EP2203693B1 - Kältemittelsystem mit umgehungsleitung und eigener strömungskompressionskammer mit economiser - Google Patents

Kältemittelsystem mit umgehungsleitung und eigener strömungskompressionskammer mit economiser Download PDF

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Publication number
EP2203693B1
EP2203693B1 EP07843032.9A EP07843032A EP2203693B1 EP 2203693 B1 EP2203693 B1 EP 2203693B1 EP 07843032 A EP07843032 A EP 07843032A EP 2203693 B1 EP2203693 B1 EP 2203693B1
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Prior art keywords
refrigerant
refrigerant system
set forth
line
economizer
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EP07843032.9A
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English (en)
French (fr)
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EP2203693A1 (de
EP2203693A4 (de
Inventor
Alexander Lifson
Michael F. Taras
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Carrier Corp
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Carrier Corp
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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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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 (which may be in a separate compressor) through an economizer circuit return line.
  • a main refrigerant stream is returned to its own dedicated main compression chamber (which may be in a separate compressor) through a suction line.
  • a bypass line communicates the two refrigerant flow lines upstream of their corresponding inlets to the dedicated compression chambers. In this arrangement, 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.
  • Figure 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.
  • Figure 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 Figures 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 Figure 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)

Claims (15)

  1. Kältemittelsystem, umfassend:
    zwei Kompressionskammern, wobei die zwei Kompressionskammern (44, 46; 54, 56; 64, 66; 84, 86) dem Komprimieren eines Kältemittels dienen;
    einen stromabwärtigen Wärmeabweisungswärmetauscher (28);
    eine Kältemittelleitung, die von dem Wärmeabweisungswärmetauscher in einen Economiser-Zyklus verläuft;
    eine Hauptkältemittelleitung, die von dem Economiser-Zyklus durch eine Hauptexpansionsvorrichtung (34) und zu einem wärmeaufnehmenden Wärmetauscher (36) verläuft;
    eine Saugleitung (38) stromabwärts des wärmeaufnehmenden Wärmetauschers und die sich zu zumindest einer ersten der zwei Kompressionskammern erstreckt, bei der es sich damit um eine eigene Hauptkältemittelkompressionskammer (46; 54; 64; 86) handelt;
    eine Rückführleitung (32), die von dem Economiser-Zyklus zu einer zweiten der zwei Kompressionskammern zurückgeführt wird, bei der es sich damit um eine eigene Economiser-Kompressionskammer (44; 54; 64; 84) handelt; und
    eine Umgehungsleitung, die die Rückführleitung und die Saugleitung kommuniziert;
    wobei die eigene Hauptkältemittelkompressionskammer und die eigene Economiser-Kompressionskammer der Aufnahme von parallelen Einlasskältemittelströmen dienen.
  2. Kältemittelsystem nach Anspruch 1, wobei die Umgehungsleitung (48; 58; 66) eine Einschränkung (49; 68) beinhaltet, um durchgehende Kommunikation zwischen der Rückführleitung (32) und der Saugleitung (38) zu ermöglichen.
  3. Kältemittelsystem nach Anspruch 2, wobei die Umgehungsleitung (58) ein elektrisch gesteuertes Ventil (59) beinhaltet, um selektive Kommunikation bereitzustellen.
  4. Kältemittelsystem nach Anspruch 3, wobei das elektrisch gesteuerte Ventil (59) ein Solenoid-Ein-/Aus-Ventil (59) ist.
  5. Kältemittelsystem nach Anspruch 3, wobei das elektrisch gesteuerte Ventil (59) durch eine Impulsbreitenmodulationstechnik gesteuert wird.
  6. Kältemittelsystem nach Anspruch 3, wobei das elektrisch gesteuerte Ventil (59) ein modulierendes Ventil ist.
  7. Kältemittelsystem nach Anspruch 3, wobei das elektrisch gesteuerte Ventil (59) geöffnet wird, um beim Herunterfahren des Kältemittelsystems oder vor dem Hochfahren Druck auszugleichen.
  8. Kältemittelsystem nach Anspruch 2, wobei die Einschränkung (49; 68) eine Öffnung ist.
  9. Kältemittelsystem nach Anspruch 2, wobei die Einschränkung (49; 68) einen Querschnittsbereich zwischen 0,1 Quadratmillimeter und 3 Quadratmillimetern aufweist.
  10. Kältemittelsystem nach Anspruch 2, wobei die Einschränkung (49; 68) eine Kapillarröhre ist.
  11. Kältemittelsystem nach Anspruch 1, ferner umfassend ein elektrisch gesteuertes Ventil (59), das parallel zu der Umgehungsleitung (66) installiert ist.
  12. Kältemittelsystem nach Anspruch 1, wobei der Economiser-Zyklus einen Entspannungstank (30) beinhaltet, um Flüssig- und Dampfkältemittelphasen zu trennen.
  13. Kältemittelsystem nach Anspruch 1, wobei sich die zwei Kompressionskammern (44, 46; 54, 56; 64, 66; 84, 86) innerhalb unabhängiger Kompressoren befinden.
  14. Kältemittelsystem nach Anspruch 1, wobei die zwei Kompressionskammern (44, 46; 54, 56; 64, 66; 84, 86) innerhalb eines einzelnen Kompressors positioniert sind.
  15. Kältemittelsystem nach Anspruch 14, wobei sich die Umgehungsleitung (48; 58; 66) extern in Bezug auf den einzelnen Kompressor befindet.
EP07843032.9A 2007-09-24 2007-09-24 Kältemittelsystem mit umgehungsleitung und eigener strömungskompressionskammer mit economiser Active EP2203693B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2007/079260 WO2009041959A1 (en) 2007-09-24 2007-09-24 Refrigerant system with bypass line and dedicated economized flow compression chamber

Publications (3)

Publication Number Publication Date
EP2203693A1 EP2203693A1 (de) 2010-07-07
EP2203693A4 EP2203693A4 (de) 2012-09-12
EP2203693B1 true EP2203693B1 (de) 2019-10-30

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US (1) US20100199715A1 (de)
EP (1) EP2203693B1 (de)
CN (1) CN101809378B (de)
ES (1) ES2754027T3 (de)
HK (1) HK1147310A1 (de)
WO (1) WO2009041959A1 (de)

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ES2754027T3 (es) 2020-04-15
CN101809378A (zh) 2010-08-18
EP2203693A1 (de) 2010-07-07
EP2203693A4 (de) 2012-09-12
CN101809378B (zh) 2014-06-25
WO2009041959A1 (en) 2009-04-02
US20100199715A1 (en) 2010-08-12
HK1147310A1 (en) 2011-08-05

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