 50 , and refrigerant flow control device 12 in sequence.
  • controller 14 controls refrigerant flow control device 12 such that an economizer refrigerant flow passes from main refrigerant circuit 16 to economizer circuit 18 , refrigerant system 10 operates in an economized mode, discussed in further detail below.
  • Refrigerant flowing through main refrigerant circuit 16 in liquid refrigerant line 32 also passes through economizer heat exchanger 44 , and is in heat exchange relationship with refrigerant in tap refrigerant line 46 of economizer circuit 18 .
  • refrigerant flowing through tap refrigerant line 46 is expanded in economizer expansion device 42 to a lower pressure and temperature, and used to further cool refrigerant in main refrigerant circuit 16 to enhance the capacity and efficiency of refrigerant system 10 as desired.
  • the two refrigerant streams are shown flowing in the same direction for illustration purposes, in practice, it is advantageous to arrange these flows in a counterflow configuration.
  • refrigerant flow control device 12 may be controlled by controller 14 such that economizer refrigerant line 50 of economizer refrigerant circuit 18 is in serial fluid communication with an intermediate pressure refrigerant line 58 , and/or a bypass refrigerant line 52 .
  • refrigerant flows out of flow control device 12 , and takes one or both of two possible paths.
  • the first path is through intermediate pressure refrigerant line 58 and into intermediate port 56 of compressor 22 .
  • the second path is into bypass refrigerant line 52 , where it combines with the refrigerant flowing in refrigerant suction line 36 and into suction port 54 of compressor 22 .
  • flow control device 12 in the economizer mode of operation, can be selectively controlled so that all of the refrigerant flowing through economizer refrigerant line 50 of economizer circuit 18 flows through intermediate pressure refrigerant line 58 and into intermediate compressor port 56 .
  • Flow control device 12 can also be controlled so that at least a portion of economizer circuit refrigerant in line 50 can be diverted through bypass refrigerant line 52 .
  • the capability of simultaneously providing these two refrigerant flows can be obtained through one of modulating or pulsating techniques.
  • the refrigerant flow control device 12 provides variable size restrictions to the two refrigerant flows, thus simultaneously changing the hydraulic resistances and controlling the amount of refrigerant delivered into the suction and intermediate ports.
  • refrigerant flow control device 12 is rapidly switched from one economized mode of operation to the other.
  • Flow control device 12 can also be controlled to a third position by controller 14 , placing refrigerant system 10 in a bypass unloaded mode of operation.
  • refrigerant flows out of intermediate port 56 of compressor 22 and into bypass refrigerant circuit 20 , i.e. through intermediate pressure refrigerant line 58 and bypass refrigerant line 52 , before merging with the refrigerant in suction refrigerant line 36 and traveling back into suction port 54 of compressor 22 .
  • bypass refrigerant circuit 20 is isolated from economizer refrigerant circuit 18 but is in fluid communication with main refrigerant circuit 16 .
  • refrigerant flow control device 12 can be controlled to regulate refrigerant flow by modulation or pulsation means.
  • Refrigerant flow control device 12 can also have a fourth position, during an economized/bypass mode, which puts the economizer and bypass circuits in fluid communication with each other.
  • the economized refrigerant flow from economizer refrigerant line 50 is combined with the bypass refrigerant flow from intermediate pressure refrigerant line 58 to be routed to bypass refrigerant line 52 .
  • Various flow combinations can be provided by precise positioning of refrigerant flow control device 12 , as will be discussed in further detail below.
  • Refrigerant line 58 can comprise two separate refrigerant lines, and intermediate port 56 of compressor 22 can comprise two separate intermediate ports, so that one of them is used during economized mode of operation, and the other is used during bypass unloaded mode of operation.
  • compressor 22 may be a single compressor unit comprising two sequential compression stages or two compressors connected in sequence with an intermediate port located in between the two compressors.
  • Refrigerant flow control device 12 can be, for instance, of piston or rotary type, where controlling an alignment of valve openings with corresponding refrigerant lines provides a desired mode of operation for refrigerant system 10 .
  • controller 14 can selectively position or adjust refrigerant flow control device 12 accordingly to match the thermal load demands in the conditioned space. For example, at moderate levels of thermal demands, controller 14 can position refrigerant flow control device 12 in the first position as described above, placing refrigerant system 10 in a normal cooling mode of operation. At high levels of thermal demand in the conditioned space and/or at high ambient temperatures, controller 14 can position refrigerant flow control device 12 into the second position described above, placing refrigerant system 10 in an economized mode of operation.
  • refrigerant flow control device 12 can be placed into the third position, operating refrigerant system 10 in a bypass mode.
  • the bypass mode can be advantageous in that at least a portion of the refrigerant in compressor 22 is not compressed fully, thus reducing the amount of work performed by the compressor and improving operational efficiency of refrigerant system 10 .
  • refrigerant flow control device 12 and controller 14 should be capable to provide this functionality.
  • the present disclosure has advantageously disclosed a single refrigerant flow control device 12 providing various combinations of operational modes for refrigerant system 10 at reduced complexity, cost, maintenance and improved reliability.
  • refrigerant system 10 may have at least nine different configurations.
  • refrigerant system 10 in configuration #1, refrigerant system 10 is capable of operating in all of the four modes described above.
  • configuration #2 refrigerant system 10 can operate in normal, bypass, and economizer modes only, and so on.
  • refrigerant system 10 can be customized to the particular needs of a customer and application requirements.
  • refrigerant flow control devices referred to herein as closed include refrigerant flow control devices such as valves which are substantially closed so as to prevent meaningful flow therethrough, such that the circuits containing the valves are substantially inactive
  • refrigerant flow control devices referred to as open include those which are substantially open so as to allow meaningful flow therethrough, such that the circuits containing these refrigerant flow control devices are substantially active.
  • refrigerant system 10 is shown in FIG. 1 , by way of example only, as having tap refrigerant line 46 of economizer circuit 18 selectively taping at least a portion of refrigerant from liquid refrigerant line 32 of main refrigeration circuit 16 upstream of the first refrigerant pass through economizer heat exchanger 44 .
  • economizer circuit 18 it is contemplated by the present disclosure for economizer circuit 18 to be located anywhere in main refrigeration circuit 16 as long as economizer heat exchanger 44 is positioned upstream of main expansion device 26 and downstream of condenser 24 .
  • economizer circuit 18 it is contemplated by the present disclosure for economizer circuit 18 to be located anywhere in main refrigeration circuit 16 as long as economizer heat exchanger 44 is positioned upstream of main expansion device 26 and downstream of condenser 24 .
  • refrigerant system 10 is shown including tap refrigerant line 46 of economizer circuit 18 selectively taping at least a portion of refrigerant from liquid refrigerant line 32 of main refrigeration circuit 16 downstream of the first pass through economizer heat exchanger 44 .
  • tap refrigerant line 46 of economizer circuit 18 selectively taping at least a portion of refrigerant from liquid refrigerant line 32 of main refrigeration circuit 16 downstream of the first pass through economizer heat exchanger 44 .
  • an economizer cycle with a flash tank may be equally utilized as well.
  • compressor types could be used in this invention.
  • scroll, screw, rotary, or reciprocating compressors can be employed.
  • the refrigerant systems that utilize this invention can be used in many different applications, including, but not limited to, air conditioning systems, heat pump systems, marine container units, refrigeration truck-trailer units, and supermarket refrigeration systems.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
US12/997,938 2007-12-20 2007-12-20 Refrigerant System and Method of Operating the Same Abandoned US20110094248A1 (en)

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PCT/US2007/026044 WO2009082367A1 (fr) 2007-12-20 2007-12-20 Système de réfrigérant et son procédé de fonctionnement

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US20140151015A1 (en) * 2011-07-26 2014-06-05 Carrier Corporation Termperature Control Logic For Refrigeration System
US20170191703A1 (en) * 2014-08-21 2017-07-06 Danfoss A/S A pulsation damper for a vapour compression system
US10107536B2 (en) 2009-12-18 2018-10-23 Carrier Corporation Transport refrigeration system and methods for same to address dynamic conditions
US10119738B2 (en) 2014-09-26 2018-11-06 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
WO2020208752A1 (fr) * 2019-04-10 2020-10-15 三菱電機株式会社 Unité extérieure, dispositif à cycle frigorifique et machine frigorifique
US10866002B2 (en) 2016-11-09 2020-12-15 Climate Master, Inc. Hybrid heat pump with improved dehumidification
US10871314B2 (en) 2016-07-08 2020-12-22 Climate Master, Inc. Heat pump and water heater
US10935260B2 (en) 2017-12-12 2021-03-02 Climate Master, Inc. Heat pump with dehumidification
WO2021048898A1 (fr) * 2019-09-09 2021-03-18 三菱電機株式会社 Unité extérieure et dispositif à cycle frigorifique
US11506430B2 (en) 2019-07-15 2022-11-22 Climate Master, Inc. Air conditioning system with capacity control and controlled hot water generation
US11592215B2 (en) 2018-08-29 2023-02-28 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater

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Cited By (25)

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Publication number Priority date Publication date Assignee Title
US10107536B2 (en) 2009-12-18 2018-10-23 Carrier Corporation Transport refrigeration system and methods for same to address dynamic conditions
US20140151015A1 (en) * 2011-07-26 2014-06-05 Carrier Corporation Termperature Control Logic For Refrigeration System
US10612819B2 (en) * 2014-08-21 2020-04-07 Danfoss A/S Pulsation damper for a vapour compression system
US20170191703A1 (en) * 2014-08-21 2017-07-06 Danfoss A/S A pulsation damper for a vapour compression system
US10119738B2 (en) 2014-09-26 2018-11-06 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
US10753661B2 (en) 2014-09-26 2020-08-25 Waterfurnace International, Inc. Air conditioning system with vapor injection compressor
US11927377B2 (en) 2014-09-26 2024-03-12 Waterfurnace International, Inc. Air conditioning system with vapor injection compressor
US11480372B2 (en) 2014-09-26 2022-10-25 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
US11448430B2 (en) 2016-07-08 2022-09-20 Climate Master, Inc. Heat pump and water heater
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
US11435095B2 (en) 2016-11-09 2022-09-06 Climate Master, Inc. Hybrid heat pump with improved dehumidification
US10935260B2 (en) 2017-12-12 2021-03-02 Climate Master, Inc. Heat pump with dehumidification
US11953239B2 (en) 2018-08-29 2024-04-09 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
US11592215B2 (en) 2018-08-29 2023-02-28 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
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EP2286162A4 (fr) 2012-09-12
EP2286162A1 (fr) 2011-02-23

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