US20080302129A1 - Refrigeration system for transcritical operation with economizer and low-pressure receiver - Google Patents

Refrigeration system for transcritical operation with economizer and low-pressure receiver Download PDF

Info

Publication number
US20080302129A1
US20080302129A1 US11/801,188 US80118807A US2008302129A1 US 20080302129 A1 US20080302129 A1 US 20080302129A1 US 80118807 A US80118807 A US 80118807A US 2008302129 A1 US2008302129 A1 US 2008302129A1
Authority
US
United States
Prior art keywords
intercooler
outlet
pressure
inlet
throttling device
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.)
Abandoned
Application number
US11/801,188
Inventor
Dieter Mosemann
Dmytro Zaytsev
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.)
MOSEMANN DR DIETER
GEA Refrigeration Germany GmbH
Original Assignee
Individual
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 Individual filed Critical Individual
Assigned to MOSEMANN, DR. DIETER reassignment MOSEMANN, DR. DIETER ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ZAYTSEV, DR. DMYTRO
Publication of US20080302129A1 publication Critical patent/US20080302129A1/en
Assigned to GRASSO GMBH REFRIGERATION TECHNOLOGY reassignment GRASSO GMBH REFRIGERATION TECHNOLOGY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MOSEMANN, DIETER
Assigned to GEA REFRIGERATION GERMANY GMBH reassignment GEA REFRIGERATION GERMANY GMBH CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: GRASSO GMBH REFRIGERATION TECHNOLOGY
Abandoned legal-status Critical Current

Links

Images

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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B40/02—Subcoolers
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B2400/13—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
    • 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
    • F25B2400/23—Separators

Definitions

  • This invention relates to a refrigeration apparatus for transcritical operation with screw compressors featuring geometrically controlled inlet and outlet ports operating at least on three pressure levels.
  • the pressure levels comprise the suction pressure prevailing on the compressor suction side and being close to the pressure in the evaporator, the intermediate pressure prevailing at the economizer port, and the discharge pressure acting on the compressor discharge side and being close to the pressure in a gas cooler.
  • the pertinent sides of the compressor are also designated as low-pressure side, intake side or suction side, and as high-pressure side or discharge side respectively.
  • the pressure on the high-pressure side is higher than the pressure at the critical point of the refrigerant. Therefore, this process is designated as transcritical or overcritical refrigeration process.
  • the economizer port is arranged between suction- and discharge side of the compressor.
  • the inlet process to the working cavity starts when there is no more flow connection of this working cavity to the compressor suction side.
  • the geometric volume of the working cavity considered has reached its maximum.
  • the geometric volume of the working cavity considered can be constant (transfer phase) or can decrease due to rotation of rotors.
  • the invention relates to a refrigeration apparatus featuring a heat exchanger, a so-called aftercooler, arranged in or at the low-pressure liquid separator and communicating with the liquid separator, and in this aftercooler the refrigerant—the working fluid—being under discharge pressure is subcooled prior to its expansion nearly to evaporation temperature, thus changing from the vaporous phase to the liquid phase, before it is expanded into the evaporators at the throttling device of the refrigeration apparatus.
  • the pressure upstream of this throttling device is kept constant by opening or closing it more or less respectively enabling the compressor to operate at constant discharge pressure.
  • the refrigerating capacity of the refrigeration apparatus changes depending on the temperature to which the refrigerant was cooled down in the gas cooler. It will be reduced as a result of higher outlet temperatures at the gas cooler, because at higher gas cooler outlet temperatures more working fluid will evaporate in the low-pressure liquid separator for cooling-down the working fluid in the aftercooler prior to expansion than at lower gas cooler outlet temperatures. Therefore, the efficiency of the refrigeration apparatus will decrease with increasing temperature at the gas cooler.
  • the object of the invention is to improve the process and to increase the efficiency of the refrigeration apparatus.
  • the refrigeration apparatus for transcritical operation comprises in addition to the components gas cooler, aftercooler, evaporator with low-pressure liquid separator, compressor, first controllable throttling device and interconnecting piping between the mentioned components a second controllable throttling device and an intercooler that comprises two flow paths separated by heat-exchanging surfaces, wherein a first flow path inlet of the intercooler is connected to the gas cooler outlet, a first flow path outlet of the intercooler is connected to the aftercooler inlet, a second flow pass inlet of the intercooler is connected to the outlet of the second throttling device and a second flow pass outlet of the intercooler is connected to the economizer port of the compressor, and the second throttling device inlet is connected to the piping either upstream or downstream of the aftercooler and the second throttling device outlet is connected to the second flow pass inlet of the intercooler.
  • a part of the refrigerant is taken from the main flow either upstream or downstream of the aftercooler and led via the second controllable throttling device, where the refrigerant pressure decreases from discharge pressure to intermediate pressure and the temperature drops, to the second flow path of the intercooler to cool down the working fluid in the first flow path of the intercooler.
  • the refrigerant being under discharge pressure is cooled down on one side of the heat-exchanging surfaces of the intercooler, while the refrigerant on the other side of the heat-exchanging surfaces of the intercooler evaporates being under intermediate pressure.
  • the refrigerant evaporated is led to the economizer port of the compressor.
  • the aftercooler Due to this operation of the intercooler, the aftercooler is unloaded. As a result of the unloading, less amount of vapor is created in the aftercooler on the side of the low-pressure liquid separator. Thus, with the same compressor size, more vapor can be taken from the evaporator. Therefore, the refrigerating capacity of the refrigeration apparatus and its efficiency will increase.
  • FIG. 1 a simplified schematic for arrangement of compressor and heat exchangers with pertinent interconnecting piping and control devices of the refrigeration apparatus according to the invention.
  • FIG. 2 a Pressure-Enthalpy diagram for a refrigeration- or air conditioning apparatus according to the invention.
  • FIG. 3 a simplified schematic for arrangement of compressor and heat exchangers with pertinent interconnecting piping and control devices for another arrangement example of a refrigeration apparatus according to the invention.
  • FIG. 4 a Pressure-Enthalpy diagram for the arrangement according to the invention in compliance with FIG. 3 .
  • the refrigeration apparatus for transcritical operation comprises a gas cooler 23 , an intercooler 24 , an evaporator 30 , a low-pressure liquid separator 25 communicating with an aftercooler 27 , a screw compressor 21 having geometrically controlled inlet and outlet ports, a first controllable throttling device 28 , a second controllable throttling device 26 and interconnecting piping between the components mentioned.
  • suction pressure 11 prevails on its suction side 29
  • discharge pressure 12 prevails on its discharge side 22 with the pressure on the discharge side 22 being higher than the pressure at the critical point of the refrigerant.
  • the compressor has an economizer port 31 at the housing enabling a flow connection to intercooler 24 , and the pressure in this pipe section lies between discharge pressure and suction pressure.
  • point 1 describes the condition on the suction side of compressor 21 .
  • the outlet condition of the refrigerant after compressor 21 is the inlet condition into gas cooler 23 .
  • the refrigerant passes gas cooler 23 which is fed by a cooling medium, e.g. cooling water, for cooling the refrigerant vapor.
  • a cooling medium e.g. cooling water
  • the refrigerant has the condition at point 3 .
  • intercooler 24 through which two refrigerant flows of the refrigeration apparatus are led, the refrigerant is cooled from point 3 to point 4 .
  • the partial refrigerant flow expanded to intermediate pressure level 10 will be evaporated and superfed via economizer port 31 into the compressor without considerably influencing the suction volume flow.
  • the refrigerant flow is further cooled from point 4 to point 5 in aftercooler 27 wherein liquid evaporates in aftercooler 27 communicating with low-pressure liquid separator 25 , and hence reducing the available volumetric refrigerating capacity by the enthalpy difference from point 1 to point 9 .
  • Point 9 corresponds to the condition of the refrigerant at the evaporator outlet 35 characterized by a two-phase mixture.
  • the intermediate pressure level 10 can be used for changing the refrigerating capacity by way of rising the intermediate pressure, and hence changing the intermediate cooling effect.
  • the refrigeration apparatus for transcritical operation according to FIG. 3 is configured similarly to FIG. 1 with the distinguishing feature that the second flow path of intercooler 24 on its inlet side is connected via piping and second controllable throttling device 32 to the outlet of an intermediate-pressure aftercooler 34 .
  • the inlet of the intermediate-pressure aftercooler 34 is connected to the outlet of the first flow path of intercooler 24 .
  • the outlet side of the second flow path of intercooler 24 is connected to economizer port 31 of compressor 21 via an intermediate-pressure liquid separator 33 .
  • Intermediate-pressure aftercooler 34 communicates with intermediate-pressure liquid separator 33 .
  • point 4 ′ describes the outlet condition from intermediate-pressure aftercooler 34
  • point 13 describes the inlet condition into intercooler 24
  • point 17 describes the outlet condition from intercooler 24 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Lubricants (AREA)

Abstract

A refrigeration apparatus for transcritical operation includes a gas cooler, an aftercooler, an evaporator with a low-pressure liquid separator, a compressor, a first controllable throttling device and interconnecting piping between the mentioned components and in addition a second controllable throttling device and an intercooler that comprises two flow paths separated by heat exchanging surfaces. A first flow path inlet of the intercooler is connected to the gas cooler outlet. A first flow path outlet of the intercooler is connected to the aftercooler inlet. A second flow path inlet of the intercooler is connected to the outlet of the second throttling device. A second flow path outlet of the intercooler is connected to the economizer port of the compressor. The second throttling device inlet is connected to the piping either upstream or downstream of the aftercooler. The second throttling device outlet is connected to the second flow path inlet of the intercooler.

Description

  • This invention relates to a refrigeration apparatus for transcritical operation with screw compressors featuring geometrically controlled inlet and outlet ports operating at least on three pressure levels. The pressure levels comprise the suction pressure prevailing on the compressor suction side and being close to the pressure in the evaporator, the intermediate pressure prevailing at the economizer port, and the discharge pressure acting on the compressor discharge side and being close to the pressure in a gas cooler. The pertinent sides of the compressor are also designated as low-pressure side, intake side or suction side, and as high-pressure side or discharge side respectively. The pressure on the high-pressure side is higher than the pressure at the critical point of the refrigerant. Therefore, this process is designated as transcritical or overcritical refrigeration process. The economizer port is arranged between suction- and discharge side of the compressor. At the economizer port, the inlet process to the working cavity starts when there is no more flow connection of this working cavity to the compressor suction side. In this phase, the geometric volume of the working cavity considered has reached its maximum. Depending on the wrap angle of the rotor profile of the male rotor, number of lobes of both rotors, the geometric volume of the working cavity considered can be constant (transfer phase) or can decrease due to rotation of rotors.
  • The invention relates to a refrigeration apparatus featuring a heat exchanger, a so-called aftercooler, arranged in or at the low-pressure liquid separator and communicating with the liquid separator, and in this aftercooler the refrigerant—the working fluid—being under discharge pressure is subcooled prior to its expansion nearly to evaporation temperature, thus changing from the vaporous phase to the liquid phase, before it is expanded into the evaporators at the throttling device of the refrigeration apparatus.
  • The pressure upstream of this throttling device is kept constant by opening or closing it more or less respectively enabling the compressor to operate at constant discharge pressure. The refrigerating capacity of the refrigeration apparatus changes depending on the temperature to which the refrigerant was cooled down in the gas cooler. It will be reduced as a result of higher outlet temperatures at the gas cooler, because at higher gas cooler outlet temperatures more working fluid will evaporate in the low-pressure liquid separator for cooling-down the working fluid in the aftercooler prior to expansion than at lower gas cooler outlet temperatures. Therefore, the efficiency of the refrigeration apparatus will decrease with increasing temperature at the gas cooler.
  • The object of the invention is to improve the process and to increase the efficiency of the refrigeration apparatus.
  • According to the invention the refrigeration apparatus for transcritical operation comprises in addition to the components gas cooler, aftercooler, evaporator with low-pressure liquid separator, compressor, first controllable throttling device and interconnecting piping between the mentioned components a second controllable throttling device and an intercooler that comprises two flow paths separated by heat-exchanging surfaces, wherein a first flow path inlet of the intercooler is connected to the gas cooler outlet, a first flow path outlet of the intercooler is connected to the aftercooler inlet, a second flow pass inlet of the intercooler is connected to the outlet of the second throttling device and a second flow pass outlet of the intercooler is connected to the economizer port of the compressor, and the second throttling device inlet is connected to the piping either upstream or downstream of the aftercooler and the second throttling device outlet is connected to the second flow pass inlet of the intercooler.
  • According to the invention, a part of the refrigerant is taken from the main flow either upstream or downstream of the aftercooler and led via the second controllable throttling device, where the refrigerant pressure decreases from discharge pressure to intermediate pressure and the temperature drops, to the second flow path of the intercooler to cool down the working fluid in the first flow path of the intercooler. In this way, the refrigerant being under discharge pressure is cooled down on one side of the heat-exchanging surfaces of the intercooler, while the refrigerant on the other side of the heat-exchanging surfaces of the intercooler evaporates being under intermediate pressure. The refrigerant evaporated is led to the economizer port of the compressor.
  • Due to this operation of the intercooler, the aftercooler is unloaded. As a result of the unloading, less amount of vapor is created in the aftercooler on the side of the low-pressure liquid separator. Thus, with the same compressor size, more vapor can be taken from the evaporator. Therefore, the refrigerating capacity of the refrigeration apparatus and its efficiency will increase.
  • In the following, the invention is explained in detail by an example of embodiment.
  • The accompanying drawings show in:
  • FIG. 1 a simplified schematic for arrangement of compressor and heat exchangers with pertinent interconnecting piping and control devices of the refrigeration apparatus according to the invention.
  • FIG. 2 a Pressure-Enthalpy diagram for a refrigeration- or air conditioning apparatus according to the invention.
  • FIG. 3 a simplified schematic for arrangement of compressor and heat exchangers with pertinent interconnecting piping and control devices for another arrangement example of a refrigeration apparatus according to the invention.
  • FIG. 4 a Pressure-Enthalpy diagram for the arrangement according to the invention in compliance with FIG. 3.
    •
  • The refrigeration apparatus for transcritical operation according to FIG. 1 comprises a gas cooler 23, an intercooler 24, an evaporator 30, a low-pressure liquid separator 25 communicating with an aftercooler 27, a screw compressor 21 having geometrically controlled inlet and outlet ports, a first controllable throttling device 28, a second controllable throttling device 26 and interconnecting piping between the components mentioned. When compressor 21 is in operation, suction pressure 11 prevails on its suction side 29, while discharge pressure 12 prevails on its discharge side 22 with the pressure on the discharge side 22 being higher than the pressure at the critical point of the refrigerant. The compressor has an economizer port 31 at the housing enabling a flow connection to intercooler 24, and the pressure in this pipe section lies between discharge pressure and suction pressure.
  • In the Pressure-Enthalpy diagram according to FIG. 2, point 1 describes the condition on the suction side of compressor 21. The outlet condition of the refrigerant after compressor 21, point 2, is the inlet condition into gas cooler 23. The refrigerant passes gas cooler 23 which is fed by a cooling medium, e.g. cooling water, for cooling the refrigerant vapor. When leaving said gas cooler 23, the refrigerant has the condition at point 3. In intercooler 24 through which two refrigerant flows of the refrigeration apparatus are led, the refrigerant is cooled from point 3 to point 4. For this purpose, the partial refrigerant flow expanded to intermediate pressure level 10 will be evaporated and superfed via economizer port 31 into the compressor without considerably influencing the suction volume flow. The refrigerant flow is further cooled from point 4 to point 5 in aftercooler 27 wherein liquid evaporates in aftercooler 27 communicating with low-pressure liquid separator 25, and hence reducing the available volumetric refrigerating capacity by the enthalpy difference from point 1 to point 9. Point 9 corresponds to the condition of the refrigerant at the evaporator outlet 35 characterized by a two-phase mixture. The intermediate pressure level 10 can be used for changing the refrigerating capacity by way of rising the intermediate pressure, and hence changing the intermediate cooling effect.
  • Due to cooling the refrigerant vapor in intercooler 24, there will be created less vapor in aftercooler 27 on the side of low-pressure liquid separator 25. Thus, with the same compressor size, more vapor can be taken from the evaporator. Therefore, the refrigerating capacity of the refrigeration apparatus and its efficiency will increase.
  • The refrigeration apparatus for transcritical operation according to FIG. 3 is configured similarly to FIG. 1 with the distinguishing feature that the second flow path of intercooler 24 on its inlet side is connected via piping and second controllable throttling device 32 to the outlet of an intermediate-pressure aftercooler 34. The inlet of the intermediate-pressure aftercooler 34 is connected to the outlet of the first flow path of intercooler 24. The outlet side of the second flow path of intercooler 24 is connected to economizer port 31 of compressor 21 via an intermediate-pressure liquid separator 33. Intermediate-pressure aftercooler 34 communicates with intermediate-pressure liquid separator 33.
  • In the Pressure-Enthalpy diagram according to FIG. 4, point 4′ describes the outlet condition from intermediate-pressure aftercooler 34, point 13 describes the inlet condition into intercooler 24 and point 17 describes the outlet condition from intercooler 24.
    • LIST OF REFERENCE NUMERALS USED
    • 1. Point
    • 2. Point
    • 3. Point
    • 4. Point
    • 4′. Point
    • 5. Point
    • 9. Point
    • 10. Intermediate-pressure level
    • 11. Suction pressure
    • 12. Discharge pressure
    • 13. Point
    • 17. Point
    • 21. Screw compressor
    • 22. Compressor discharge side
    • 23. Gas cooler
    • 24. Intercooler
    • 25. Low-pressure liquid separator
    • 26. Second controllable throttling device
    • 27. Aftercooler
    • 28. First controllable throttling device
    • 29. Compressor suction side
    • 30. Evaporator
    • 31. Economizer port
    • 32. Second controllable throttling device
    • 33. Intermediate-pressure liquid separator
    • 34. Intermediate-pressure aftercooler
    • 35. Evaporator outlet
    • 36. First flow path
    • 37. Second flow path
    • 38. First flow path inlet/Gas cooler outlet
    • 39. First flow path outlet
    • 40. Second flow path inlet
    • 41. Second flow path outlet
    • 42. Inlet of the second controllable throttling device
    • 43. Outlet of the second controllable throttling device
    • 44. Aftercooler inlet
    • 45. Piping

Claims (3)

1. A refrigeration apparatus for transcritical operation comprising a screw compressor featuring inlet and outlet ports geometrically controlled by rotation of male and female rotors operating at least on three pressure levels: suction pressure on the compressor suction side, intermediate pressure at the economizer port and discharge pressure at the compressor discharge side, a gas cooler, a low-pressure liquid separator, an aftercooler communicating with said low-pressure liquid separator, a first controllable throttling device and an evaporator, wherein there is a second controllable throttling device and an intercooler that comprises a first and a second flow path separated by heat-exchanging surfaces.
2. A refrigeration apparatus according to claim 1 wherein a first flow path inlet of said intercooler is connected to the gas cooler outlet, a first flow path outlet of said intercooler is connected to the aftercooler inlet, a second flow pass inlet of said intercooler is connected to the outlet of said second controllable throttling device and a second flow pass outlet of said intercooler is connected to the economizer port of the compressor.
3. A refrigeration apparatus according to claim 1 wherein the inlet of said second controllable throttling device is connected to the piping either upstream or downstream of the aftercooler and the outlet of said second controllable throttling device is connected to said second flow pass inlet of said intercooler.
US11/801,188 2006-08-01 2007-05-09 Refrigeration system for transcritical operation with economizer and low-pressure receiver Abandoned US20080302129A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEDE102006035784.1 2006-08-01
DE102006035784.1A DE102006035784B4 (en) 2006-08-01 2006-08-01 Refrigeration system for transcritical operation with economiser and low pressure collector

Publications (1)

Publication Number Publication Date
US20080302129A1 true US20080302129A1 (en) 2008-12-11

Family

ID=38529098

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/801,188 Abandoned US20080302129A1 (en) 2006-08-01 2007-05-09 Refrigeration system for transcritical operation with economizer and low-pressure receiver

Country Status (5)

Country Link
US (1) US20080302129A1 (en)
JP (1) JP2008039383A (en)
DE (1) DE102006035784B4 (en)
GB (1) GB2440669B (en)
IT (1) ITRM20070158A1 (en)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070264146A1 (en) * 2006-05-10 2007-11-15 Dieter Mosemann Screw compressor for high input power
CN103175323A (en) * 2011-12-23 2013-06-26 东普雷股份有限公司 Refrigeration device using ternary pipe-type heat exchanger
CZ306581B6 (en) * 2013-04-11 2017-03-15 Miroslav Petrák A cooling device for cooling and heating with the internal extra cooling of the coolant
US10119738B2 (en) 2014-09-26 2018-11-06 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
CN109357403A (en) * 2018-10-15 2019-02-19 四川长虹电器股份有限公司 Carbon dioxide air source water heater
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
US11506430B2 (en) 2019-07-15 2022-11-22 Climate Master, Inc. Air conditioning system with capacity control and controlled hot water generation
US11592215B2 (en) 2018-08-29 2023-02-28 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
WO2023191313A1 (en) * 2022-03-31 2023-10-05 Hanon Systems Receiver drier and economizer integration for vapor injection system

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018127108B4 (en) * 2018-10-30 2021-04-22 Hanon Systems Devices for an air conditioning system of a motor vehicle and a method for operating the devices
US11879675B2 (en) * 2020-01-15 2024-01-23 Heatcraft Refrigeration Products Llc Cooling system with flooded low side heat exchangers

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3796526A (en) * 1972-02-22 1974-03-12 Lennox Ind Inc Screw compressor
US3856493A (en) * 1973-05-08 1974-12-24 Dunham Bush Inc Energy recovery system for oil injected screw compressors
US6058727A (en) * 1997-12-19 2000-05-09 Carrier Corporation Refrigeration system with integrated oil cooling heat exchanger
US6519967B1 (en) * 2001-08-03 2003-02-18 Grasso Gmbh Refrigeration Technology Arrangement for cascade refrigeration system
US7114349B2 (en) * 2004-12-10 2006-10-03 Carrier Corporation Refrigerant system with common economizer and liquid-suction heat exchanger
US7353659B2 (en) * 2004-05-28 2008-04-08 York International Corporation System and method for controlling an economizer circuit
US7424807B2 (en) * 2003-06-11 2008-09-16 Carrier Corporation Supercritical pressure regulation of economized refrigeration system by use of an interstage accumulator

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH085185A (en) * 1994-06-16 1996-01-12 Mitsubishi Electric Corp Refrigerating cycle system
US6047556A (en) * 1997-12-08 2000-04-11 Carrier Corporation Pulsed flow for capacity control
DE19903833A1 (en) * 1999-02-01 2000-08-03 Behr Gmbh & Co Integrated collector heat exchanger assembly
EP1099918A1 (en) * 1999-11-09 2001-05-16 Maersk Container Industri As Cooling unit
JP4658347B2 (en) * 2001-01-31 2011-03-23 三菱重工業株式会社 Supercritical vapor compression refrigeration cycle
US6463757B1 (en) * 2001-05-24 2002-10-15 Halla Climate Controls Canada, Inc. Internal heat exchanger accumulator
JP4126408B2 (en) * 2002-09-05 2008-07-30 株式会社ヴァレオサーマルシステムズ Accumulator and refrigeration cycle using the same
JP4140488B2 (en) * 2003-09-09 2008-08-27 ダイキン工業株式会社 Screw compressor and refrigeration equipment
DE10358428A1 (en) * 2003-12-13 2005-07-07 Grasso Gmbh Refrigeration Technology Refrigerating plant for a supercritical operating method with an economizer has a condenser with a coolant like carbon dioxide with its condensing pressure in a supercritical range
JP4442237B2 (en) * 2004-01-30 2010-03-31 三菱電機株式会社 Air conditioner
DE102004050409A1 (en) * 2004-10-15 2006-04-27 Valeo Klimasysteme Gmbh Accumulator with internal heat exchanger for air conditioning
CN101171464B (en) * 2005-05-04 2011-11-23 开利公司 Refrigerant system with variable speed scroll compressor and economizer circuit and operation method
CN101432385A (en) * 2005-06-08 2009-05-13 开利公司 Method and apparatus for operating air conditioning system by saver

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3796526A (en) * 1972-02-22 1974-03-12 Lennox Ind Inc Screw compressor
US3856493A (en) * 1973-05-08 1974-12-24 Dunham Bush Inc Energy recovery system for oil injected screw compressors
US6058727A (en) * 1997-12-19 2000-05-09 Carrier Corporation Refrigeration system with integrated oil cooling heat exchanger
US6519967B1 (en) * 2001-08-03 2003-02-18 Grasso Gmbh Refrigeration Technology Arrangement for cascade refrigeration system
US7424807B2 (en) * 2003-06-11 2008-09-16 Carrier Corporation Supercritical pressure regulation of economized refrigeration system by use of an interstage accumulator
US7353659B2 (en) * 2004-05-28 2008-04-08 York International Corporation System and method for controlling an economizer circuit
US7114349B2 (en) * 2004-12-10 2006-10-03 Carrier Corporation Refrigerant system with common economizer and liquid-suction heat exchanger

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070264146A1 (en) * 2006-05-10 2007-11-15 Dieter Mosemann Screw compressor for high input power
CN103175323A (en) * 2011-12-23 2013-06-26 东普雷股份有限公司 Refrigeration device using ternary pipe-type heat exchanger
CZ306581B6 (en) * 2013-04-11 2017-03-15 Miroslav Petrák A cooling device for cooling and heating with the internal extra cooling of the coolant
US10119738B2 (en) 2014-09-26 2018-11-06 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
US10753661B2 (en) 2014-09-26 2020-08-25 Waterfurnace International, Inc. Air conditioning system with vapor injection compressor
US11927377B2 (en) 2014-09-26 2024-03-12 Waterfurnace International, Inc. Air conditioning system with vapor injection compressor
US11480372B2 (en) 2014-09-26 2022-10-25 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
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
US11953239B2 (en) 2018-08-29 2024-04-09 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
US11592215B2 (en) 2018-08-29 2023-02-28 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
CN109357403A (en) * 2018-10-15 2019-02-19 四川长虹电器股份有限公司 Carbon dioxide air source water heater
US11506430B2 (en) 2019-07-15 2022-11-22 Climate Master, Inc. Air conditioning system with capacity control and controlled hot water generation
WO2023191313A1 (en) * 2022-03-31 2023-10-05 Hanon Systems Receiver drier and economizer integration for vapor injection system

Also Published As

Publication number Publication date
DE102006035784A1 (en) 2008-02-07
DE102006035784B4 (en) 2020-12-17
GB2440669A (en) 2008-02-06
GB0714959D0 (en) 2007-09-12
JP2008039383A (en) 2008-02-21
ITRM20070158A1 (en) 2008-02-02
GB2440669B (en) 2011-03-16

Similar Documents

Publication Publication Date Title
US20080302129A1 (en) Refrigeration system for transcritical operation with economizer and low-pressure receiver
EP3203165B1 (en) Air conditioner
JP5241872B2 (en) Refrigeration cycle equipment
EP1139039B1 (en) Economizer circuit enhancement
EP2543941B1 (en) Chiller
US20100058781A1 (en) Refrigerant system with economizer, intercooler and multi-stage compressor
US7225635B2 (en) Refrigerant cycle apparatus
US7640762B2 (en) Refrigeration apparatus
US20190017730A1 (en) Refrigerating machine and control method thereof
JP4550153B2 (en) Heat pump device and outdoor unit of heat pump device
US11402134B2 (en) Outdoor unit and control method thereof
KR20130026674A (en) Air conditioner
JP2011214753A (en) Refrigerating device
JP2011017455A (en) Turbo refrigerator
KR20210096522A (en) Air conditioning apparatus
KR20210100461A (en) Air conditioning apparatus
JP2011196684A (en) Heat pump device and outdoor unit of the heat pump device
JP5237157B2 (en) Air heat source turbo heat pump
US11512880B2 (en) Refrigeration cycle device
JP6176470B2 (en) refrigerator
WO2011072679A1 (en) A vapour compression system with split evaporator
KR20210096521A (en) Air conditioning apparatus
JP2009243881A (en) Heat pump device and outdoor unit of heat pump device
JP4767340B2 (en) Heat pump control device
WO2022013982A1 (en) Refrigeration cycle device

Legal Events

Date Code Title Description
AS Assignment

Owner name: MOSEMANN, DR. DIETER, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:ZAYTSEV, DR. DMYTRO;REEL/FRAME:019461/0487

Effective date: 20070215

AS Assignment

Owner name: GRASSO GMBH REFRIGERATION TECHNOLOGY, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:MOSEMANN, DIETER;REEL/FRAME:023344/0208

Effective date: 20090826

AS Assignment

Owner name: GEA REFRIGERATION GERMANY GMBH, GERMANY

Free format text: CHANGE OF NAME;ASSIGNOR:GRASSO GMBH REFRIGERATION TECHNOLOGY;REEL/FRAME:028735/0298

Effective date: 20120119

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION