EP2203693A1 - Système réfrigérant ayant une conduite de dérivation et une chambre de compression de flux d'économiseur spécialisée - Google Patents

Système réfrigérant ayant une conduite de dérivation et une chambre de compression de flux d'économiseur spécialisée

Info

Publication number
EP2203693A1
EP2203693A1 EP07843032A EP07843032A EP2203693A1 EP 2203693 A1 EP2203693 A1 EP 2203693A1 EP 07843032 A EP07843032 A EP 07843032A EP 07843032 A EP07843032 A EP 07843032A EP 2203693 A1 EP2203693 A1 EP 2203693A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
set forth
refrigerant system
line
compression chambers
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP07843032A
Other languages
German (de)
English (en)
Other versions
EP2203693B1 (fr
EP2203693A4 (fr
Inventor
Alexander Lifson
Michael F. Taras
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP2203693A1 publication Critical patent/EP2203693A1/fr
Publication of EP2203693A4 publication Critical patent/EP2203693A4/fr
Application granted granted Critical
Publication of EP2203693B1 publication Critical patent/EP2203693B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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. 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.
  • 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.
  • Figure 1 shows a prior art system.
  • Figure 2 shows a schematic of a first embodiment.
  • Figure 3 shows a schematic of a second embodiment.
  • Figure 4 shows a schematic of a third embodiment.
  • Figure 5 shows a schematic of a fourth embodiment.
  • 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.
  • 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. However, 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, Rl 34a, 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.

Abstract

La présente invention concerne un système réfrigérant qui a un cycle économique. Un fluide frigorigène en phase vapeur provenant de la boucle d'économiseur est renvoyé à une chambre de compression d'économiseur spécialisée. Un fluide frigorigène principal est renvoyé à une chambre de compression principale spécialisée. Une conduite de dérivation communique avec les écoulements de fluide frigorigène.
EP07843032.9A 2007-09-24 2007-09-24 Système réfrigérant ayant une conduite de dérivation et une chambre de compression de flux d'économiseur spécialisée Active EP2203693B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2007/079260 WO2009041959A1 (fr) 2007-09-24 2007-09-24 Système réfrigérant ayant une conduite de dérivation et une chambre de compression de flux d'économiseur spécialisée

Publications (3)

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

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07843032.9A Active EP2203693B1 (fr) 2007-09-24 2007-09-24 Système réfrigérant ayant une conduite de dérivation et une chambre de compression de flux d'économiseur spécialisée

Country Status (6)

Country Link
US (1) US20100199715A1 (fr)
EP (1) EP2203693B1 (fr)
CN (1) CN101809378B (fr)
ES (1) ES2754027T3 (fr)
HK (1) HK1147310A1 (fr)
WO (1) WO2009041959A1 (fr)

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Publication number Publication date
CN101809378B (zh) 2014-06-25
US20100199715A1 (en) 2010-08-12
WO2009041959A1 (fr) 2009-04-02
EP2203693B1 (fr) 2019-10-30
EP2203693A4 (fr) 2012-09-12
HK1147310A1 (en) 2011-08-05
ES2754027T3 (es) 2020-04-15
CN101809378A (zh) 2010-08-18

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