US20100199715A1 - Refrigerant system with bypass line and dedicated economized flow compression chamber - Google Patents
Refrigerant system with bypass line and dedicated economized flow compression chamber Download PDFInfo
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- US20100199715A1 US20100199715A1 US12/667,280 US66728007A US2010199715A1 US 20100199715 A1 US20100199715 A1 US 20100199715A1 US 66728007 A US66728007 A US 66728007A US 2010199715 A1 US2010199715 A1 US 2010199715A1
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- refrigerant
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- refrigerant system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
Definitions
- This application relates to a refrigerant system having an economizer cycle, and wherein an economized refrigerant flow is returned to an economizer compression chamber of a compression unit, and a main refrigerant flow is returned to a main compression chamber of a compression unit, wherein a bypass refrigerant line communicates the two refrigerant flows upstream of their corresponding compression chambers.
- Refrigerant compressors compress and circulate a refrigerant throughout a refrigerant system to condition a secondary fluid, typically delivered to a climate-controlled space.
- a compressor compresses a refrigerant and delivers it to a heat rejection heat exchanger.
- Refrigerant from the heat rejection heat exchanger passes through an expansion device, in which its pressure and temperature are reduced. Downstream of the expansion device, the refrigerant passes through a heat accepting heat exchanger, and then back to the compressor.
- the heat accepting heat exchanger is typically an evaporator
- the heat rejecting heat exchanger is a condenser for subcritical applications and a gas cooler for transcritical applications.
- a portion of refrigerant is tapped from a main refrigerant stream downstream of the heat rejection heat exchanger.
- this tapped refrigerant is passed through an auxiliary expansion device, to be expanded to an intermediate pressure and temperature, and then this partially expanded tapped refrigerant passes in heat exchange relationship with a main refrigerant flow in an economizer heat exchanger.
- the main refrigerant flow is cooled such that it will have a greater thermodynamic potential when it reaches the heat accepting heat exchanger.
- the tapped refrigerant typically in a superheated thermodynamic state, is returned to the compressor.
- an economizer function can be performed in either a flash tank or in an economizer heat exchanger.
- the two devices will be both known as an “economizer heat exchanger.”
- the vapor refrigerant is returned to a dedicated economizer compression chamber or a compressor.
- the main refrigerant flow is returned from the heat accepting heat exchanger back to its own dedicated compression chamber or compressor.
- This known system maintains the economizer and suction refrigerant flows completely isolated from each other.
- a purpose of the dedicated compression chambers is to have two separate non-mixing inlet refrigerant streams, each compressing refrigerant from a particular thermodynamic state to a common discharge thermodynamic state.
- a refrigerant system is provided with an economizer cycle, where an economized refrigerant stream is returned from the economizer circuit back to a dedicated economizer compression chamber (or a separate compressor) through an economizer circuit return line.
- a main refrigerant stream is returned to its own dedicated main compression chamber (or a compressor) through a suction line.
- a bypass line communicates the two refrigerant flow lines upstream of their corresponding inlets to the dedicated compression chambers (or compressors).
- the two inlet refrigerant streams are allowed to selectively communicate and mix with each other via the bypass line.
- the bypass line may have a small orifice which always communicates the two refrigerant streams.
- the bypass line may include a controlled valve.
- the bypass line may include a combination of these two options.
- FIG. 1 shows a prior art system
- FIG. 2 shows a schematic of a first embodiment.
- FIG. 3 shows a schematic of a second embodiment.
- FIG. 4 shows a schematic of a third embodiment.
- FIG. 5 shows a schematic of a fourth embodiment.
- FIG. 1 shows a prior art refrigerant system 20 .
- a compression unit 22 includes at least two chambers, cylinders, or compressors 24 and 26 .
- the two compression chambers compress refrigerant and deliver it downstream to a heat rejection exchanger 28 .
- the heat rejection exchanger 28 can be a condenser (if the refrigerant discharge thermodynamic state is below the critical point) or a gas cooler (if the refrigerant discharge thermodynamic state is above the critical point).
- An expansion device 29 is positioned downstream of the heat rejection heat exchanger, and partially expands refrigerant passing into a flash tank 30 to an intermediate pressure.
- An expansion device 34 is positioned downstream of the flash tank 30 , to control the amount of refrigerant reaching an evaporator 36 , and expands this refrigerant to a pressure approximating the suction pressure.
- a liquid refrigerant is separated from a vapor refrigerant.
- the liquid refrigerant from the flash tank 30 is expanded to a two-phase thermodynamic state in the expansion device 34 , flows through the evaporator 36 , where it evaporates and is typically superheated, passes through a suction line 38 and is returned to the dedicated main compression chamber 26 .
- the separated vapor refrigerant passes through a return line 32 of the economizer circuit to its dedicated compression chamber 24 .
- the lines 32 and 38 are maintained strictly separate.
- a purpose of the two separate lines delivering refrigerant to two dedicated compression chambers 24 and 26 is to have refrigerant in each of the compression chambers be closer to homogeneous conditions than if the two refrigerant flows were allowed to mix.
- FIG. 2 shows an embodiment 40 wherein the compression unit 42 has a dedicated economizer compression chamber 44 and a dedicated main compression chamber 46 .
- a bypass line 48 including a restriction 49 is provided to communicate an economizer refrigerant flow and a main refrigerant flow.
- This restriction can be in a form of an orifice; however it can also be a capillary tube or any other type of a restriction that throttles the refrigerant flow.
- the size of the orifice is selected to have a cross-sectional area between 0.1 to 3 square millimeters.
- Other restriction types may have a different cross-sectional area; however their effective cross-sectional area is sized to correspond to an equivalent orifice area in the range mentioned above.
- bypass line 48 A purpose of this bypass line 48 is to allow pressure equalization on startup. This will allow reduce motor starting torque, resulting in a more efficient operation, and allow the use of smaller and less expensive motors. Also, the orifice allows drainage of lubricating oil from the economizer line 32 to the suction line 38 after shutdown. A shutoff valve 33 may be included on the economizer circuit return line 32 .
- FIG. 3 shows an embodiment 50 having a compression unit 52 having dedicated compression chambers 54 and 56 .
- the bypass line 58 includes an electrically controlled valve, which in this embodiment is disclosed as a controlled solenoid valve 59 , which may be opened or closed.
- the solenoid valve may be opened to allow mixing of main and economized refrigerant streams during continuous operation, or can be opened prior to startup for pressure equalization, or can be opened at or after shutdown for oil return.
- the valve 59 may be operated in a pulse mode such as, for instance, to facilitate oil return or unload the compression unit 50 .
- the valve 59 may be of a modulating type to tailor valve opening to specific operating conditions (operating pressures, in particular) and precisely match thermal load demands in the conditioned space.
- a refrigerant system 60 has a compression unit 62 with dedicated compression chambers 64 and 66 , as in the prior embodiments.
- the bypass function now has both the solenoid valve 59 on the bypass line 58 and an orifice 68 on a branch bypass line 66 .
- the embodiment 60 would achieve the benefits of each of the embodiments of FIGS. 2 and 3 , and allow the control at shutdown or startup without the need to open the valve 59 .
- the bypass lines 58 and 66 may be arranged in a parallel configuration, between the economizer circuit return line 32 and the main circuit suction line 38 , as well.
- FIG. 5 shows yet another embodiment 80 having a compression unit 82 with separate compression chambers 84 and 86 .
- the economizer function is provided by an economizer heat exchanger 94 , rather than the flash tank 30 of previous embodiments.
- a tap line 90 taps a portion of refrigerant from a main refrigerant flowing through a liquid line 88 and passes this refrigerant through an economizer expansion device 92 , where it is expanded to a lower intermediate pressure and temperature. This would allow the refrigerant in the tap line 90 to further cool the main refrigerant in the liquid line 88 , while passing through the economizer heat exchanger 94 .
- the economized refrigerant typically in the vapor thermodynamic state, flows into the return line 96 of the economizer circuit.
- a main circuit expansion device 34 is positioned downstream of the economizer heat exchanger 94 to control the amount of liquid refrigerant reaching the evaporator 36 . While the economized refrigerant flow in the tap line 90 and the main refrigerant flow in the liquid line 88 are shown passing through the economizer heat exchanger 94 in the same direction, in practice, they are preferably flown in counterflow relationship. The two refrigerant streams are shown flowing in the same direction for illustration simplicity only. Furthermore, the tap line 90 may be positioned downstream of the economizer heat exchanger 94 .
- bypass line 58 is shown with the solenoid valve 59 .
- the economizer heat exchanger 94 may be utilized in the embodiments of FIG. 2 or 4 as well, instead of the flash tank 30 .
- the flow control device 59 may have an adjustable orifice to control the amount of communicated refrigerant between the dedicated economizer and main compression chambers, based, for instance, on operating conditions and thermal load demand in the conditioned space.
- the solenoid valve 59 may be controlled by a pulse width modulation technique to achieve similar results for compressor unit unloading or to facilitate oil return and assure reliable compressor operation.
- each compression chamber can be represented by a single cylinder or multiple cylinders, as for example, may be the case for a reciprocating compressor.
- the bypass line can be located internally or externally, in relation to the compressor shell. If the compression chambers are independent compressors then the preferable location for the bypass line would be external to these compressors.
- each of the dedicated compression chambers may have a number of sequential compression stages, with the dedicated main compression chambers having a higher number of sequential compression stages then the dedicated economizer compression chambers, since they operate between higher pressure differentials.
- This invention would apply to a broad range of refrigerants including, but not limited to, R744, R22, R134a, R410A, R407C, R290, R600a and their combinations.
- 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.
- the refrigerant system of this invention can be a subcritical of transcritical system.
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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)
- Applications Or Details Of Rotary Compressors (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
A refrigerant system has an economizer cycle. A vapor refrigerant from the economizer loop is returned to a dedicated economizer compression chamber. A main refrigerant is returned to a dedicated main compressor chamber. A bypass line communicates the two refrigerant flows.
Description
- This application relates to a refrigerant system having an economizer cycle, and wherein an economized refrigerant flow is returned to an economizer compression chamber of a compression unit, and a main refrigerant flow is returned to a main compression chamber of a compression unit, wherein a bypass refrigerant line communicates the two refrigerant flows upstream of their corresponding compression chambers.
- Refrigerant compressors compress and circulate a refrigerant throughout a refrigerant system to condition a secondary fluid, typically delivered to a climate-controlled space. In a basic refrigerant system, a compressor compresses a refrigerant and delivers it to a heat rejection heat exchanger. Refrigerant from the heat rejection heat exchanger passes through an expansion device, in which its pressure and temperature are reduced. Downstream of the expansion device, the refrigerant passes through a heat accepting heat exchanger, and then back to the compressor. As known, the heat accepting heat exchanger is typically an evaporator, and the heat rejecting heat exchanger is a condenser for subcritical applications and a gas cooler for transcritical applications.
- One option in a refrigerant system design to enhance performance is the use of an economizer, or vapor injection function. When an economizer function is activated, a portion of refrigerant is tapped from a main refrigerant stream downstream of the heat rejection heat exchanger. In one configuration, this tapped refrigerant is passed through an auxiliary expansion device, to be expanded to an intermediate pressure and temperature, and then this partially expanded tapped refrigerant passes in heat exchange relationship with a main refrigerant flow in an economizer heat exchanger. In this manner, the main refrigerant flow is cooled such that it will have a greater thermodynamic potential when it reaches the heat accepting heat exchanger. The tapped refrigerant, typically in a superheated thermodynamic state, is returned to the compressor.
- As known, an economizer function can be performed in either a flash tank or in an economizer heat exchanger. For purposes of this application, the two devices will be both known as an “economizer heat exchanger.”
- As described in European Patent Application EP1498667, the vapor refrigerant is returned to a dedicated economizer compression chamber or a compressor. The main refrigerant flow is returned from the heat accepting heat exchanger back to its own dedicated compression chamber or compressor. This known system maintains the economizer and suction refrigerant flows completely isolated from each other. A purpose of the dedicated compression chambers is to have two separate non-mixing inlet refrigerant streams, each compressing refrigerant from a particular thermodynamic state to a common discharge thermodynamic state.
- In a disclosed embodiment of this invention, a refrigerant system is provided with an economizer cycle, where an economized refrigerant stream is returned from the economizer circuit back to a dedicated economizer compression chamber (or a separate compressor) through an economizer circuit return line. A main refrigerant stream is returned to its own dedicated main compression chamber (or a compressor) through a suction line. A bypass line communicates the two refrigerant flow lines upstream of their corresponding inlets to the dedicated compression chambers (or compressors). In this arrangement, the two inlet refrigerant streams are allowed to selectively communicate and mix with each other via the bypass line. In one embodiment, the bypass line may have a small orifice which always communicates the two refrigerant streams. In a second embodiment, the bypass line may include a controlled valve. In a third embodiment, the bypass line may include a combination of these two options.
- 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.
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FIG. 1 shows a prior art system. -
FIG. 2 shows a schematic of a first embodiment. -
FIG. 3 shows a schematic of a second embodiment. -
FIG. 4 shows a schematic of a third embodiment. -
FIG. 5 shows a schematic of a fourth embodiment. -
FIG. 1 shows a priorart refrigerant system 20. As known acompression unit 22 includes at least two chambers, cylinders, orcompressors heat rejection exchanger 28. Theheat rejection exchanger 28 can be a condenser (if the refrigerant discharge thermodynamic state is below the critical point) or a gas cooler (if the refrigerant discharge thermodynamic state is above the critical point). Anexpansion device 29 is positioned downstream of the heat rejection heat exchanger, and partially expands refrigerant passing into aflash tank 30 to an intermediate pressure. Anexpansion device 34 is positioned downstream of theflash tank 30, to control the amount of refrigerant reaching anevaporator 36, and expands this refrigerant to a pressure approximating the suction pressure. In theflash tank 30, a liquid refrigerant is separated from a vapor refrigerant. The liquid refrigerant from theflash tank 30 is expanded to a two-phase thermodynamic state in theexpansion device 34, flows through theevaporator 36, where it evaporates and is typically superheated, passes through asuction line 38 and is returned to the dedicatedmain compression chamber 26. The separated vapor refrigerant passes through areturn line 32 of the economizer circuit to itsdedicated compression chamber 24. In the known prior art system, thelines dedicated compression chambers -
FIG. 2 shows anembodiment 40 wherein thecompression unit 42 has a dedicatedeconomizer compression chamber 44 and a dedicatedmain compression chamber 46. However, abypass line 48 including arestriction 49 is provided to communicate an economizer refrigerant flow and a main refrigerant flow. This restriction can be in a form of an orifice; however it can also be a capillary tube or any other type of a restriction that throttles the refrigerant flow. Typically the size of the orifice is selected to have a cross-sectional area between 0.1 to 3 square millimeters. Other restriction types may have a different cross-sectional area; however their effective cross-sectional area is sized to correspond to an equivalent orifice area in the range mentioned above. - A purpose of this
bypass line 48 is to allow pressure equalization on startup. This will allow reduce motor starting torque, resulting in a more efficient operation, and allow the use of smaller and less expensive motors. Also, the orifice allows drainage of lubricating oil from theeconomizer line 32 to thesuction line 38 after shutdown. Ashutoff valve 33 may be included on the economizercircuit return line 32. -
FIG. 3 shows anembodiment 50 having acompression unit 52 havingdedicated compression chambers bypass line 58 includes an electrically controlled valve, which in this embodiment is disclosed as a controlledsolenoid valve 59, which may be opened or closed. The solenoid valve may be opened to allow mixing of main and economized refrigerant streams during continuous operation, or can be opened prior to startup for pressure equalization, or can be opened at or after shutdown for oil return. Also, in some circumstances, thevalve 59 may be operated in a pulse mode such as, for instance, to facilitate oil return or unload thecompression unit 50. Further, thevalve 59 may be of a modulating type to tailor valve opening to specific operating conditions (operating pressures, in particular) and precisely match thermal load demands in the conditioned space. - As shown in
FIG. 4 , arefrigerant system 60 has acompression unit 62 withdedicated compression chambers solenoid valve 59 on thebypass line 58 and anorifice 68 on abranch bypass line 66. Theembodiment 60 would achieve the benefits of each of the embodiments ofFIGS. 2 and 3 , and allow the control at shutdown or startup without the need to open thevalve 59. Thebypass lines circuit return line 32 and the maincircuit suction line 38, as well. -
FIG. 5 shows yet anotherembodiment 80 having acompression unit 82 withseparate compression chambers embodiment 80, the economizer function is provided by aneconomizer heat exchanger 94, rather than theflash tank 30 of previous embodiments. As known, atap line 90 taps a portion of refrigerant from a main refrigerant flowing through aliquid line 88 and passes this refrigerant through aneconomizer expansion device 92, where it is expanded to a lower intermediate pressure and temperature. This would allow the refrigerant in thetap line 90 to further cool the main refrigerant in theliquid line 88, while passing through theeconomizer heat exchanger 94. The economized refrigerant, typically in the vapor thermodynamic state, flows into thereturn line 96 of the economizer circuit. A maincircuit expansion device 34 is positioned downstream of theeconomizer heat exchanger 94 to control the amount of liquid refrigerant reaching theevaporator 36. While the economized refrigerant flow in thetap line 90 and the main refrigerant flow in theliquid line 88 are shown passing through theeconomizer heat exchanger 94 in the same direction, in practice, they are preferably flown in counterflow relationship. The two refrigerant streams are shown flowing in the same direction for illustration simplicity only. Furthermore, thetap line 90 may be positioned downstream of theeconomizer heat exchanger 94. - Similar to previous embodiments, the
bypass line 58 is shown with thesolenoid valve 59. Further, theeconomizer heat exchanger 94 may be utilized in the embodiments ofFIG. 2 or 4 as well, instead of theflash tank 30. - As stated above, the
flow control device 59 may have an adjustable orifice to control the amount of communicated refrigerant between the dedicated economizer and main compression chambers, based, for instance, on operating conditions and thermal load demand in the conditioned space. On the other hand, thesolenoid valve 59 may be controlled by a pulse width modulation technique to achieve similar results for compressor unit unloading or to facilitate oil return and assure reliable compressor operation. - It should be pointed out that many different compressor types could be used in this invention. For example, scroll, screw, rotary, or reciprocating compressors can be employed. The economized flow and main flow chambers can be separate compressors, or these compression chambers can be positioned within a single compressor. In the context of this invention, each compression chamber can be represented by a single cylinder or multiple cylinders, as for example, may be the case for a reciprocating compressor. If the compression chambers are located within a single compressor, then the bypass line can be located internally or externally, in relation to the compressor shell. If the compression chambers are independent compressors then the preferable location for the bypass line would be external to these compressors. Further, each of the dedicated compression chambers may have a number of sequential compression stages, with the dedicated main compression chambers having a higher number of sequential compression stages then the dedicated economizer compression chambers, since they operate between higher pressure differentials.
- This invention would apply to a broad range of refrigerants including, but not limited to, R744, R22, R134a, R410A, R407C, R290, R600a and their combinations.
- 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. The refrigerant system of this invention can be a subcritical of transcritical system.
- Although an 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 (25)
1. A refrigerant system comprising:
at least two compression chambers, said at least two compression chambers for compressing a refrigerant, a downstream heat rejection heat exchanger, a refrigerant line passing from the heat rejection heat exchanger into an economizer cycle, and a main refrigerant line passing from the economizer cycle through a main expansion device and to a heat accepting heat exchanger, a suction line downstream of said heat accepting heat exchanger and extending to at least one of the at least two compression chambers;
a return line being returned from the economizer cycle to at least one other of the at least two compression chambers; and
a bypass line communicating the return line and the suction line.
2. The refrigerant system as set forth in claim 1 , wherein said bypass line includes a restriction to allow continuous communication between the return line and the suction line.
3. The refrigerant system as set forth in claim 2 , wherein said bypass line includes an electrically controlled valve to provide selective communication.
4. The refrigerant system as set forth in claim 3 , wherein said electrically controlled valve is a solenoid on/off valve.
5. The refrigerant system as set forth in claim 3 , wherein said electrically controlled valve is controlled by a pulse width modulation technique.
6. The refrigerant system as set forth in claim 3 , wherein said electrically controlled valve is a modulating valve.
7. The refrigerant system as set forth in claim 3 , wherein said electrically controlled valve is opened to equalize pressure upon refrigerant system shutdown or before startup.
8. The refrigerant system as set forth in claim 2 , wherein said restriction is an orifice.
9. The refrigerant system as set forth in claim 2 , wherein said restriction has a cross-section area between 0.1 square millimeter and 3 square millimeters.
10. The refrigerant system as set forth in claim 2 , wherein said restriction is a capillary tube.
11. The refrigerant system as set forth in claim 1 , further comprising an electrically controlled valve installed in parallel with said bypass line.
12. The refrigerant system as set forth in claim 1 , wherein said economizer cycle includes a flash tank to separate liquid and vapor refrigerant phases.
13. The refrigerant system as set forth in claim 1 , wherein said compression chambers are independent compressors.
14. The refrigerant system as set forth in claim 1 , wherein said compression chambers are positioned within a single compressor.
15. The refrigerant system as set forth in claim 14 , wherein said bypass line is located externally in relation to the compressor.
16. The refrigerant system as set forth in claim 14 , wherein said bypass line is located internally in relation to the compressor.
17. The refrigerant system as set forth in claim 14 , wherein said compressor is reciprocating compressor and said compression chambers are reciprocating compressor cylinders.
18. The refrigerant system as set forth in claim 1 , wherein at least one of said at least two compression chambers is represented by sequential compression stages.
19. The refrigerant system as set forth in claim 1 , wherein said economizer cycle includes an economizer heat exchanger having an economizer expansion device expanding a tapped portion of refrigerant and passing it through the economizer heat exchanger to exchange heat with the main refrigerant, with said tapped refrigerant being returned through the return line.
20. The refrigerant system as set forth in claim 1 , wherein at least one said compression chamber is a part of at least one reciprocating compressor cylinder.
21. The refrigerant system as set forth in claim 1 , wherein the refrigerant streams in said return line and suction line are partially combined together at subcritical pressure.
22. The refrigerant system as set forth in claim 1 , wherein said refrigerant is selected from a group consisting of R744, R22, R410A, R134a, R407C, R290, R600a refrigerants or their combinations.
23. A method of operating a refrigerant system comprising:
providing at least two compression chambers, said at least two compression chambers compressing refrigerant and delivering the refrigerant to a downstream heat rejection heat exchanger, refrigerant passing from the heat rejection heat exchanger into an economizer cycle, and a main flow of refrigerant passing from the economizer cycle through a main expansion device and to a heat accepting heat exchanger, refrigerant from the heat accepting heat exchanger passing through a suction line to at least one of the at least two compression chambers;
an economized flow of refrigerant, that is at least largely vapor, being returned from the economizer cycle to at least one other of the at least two compression chambers through a return line; and
communicating the return line and the suction line through a bypass line.
24. The method as set forth in claim 23 , wherein an electrically controlled valve on said bypass line is opened to unload the refrigerant system.
25. The method as set forth in claim 23 , wherein an electrically controlled valve on said bypass line is opened to return oil.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/US2007/079260 WO2009041959A1 (en) | 2007-09-24 | 2007-09-24 | Refrigerant system with bypass line and dedicated economized flow compression chamber |
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US12/831,108 Division US20110027787A1 (en) | 2004-11-08 | 2010-07-06 | Methods and systems for identifying and isolating stem cells and for observing mitochondrial structure and distribution in living cells |
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US20100199715A1 true US20100199715A1 (en) | 2010-08-12 |
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US12/667,280 Abandoned US20100199715A1 (en) | 2007-09-24 | 2007-09-24 | Refrigerant system with bypass line and dedicated economized flow compression chamber |
Country Status (6)
Country | Link |
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US (1) | US20100199715A1 (en) |
EP (1) | EP2203693B1 (en) |
CN (1) | CN101809378B (en) |
ES (1) | ES2754027T3 (en) |
HK (1) | HK1147310A1 (en) |
WO (1) | WO2009041959A1 (en) |
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US20100024470A1 (en) * | 2007-05-23 | 2010-02-04 | Alexander Lifson | Refrigerant injection above critical point in a transcritical refrigerant system |
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US8631666B2 (en) | 2008-08-07 | 2014-01-21 | Hill Phoenix, Inc. | Modular CO2 refrigeration system |
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US20160258662A1 (en) * | 2015-03-04 | 2016-09-08 | Heatcraft Refrigeration Products Llc | Modulated oversized compressors configuration for flash gas bypass in a carbon dioxide refrigeration system |
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US10598395B2 (en) | 2018-05-15 | 2020-03-24 | Emerson Climate Technologies, Inc. | Climate-control system with ground loop |
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 |
US11149971B2 (en) | 2018-02-23 | 2021-10-19 | Emerson Climate Technologies, Inc. | Climate-control system with thermal storage device |
US11346583B2 (en) * | 2018-06-27 | 2022-05-31 | Emerson Climate Technologies, Inc. | Climate-control system having vapor-injection compressors |
US11506430B2 (en) | 2019-07-15 | 2022-11-22 | Climate Master, Inc. | Air conditioning system with capacity control and controlled hot water generation |
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US20100024470A1 (en) * | 2007-05-23 | 2010-02-04 | Alexander Lifson | Refrigerant injection above critical point in a transcritical refrigerant system |
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US9360237B2 (en) * | 2011-04-21 | 2016-06-07 | Carrier Corporation | Transcritical refrigerant vapor system with capacity boost |
US20140053585A1 (en) * | 2011-04-21 | 2014-02-27 | Carrier Corporation | Transcritical Refrigerant Vapor System With Capacity Boost |
US9353980B2 (en) | 2013-05-02 | 2016-05-31 | Emerson Climate Technologies, Inc. | Climate-control system having multiple compressors |
WO2014179699A1 (en) * | 2013-05-02 | 2014-11-06 | Emerson Climate Technologies, Inc. | Climate-control system having multiple compressors |
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US10753661B2 (en) | 2014-09-26 | 2020-08-25 | Waterfurnace International, Inc. | Air conditioning system with vapor injection compressor |
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US11480372B2 (en) | 2014-09-26 | 2022-10-25 | Waterfurnace International Inc. | Air conditioning system with vapor injection compressor |
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US20160195305A1 (en) * | 2015-01-05 | 2016-07-07 | General Electric Company | Electrochemical refrigeration systems and appliances |
US20160195306A1 (en) * | 2015-01-05 | 2016-07-07 | General Electric Company | Electrochemical refrigeration systems and appliances |
US20160195307A1 (en) * | 2015-01-05 | 2016-07-07 | General Electric Company | Electrochemical refrigeration systems and appliances |
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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 |
US11585608B2 (en) * | 2018-02-05 | 2023-02-21 | Emerson Climate Technologies, Inc. | Climate-control system having thermal storage tank |
US11149971B2 (en) | 2018-02-23 | 2021-10-19 | Emerson Climate Technologies, Inc. | Climate-control system with thermal storage device |
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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 |
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Also Published As
Publication number | Publication date |
---|---|
ES2754027T3 (en) | 2020-04-15 |
HK1147310A1 (en) | 2011-08-05 |
EP2203693B1 (en) | 2019-10-30 |
WO2009041959A1 (en) | 2009-04-02 |
CN101809378B (en) | 2014-06-25 |
EP2203693A1 (en) | 2010-07-07 |
EP2203693A4 (en) | 2012-09-12 |
CN101809378A (en) | 2010-08-18 |
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Owner name: CARRIER CORPORATION, CONNECTICUT Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:LIFSON, ALEXANDER;TARAS, MICHAEL F.;REEL/FRAME:023717/0182 Effective date: 20070919 |
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