EP0527993B1 - Machine thermique et frigorifique a regeneration et chauffee par l'exterieur - Google Patents

Machine thermique et frigorifique a regeneration et chauffee par l'exterieur Download PDF

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Publication number
EP0527993B1
EP0527993B1 EP92905628A EP92905628A EP0527993B1 EP 0527993 B1 EP0527993 B1 EP 0527993B1 EP 92905628 A EP92905628 A EP 92905628A EP 92905628 A EP92905628 A EP 92905628A EP 0527993 B1 EP0527993 B1 EP 0527993B1
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EP
European Patent Office
Prior art keywords
piston
pressure vessel
heat exchangers
spaces
machine
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Expired - Lifetime
Application number
EP92905628A
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German (de)
English (en)
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EP0527993A1 (fr
Inventor
Peter Hofbauer
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Viessmann Werke GmbH and Co KG
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Viessmann Werke GmbH and Co KG
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    • 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 an externally heated, regenerative heating and cooling machine according to the preamble of claims 1 and 7 respectively.
  • Such heating and cooling machines have been developed based on the Vuilleumier cycle, which has been known since 1918, and have u. a. the advantage that they can be operated with helium or hydrogen gas instead of environmentally harmful CFCs.
  • the invention is based on the task of redesigning and improving a machine of the type mentioned in such a way that the effort for the movement drive and for the sealing is eliminated and the whole machine can be made more compact than a self-contained, cylindrical pressure vessel.
  • thermodynamic processes do not require any further explanation, especially since they are discussed in detail in the aforementioned publications.
  • the entire machine advantageously consists of only two moving parts, namely the pressure vessel, in the appropriately designed and limited by the "outer" envelope with respect to the rolling envelope of the non-driven and only held in position by gravity rolls relatively on the envelope curve, whereby only the pressure vessel requires storage on the enclosure and, as is known, a small additional external drive (electric motor) only for loss compensation in the system (friction and pressure differences due to flow resistance) and for speed control.
  • the pressure vessel in the appropriately designed and limited by the "outer" envelope with respect to the rolling envelope of the non-driven and only held in position by gravity rolls relatively on the envelope curve, whereby only the pressure vessel requires storage on the enclosure and, as is known, a small additional external drive (electric motor) only for loss compensation in the system (friction and pressure differences due to flow resistance) and for speed control.
  • the heat exchangers arranged laterally on the pressure vessel at the same time form the radial boundary walls of the rooms which are not in direct connection with the heat exchanger which is exposed to heat from the outside.
  • the regenerators are then arranged inside the pressure vessel on the outside along the heat exchangers.
  • the heating and cooling machine consists of movable separators K (piston) volume-changing rooms 6-9 for the heating circuit HK on the one hand and for the cooling circuit KK on the other hand, the heating and cooling circuits HK, KK each having heat exchangers 10-13 assigned to the volume-changing rooms 6-9.
  • Thermal regenerators 14, 15 are arranged between the heat exchangers 10, 11, 12, 13 of each circuit, and the two circuits HK, KK are connected to one another at point 138 (see FIG. 5 or 20).
  • FIG. 5 or 20 For this switching principle known per se, it is essential according to the invention, as can be seen from FIG.
  • the spaces 6-9 and the separating elements K are designed in the form of a rotary piston machine, which comprises a pressure container 1 rotatably mounted in a housing 16 a roller piston 2 arranged therein without a drive and separating the spaces 6-9 is formed, the heat exchangers 10-13 and the regenerators 14, 15 being arranged on the rotatable pressure vessel 1, that is to say they rotate with the latter.
  • the stationary heat supply source 3 is arranged in the arrangement area of the heat exchanger 10 connected between the space 6 and the regenerator 14, which extends over the entire circumference.
  • the assignment of the heat exchangers 10 to 13 is illustrated in a highly schematic manner as a pure circuit diagram in FIG. 3, in which the corresponding reference numerals are used and which represents the prior art.
  • the pressure vessel 1 is mounted in the containment housing 16, in which the burner forming the heat supply source 3 is also arranged under the pressure vessel 1, with which the heat exchanger 10 is acted upon.
  • An exhaust hood 17 which extends upward around the pressure vessel removes the exhaust gases.
  • the two-sided bearing extensions 22 of the pressure vessel 1 simultaneously form the supply openings 22 'for the medium with which the heat exchangers 11, 12, 13 arranged on the end face of the pressure vessel are acted upon.
  • the end faces 1 'of the pressure vessel 1 are provided with radially oriented ribs 23 which on the one hand promote the media flowing through and on the other hand contribute to increasing the heat transfer areas.
  • the pressure vessel 1 is coupled to an electric motor 26 for the reasons mentioned, which, however, apart from the starting phase, does not have the task of driving the whole thing, since the drive energy is introduced via the heat exchanger 10 acted upon by the heat source 3.
  • the rolling piston 2 Since the rolling piston 2 is located without a drive in the interior 4 of the pressure container 1, eccentrically below its axis of rotation 1 ", it is filled with a material of higher specific weight. With regard to the configurations of the rolling piston 2 and the interior 4, reference is made to FIG. 2 , 3 referenced, which correspond to a rotary lobe machine type KA 4.
  • the machine is designed in such a way that the rolling piston 2 is provided on its side flanks 2 'with coaxial, reduced-diameter and disk-shaped, externally toothed extensions 18 and provided with corresponding internal teeth 19, wherein the internal toothing diameter is larger than the external toothing diameter of the extensions 18.
  • These extensions 18 are expediently used to attach the aforementioned additional load bodies 21 to them.
  • FIG. 4 The relative movement of the rolling piston 2, which remains at the bottom due to the force of gravity when the pressure vessel 1 rotates, is schematically illustrated in FIG. 4.
  • the envelope of the interior 4 is shown as being stationary. This does not require a special explanation, since in relation to the rolling piston movement to the individual rooms 6-9, analogy to the known machine according to FIG. 20 takes place.
  • the medium displaced from the space 6 passes through the slot 24 or 6 ′ into the heat exchanger 10 and after flowing through a channel 27 into the regenerator 14 and after its passage into the heat exchanger 11 and after this into the enlarging space 9.
  • the filling gas flows from space 8 through 8 'to heat exchanger 12, through regenerator 15 via heat exchanger 13 and slot 7' into space 7.
  • FIG. 3 The slots and flow guides in the developments A, B of Figures 6, 7 are provided with corresponding reference numerals; 6, 7 also illustrate the arrangements and extensions of the heat exchangers and the regenerators 14, 15 on the circumference of the pressure vessel 1.
  • All of the heat exchangers, regenerators and the spaces 6-9 form a self-contained pressure system in which the filling gas goes back and forth is pumped, the heat supply source 3 causing the actual drive.
  • this pressure system namely along the end faces 1 'of the pressure vessel 1, the medium that is heating up there on one side WS and the medium that is cooling there (preferably air) sweeps past.
  • FIGS. 8, 9 illustrate the heat exchangers 11-13, to which the air supplied through both bearing extensions 22, for example at 25 ° C., is guided in the direction of the arrows in FIG. 1 and on the warm side WS with, for example, 95 ° C and on the cooling side KS flows at 10 ° C. These temperatures are only to be understood as examples.
  • a machine of type KA 3 is shown, in connection with the heat exchangers 10-12 and the two regenerators 14, 15.
  • rooms 9, 7 are represented by only one chamber and the connection of the two circles HK and KK takes place on or with this chamber at 138.
  • FIGS. 10-18 in which reference numerals from 100 are used, which refer to corresponding elements.
  • the heat exchangers 111, 112, 113 form the radial boundary walls of the rooms 107, 108, 109 and the regenerators 114, 115 are arranged on the outside, but within the pressure vessel 100 along the heat exchangers 111, 112, 113.
  • This results in an extremely advantageous construction of the machine namely in such a way that the heat exchangers 111, 112, 113, the regenerators 114, 115 and the rotary piston 102 can be formed in the form of a disk-shaped package 128 between two housing shells 129 forming the pressure container 101.
  • 128 circular disks 128 "with openings 137 for supplying and discharging the heat transfer medium to and from the heat exchangers 111, 112, 113 are arranged on both sides.
  • the heat exchangers 111, 112, 113 are formed from tubes 136, which are provided at their ends 133 with widenings 134, the cross section of which corresponds to polygons, which form a honeycomb structure with contiguous side flanks of the expansions 134 are joined together and are connected to one another in a liquid-tight and gas-tight manner at the expansion ends 135.
  • These tubes 136 extend parallel to the machine axis 139, ie the hatching chosen for this in FIG. 13 does not correspond to the actual tube orientation.
  • the regenerators 114, 115 are designed in a correspondingly arcuate manner and are formed, for example, from sintered metal.
  • Partitions 142 inserted into the heat exchangers 111, 112, 113 ensure a meandering flow through the heat exchangers of the operating medium contained in the two closed circuits, which are connected to one another at 138.
  • the pressure container 101 is designed as a stator, and at least one electromagnet 132, which is controlled in the sense of the piston movement, is arranged on at least one side adjacent to the piston driven as a rotary piston 102.
  • the accommodation spaces 144 can also be hermetically sealed by disks 145 with respect to the high-pressure and gas-carrying spaces, so that they no longer have to be charged for the total dead volume of the machine.
  • the advantageous design of the machine in the shell design, in which the disk-shaped package 128 is enclosed also forms the prerequisite for an embodiment according to FIG. 17 in that the disk-shaped package 128 is divided into two chambers in which the rooms 106, 107 and the Rooms 108, 109 are arranged offset by 90 ° to one another; A rotary piston 102 is arranged in each chamber 130; the two rotary pistons 102 are firmly connected to one another, whereby a division into a "warm and cold" side can be achieved, and heat insulation 131 can also be arranged in disk form between the two chamber packages 128 'without any problems, in order to allow an internal heat flow from the warm to the largely prevent cold side.
  • the pressure container 100 is rotatably mounted in a suitable manner, which is indicated only schematically with bearings 150.
  • the connections 143 are, as shown, designed as rotary guides, the left connection 143 for the supply of the Heat exchanger 111 and the right one is used to supply heat exchangers 112 and 113.
  • the further connection openings 143 'leading to the outside are located in front of or behind the display level.
  • FIGS. 10 and 11 the flow arrows for the operating medium (for example helium) are shown in FIGS. 10 and 11. Openings 151 for the heat exchanger 111, openings 152 for the heat exchanger 112 and openings 153 for the heat exchanger 113 are provided for the media (for example water) to be supplied to the heat exchangers 111, 112, 113 from the outside via the rotary guides 143 or to be discharged to the outside. With 154 thermal insulation in the pressure vessel 101 is designated.
  • the electromagnets 132 are controlled via a control circuit 155, which is only schematically indicated in FIG. 18.
  • the reference numeral 156 in FIG. 19 denotes an additional regenerator in the poor area between the cold and the hot side of the machine.
  • Such an additional regenerator 156 is also present in the machine according to FIGS. 10 to 12 or 17, which is installed in the partition between the two packets 128 ′ or the chambers 130. With this additional regenerator 156, the temperature values between the cold and hot iron of the machine can be better separated, i.e. there are different temperatures even in the warm area.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Hydraulic Motors (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Encapsulation Of And Coatings For Semiconductor Or Solid State Devices (AREA)

Claims (15)

  1. Machine thermique et frigorifique à régénération chauffée de l'extérieur, et fonctionnant selon le cycle de Vuilleumier, constituée d'espaces (6 à 9) dont le volume est variable par des éléments de séparation mobiles (K) qui sont destinés au circuit de chauffage (HK) d'une part, et au circuit de refroidissement (KK) d'autre part, les circuits de chauffage et de refroidissement (HK, KK) comportant des échangeurs thermiques (10 à 13) respectivement associés aux espaces (6 à 9) à volume variable, des régénérateurs thermiques (14, 15) étant disposés entre les échangeurs thermiques (10, 11, 12, 13) de chaque circuit, et les deux circuits (HK, KK) étant reliés entre eux, les espaces (6 à 9) et les éléments de séparation (K) étant en outre réalisés sous la forme d'une machine à piston rotatif,
       caractérisée en ce que,
       le piston de la machine à piston rotatif est disposé en tant que piston à rouleaux (2) non entraîné dans une enceinte sous pression (1) contenant les espaces (6 à 9), qui est entraînée en rotation autour de son axe longitudinal (1") situé à l'horizontale, ce piston étant constitué d'un matériau de poids spécifique élevé ou son espace intérieur étant rempli d'un matériau de poids spécifique élevé, et par des corps de charge (21), qui sont disposés coaxialement à l'axe du piston à rouleaux sur les flancs latéraux (2') du piston à rouleaux (2) dans des chambres séparées (20) de l'enceinte sous pression (1) et reliés au piston à rouleaux (2), il est de ce fait maintenu dans une position dans laquelle il se découle par rapport à l'enceinte sous pression (1) rotative, et en ce que la source stationnaire d'apport de chaleur (3) est disposée au niveau de l'échangeur thermique (10) monté entre l'un (6) des espaces (6 à 9) et l'un (14) des régénérateurs (14, 15).
  2. Machine selon la revendication 1,
       caractérisée en ce que,
       l'espace intérieur (4) de l'enceinte sous pression (1) comportant les espaces (6 à 9) et le piston à rouleaux (2) associé correspondant à une machine trochoïde de type "KA 4" ou "KA 3" en ce qui concerne leurs contours.
  3. Machine selon la revendication 1 ou 2,
       caractérisée en ce que,
       au niveau d'au moins un de ses flancs latéraux, le piston à rouleaux (2) est muni d'un prolongement (18) en forme de disque comportant une denture extérieure, et en ce que dans l'espace intérieur (4) de l'enceinte sous pression (1), il est disposé une entretoise (19) associée au prolongement (18) à denture intérieure correspondante, qui constitue le cercle de roulement pour le prolongement (18) du piston à rouleaux (2).
  4. Machine selon l'une des revendications 1 à 3,
       caractérisée en ce que,
       les faces frontales de l'enceinte sous pression (1) sont réalisées sous la forme d'échangeurs thermiques (11, 12, 13), les échangeurs thermiques (11, 13) étant disposés du côté du chauffage (WS) et l'échangeur thermique (12) du côté du refroidissement (KS).
  5. Machine selon la revendication 4,
       caractérisée en ce que,
       des ailettes (23) agrandissant les surfaces d'échange thermique et activant le transfert radial sont disposées sur l'extérieur des surfaces frontales (1') de l'enceinte sous pression (1).
  6. Machine selon l'une des revendications 1 à 5,
       caractérisée en ce que,
       les échangeurs thermiques forment les parois de délimitation radiale des espaces (7 à 9), et en ce que les régénérateurs (14, 15) sont disposés à l'extérieur le long des échangeurs thermiques (11 à 13).
  7. Machine thermique et frigorifique à régénération chauffée de l'extérieur, et fonctionnant selon le cycle de Vuilleumier, constituée d'espaces (106 à 109) dont le volume est variable par des éléments de séparation mobiles (K) qui sont destinés au circuit de chauffage (HK) d'une part, et au circuit de refroidissement (KK) d'autre part, les circuits de chauffage et de refroidissement (HK, KK) comportant des échangeurs thermiques (110 à 113) respectivement associés aux espaces (106 à 109) à volume variable, des régénérateurs thermiques (114, 115) étant disposés entre les échangeurs thermiques (110, 111, 112, 113) de chaque circuit, et les deux circuits (HK, KK) étant reliés entre eux, les espaces (106 à 109) et les éléments de séparation (K) étant en outre réalisés sous la forme d'une machine à piston rotatif,
       caractérisée en ce que,
       le piston de la machine à piston rotatif est un piston à rouleaux guidé en tant que piston rotatif (102), qui est disposé dans une enceinte sous pression (100) contenant les espaces (106 à 109) qui est réalisée sous la forme d'un stator, en ce qu'au moins d'un côté voisin du piston rotatif (102), au moins trois électro-aimants commandés dans le sens du mouvement du piston sont disposés dans l'enceinte sous pression (100) pour entraîner le piston rotatif (102) par rapport à l'enceinte sous pression (100), en ce que les échangeurs thermiques (111 à 113) forment les parois de délimitation radiale des espaces (107 à 109), et en ce que les régénérateurs (114, 115) sont disposés à l'extérieur le long des échangeurs thermiques (111 à 113).
  8. Machine selon la revendication 7,
       caractérisée en ce que,
       les échangeurs thermiques (111 à 113), les régénérateurs (114, 115) et le piston rotatif (102) sont disposés en tant que paquet (128) en forme de disque entre deux coquilles du carter (129) constituant l'enceinte sous pression (101).
  9. Machine selon la revendication 8,
       caractérisée en ce que,
       des deux côtés du paquet (128), il est disposé des disques circulaires (128") comportant des passages (137) pour l'arrivée et l'évacuation du fluide caloporteur aux et à partir des échangeurs thermiques (111 à 113).
  10. Machine selon la revendication 8 ou 9,
       caractérisée en ce que,
       le paquet (128) en forme de disque est subdivisé en deux chambres, dans lesquelles les espaces (106, 107) et les espaces (108, 109) sont décalés de 90° les uns par rapport aux autres, en ce qu'un piston rotatif (102) est disposé dans chaque chambre (130), et en ce que les deux pistons rotatifs (102) sont reliés solidairement entre eux.
  11. Machine selon la revendication 10,
       caractérisée en ce que,
       une isolation thermique (131) est disposée entre les deux paquets (128') de chambres.
  12. Machine selon l'une des revendications 7 à 11,
       caractérisée en ce que,
       les échangeurs thermiques (111 à 113) sont réalisés en tant qu'éléments pouvant être traversés sous forme de méandres.
  13. Machine selon l'une des revendications 7 à 12,
       caractérisée en ce que,
       les régénérateurs (114, 115) sont réalisés en métal fritté.
  14. Machine selon l'une des revendications 7 à 13,
       caractérisée en ce que,
       les échangeurs thermiques (111 à 113) sont constitués de tubes (136) et que les extrémités (133) de ces derniers comportent des évasements (134), dont la section transversale correspond à des carrés, qui sont assemblés sans instertices en une structure alvéolaire par les flancs latéraux accolés des évasements (134) et qui, au niveau des extrémités (135) des évasements, sont reliés entre eux de façon étanche aux liquides et aux gaz.
  15. Machine selon la revendication 10,
       caractérisée en ce que,
       un générateur additionnel (156) est disposé entre les deux chambres (130).
EP92905628A 1991-03-06 1992-03-05 Machine thermique et frigorifique a regeneration et chauffee par l'exterieur Expired - Lifetime EP0527993B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4107092 1991-03-06
DE4107092A DE4107092A1 (de) 1991-03-06 1991-03-06 Aussenbeheizte, regenerative waerme- und kaeltemaschine
PCT/DE1992/000186 WO1992015826A1 (fr) 1991-03-06 1992-03-05 Machine thermique et frigorifique a regeneration et chauffee par l'exterieur

Publications (2)

Publication Number Publication Date
EP0527993A1 EP0527993A1 (fr) 1993-02-24
EP0527993B1 true EP0527993B1 (fr) 1996-05-15

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EP92905628A Expired - Lifetime EP0527993B1 (fr) 1991-03-06 1992-03-05 Machine thermique et frigorifique a regeneration et chauffee par l'exterieur

Country Status (6)

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EP (1) EP0527993B1 (fr)
AT (1) ATE138183T1 (fr)
DE (2) DE4107092A1 (fr)
DK (1) DK0527993T3 (fr)
ES (1) ES2088131T3 (fr)
WO (1) WO1992015826A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19516499A1 (de) * 1995-05-05 1996-12-05 Bosch Gmbh Robert Verfahren zur Abgaswärmenutzung bei Wärme- und Kältemaschinen
BE1011918A3 (fr) * 1998-05-15 2000-03-07 Belge De Construction Et D Eng Procede de transformation de chaleur et installation pour sa realisation.
US9908706B1 (en) 2016-10-12 2018-03-06 Goodrich Corporation Electric motor power drive unit for an aircraft cargo hold floor system

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1556302A (fr) * 1967-12-13 1969-02-07
DE3602634A1 (de) * 1986-01-29 1987-07-30 Helmut Prof Dr Rer Nat Krauch Regenerative waermemaschine

Also Published As

Publication number Publication date
DE4107092A1 (de) 1992-09-10
DK0527993T3 (da) 1996-09-23
WO1992015826A1 (fr) 1992-09-17
EP0527993A1 (fr) 1993-02-24
DE59206284D1 (de) 1996-06-20
ES2088131T3 (es) 1996-08-01
ATE138183T1 (de) 1996-06-15

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