EP0665940B1 - Wärme- und kältemaschine - Google Patents
Wärme- und kältemaschine Download PDFInfo
- Publication number
- EP0665940B1 EP0665940B1 EP94926210A EP94926210A EP0665940B1 EP 0665940 B1 EP0665940 B1 EP 0665940B1 EP 94926210 A EP94926210 A EP 94926210A EP 94926210 A EP94926210 A EP 94926210A EP 0665940 B1 EP0665940 B1 EP 0665940B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- heat transfer
- heat
- cold
- transfer means
- 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.)
- Expired - Lifetime
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
- F25B9/14—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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G1/00—Hot gas positive-displacement engine plants
- F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G1/00—Hot gas positive-displacement engine plants
- F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
- F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
- F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
- F02G1/0445—Engine plants with combined cycles, e.g. Vuilleumier
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G2250/00—Special cycles or special engines
- F02G2250/18—Vuilleumier cycles
Definitions
- the invention relates to a regenerative Gas cycle heat and chiller working with two In a pressure-tight housing, the piston moves linearly together limit a warm work volume and of which the one piston in the housing is a hot one, with warmth applied working volume and the other piston cold working volume limited, the three Working volumes with the interposition of regenerators and heat exchangers are interconnected and a Drive and / or a control for the pistons provided is.
- the invention is based on the task, a heat and Chiller of the type defined in the beginning to train that a high Heat transfer efficiency results in a compact design.
- the solution to this problem by the invention is characterized in that the warm and cold Working volume through its piston crown from each other separating piston is cup-shaped and that be Piston jacket as a separation between the outside warm Heat exchanger and the internal cold Heat exchanger is used, the heat transfer from the or to the working medium in both heat exchangers between the outer and the inner surface of the Piston jacket and the associated surface of each Heat exchanger takes place.
- the inventive arrangement of the cold heat exchanger results in a cup-shaped cold piston a short and small diameter construction of the Machine. A further reduction in the construction volume will achieved in that the piston skirt at the same time as a separation between the hot and cold heat exchanger.
- the Construction according to the invention also creates a high efficiency for heat transfer because additional Partitions are eliminated, the heat and flow losses Episode.
- the cold one Piston according to another feature of the invention at least partially made of poorly heat-conducting material.
- the cold piston is preferably at least on one Provide side with poor heat-conducting material.
- the surface affected by the working medium the heat exchanger by applying porous material, by corrugations or grooves and / or by use corrugated or grooved sheets can be enlarged.
- the heat exchangers in two parts each with an open Provided channels, as a liner for the cold piston trained body and from an open side of the Channels sealing body formed. Because of the pressure in the channels of the heat exchanger considerably less than is the pressure of the working medium, presses the working medium the body in both heat exchangers against the Sealing body, so that special and expensive sealing measures in the heat exchangers designed according to the invention can be dispensed with. As the overpressure of the Working medium over the base body also the sealing body of the presses the warm heat exchanger against the machine housing, can the connections for the warm heat exchanger flowing medium can be carried out easily.
- the sealing body the heat exchanger made of heat-insulating material manufactured, which is a significant reduction in unwanted heat conduction from the respective heat exchanger in the housing results.
- the invention proposes between the warm heat exchanger and this on the process side downstream regenerator interacting with the piston skirt To arrange sealing ring. This will turn on easily achieved that the working medium after Leaving the warm heat exchanger via the downstream one Regenerator is led to the cold heat exchanger.
- Heating and cooling machine in a longitudinal section shown.
- the machine shown in longitudinal section includes a as Circular cylinder formed pressure-tight housing 1, the is provided at one end with a flange la to which a motor housing 2 screwed with a corresponding flange 2a becomes.
- the motor housing 2 is only partially shown.
- the pressure-tight housing 1 with one Provided housing cover 4, which in the exemplary embodiment Thread is screwed to the cylindrical housing 1 and in which a heat generator in the form of a gas burner 5 is arranged.
- This gas burner comprises a cylindrical one Supply pipe 5a for the fuel gas, the outlet side with a metering hemisphere 5b is provided.
- Concentric too this dosing hemisphere 5b is a reaction surface acting burner surface 5c made of a stainless steel mesh arranged, which limits the gas inflow chamber and at Operation of the gas burner glows, so that the gas burner 5 one Most of the heat generated is emitted by radiation.
- the resulting flue gases become hemispherical Burner surface 5c surrounding combustion chamber 5d through an exhaust pipe 5e deducted, the supply pipe 5a of the gas burner 5 concentric surrounds.
- the heat generated by the gas burner 5 is generated by radiation and Convection delivered to a partition 6, which is rotationally symmetrical Conic section, in the embodiment is designed as a hemisphere and in the interior of the housing 1 bulges.
- the hemispherical runs Curvature with constant distance to semi-conical burner surface 5c of the gas burner 5.
- the partition designed as part of the pressure-tight housing 1 6 is attached to a support ring 6a, which has a membrane-like extension 6b with the end of the cylindrical Housing 1 is connected. In the embodiment both connections by welding.
- Isolation rings 7a and 7b each on one side of the membrane-like extension 6b on the one hand to the housing cover 4 and on the other hand to the housing 1, the Heat dissipation from that heated by the gas burner 5 Partition 6 to the housing 1 and its housing cover 4 and thus significantly reduced to the environment.
- the heat generated by the gas burner 5 and absorbed by the partition is given off from the inside of the partition 6 to a working medium, preferably helium, which is in a hot working volume V h .
- This hot working volume V h is limited on the one hand by the partition 6 and on the other hand by the piston crown 8a of a piston 8 which is arranged in the housing 1 so as to be linearly movable.
- This piston 8 is connected via a piston rod 8b to a motor or controller arranged in the motor housing 2, which are not shown in the drawing.
- These three volumes are interconnected with the interposition of regenerators R h , R k and heat exchangers W w , W k .
- the regenerator R h arranged in the hot part of the housing 1 stores part of the heat given off to the hot working volume V h during the course of the regenerative gas cycle process; the regenerator R k arranged in the cold part of the housing 1 performs the corresponding function with regard to the cold working volume V k .
- the heat exchanger W k which in the exemplary embodiment is arranged within the cold piston 9 in a stationary manner on the base 3, is continuously supplied with a medium taken from the environment via a line 3 a arranged in the base 3, which medium is returned to the environment via a line 3 b after a portion of its heat content has been removed becomes.
- the heat exchanger W w is fed through connecting lines 10a, 10b with a heat transfer medium, the heating of which, when the machine is used, serves as a heat machine for generating energy.
- the shape of the piston crown 8a of the hot piston 8 is adapted to the shape of the curved partition 6.
- a high flow velocity and thus a better heat transfer is achieved by this adapted shape, when the working medium from the shrinking hot working volume V h via the regenerator R h and the heat exchanger W w into the space for the warm working volume V w when the cycle is complete flows, which is formed between the two pistons 8 and 9.
- a baffle 11 is arranged in the edge region of the partition 6. This baffle 11 forms flow channels with a small flow cross-section in the edge region of the partition wall 6, so that the working medium leaving the hot working volume V h is passed at high flow velocity over the edge region of the partition wall 6 before the working medium enters the regenerator R h .
- the cold piston 9 separating the warm working volume V w from the cold working volume V k by its piston crown 9a is cup-shaped and provided with an insulating layer 9c on the inside of both its piston crown 9a and its piston skirt 9b.
- the piston jacket 9b serves as a separation between the external heat exchanger W w and the internal cold heat exchanger W k .
- heat is transferred in an annulus.
- this is formed by the outer lateral surface of the piston jacket 9b and the inner surface of the heat exchanger W w .
- the annular space results between the inner jacket surface of the piston jacket 9b provided with the insulating layer 9c and the surface of the cold heat exchanger W k .
- both heat exchangers W w and W k are formed in two parts from a base body 12 and 13 and from a sealing body 14 and 15, respectively.
- the base body 12 and 13 also serves as a liner for the cold piston 9.
- each base body 12 and 13 is provided with channels 12a and 13a through which the respective heat transfer medium flows and which leads to the connecting lines 10a , 10b and 3a, 3b are connected.
- the channels 12a and 13a which are open on one side, are covered by the respective sealing body 14 and 15, respectively.
- the connecting lines 10a and 10b of the warm heat exchanger W w leading into the pressure-tight housing 1 can also be designed without problems.
- the surface of the base body 12 or base body 13 serving as the running surface for the piston 9 is designed with grooves 12b or 13b through which the working medium flows and which at the same time the surface of the heat exchanger W participating in the heat transfer Increase w or W k .
- the base bodies 12 and 13 can also be corrugated or be formed with a porous surface.
- the sealing body 14 and 15 are preferably made of heat-insulating material in order to avoid unwanted heat dissipation from the respective heat exchanger W w or W k .
- a sealing ring 16 which interacts with the piston skirt 9a is arranged between the warm heat exchanger W w and the regenerator R k connected downstream on the process side thereof. This sealing ring 16 ensures that the working medium in its flow between the heat exchangers W w and W k is passed through the cold regenerator R k , which is arranged in an extension of the base body 12 on the inside of the housing 1.
Abstract
Description
- 1
- Gehäuse
- 1a
- Flansch
- 2
- Motorgehäuse
- 2a
- Flansch
- 3
- Boden
- 3a
- Leitung
- 3b
- Leitung
- 4
- Gehäusedeckel F
- 5
- Gasbrenner
- 5a
- Zufuhrrohr
- 5b
- Dosierhalbkugel
- 5c
- Brennerfläche
- 5d
- Brennraum
- 5e
- Abgasrohr
- 6
- Trennwand
- 6a
- Tragring
- 6b
- Verlängerung
- 7a
- Isolierring
- 7b
- Isolierring
- 8
- heißer Kolben
- 8a
- Kolbenboden
- 8b
- Kolbenstange
- 9
- kalter Kolben
- 9a
- Kolbenboden
- 9b
- Kolbenmantel
- 9c
- Isolierschicht
- 10a
- Anschlußleitung
- 10b
- Anschlußleitung
- 11
- Leitblech
- 12
- Grundkörper
- 12a
- Kanal
- 12b
- Nut
- 13
- Grundkörper
- 13a
- Kanal
- 13b
- Nut
- 14
- Dichtkörper
- 15
- Dichtkörper
- 16
- Dichtring
- Vh
- heißes Arbeitsvolumen
- Vw
- warmes Arbeitsvolumen
- Vk
- kaltes Arbeitsvolumen
- Rh
- heißer Regenerator
- Rk
- kalter Regenerator
- Ww
- Wärmeübertrager
- Wk
- Wärmeübertrager
Claims (7)
- Nach einem regenerativen Gaskreisprozeß arbeitende Wärme- und Kältemaschine mit zwei in einem druckdichten Gehäuse (1) linear beweglichen Kolben (8,9), die gemeinsam ein warmes Arbeitsvolumen (Vw) begrenzen und von denen der eine Kolben (8) im Gehäuse (1) ein heißes, mit Wärme beaufschlagtes Arbeitsvolumen (Vh) und der andere Kolben (9) ein kaltes Arbeitsvolumen (Vk) begrenzt, wobei die drei Arbeitsvolumina (Vh, VW, Vk) unter Zwischenschaltung von Regeneratoren (Rh, Rk) und Wärmeübertragern (Ww, Wk) miteinander verbunden sind und ein Antrieb und/oder eine Steuerung für die Kolben (8,9) vorgesehen ist,
dadurch gekennzeichnet,
daß der das warme und kalte Arbeitsvolumen (Vw, Vk) durch seinen Kolbenboden (9a) voneinander trennende Kolben (9) topfförmig ausgebildet ist und daß sein Kolbenmantel (9b) als Trennung zwischen dem außenliegenden warmen Wärmeübertrager (Ww) und dem innenliegenden kalten Wärmeübertrager (Wk) dient, wobei die Wärmeübertragung von dem bzw. an das Arbeitsmedium bei beiden Wärmeübertragern (Ww, Wk) zwischen der äußeren bzw. der inneren Mantelfläche des Kolbenmantels (9b) und der zugehörigen Oberfläche des jeweiligen Wärmeübertragers (Ww bzw. Wk) erfolgt. - Wärme- und Kältemaschine nach Anspruch 1, dadurch gekennzeichnet, daß der das kalte Arbeitsvolumen begrenzende Kolben (9) zumindest teilweise aus schlecht wärmeleitendem Material hergestellt ist.
- Wärme- und Kältemaschine nach Anspruch 2, dadurch gekennzeichnet, daß der das kalte Arbeitsvolumen begrenzende Kolben (9) mindestens auf einer Seite mit schlecht wärmeleitendem Material (Isolierschicht 9c) versehen ist.
- Wärme- und Kältemaschine nach mindestens einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die vom Arbeitsmedium beaufschlagte Oberfläche der Wärmeübertrager (Ww, Wk) durch Aufbringen von porösem Material, durch Riffeln oder Nuten (12b,13b) und/oder durch die Verwendung geriffelter bzw. genuteter Bleche vergrößert ist.
- Wärme- und Kältemaschine nach mindestens einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Wärmeübertrager (Ww, Wk) jeweils zweiteilig aus einem mit offenen Kanälen (12a bzw. 13a) versehenen, als Laufbuchse für den Kolben (9) ausgebildeten Grundkörper (12 bzw. 13) und aus einem die offene Seite der Kanäle (12a bzw. 13a) verschließenden Dichtkörper (14 bzw. 15) ausgebildet sind.
- Wärme- und Kältemaschine nach Anspruch 5, dadurch gekennzeichnet, daß der Dichtkörper (14,15) aus wärmeisolierendem Material hergestellt ist.
- Wärme- und Kältemaschine nach mindestens einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß zwischen dem warmen Wärmeübertrager (Ww) und dem diesem prozeßseitig nachgeschalteten Regenerator (Rk) ein mit dem Kolbenmantel (9b) zusammenwirkender Dichtring (16) angeordnet ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4328993A DE4328993C2 (de) | 1993-08-28 | 1993-08-28 | Maschine zum Heizen und/oder Kühlen |
DE4328993 | 1993-08-28 | ||
PCT/EP1994/002753 WO1995006847A1 (de) | 1993-08-28 | 1994-08-19 | Wärme- und kältemaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0665940A1 EP0665940A1 (de) | 1995-08-09 |
EP0665940B1 true EP0665940B1 (de) | 1998-03-04 |
Family
ID=6496259
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP94926210A Expired - Lifetime EP0665940B1 (de) | 1993-08-28 | 1994-08-19 | Wärme- und kältemaschine |
Country Status (7)
Country | Link |
---|---|
EP (1) | EP0665940B1 (de) |
JP (1) | JPH08503062A (de) |
KR (1) | KR950704661A (de) |
BR (1) | BR9405561A (de) |
DE (1) | DE4328993C2 (de) |
ES (1) | ES2114219T3 (de) |
WO (1) | WO1995006847A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4401247C2 (de) * | 1994-01-18 | 1998-10-08 | Bosch Gmbh Robert | Wärmeübertrager |
DE19516499A1 (de) * | 1995-05-05 | 1996-12-05 | Bosch Gmbh Robert | Verfahren zur Abgaswärmenutzung bei Wärme- und Kältemaschinen |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1240862A (en) * | 1915-09-21 | 1917-09-25 | Ivar Lundgaard | Refrigerating-machine. |
US1275507A (en) * | 1917-01-29 | 1918-08-13 | Rudolph Vuilleumier | Method and apparatus for inducing heat changes. |
JPH0660770B2 (ja) * | 1986-03-25 | 1994-08-10 | 川崎重工業株式会社 | 熱駆動ヒ−トポンプ |
JP2500447Y2 (ja) * | 1991-03-28 | 1996-06-05 | サムスン エレクトロニクス カンパニー リミテッド | ボルマイア―ヒ―トポンプ |
DE4206957A1 (de) * | 1992-03-05 | 1993-09-16 | Viessmann Werke Kg | Aussenbeheizte, regenerative, nach dem vuilleumier-kreisprozess arbeitende waerme- und kaeltemaschine |
-
1993
- 1993-08-28 DE DE4328993A patent/DE4328993C2/de not_active Expired - Fee Related
-
1994
- 1994-08-19 EP EP94926210A patent/EP0665940B1/de not_active Expired - Lifetime
- 1994-08-19 JP JP7507906A patent/JPH08503062A/ja active Pending
- 1994-08-19 KR KR1019950701605A patent/KR950704661A/ko not_active Application Discontinuation
- 1994-08-19 ES ES94926210T patent/ES2114219T3/es not_active Expired - Lifetime
- 1994-08-19 WO PCT/EP1994/002753 patent/WO1995006847A1/de active IP Right Grant
- 1994-08-19 BR BR9405561-0A patent/BR9405561A/pt not_active Application Discontinuation
Also Published As
Publication number | Publication date |
---|---|
BR9405561A (pt) | 1999-09-08 |
EP0665940A1 (de) | 1995-08-09 |
ES2114219T3 (es) | 1998-05-16 |
KR950704661A (ko) | 1995-11-20 |
DE4328993C2 (de) | 1995-11-30 |
DE4328993A1 (de) | 1995-03-09 |
WO1995006847A1 (de) | 1995-03-09 |
JPH08503062A (ja) | 1996-04-02 |
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