EP1983275A1 - Système réfrigérant à compresseur à spirales à plusieurs vitesses et circuit économiseur - Google Patents

Système réfrigérant à compresseur à spirales à plusieurs vitesses et circuit économiseur Download PDF

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Publication number
EP1983275A1
EP1983275A1 EP07251620A EP07251620A EP1983275A1 EP 1983275 A1 EP1983275 A1 EP 1983275A1 EP 07251620 A EP07251620 A EP 07251620A EP 07251620 A EP07251620 A EP 07251620A EP 1983275 A1 EP1983275 A1 EP 1983275A1
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EP
European Patent Office
Prior art keywords
compressor
refrigerant
set forth
economizer
port
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP07251620A
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German (de)
English (en)
Inventor
Alexander Lifson
Michael F. Taras
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Danfoss Scroll Technologies LLC
Original Assignee
Scroll Technologies LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Scroll Technologies LLC filed Critical Scroll Technologies LLC
Priority to EP07251620A priority Critical patent/EP1983275A1/fr
Publication of EP1983275A1 publication Critical patent/EP1983275A1/fr
Ceased 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
    • 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
    • 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
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • 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
    • F25B49/025—Motor 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
    • F25B2400/13—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
    • F25B2600/0252—Compressor control by controlling speed with two speeds
    • 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

Definitions

  • This invention relates to a two-speed scroll compressor that is operable in a refrigerant system with an economizer function and other means of capacity modulation.
  • Refrigerant systems are utilized in many applications to condition an environment.
  • air conditioners and heat pumps are employed to cool and/or heat a secondary fluid such as air entering an environment.
  • the cooling or heating load of the environment may vary with ambient conditions, occupancy level, other changes in sensible and latent load demands, and as the temperature and/or humidity set points are adjusted by an occupant of the building.
  • refrigerant systems can be provided with sophisticated controls, and a number of optional components and features to adjust cooling and/or heating capacity.
  • Known options include the ability to bypass refrigerant which has been at least partially compressed by a compressor back to a suction line. This function is also known as an unloader bypass function. This additional step in operation is taken to reduce system capacity.
  • Another option includes a so-called economizer cycle.
  • a main refrigerant flow heading to an evaporator is subcooled in an economizer heat exchanger.
  • the main refrigerant flow is subcooled by a tapped refrigerant that is expanded to some intermediate pressure and temperature levels and then passed through the economizer heat exchanger.
  • This tapped refrigerant is then returned to a compressor at an intermediate point in the compression cycle.
  • the economizer cycle provides an additional step in operation to vary system capacity by switching between economized and other modes (or steps) of operation.
  • controls can be programmed to optionally actuate any one of these various control functions.
  • the capacity provided by these functions is increased or decreased in relatively large discrete steps. It would be desirable to provide the ability to vary the capacity while the system is running at any of the above described modes of operation, in order to more closely match external load demands.
  • Motor drives are known for driving compressors at two speeds in a refrigerant system. By driving the compressor at a higher or lower speed, the amount of refrigerant that is compressed and circulated throughout the system changes, and thus the system capacity can be changed accordingly.
  • a scroll compressor In a scroll compressor, a pair of scroll members orbits relative to each other to compress an entrapped refrigerant.
  • One design configuration of a scroll compressor utilizes both economizer and various unloader functions. Further, this scroll compressor may employ a single intermediate port to provide both functions alternatively or simultaneously. This scroll compressor is disclosed in United States Patent Application 5,996,364 .
  • scroll compressors have not been utilized in combination with a two-speed drive for its motor and an economizer cycle to obtain additional flexibility in system operation and control.
  • a scroll compressor is provided in a refrigerant system with an economizer circuit.
  • the scroll compressor has a motor that can be driven at multiple discreet speeds. For illustration purposes, the discussion below deals with a two-speed motor. However, the scroll compressor can be run at more than two distinct speeds.
  • the controller can increase or decrease the capacity of the refrigerant system. Further, by varying the speed of the motor, system capacity within each mode of operation can be adjusted to provide additional control flexibility.
  • a controller identifies a desired capacity level, and then achieves this desired capacity level by actuating the economizer circuit, if increased capacity is desired, or not actuating the economizer cycle if extra capacity is not required, or providing additional means of unloading to reduce the capacity even further, and determining a desired motor speed for achieving the exact capacity level. Since the refrigerant compressor provides efficient and reliable operation only within a certain speed range, additional steps of capacity correction, such as the unloader function, with or without the economizer circuit engaged, may be desired and similarly utilized with the corresponding compressor motor speed adjustment to closely control the capacity level or achieve more efficient unit operation. Additionally, the controller may monitor the system efficiency level and select the most desirable mode of operation and motor speed. In this case, both capacity and efficiency considerations are taken into account to establish the optimum unit operation.
  • the present invention allows an end user to closely tailor the system capacity and/or efficiency, or a combination of these two parameters, to a desired level.
  • an additional throttling device often called a suction modulation valve (SMV) may be provided to further reduce the capacity to the level below the level that would be normally achievable through the unloading mechanisms and reduction in motor speed.
  • SMV suction modulation valve
  • a refrigerant system 20 is illustrated in Figure 1A having a compressor 22 and a controller 44.
  • a motor 24 for the compressor 22 can be driven at two speeds such that the amount of refrigerant compressed and circulated throughout the system by the compressor 22 can be varied. That is, the compressor can be driven at one of two non-zero speeds at steady state operation.
  • the compressor 22 is a scroll compressor having an orbiting scroll member 26 and a non-orbiting scroll member 28.
  • a number of compression chambers are defined between the two scroll members to compress an entrapped refrigerant when the orbiting scroll member 26 is driven to orbit by the electric motor 24.
  • a suction tube 30 leads refrigerant into a suction chamber 31 surrounding the motor and leading into the compression chambers. Once the refrigerant is compressed, it is driven into a discharge chamber 33 communicating with a discharge port 32.
  • the general structure of a scroll compressor is known.
  • an injection line 34 to be disclosed below, communicates with a port (or ports) 51 that is positioned at an intermediate compression point.
  • Refrigerant compressed by the compressor 22 is discharged from the discharge port 32, and then to an outdoor heat exchanger 46, which would be the condenser in a cooling mode.
  • Fan 47 moves air over the heat exchanger 46.
  • Downstream of the condenser 46 is an economizer heat exchanger 48.
  • the economizer heat exchanger 48 may be a conventional heat exchanger or may be of a flash tank type. As is known, the economizer heat exchanger receives a tapped refrigerant from a tap line 45 passing through an economizer expansion device 49, and a main refrigerant from a liquid line 41.
  • the two refrigerant streams are shown flowing in the same direction in Figure 1 , this is merely to simplify the illustration. In practice, it is generally preferred to have the two flows flowing in a counterflow arrangement.
  • the tapped refrigerant in the tap line 45 subcools the refrigerant in the liquid line 41, such that after passing through a main expansion device 52, it will have a higher cooling potential prior to entering an evaporator 54.
  • Fan 55 moves air over the evaporator 54.
  • the refrigerant returns to a suction line 30 leading back to the compressor 22.
  • An optional suction modulation valve 61 can be positioned in the suction line 30 between the compressor 22 and evaporator 54.
  • the tapped refrigerant from the tap line 45 passes through the return injection line 34 to enter the intermediate compression point or injection port (or plurality of ports) 51 in the compressor 22.
  • a bypass line 19 may selectively bypass refrigerant from the compressor 22 back to the suction line 30 when a bypass valve 40 is opened.
  • the economizer expansion device 49 also preferably incorporates a shutoff feature, or a separate shutoff device 36 is provided.
  • the shutoff device 36 is preferably closed, and when the shutoff device 36 is opened, the bypass valve 40 is typically closed; however, it is also possible to operate with both shutoff valve 36 and bypass valve 40 open.
  • the same port of the injection line 34 can be used to deliver the refrigerant from the economizer heat exchanger as well as to bypass the refrigerant back to the suction line.
  • the bypass and refrigerant injection functions can utilize different ports, instead of the common port 51.
  • the bypass valve 40 is opened when part-load capacity of the compressor 22 is desirable. Thus, partially compressed refrigerant is returned to the suction line 30, and the cooling capacity of the refrigerant system is reduced. If a capacity increase is desired, then the bypass valve 40 is closed. If even further capacity augmentation is desired, then the bypass valve 40 is closed and the economizer expansion device 49 (or shutoff device 36) is opened to provide the economizer function. An enhanced capacity is then provided.
  • a control 44 for refrigerant cycle 20 is able to identify a desired cooling capacity, and operate the bypass function and/or the economizer function as necessary.
  • the prior art system provides varying stages of capacity. One stage corresponds to operation in the economized mode; another stage corresponds to operation in the economized and bypass modes engaged at the same time; still another stage corresponds to non-economized mode; and yet another stage corresponds to the bypass mode of operation. If there is an additional SMV present, then, as shown, by throttling the SMV between the modes of operation mentioned above the capacity can be adjusted between these modes. However, the SMV operation is inefficient, and in general should be avoided if possible.
  • the control 44 controls each of these options and changes the speed (see Figure 3 ) of the compressor motor between the two available speeds to achieve a capacity, which closely matches the needed capacity.
  • the control can change mode or speed under any algorithm that may determine the most desired operation, the mostly preferred control logic would be based on efficiency and reliability considerations.
  • the present invention is thus able to better tailor the provided capacity to the required capacity to meet external load demands by utilizing each of these several options.
  • Figure 1B shows another embodiment, wherein the compressor 122 is shown schematically, but wherein the economizer injection line 134 and the unloader line 136 communicate with distinct ports in the compressor 122.
  • This figure shows this feature somewhat schematically (note that suction and discharge port of the compressor 122 are not exhibited), but a worker of ordinary skill in the art would recognize how to achieve this structure.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP07251620A 2007-04-17 2007-04-17 Système réfrigérant à compresseur à spirales à plusieurs vitesses et circuit économiseur Ceased EP1983275A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07251620A EP1983275A1 (fr) 2007-04-17 2007-04-17 Système réfrigérant à compresseur à spirales à plusieurs vitesses et circuit économiseur

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Application Number Priority Date Filing Date Title
EP07251620A EP1983275A1 (fr) 2007-04-17 2007-04-17 Système réfrigérant à compresseur à spirales à plusieurs vitesses et circuit économiseur

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EP1983275A1 true EP1983275A1 (fr) 2008-10-22

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2440861A4 (fr) * 2009-06-12 2015-08-12 Carrier Corp Système réfrigérant à modes de chargement multiples
EP3043125A1 (fr) * 2015-01-12 2016-07-13 LG Electronics Inc. Climatiseur
US10119738B2 (en) 2014-09-26 2018-11-06 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
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
US11131491B1 (en) 2020-08-07 2021-09-28 Emerson Climate Technologies, Inc. Systems and methods for multi-stage operation of a compressor
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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050086957A1 (en) * 2003-10-28 2005-04-28 Alexander Lifson Refrigerant cycle with operating range extension
WO2005119141A1 (fr) * 2004-05-28 2005-12-15 York International Corporation Systeme et procede de commande d'un circuit economiseur
WO2006118573A1 (fr) * 2005-05-04 2006-11-09 Carrier Corporation Systeme refrigerant comprenant un compresseur a spirale a vitesse variable et un circuit economiseur
WO2006132638A1 (fr) * 2005-06-07 2006-12-14 Carrier Corporation Commande de moteur de compresseur à vitesse variable pour fonctionnement à faible vitesse

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050086957A1 (en) * 2003-10-28 2005-04-28 Alexander Lifson Refrigerant cycle with operating range extension
WO2005119141A1 (fr) * 2004-05-28 2005-12-15 York International Corporation Systeme et procede de commande d'un circuit economiseur
WO2006118573A1 (fr) * 2005-05-04 2006-11-09 Carrier Corporation Systeme refrigerant comprenant un compresseur a spirale a vitesse variable et un circuit economiseur
WO2006132638A1 (fr) * 2005-06-07 2006-12-14 Carrier Corporation Commande de moteur de compresseur à vitesse variable pour fonctionnement à faible vitesse

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9677788B2 (en) 2009-06-12 2017-06-13 Carrier Corporation Refrigerant system with multiple load modes
EP2440861A4 (fr) * 2009-06-12 2015-08-12 Carrier Corp Système réfrigérant à modes de chargement multiples
US11480372B2 (en) 2014-09-26 2022-10-25 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
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
US9958189B2 (en) 2015-01-12 2018-05-01 Lg Electronics Inc. Air conditioner
EP3043125A1 (fr) * 2015-01-12 2016-07-13 LG Electronics Inc. Climatiseur
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
US11592215B2 (en) 2018-08-29 2023-02-28 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
US11953239B2 (en) 2018-08-29 2024-04-09 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
US11506430B2 (en) 2019-07-15 2022-11-22 Climate Master, Inc. Air conditioning system with capacity control and controlled hot water generation
US11131491B1 (en) 2020-08-07 2021-09-28 Emerson Climate Technologies, Inc. Systems and methods for multi-stage operation of a compressor
US11585581B2 (en) 2020-08-07 2023-02-21 Emerson Climate Technologies, Inc. Systems and methods for multi-stage operation of a compressor

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