US20100263392A1 - Refrigerator - Google Patents

Refrigerator Download PDF

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Publication number
US20100263392A1
US20100263392A1 US12/681,489 US68148908A US2010263392A1 US 20100263392 A1 US20100263392 A1 US 20100263392A1 US 68148908 A US68148908 A US 68148908A US 2010263392 A1 US2010263392 A1 US 2010263392A1
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US
United States
Prior art keywords
heat
heat exchangers
refrigerator
heat exchanger
working cylinder
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
US12/681,489
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English (en)
Inventor
Jürgen K. Misselhorn
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.)
Maschinenwerk Misselhorn MWM GmbH
Original Assignee
Maschinenwerk Misselhorn MWM GmbH
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 Maschinenwerk Misselhorn MWM GmbH filed Critical Maschinenwerk Misselhorn MWM GmbH
Assigned to MASCHINENWERK MISSELHORN MWM GMBH reassignment MASCHINENWERK MISSELHORN MWM GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MISSELHORN, JURGEN K.
Publication of US20100263392A1 publication Critical patent/US20100263392A1/en
Abandoned legal-status Critical Current

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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
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle

Definitions

  • the present invention relates to a refrigerator that functions according to the principle of a cyclic process having six changes of state: two isochors, two isobars, two isotherms.
  • the object of the present invention is to provide a refrigerating process having improved efficiency as well as a refrigerator, which applies said process.
  • this object is achieved by a process, in which six changes of state of an enclosed working gas take place between two temperature levels in a cycle according to the following sequence: isochoric heat absorption, isothermal compression, isobaric condensation, isochoric heat dissipation, isothermal expansion, isobaric vaporization.
  • compression and expansion are preferably carried out simultaneously by a compressor.
  • the refrigeration process takes place simultaneously but chronologically displaced in several heat exchangers. Thereby a higher degree of efficiency may be achieved.
  • the refrigeration process preferably takes place in at least three heat exchangers. It is particularly advantageous if the refrigeration process takes place in six heat exchangers. The advantage being that every step of the process is executed simultaneously in a heat exchanger.
  • a refrigerator comprising at least one heat exchanger having two sections, which are fluidly interconnected with each other by a closing device in such a way, that the working fluid may flow in a gaseous or liquid state from one half to the other and may spread evenly.
  • a warm medium flows about one section of the heat exchanger and a cold medium flows about the other section.
  • Means for turning the heat exchangers are provided allowing liquid fluid to pass from one section of the heat exchangers to the other section.
  • a working cylinder is provided, wherein said working cylinder is selectively connected by a connecting pipe and a valve with one section of the heat exchangers, when the valve is in its open position, and wherein said working cylinder is separated from the heat exchanger, when the valve is in its closed position. Furthermore an actuator is provided, which actuates the valves and the closing device selectively, in order to execute the above described steps of the refrigeration process.
  • the two sections of the heat exchanger are thermally isolated from each other by insulation.
  • the warm and the cold medium may be gaseous or liquid.
  • connection between the heated and the cooled half may be closed temporarily by the closing device.
  • the refrigerator comprises at least three heat exchangers. It is especially preferred that the refrigerator comprises six heat exchangers. The advantage being that every step of the process is executed simultaneously in a heat exchanger.
  • a refrigerator is preferred, in which the heat exchangers are arranged in a star shaped manner around the longitudinal axis of the working cylinder and the connecting pipes are connected alternately to either side of the working cylinder.
  • the heat exchangers are rigidly connected to the working cylinder and are suspended with the working cylinder being rotatable around the common longitudinal axis.
  • a motor for rotating the heat exchangers and the working cylinder is provided, and directing means are provided, which direct the hot and the cold medium in such a manner that each heat exchanger is moved through the cold medium for half of one rotation, whereas each heat exchanger is moved in the hot medium during the other half of the rotation.
  • the working cylinder in the refrigerator is a double-acting working cylinder, in which the compressions and expansions take place not only on one side but on both sides of the piston.
  • the actuator for actuating the valves is a cam disk.
  • the refrigerator may preferably be used as a heat pump for generating heat which may be delivered to a heating installation or a different process, by extracting said heat from a colder gaseous or fluid medium.
  • radiation heat may preferably be used for purposes of heating and evaporation, and for purposes of cooling and condensation heat may be dissipated by radiation instead of dissipating the heat to a gaseous or fluid medium.
  • a refrigerator arrangement consisting of several refrigerators according to one of the preceding claims which are arranged in series in the hot and the cold medium, wherein the warm medium flows in a cascade manner successively through the different refrigerators and wherein the temperature increases when flowing through the heat exchangers of the different refrigerators.
  • the cold medium flows through the same refrigerators in a reverse order in a cascade manner in the opposite direction, wherein the temperature of the cold medium decreases when flowing through the heat exchangers of the different refrigerators und wherein the temperature difference between the warm and the cold medium remains constant.
  • the aim is to achieve a very extensive cooling and heating, respectively.
  • the present invention is concerned with a refrigerator which achieves a high coefficient of performance (COP) by means of six changes in state.
  • COP coefficient of performance
  • this refrigerator which may also be used as a heat pump, a heat exchange between two media is to be caused via external work, wherein the heat flow occurs from the medium with the lower temperature to the medium with the higher temperature.
  • FIG. 1 a schematic diagram of a model of a refrigerator, in which essential components and their relationships to each other are shown to describe the implementation of the refrigeration cycle;
  • FIG. 2 the valve control embodied as cam disk having cam-actuated valves
  • FIG. 3 a schematic diagram of a rotor of a refrigerator having six heat exchangers
  • FIG. 4A a description of the symbols used in FIGS. 4B and 4C ;
  • FIG. 4B a graph of strokes 1 to 4 of the refrigeration cycle
  • FIG. 4C a graph of strokes 5 and 6 of the refrigeration cycle
  • FIG. 5 a pressure-enthalpy-graph of C 2 H 2 F 2 , refrigerant R134a, a working fluid
  • FIG. 6 a P-v-diagram related to the P-h-graph shown in FIG. 5 ;
  • FIG. 7 a T-s-diagram related to the P-h-graph shown in FIG. 5
  • the refrigerator 100 comprises six heat exchangers 10 , each of which consists of two halves. Each heat exchanger 10 is connected to a compression cylinder 20 by a connecting pipe 30 . A valve 40 is located in the connecting pipe 30 .
  • the compression cylinder 20 comprises a double-acting piston 22 .
  • each heat exchanger 10 consists of two halves 11 , 12 which are thermally insulated by an insulation 13 .
  • Each heat exchanger 10 comprises opposed pairs of pipes 14 (in the figure two pairs of pipes are shown for each heat exchanger 10 ), that are respectively connected to each other via a common closing device 16 .
  • the closing device 16 When the closing device 16 is open, as is shown at “A” and “X”, the pipes of each pair of pipes 14 are connected to each other.
  • the closing device 16 is closed, the connection between both pipes of each pair of pipes are sealed in a gas-tight manner.
  • the individual pipes of the heat exchanger 10 may comprise fins 15 , as shown, or may be smooth.
  • the heat exchangers do not necessarily consist of pipes, but may also have any other shape that is pressure resistant. Both halves 11 , 12 of the heat exchangers 10 may also differ from each other. The only important aspect is an appropriate heat exchange.
  • the closing device 16 is located between the two halves 11 , 12 of the heat exchangers 10 .
  • the closing device 16 is spring loaded towards a closed position.
  • An actuation device 17 opens the closing device 16 .
  • said actuation device 17 consists of a roller 18 that rolls on a cam disk 19 .
  • the piston 22 is double-acting. While compression takes place on one side of the piston 22 expansion or intake takes place on the other side.
  • the piston 22 may be driven in different manners.
  • the piston 22 may be driven by a crank shaft and a piston rod or a connecting rod or also by an electrical linear motor.
  • the compressions and expansions may take place not only on one side but on both sides of the piston 22 . While compression takes place on one side, expansion simultaneously takes places on the other side.
  • the working gas is compressed into a heat exchanger 10 with every movement of the piston while the working gas is simultaneously sucked out of a different heat exchanger 10 .
  • each of the valves 40 comprises a tappet 41 and a roller 42 .
  • the valves 40 are arranged in a star shaped manner around a cam disk 50 .
  • the cam disk 50 comprises cams 51 and a base circle 52 .
  • Other types of valve controls such as solenoid or pneumatic valves, are also applicable.
  • valve A is open, whereas valves B and C are closed.
  • the valves 40 are located in the connecting pipe 30 .
  • the heat exchangers 10 are arranged in a star shaped manner around the compression cylinder 20 and are firmly connected thereto.
  • One half of the heat exchanger 10 is connected to the front side of the compression cylinder 20 and the other half is connected to the rear side.
  • the heat exchangers 10 are shown as single pipes 14 , but they may represent a gallery of pipes 14 .
  • a motor (not shown) is provided to rotate the complete arrangement of heat exchangers (heat exchanger block) around the central axis. The rotational direction is counter clockwise.
  • a hot medium flows around one half 12 of the heat exchangers 10 which is connected to the connecting pipe 30 leading to the compression cylinder 20 , whereas a cooling medium flows around the other half 11 of the heat exchangers 10 .
  • FIGS. 3 , and 4 A- 4 C the strokes of the refrigerator are shown successively.
  • FIG. 4A-4C show a representation of the process sequence on the basis of the model, shown in FIG. 3 .
  • the respective movement of the piston, the position of the valve and the position of the closing device between the individual halves of the heat exchanger, and the progress of the individual heat exchangers within a rotation are shown schematically.
  • the closing device 8 is shown as a circle having a bar between the heat exchanger halves 11 , 12 . If the bar is parallel to the longitudinal axis of the heat exchanger 10 , the closing device 16 is open. If the bar is transverse to the longitudinal axis of the heat exchangers 10 , the closing device 16 is closed.
  • Valves opened by tappets following the cam disk and closed via spring pressure are illustrated “from above”.
  • the mode of operation corresponds to the representation in FIG. 2 .
  • This type of valves is most convenient with regard to the explanation, but any appropriate type of valve may be employed.
  • the heat exchangers 10 rotate around the central axis according to the displayed arrows.
  • the areas in which the valves 40 are open and the closing devices are closed are shown in the figures.
  • the compression cylinder 20 is seen from the front and is shown as a circle in FIG. 3 . On the basis of this illustration the sequence of the refrigeration cycle process will be explained.
  • FIG. 3 arrows show the direction of rotation.
  • the separation of the individual changes of state of the working fluid is marked by the numbers on the outside of the rotor consisting of the heat exchangers 10 and the working cylinder 20 . These numbers are also incorporated at the respective points in the thermodynamic graphs of FIG. 5 to 7 .
  • the heat exchanger 10 has just left the cooling zone in position ( 1 ).
  • the enclosed working fluid is fully evaporated.
  • the closing device 16 is closed.
  • the inner heat exchanger half 12 moves into the heating zone and is heated there.
  • the closing device 16 and the valve 40 are closed, the vapor of the working fluid is contained in a space of constant volume.
  • the working fluid is heated in a constant volume to the temperature of the hot medium by the hot medium flowing around the heat exchanger. The pressure increases.
  • valve 40 opens and additional vapor of the working fluid is pressed out of the compression cylinder 20 into the heat exchanger 10 by the piston 22 .
  • the pressure within the heat exchanger 10 increases.
  • the adiabatic heat of the compression is extracted by the hot medium, so that an isothermal compression takes place. Since the pressure in the heat exchanger 10 is higher than the vapor pressure of the working fluid, the working fluid condenses.
  • the valve 40 closes.
  • the working fluid condenses until the vapor pressure of the working fluid at the temperature of the hot medium is reached.
  • the condensation heat is extracted by the hot medium.
  • the heat exchanger 10 is adapted in such a manner that this process is completed when position ( 4 ) has been reached.
  • the closing device 16 is open.
  • the condensate of the working fluid may now flow into the cooled half 11 of the heat exchanger 10 (condenser).
  • the condensate is cooled to the lower temperature level of the cooling medium. Due to the lower vapor pressure of the working medium at this temperature, additional vapor is condensed until the vapor pressure of the working fluid at this temperature is reached.
  • the total mass of the working fluid is cooled to the lower temperature level at position ( 5 ). Since the volume in the heat exchanger 10 is unchanged during the full track (valve 40 closed, closing device 16 open) cooling takes place at a constant volume.
  • the valve 40 is open at position ( 5 ).
  • Working fluid is sucked out of the heat exchanger 10 by the compression cylinder 20 due a negative pressure.
  • the pressure drops below the vapor pressure of the working fluid at the lower temperature.
  • the working fluid evaporates. Since heat is constantly supplied by the cooling medium, this evaporation takes place at a constant temperature. Therefore an isothermal expansion and evaporation takes place.
  • the valve 40 closes.
  • the working fluid evaporates at negative pressure in the heat exchanger 10 until the vapor pressure of the working fluid at the lower temperature is reached.
  • the evaporation heat is caused by the cooling medium.
  • the heat exchangers 10 are constructed such that this process is completed when position ( 1 ) is reached again.
  • FIG. 4A to 4C the alternating changes of the processes in the different heat exchangers and the relationship among each other and to the compression cylinder 20 can easily be understood.
  • the rotation of the heat exchangers 10 has proceeded by 60° with every shown stroke.
  • the piston 3 changes its direction after every rotation by 60°, and three complete strokes (back and forth) are executed with every full rotation of the rotor consisting of the heat exchangers and the compression cylinder.
  • the piston will execute as many cycles as heat exchangers are connected to one side of the compression cylinder 20 .
  • the number of heat exchangers in the refrigerator may be a multiple of three. Further it is an advantageous alternative that the number of heat exchangers is a multiple of six.
  • a correspondingly connected working cylinder may be selectively connected on its one side with a heat exchanger into which the working fluid is to be pumped, while at the same time a different heat exchanger may be connected with the opposite side of the working cylinder, out of which the working fluid is to be pumped.
  • the main difference of the present invention to the state of art is that several heat exchangers, consisting of evaporator and condenser, are operated at the same time, but the sequences of the refrigeration cycle process take place simultaneously but chronologically displaced, and the changes of state, expansion and compression are always effected in every heat exchanger by a common compressor.
  • the mode of operation of this invention differs from all conventional refrigeration cycles due to the six necessary changes of state.
  • Conventional cycles essentially consist (refraining from overheating of the vapor of the working fluid or integrated intermediate cycles) of four changes of state.
  • This invention further distinguishes itself by a higher theoretical degree of efficiency than conventional refrigeration cycles.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
US12/681,489 2007-10-05 2008-10-06 Refrigerator Abandoned US20100263392A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007047642.8 2007-10-05
DE102007047642A DE102007047642B4 (de) 2007-10-05 2007-10-05 Kältemaschine
PCT/EP2008/008424 WO2009046953A1 (fr) 2007-10-05 2008-10-06 Machine frigorifique

Publications (1)

Publication Number Publication Date
US20100263392A1 true US20100263392A1 (en) 2010-10-21

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ID=40242652

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/681,489 Abandoned US20100263392A1 (en) 2007-10-05 2008-10-06 Refrigerator

Country Status (4)

Country Link
US (1) US20100263392A1 (fr)
EP (1) EP2212627A1 (fr)
DE (1) DE102007047642B4 (fr)
WO (1) WO2009046953A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9816739B2 (en) 2011-09-02 2017-11-14 Carrier Corporation Refrigeration system and refrigeration method providing heat recovery
WO2019126899A1 (fr) * 2017-12-29 2019-07-04 Ahr Energy Spa Méthode pour produire un transfert de chaleur entre au moins deux milieux et système permettant d'exécuter ladite méthode

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020207306A1 (de) 2020-06-11 2021-12-16 Volkswagen Aktiengesellschaft Klimatisierungseinrichtung für ein Kraftfahrzeug und Schaltmitteleinheit für eine Klimatisierungseinrichtung

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3981702A (en) * 1973-12-10 1976-09-21 Michael Eskeli Heat exchanger
US4420945A (en) * 1982-10-25 1983-12-20 Centrifugal Piston Expander, Inc. Method and apparatus for extracting energy from a pressured gas
US4520632A (en) * 1982-10-25 1985-06-04 Centrifugal Piston Expander, Inc. Method and apparatus for extracting heat and mechanical energy from a pressured gas
US4854279A (en) * 1987-12-21 1989-08-08 Seno Cornelio L Three chamber continuous combustion engine
US5638684A (en) * 1995-01-16 1997-06-17 Bayer Aktiengesellschaft Stirling engine with injection of heat transfer medium
US5737924A (en) * 1995-09-19 1998-04-14 Sanyo Electric Co., Ltd. Gas compressor expander

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005013287B3 (de) * 2005-01-27 2006-10-12 Misselhorn, Jürgen, Dipl.Ing. Wärmekraftmaschine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3981702A (en) * 1973-12-10 1976-09-21 Michael Eskeli Heat exchanger
US4420945A (en) * 1982-10-25 1983-12-20 Centrifugal Piston Expander, Inc. Method and apparatus for extracting energy from a pressured gas
US4520632A (en) * 1982-10-25 1985-06-04 Centrifugal Piston Expander, Inc. Method and apparatus for extracting heat and mechanical energy from a pressured gas
US4854279A (en) * 1987-12-21 1989-08-08 Seno Cornelio L Three chamber continuous combustion engine
US5638684A (en) * 1995-01-16 1997-06-17 Bayer Aktiengesellschaft Stirling engine with injection of heat transfer medium
US5737924A (en) * 1995-09-19 1998-04-14 Sanyo Electric Co., Ltd. Gas compressor expander

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9816739B2 (en) 2011-09-02 2017-11-14 Carrier Corporation Refrigeration system and refrigeration method providing heat recovery
WO2019126899A1 (fr) * 2017-12-29 2019-07-04 Ahr Energy Spa Méthode pour produire un transfert de chaleur entre au moins deux milieux et système permettant d'exécuter ladite méthode
KR20200104860A (ko) * 2017-12-29 2020-09-04 에이에이치알 에너지 에스피에이 두 개 이상의 매체 사이에서 열을 전달하기 위한 방법 및 상기 방법을 수행하기 위한 시스템
TWI709722B (zh) * 2017-12-29 2020-11-11 智利商Ａｈｒ能源公司 在兩個或多個構件之間產生熱傳遞的方法以及執行此方法的系統
US11333387B2 (en) 2017-12-29 2022-05-17 Energy Innovation Systems Limited Method for transferring heat between two or more media and system for carrying out said method
KR102625453B1 (ko) * 2017-12-29 2024-01-16 에너지 이노베이션 시스템스 리미티드 두 개 이상의 매체 사이에서 열을 전달하기 위한 방법 및 상기 방법을 수행하기 위한 시스템
AU2018397717B2 (en) * 2017-12-29 2024-02-01 Energy Innovation Systems Limited Method for transferring heat between two or more media and system for carrying out said method

Also Published As

Publication number Publication date
EP2212627A1 (fr) 2010-08-04
DE102007047642B4 (de) 2010-01-14
DE102007047642A1 (de) 2009-04-23
WO2009046953A1 (fr) 2009-04-16

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AS Assignment

Owner name: MASCHINENWERK MISSELHORN MWM GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:MISSELHORN, JURGEN K.;REEL/FRAME:024644/0215

Effective date: 20100624

STCB Information on status: application discontinuation

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