US20080223057A1 - Refrigerant System with Pulse Width Modulated Components and Variable Speed Compressor - Google Patents

Refrigerant System with Pulse Width Modulated Components and Variable Speed Compressor Download PDF

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US20080223057A1
US20080223057A1 US12/088,022 US8802208A US2008223057A1 US 20080223057 A1 US20080223057 A1 US 20080223057A1 US 8802208 A US8802208 A US 8802208A US 2008223057 A1 US2008223057 A1 US 2008223057A1
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Prior art keywords
compressor
system
set forth
refrigerant
refrigerant system
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Abandoned
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US12/088,022
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Alexander Lifson
Sriram Srinivasan
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Carrier Corp
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Carrier Corp
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Priority to PCT/US2005/038726 priority Critical patent/WO2007050063A1/en
Assigned to CARRIER CORPORATION reassignment CARRIER CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LIFSON, ALEXANDER, SRINIVASAN, SRIRAM
Publication of US20080223057A1 publication Critical patent/US20080223057A1/en
Application status is Abandoned legal-status Critical

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B49/00Arrangement or mounting of control or safety devices
    • F25B49/02Arrangement or mounting of control or safety devices for compression type machines, plant or systems
    • F25B49/025Motor control arrangements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/08Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04Heating; Cooling; Heat insulation
    • F04C29/042Heating; Cooling; Heat insulation by injecting a fluid
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B1/00Compression machines, plant, or systems with non-reversible cycle
    • F25B1/04Compression machines, plant, or systems with non-reversible cycle with compressor of rotary type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General 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
    • F25B2400/13Economisers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2600/00Control issues
    • F25B2600/02Compressor control
    • F25B2600/025Compressor control by controlling speed
    • F25B2600/0253Compressor control by controlling speed with variable speed
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2600/00Control issues
    • F25B2600/02Compressor control
    • F25B2600/026Compressor control by controlling unloaders
    • F25B2600/0261Compressor control by controlling unloaders external to the compressor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2600/00Control issues
    • F25B2600/25Control of valves
    • F25B2600/2521On-off valves controlled by pulse signals
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements, e.g. for transferring liquid from evaporator to boiler
    • F25B41/04Disposition of valves
    • F25B41/043Disposition of valves in the circuit between evaporator and compressor
    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02BCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70Efficient control or regulation technologies
    • Y02B30/74Technologies based on motor control
    • Y02B30/741Speed regulation of the compressor

Abstract

A variable speed drive is provided for operating a compressor motor in a refrigerant system. When a low load situation has been determined by the refrigerant system controls, the variable speed drive operates the compressor motor at lower speed mode of operation. Further, the operation of the variable speed drive is combined with a pulse width modulation control of different system components. In particular, at least one valve or compressor can be can be rapidly cycled by the control to regulate amount of refrigerant passing through the valve or compressor. Example valves would include a shut-off valve for an economizer cycle, an unloader valve, or a suction modulation valve.

Description

    BACKGROUND OF THE INVENTION
  • This application relates to a control for a refrigerant system having a variable speed compressor, and wherein pulse width modulation technologies are utilized to provide further control over the system.
  • Refrigerant systems are utilized in many applications to condition an environment. In particular, air conditioners and heat pumps are employed to cool and/or heat air entering the 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 environment.
  • A feature that is known for improving the efficiency of refrigerant systems is the use of a variable speed drive for the compressor motor. Often, the compressor need not be operated at full speed, such as when the cooling load on the refrigerant system is relatively low. Under such circumstances, it might be desirable to reduce the compressor speed, and thus reduce the overall energy consumption of the refrigerant system. Implementation of a variable speed drive is one of the most efficient techniques to enhance system performance and reduce life-cycle cost of the equipment over a wide spectrum of operating environments and potential applications, especially at part-load conditions.
  • However, compelling reliability concerns set a lower limit to the desirable compressor speed reduction. As an example, inadequate lubrication of the compressor elements may present a problem at low operating speeds. Further, certain types of compressors require a minimum operating speed to provide radial compliance. As an example, a scroll compressor could have a dramatic loss in performance due to a loss of radial compliance should it operate below a minimum speed.
  • Various other features are known for providing variations in system capacity in a manner other than lowering the speed of the compressor. As an example, economizer cycles are known as are unloader cycles. However, even with the provision of these cycles in a system having a variable speed drive for its compressor, it would be desirable to provide even more variability in the system capacity.
  • Another approach which has been utilized in the prior art to change the capacity of a refrigerant system is the use of pulse width modulation to control valves such as a shut-off valve on an economizer cycle, and/or a shut-off valve on an unloader line, and/or a shut off valve on a suction. By rapidly cycling these valves utilizing pulse width modulation techniques, additional capacity control is provided. The pulse width modulation of the internal scroll elements can also be applied in conjunction with variable speed drive operation. In this case, as known in the art, the scroll elements are separated from each other in a pulse width manner to control the amount of refrigerant pumped by the compressor. These pulse width modulation techniques for control of a valve or internal scroll compression elements have not been utilized, however, in refrigerant systems having a variable speed drive compressor.
  • SUMMARY OF THE INVENTION
  • In the disclosed embodiment of this invention, a compressor is provided with a variable speed drive. When a need for a low capacity is detected, the compressor is moved to a low speed to maintain adequate conditions in the environment without switching to a start-stop mode of operation. The compressor is incorporated into a refrigerant system, which has a pulse width modulation control for cycling some component in the system, other than cycling on and off the compressor motor. In disclosed embodiments, the cycled component is a valve, and may be a suction valve, and/or an economizer cycle shut-off valve and/or an unloader valve and/or cycled component is one of the scroll compressor pumping elements. By cycling these components on and off, the amount of refrigerant delivered to various locations in the refrigerant cycle is lowered, and thus the capacity can be lowered without lowering the compressor motor speed beyond the safe regime.
  • Although, for illustrative purposes, the operation of the valves in this invention is described in relation to refrigerant systems incorporating scroll compressors, it could be applicable to any variable speed compressor.
  • These and other features of the present invention can be best understood from the following specification and drawings, the following of which is a brief description.
  • BRIEF DESCRIPTION OF THE DRAWINGS
  • FIG. 1A is a schematic view of a refrigerant system incorporating the present invention.
  • FIG. 1B shows an alternative embodiment.
  • FIG. 2 shows another schematic of a refrigerant system.
  • DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
  • A refrigerant system 19 is illustrated in FIG. 1 having a scroll compressor 21 incorporating a non-orbiting scroll member 22 and an orbiting scroll member 24. As is known, shaft 26 is driven by an electric motor 28 to cause the orbiting scroll member 24 to orbit. As shown, a variable speed drive 30 is schematically connected to drive the electric motor 28. An oil sump 32 and an oil passage 34 in the shaft 26 supply oil to the various moving elements in the compressor 21, as known.
  • A condenser 36 is positioned downstream of the compressor 21, an expansion device 38 is located downstream of the condenser 36, and an evaporator 40 is positioned downstream of the expansion device 38, as known. As is also known, the compressor 21 is driven by the electric motor 28 to compress the refrigerant vapor and to drive it through the refrigerant system 19. Oil from the oil sump 32 is delivered to the compressor elements to provide proper lubrication of the compressor components such as the crankcase bearing 100, orbiting scroll bearing 102, the non-orbiting scroll 22 and the orbiting scroll 24, while some amount of oil leaves the compressor 21 with the refrigerant and is circulated through the refrigerant system 19. One of the most typical oil delivery systems of a scroll compressor is also shown in FIG. 1, where the oil from the oil sump 32 is picked up by the oil pick up tube 110, and delivered along the oil passage 34 to various compressor components as described above. Some of the oil can also be delivered through the suction port 120 by a refrigerant entering the compressor. However most of the oil delivery is accomplished by delivering the oil from the oil sump as described above. In the prior art, when a variable speed drive has been implemented in a refrigerant system, the designer has been limited by a minimum operational speed of the shaft 26 for the compressor 21. If the speed dropped below a certain level for extended period of time, an insufficient amount of oil would be delivered through the oil passage into the compressor components that need to be lubricated. Thus, for a low cooling load situation, where only a small amount of the compressed refrigerant mass flow is needed to be circulated through the system, a minimum speed requirement (for example 45 Hz) is often a limiting factor in ensuring that adequate amount of oil is provided to the compressor components. Further, the operation above a minimum speed would also ensure that the radial compliance necessary for efficient operation of the scroll compressor is not lost due to unduly low motor speed. As known, it is important to match the delivered capacity to the system load. Since the compressor operating speed often cannot be reduced below a certain threshold for capacity shedding, additional efficient means are required to reduce the capacity delivered by the unit without cycling the unit on and off for tight temperature control within the cooled environment. The description below provides additional means of efficiently shedding the capacity by coupling the compressor variable speed operation with pulse width modulation of different system components.
  • FIG. 1 shows additional features that may be incorporated into the refrigerant system 19. As an example, an economizer cycle is included and has an economizer heat exchanger 18. A main liquid line 13 has a tap line 11 tapped off of the main liquid line and passed through an economizer expansion device 115. The tap line 11 and the main liquid line 13 both pass through the economizer heat exchanger 18. In fact, and in practice, the refrigerant flow in the tap line is typically in the counterflow direction through the economizer heat exchanger in relation to the flow in the main liquid line 13. However, to simplify the illustration in this figure, they are shown in the same direction. As is known, the economizer circuit subcools the refrigerant in the main liquid line, and thus enhances performance (capacity and/or efficiency) of the refrigerant system 19. An economizer injection line 20 is shown extending back to the compressor 21, and injects an intermediate pressure refrigerant into compression chambers through passages such as passage 23. The function and structure of the economizer circuit is known, however, its inclusion with the inventive motor control 30 provides a refrigerant system that has even greater flexibility to enhance operation of the refrigerant system 19.
  • An optional unloader line 17 includes an unloader valve 200. The unloader valve 200 is selectively opened to return partially compressed refrigerant from the compression chambers through the passages 23 back to a suction port 120 of the compressor 21. The unloader function presents a refrigerant system designer with an extra degree of freedom for performance adjustment and optimization. The unloader valve can be located inside or outside of the compressor, as known.
  • Essentially, when a greater system capacity is desired, the economizer function may be utilized with the unloader valve shut. Alternatively, if a lower capacity is necessary, the economizer expansion device 115 (or a separate shut-off device) is shut, with the unloader valve 200 opened. In this manner, the amount of compressed refrigerant delivered to the condenser 36 is reduced. Also, if desired to provide another intermediate stage of capacity for the refrigerant system 19, the economizer function can be combined with the unloader function by opening both the economizer expansion device 115 and the unloader valve 200. Shutting the flow in the economizer injection line and closing the unloader valve 200 also achieve another alternate intermediate stage of capacity unloading.
  • These system configurations in combination with the variable speed motor control disclosed below provides even greater freedom and flexibility to a refrigerant system designer for controlling the delivered system capacity
  • In this case, the control 30 may incorporate more than a variable speed drive, but may also be a microprocessor or other type control that is capable of providing pulse width modulation control to the economizer valve 115 (which in this case would be a shut-off valve), and/or the unloader valve 200, and/or a suction modulation valve 210.
  • Also as known in the art, the pulse width modulation can also be used to pulse width modulate the scroll compression elements itself, in this case the scroll elements would be separated from each other in a pulse width manner to control the amount of the refrigerant pumped by the compressor.
  • FIG. 1B shows an embodiment 301, schematically. It is known that the orbiting scroll member 302 and the non-orbiting scroll member 304 may be biased together by a gas in a chamber 306. Opening and closing the valve 310 can control pressure in chamber 306. As shown, the valve 312 communicates via line 308 with another pressure source that is at different pressure than pressure in the chamber 306 when the valve 310 is closed. When the pressure in the chamber 306 is reduced below a certain level the scroll members will separate from each and the amount of refrigerant pumped by the compressor is then reduced. When the pressure in the chamber 306 is increased above certain level the scrolls will come into contact with each other and then the normal compression process will resume. The valve can be controlled by a pulse width modulation control 312. Thus, by modulating the pressure in the chamber 306, the two scroll members 302 and 304 can be allowed to periodically move away from, and come into contact with, each other. It should be noted that the schematic shown in FIG. 1B is presented for an illustration purpose only. For example, instead of allowing the scroll 304 to move axially in and out of contact with the scroll 302, the scroll 302 can be allowed to move axially while the scroll 304 remains essentially stationary in the axial direction. The valve 312 can be located internal or external to the compressor.
  • While the schematic shows the control providing pulse width modulation control to each of these valves and/or compressor elements, in other embodiments any combination of the three vales and/or compressor, or even other valves can be utilized. By rapidly cycling these valves to open and closed position (closing can be partial or complete), the amount of refrigerant passing through any one of the valves and compressor can be varied to vary capacity. As an example, once the compressor speed has been lowered, and additional capacity reduction is desired, a valve or compressor can be cycled to further reduce the system capacity. It should be noted that normally the compressor speed reduction would be applied first to shed the capacity, since this is the most efficient means to do so than other methods of unloading.
  • The present invention provides efficient means to efficiently and precisely control capacity of the refrigerant system 19 by employing varying methods of pulse width modulation of various system components coupled with the use of a variable speed drive motor. The motor drive can be varied in speed when there is a need for capacity adjustment. The economizer circuit can also be turned on or off to vary capacity. The unloader function can also be utilized. In addition, and in combination with each of the above options for this control, the present invention also allows the control to modulate the flow of refrigerant through any one of valves 115, 200 and 210 and/or through modulation of the compressor pumping elements itself. In this manner, the capacity can be further reduced without unduly lowering the speed of the compressor motor 28 beyond its safe threshold of operation.
  • FIG. 2 shows another embodiment 300 wherein the valves 200 and 210 are internal of the compressor shell as are the flow passages. It should be noted that while in FIG. 2 the valves are all shown as located inside the compressor, a compressor designer may choose to locate some of them internally and some of them externally. In addition, the shut-off valve 220 for the economizer line is shown to be separate from the expansion valve. If the valve 220 is located externally, its function can be combined with the use of an expansion valve. Also while valves are shown as separate components, its function can be combined into a single three-way valve as known in the art. Each or some of the valves 220, 200 and 210 can be controlled by pulse width modulation techniques.
  • It should be understood that the motor control 30 includes a program that takes in inputs from various locations within the refrigerant system, and determines when a lower speed for the compressor motor would be desirable and when the pulse width modulation of the pulse width modulated components needs to be initiated. The controller can also decide when the system needs to be operated in economized, non-economized, and by-pass unloading modes or any of its combinations as described above. Controls capable of performing this invention with such valves and compressors are known.
  • A worker of ordinary skill in the art would recognize when a lower speed might be desirable and preferred in comparison or in addition to other available options.
  • It should be understood that although this invention is described in relation to refrigerant systems incorporating scroll compressors, it could be applicable to any variable speed compressor, including scroll compressors, screw compressors, reciprocating compressors, rotary compressors, etc. The application of this technique can for example, be applied to refrigeration systems used in transportation container units, truck/trailer application, supermarket refrigeration application, as well as cooling or heating industrial buildings and residential houses as well as used for water heating applications. Although a preferred embodiment of this invention has been disclosed, a worker of ordinary skill in this art would recognize that certain modifications would come within the scope of this invention. For that reason, the following claims should be studied to determine the true scope and content of this invention.

Claims (23)

1. A refrigerant system comprising:
a compressor and an electric motor for driving said compressor, a variable speed drive for varying a speed of operation of said electric motor;
a condenser downstream of said compressor, an expansion device downstream of said condenser, and an evaporator downstream of said expansion device;
said variable speed drive moving said motor to low speed operation, and said variable speed drive operating said motor at a low level of speed; and
a pulse width modulation control for controlling at least one system component.
2. The refrigerant system as set forth in claim 1, wherein said pulse width modulation control controls at least one valve.
3. The refrigerant system as set forth in claim 2, wherein an economizer circuit is incorporated into the refrigerant system.
4. The refrigerant system as set forth in claim 3, wherein the said at least one system component is a shut-off valve associated with said economizer circuit.
5. The refrigerant system as set forth in claim 2, wherein said compressor is provided with an unloader circuit.
6. The refrigerant system as set forth in claim 5, wherein said at least one system component is a valve associated with said unloader circuit.
7. The refrigerant system as set forth in claim 2, wherein the refrigerant system is provided with both an economizer circuit and an unloader circuit.
8. The refrigerant system as set forth in claim 7, wherein said at least one system component includes a valve associated with said economizer circuit and a valve associated with said unloader circuit.
9. The refrigerant system as set forth in claim 2, wherein said at least one system component is a valve for controlling the mass flow of refrigerant delivered to said compressor from said evaporator.
10. The refrigerant system as set forth in claim 1, wherein said at least one system component is external to a shell for said compressor.
11. The refrigerant system as set forth in claim 1, wherein said at least one system component is internal to a shell for said compressor.
12. The refrigerant system as set forth in claim 1, wherein said compressor is selected from the group consisting of a scroll compressor, a rotary compressor, a reciprocating compressor, and a screw compressor.
13. The refrigerant system as set forth in claim 1, wherein said at least one component is a pulse width modulated control to hold the orbiting and non-orbiting scroll member in a scroll compressor together or allow them to move away from each other.
14. The refrigerant system as set forth in claim 1, wherein said system is selected from the group consisting of a container refrigeration system, a truck/trailer system, a supermarket refrigeration system, a residential air conditioning system, a residential heat pump system, a commercial air conditioning system, a commercial heat pump system, and a water heating system.
15. A method of operating a refrigerant system comprising the steps of:
(1) providing a compressor with a variable speed drive, and monitoring a load on a refrigerant system associated with said compressor;
(2) identifying a low load situation, and moving said compressor to a low speed operation when a low load situation has been identified; and
(3) providing pulse width modulation control for a system component to allow the variation of capacity from the refrigerant system by both varying the speed of the compressor, and varying the operation of said other component.
16. The method as set forth in claim 15, wherein said pulse width modulation control controls at least one valve.
17. The method as set forth in claim 16, wherein an economizer circuit is incorporated into the refrigerant system, and said at least one system component a shut-off valve associated with said economizer circuit.
18. The method as set forth in claim 16, wherein said compressor is provided with an unloader circuit, and said at least one system component at is a valve associated with said unloader circuit.
19. The method as set forth in claim 16, wherein the refrigerant system is provided with both an economizer circuit and an unloader circuit, and said at least one system component includes a valve associated with said economizer circuit and a valve associated with said unloader circuit.
20. The method as set forth in claim 15, wherein said at least one component is external to a shell for said compressor.
21. The method as set forth in claim 15, wherein said at least one component is internal to a shell for said compressor.
22. The method as set forth in claim 15, wherein said other component is a valve for controlling the amount of refrigerant delivered to said compressor from said evaporator.
23. The method as set forth in claim 15, wherein said at least one component is a pulse width modulated control to hold the orbiting and non-orbiting scroll member in a scroll compressor together or allow them to move away from each other.
US12/088,022 2005-10-26 2005-10-26 Refrigerant System with Pulse Width Modulated Components and Variable Speed Compressor Abandoned US20080223057A1 (en)

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Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080286118A1 (en) * 2007-05-18 2008-11-20 Emerson Climate Technologies, Inc. Capacity modulated scroll compressor system and method
US20090013701A1 (en) * 2006-03-10 2009-01-15 Alexander Lifson Refrigerant system with control to address flooded compressor operation
US20100011806A1 (en) * 2008-07-16 2010-01-21 Lg Electronics Inc. Motor, compressor and air conditioning system having the same
US20100011792A1 (en) * 2006-11-07 2010-01-21 Alexander Lifson Refrigerant system with pulse width modulation control in combination with expansion device control
USRE41955E1 (en) 2001-04-25 2010-11-23 Emerson Climate Technologies, Inc. Capacity modulation for plural compressors
US20110268597A1 (en) * 2009-04-07 2011-11-03 Masao Akei Compressor having capacity modulation assembly
US8069685B2 (en) * 2008-07-16 2011-12-06 Lg Electronics Inc. Capacity modulation compressor and air conditioning system having the same
US20120174609A1 (en) * 2009-11-13 2012-07-12 Mitsubishi Heavy Industries, Ltd. Heat source system
US9127677B2 (en) 2012-11-30 2015-09-08 Emerson Climate Technologies, Inc. Compressor with capacity modulation and variable volume ratio
US9249802B2 (en) 2012-11-15 2016-02-02 Emerson Climate Technologies, Inc. Compressor
US9435340B2 (en) 2012-11-30 2016-09-06 Emerson Climate Technologies, Inc. Scroll compressor with variable volume ratio port in orbiting scroll
US9651043B2 (en) 2012-11-15 2017-05-16 Emerson Climate Technologies, Inc. Compressor valve system and assembly
US9739277B2 (en) 2014-05-15 2017-08-22 Emerson Climate Technologies, Inc. Capacity-modulated scroll compressor
US9790940B2 (en) 2015-03-19 2017-10-17 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US9835360B2 (en) 2009-09-30 2017-12-05 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
US9989057B2 (en) 2014-06-03 2018-06-05 Emerson Climate Technologies, Inc. Variable volume ratio scroll compressor
US10066622B2 (en) 2015-10-29 2018-09-04 Emerson Climate Technologies, Inc. Compressor having capacity modulation system
US10378540B2 (en) 2015-07-01 2019-08-13 Emerson Climate Technologies, Inc. Compressor with thermally-responsive modulation system
US10495086B2 (en) 2017-05-05 2019-12-03 Emerson Climate Technologies, Inc. Compressor valve system and assembly

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2220450B1 (en) 2007-11-09 2015-06-17 Carrier Corporation Transport refrigeration system and method of operation
JP5965895B2 (en) * 2011-02-22 2016-08-10 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー(ホンコン)リミテッド Refrigeration cycle equipment

Citations (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3410105A (en) * 1967-02-15 1968-11-12 Philco Ford Corp Air conditioner
US5079929A (en) * 1979-07-31 1992-01-14 Alsenz Richard H Multi-stage refrigeration apparatus and method
US5086626A (en) * 1988-01-13 1992-02-11 Kabushiki Kaisha Toshiba Air conditioner with function for temperature control of radiant heat exchanger
US5123080A (en) * 1987-03-20 1992-06-16 Ranco Incorporated Of Delaware Compressor drive system
US5245836A (en) * 1989-01-09 1993-09-21 Sinvent As Method and device for high side pressure regulation in transcritical vapor compression cycle
US5255529A (en) * 1990-09-14 1993-10-26 Nartron Corporation Environmental control system
US5431026A (en) * 1994-03-03 1995-07-11 General Electric Company Refrigerant flow rate control based on liquid level in dual evaporator two-stage refrigeration cycles
US5490394A (en) * 1994-09-23 1996-02-13 Multibras S/A Eletrodomesticos Fan control system for the evaporator of refrigerating appliances
US5568732A (en) * 1994-04-12 1996-10-29 Kabushiki Kaisha Toshiba Air conditioning apparatus and method of controlling same
US5613369A (en) * 1994-09-28 1997-03-25 Kabushiki Kaisha Toshiba Air conditioner and control method for an air conditioner
US5628201A (en) * 1995-04-03 1997-05-13 Copeland Corporation Heating and cooling system with variable capacity compressor
US5657638A (en) * 1995-10-02 1997-08-19 General Electric Company Two speed control circuit for a refrigerator fan
US5694783A (en) * 1994-10-26 1997-12-09 Bartlett; Matthew T. Vapor compression refrigeration system
US5782101A (en) * 1997-02-27 1998-07-21 Carrier Corporation Heat pump operating in the heating mode refrigerant pressure control
US5797276A (en) * 1993-07-28 1998-08-25 Howenstine; Mervin W. Methods and devices for energy conservation in refrigerated chambers
US6047556A (en) * 1997-12-08 2000-04-11 Carrier Corporation Pulsed flow for capacity control
US6058729A (en) * 1998-07-02 2000-05-09 Carrier Corporation Method of optimizing cooling capacity, energy efficiency and reliability of a refrigeration system during temperature pull down
US6073457A (en) * 1997-03-28 2000-06-13 Behr Gmbh & Co. Method for operating an air conditioner in a motor vehicle, and an air conditioner having a refrigerant circuit
US6206652B1 (en) * 1998-08-25 2001-03-27 Copeland Corporation Compressor capacity modulation
US6213731B1 (en) * 1999-09-21 2001-04-10 Copeland Corporation Compressor pulse width modulation
US6397610B1 (en) * 2001-05-01 2002-06-04 Cohand Technology Co., Ltd. Method for controlling air conditioner/heater by coil temperature
US6415617B1 (en) * 2001-01-10 2002-07-09 Johnson Controls Technology Company Model based economizer control of an air handling unit
US20030000232A1 (en) * 2001-06-29 2003-01-02 International Business Machines Corporation Logic module refrigeration system with condensation control
US20030033823A1 (en) * 2001-03-16 2003-02-20 Pham Hung M. Digital scroll condensing unit controller
US6560980B2 (en) * 2000-04-10 2003-05-13 Thermo King Corporation Method and apparatus for controlling evaporator and condenser fans in a refrigeration system
US6619062B1 (en) * 1999-12-06 2003-09-16 Daikin Industries, Ltd. Scroll compressor and air conditioner
US6694763B2 (en) * 2002-05-30 2004-02-24 Praxair Technology, Inc. Method for operating a transcritical refrigeration system
US20040065100A1 (en) * 2001-05-09 2004-04-08 Maersk Container Industri A/S Cooling unit and container with this unit
US6931867B2 (en) * 2002-07-15 2005-08-23 Copeland Corporation Cooling system with isolation valve
US6968708B2 (en) * 2003-06-23 2005-11-29 Carrier Corporation Refrigeration system having variable speed fan

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1099918A1 (en) * 1999-11-09 2001-05-16 Maersk Container Industri As Cooling unit
US6925823B2 (en) * 2003-10-28 2005-08-09 Carrier Corporation Refrigerant cycle with operating range extension

Patent Citations (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3410105A (en) * 1967-02-15 1968-11-12 Philco Ford Corp Air conditioner
US5079929A (en) * 1979-07-31 1992-01-14 Alsenz Richard H Multi-stage refrigeration apparatus and method
US5123080A (en) * 1987-03-20 1992-06-16 Ranco Incorporated Of Delaware Compressor drive system
US5086626A (en) * 1988-01-13 1992-02-11 Kabushiki Kaisha Toshiba Air conditioner with function for temperature control of radiant heat exchanger
US5245836A (en) * 1989-01-09 1993-09-21 Sinvent As Method and device for high side pressure regulation in transcritical vapor compression cycle
US5255529A (en) * 1990-09-14 1993-10-26 Nartron Corporation Environmental control system
US5797276A (en) * 1993-07-28 1998-08-25 Howenstine; Mervin W. Methods and devices for energy conservation in refrigerated chambers
US5431026A (en) * 1994-03-03 1995-07-11 General Electric Company Refrigerant flow rate control based on liquid level in dual evaporator two-stage refrigeration cycles
US5568732A (en) * 1994-04-12 1996-10-29 Kabushiki Kaisha Toshiba Air conditioning apparatus and method of controlling same
US5490394A (en) * 1994-09-23 1996-02-13 Multibras S/A Eletrodomesticos Fan control system for the evaporator of refrigerating appliances
US5613369A (en) * 1994-09-28 1997-03-25 Kabushiki Kaisha Toshiba Air conditioner and control method for an air conditioner
US5694783A (en) * 1994-10-26 1997-12-09 Bartlett; Matthew T. Vapor compression refrigeration system
US5628201A (en) * 1995-04-03 1997-05-13 Copeland Corporation Heating and cooling system with variable capacity compressor
US5657638A (en) * 1995-10-02 1997-08-19 General Electric Company Two speed control circuit for a refrigerator fan
US5782101A (en) * 1997-02-27 1998-07-21 Carrier Corporation Heat pump operating in the heating mode refrigerant pressure control
US6073457A (en) * 1997-03-28 2000-06-13 Behr Gmbh & Co. Method for operating an air conditioner in a motor vehicle, and an air conditioner having a refrigerant circuit
US6047556A (en) * 1997-12-08 2000-04-11 Carrier Corporation Pulsed flow for capacity control
US6058729A (en) * 1998-07-02 2000-05-09 Carrier Corporation Method of optimizing cooling capacity, energy efficiency and reliability of a refrigeration system during temperature pull down
US6206652B1 (en) * 1998-08-25 2001-03-27 Copeland Corporation Compressor capacity modulation
US6213731B1 (en) * 1999-09-21 2001-04-10 Copeland Corporation Compressor pulse width modulation
US6619062B1 (en) * 1999-12-06 2003-09-16 Daikin Industries, Ltd. Scroll compressor and air conditioner
US6560980B2 (en) * 2000-04-10 2003-05-13 Thermo King Corporation Method and apparatus for controlling evaporator and condenser fans in a refrigeration system
US6415617B1 (en) * 2001-01-10 2002-07-09 Johnson Controls Technology Company Model based economizer control of an air handling unit
US20030033823A1 (en) * 2001-03-16 2003-02-20 Pham Hung M. Digital scroll condensing unit controller
US6397610B1 (en) * 2001-05-01 2002-06-04 Cohand Technology Co., Ltd. Method for controlling air conditioner/heater by coil temperature
US20040065100A1 (en) * 2001-05-09 2004-04-08 Maersk Container Industri A/S Cooling unit and container with this unit
US20030000232A1 (en) * 2001-06-29 2003-01-02 International Business Machines Corporation Logic module refrigeration system with condensation control
US6694763B2 (en) * 2002-05-30 2004-02-24 Praxair Technology, Inc. Method for operating a transcritical refrigeration system
US6931867B2 (en) * 2002-07-15 2005-08-23 Copeland Corporation Cooling system with isolation valve
US6968708B2 (en) * 2003-06-23 2005-11-29 Carrier Corporation Refrigeration system having variable speed fan

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE41955E1 (en) 2001-04-25 2010-11-23 Emerson Climate Technologies, Inc. Capacity modulation for plural compressors
US9494352B2 (en) * 2006-03-10 2016-11-15 Carrier Corporation Refrigerant system with control to address flooded compressor operation
US20090013701A1 (en) * 2006-03-10 2009-01-15 Alexander Lifson Refrigerant system with control to address flooded compressor operation
US20100011792A1 (en) * 2006-11-07 2010-01-21 Alexander Lifson Refrigerant system with pulse width modulation control in combination with expansion device control
US20080286118A1 (en) * 2007-05-18 2008-11-20 Emerson Climate Technologies, Inc. Capacity modulated scroll compressor system and method
US8485789B2 (en) * 2007-05-18 2013-07-16 Emerson Climate Technologies, Inc. Capacity modulated scroll compressor system and method
US20100011806A1 (en) * 2008-07-16 2010-01-21 Lg Electronics Inc. Motor, compressor and air conditioning system having the same
US8069685B2 (en) * 2008-07-16 2011-12-06 Lg Electronics Inc. Capacity modulation compressor and air conditioning system having the same
US8585382B2 (en) * 2009-04-07 2013-11-19 Emerson Climate Technologies, Inc. Compressor having capacity modulation assembly
US20110268597A1 (en) * 2009-04-07 2011-11-03 Masao Akei Compressor having capacity modulation assembly
US9879674B2 (en) 2009-04-07 2018-01-30 Emerson Climate Technologies, Inc. Compressor having capacity modulation assembly
US9303642B2 (en) 2009-04-07 2016-04-05 Emerson Climate Technologies, Inc. Compressor having capacity modulation assembly
US10072876B2 (en) 2009-09-30 2018-09-11 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
US9835360B2 (en) 2009-09-30 2017-12-05 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
US20120174609A1 (en) * 2009-11-13 2012-07-12 Mitsubishi Heavy Industries, Ltd. Heat source system
US9206994B2 (en) * 2009-11-13 2015-12-08 Mitsubishi Heavy Industries, Ltd. Heat source system
US9651043B2 (en) 2012-11-15 2017-05-16 Emerson Climate Technologies, Inc. Compressor valve system and assembly
US10094380B2 (en) 2012-11-15 2018-10-09 Emerson Climate Technologies, Inc. Compressor
US9249802B2 (en) 2012-11-15 2016-02-02 Emerson Climate Technologies, Inc. Compressor
US9127677B2 (en) 2012-11-30 2015-09-08 Emerson Climate Technologies, Inc. Compressor with capacity modulation and variable volume ratio
US9777730B2 (en) 2012-11-30 2017-10-03 Emerson Climate Technologies, Inc. Scroll compressor with variable volume ratio port in orbiting scroll
US9435340B2 (en) 2012-11-30 2016-09-06 Emerson Climate Technologies, Inc. Scroll compressor with variable volume ratio port in orbiting scroll
US9494157B2 (en) 2012-11-30 2016-11-15 Emerson Climate Technologies, Inc. Compressor with capacity modulation and variable volume ratio
US9739277B2 (en) 2014-05-15 2017-08-22 Emerson Climate Technologies, Inc. Capacity-modulated scroll compressor
US9989057B2 (en) 2014-06-03 2018-06-05 Emerson Climate Technologies, Inc. Variable volume ratio scroll compressor
US9790940B2 (en) 2015-03-19 2017-10-17 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US10323638B2 (en) 2015-03-19 2019-06-18 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US10323639B2 (en) 2015-03-19 2019-06-18 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US10378540B2 (en) 2015-07-01 2019-08-13 Emerson Climate Technologies, Inc. Compressor with thermally-responsive modulation system
US10087936B2 (en) 2015-10-29 2018-10-02 Emerson Climate Technologies, Inc. Compressor having capacity modulation system
US10066622B2 (en) 2015-10-29 2018-09-04 Emerson Climate Technologies, Inc. Compressor having capacity modulation system
US10495086B2 (en) 2017-05-05 2019-12-03 Emerson Climate Technologies, Inc. Compressor valve system and assembly

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ES2692800T3 (en) 2018-12-05
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WO2007050063A1 (en) 2007-05-03
EP1941219A4 (en) 2010-08-25

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