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EP0523035B1 - Processus de fonctionnement d'une thermopompe a compression et thermopompe a compression - Google Patents

Processus de fonctionnement d'une thermopompe a compression et thermopompe a compression Download PDF

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Publication number
EP0523035B1
EP0523035B1 EP90905521A EP90905521A EP0523035B1 EP 0523035 B1 EP0523035 B1 EP 0523035B1 EP 90905521 A EP90905521 A EP 90905521A EP 90905521 A EP90905521 A EP 90905521A EP 0523035 B1 EP0523035 B1 EP 0523035B1
Authority
EP
European Patent Office
Prior art keywords
vapour
nozzle
liquid
jet
heat pump
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
Application number
EP90905521A
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German (de)
English (en)
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EP0523035A1 (fr
Inventor
Karl Friedrich Vedder
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.)
Masur Walter
Original Assignee
Masur Walter
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Filing date
Publication date
Application filed by Masur Walter filed Critical Masur Walter
Priority to AT90905521T priority Critical patent/ATE112843T1/de
Publication of EP0523035A1 publication Critical patent/EP0523035A1/fr
Application granted granted Critical
Publication of EP0523035B1 publication Critical patent/EP0523035B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0015—Ejectors not being used as compression device using two or more ejectors
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the invention relates to a method for operating a compression heat pump with evaporator, compressor, condenser and hot liquid jet pump as a relaxation device for the condensed refrigerant, and a compression heat pump.
  • Multi-stage compression heat pumps and the underlying thermodynamic process and procedural sequence allow a higher pressure difference between evaporation and condensing pressure to be overcome more effectively.
  • suitable refrigerants for example, even if it takes more construction work, higher flow temperatures for heat utilization systems can be achieved than with single-stage compression machines; but also by means of electrically driven heat pumps while reducing the total amount of exergy used, e.g. among other things, operate the widespread hot water heating systems as a heat utilization system in monovalent operation, provided that supply temperatures between 90 ° C and 70 ° C can be achieved even at low heat source temperatures in high winter and that the overall cost of such a heat generator is reasonable.
  • a compressor heat pump according to DE-A-36 22 743 in which the hot condensate is expanded via a downstream ejector with a coupled separator, should be able to achieve an approximately the same rate of increase for the entire process.
  • the liquid phase is separated from the steam behind the injector nozzle.
  • the collecting vessel has an outlet connected to the evaporator and an outlet connected to the suction connection of the compressor.
  • a liquid-operated pump is known with an acceleration nozzle for the drive liquid, which opens into a pump chamber.
  • the pump chamber has a vacuum connection.
  • the expansion nozzle is designed as a multi-jet nozzle in which the outer nozzle channels are inclined radially inwards.
  • This known jet pump is used as a laboratory pump for evacuation.
  • the invention has for its object to provide a method for operating a compression heat pump and a compression heat pump that works economically even with high heat utilization temperatures and low heat source temperatures with the least possible construction costs.
  • the advantages that can be achieved with this method are based on the multi-stage design of the hot-liquid radiators, in that at least two hot-liquid jet stages, in alternation with the application , enable a variable temperature bandwidth adaptation in the preliminary stage range to changing temperatures of the heat extraction source Q o .
  • the expansion nozzle of the hot liquid jet pump disassembles the liquid jet into a plurality of individual jets, the angular position of which toward the center of the nozzle, viewed in the jet direction, has a tangential and a radially inwardly pointing component.
  • the multi-jet expansion nozzle for the hot liquid jet pump makes it possible, even in intermittent mode of operation, to influence the resulting excess steam formation by adjusting the number and size of the individual jet channels to the pressure level specified in the system so that the residual moisture in the steam liquid mixtures of the cyclones is only reduced has a small percentage and, on the other hand, the shock losses that often occur with radiators hardly occur.
  • the steam supplied to the compressor can be dried by the heat of the working medium.
  • the partial process sequence in the wet steam area makes it necessary to expel the residual moisture, so that when the heat is exchanged with hot gas from the superheating heat of the compressor, the still slightly moist working fluid steam stream is converted into slightly superheated steam.
  • a further development of the invention provides that the temperature bandwidth is controlled by changing the interval times when the hot liquid heater stages are exposed to condensate.
  • this process concept also makes it possible, when the heat removal temperature from Q o changes, to adjust the temperature bandwidth by shifting cyclone condensate by means of a control valve while changing the pressure gradation in the cyclones of the hot liquid jet stages by using different interval times when hot condenser stages are exposed to hot condensate this is introduced in the unequal amount of working fluid as cyclone condensate into the respective stage concerned.
  • the propulsion jet nozzle design of the multi-jet nozzle creates a radiator in which a funnel-shaped one is used to achieve optimal, almost shock-free relaxation of the working medium
  • Nozzle cone is provided and centripetal flowing individual jets of the working fluid are formed.
  • the course of the nozzle channels in the nozzle cone is inclined both tangentially and radially inwards.
  • the tangential inclination extends in the direction of the narrowing spiral arrangement of the nozzle channels.
  • the individual jets are rotated in a plane orthogonal to the jet direction by an angle corresponding to the inclination from the vertical in the further course of the flowing jet.
  • the hot liquid radiators 4 and 5 are assigned cyclones 6 and 7 of different sizes and variable volumes, which in operation results in an accumulation of excess steam with heat of a temperature which is above the temperature of the cold steam isobars of T o 1. Spotlight level is around Q o (Fig. 1), and further the size of this excess steam is very much dependent on the design and construction of the jet nozzle (Fig. 3) and ultimately a residual partial relaxation of fluid from the cyclones 6 and 7 along one shortened isenthalpics (Fig.
  • the temperature bandwidth control of the radiator stage region at a temperature of T o changing by Q o is also controlled by means of different fluid mass distribution (see FIG. 2a, points 9 and 2b and 2c) o 1st emitter stage carried out.
  • FIGS. 1 and 2 The consideration of a working cycle in the new method expediently begins with the aid of FIGS. 1 and 2, functionally, with the exit of the liquid working fluid from the heat exchanger 2 of the heat utilization system, which in FIG. 1 shows the end point of the liquefaction isobars on the left saturation line in the log p-diagram.
  • the still hot fluid is then intermittently brought to partial relaxation by the hot liquid emitters 4 and 5 with the delivery of pump energy into the cyclones 6 and 7, in the course of which incoming cold steam is drawn in from T o 1st radiator stage by Q o and also from T o 2.
  • Radiator stage FIG.
  • the volume-related fluid mass fraction in the cyclones with a changing T o 1st radiator stage corresponds to its temperature-dependent size changed on the one hand in such a way that a controllable fluid valve 9 lets in fluid from the cyclone with higher pressure into that with lower pressure and greater volume; on the other hand, if it is necessary to shift the fluid in the opposite direction or in the same direction, depending on the temperature by Q o , this is also achieved over a different time interval of the hot fluid supply by means of a shuttle valve 3 into the radiators and exit via the expansion element 8.
  • the upper part of the mixing nozzle 12 with the length L 1 is dimensioned with respect to its taper in the transition to the neck diameter at this point in such a way that, in operation, the peripheral individual jets from the multi-jet nozzle in the narrowest cross section (BB) cover approximately the same circular area as this cross section, without turbulence.
  • the length L2 of the mixer nozzle neck is optimized in accordance with the pressure behavior of the working medium in the range of defined operating parameters by empirically determined measured values.
  • generate from the spiral mainly in the peripheral peripheral zone of the mixing jet nozzle channels in the core area of the mixer nozzle over the length L1 a zone C with a strong pressure drop.
  • the expansion nozzle consists of a multi-jet nozzle 12, the nozzle channels 16 of which are inclined tangentially and radially inward, the inlet openings 18 of the nozzle channels 16 being arranged in the inner conical lateral surface 24 of the multi-jet nozzle 12.
  • the nozzle channels 16 end in outlet openings 19 in the outer lateral surface the multi-jet nozzle 12, the view of which is shown in FIG. 4b.
  • the inlet openings 18 and outlet openings 19 of the nozzle channels 16 are arranged spirally in the peripheral region of the multi-jet nozzle 12, the tangential inclination of the nozzle channels 16 running in the direction of the decreasing distances between the spiral arranged inlet openings 18.
  • the multi-jet nozzle 12 has an inner cone 20 protruding toward the nozzle inlet opening 22 in the region free of nozzle channels 16.
  • the inner cone 20 can be arranged eccentrically and induce a spiral flow of the condensate entering the inlet openings 18.
  • the nozzle channels 16 are inclined on the one hand towards the nozzle axis or the jet axis and on the other hand in a tangential plane to the circular or spiral arrangement of the nozzle channels 16 from the parallel to the jet axis in the direction of decreasing distances between the nozzle channels 16.
  • the inclination in the tangential plane preferably takes place in the direction of the narrowing spiral line.
  • the size and number of the spiral-shaped nozzle channels affect the steam yield, depending on the outer jet circumference, due to the selected nozzle channel diameter, a large number of small holes compared to a small number of larger holes, depending on the specific steam condition of the working fluid in the cyclone delivers greater steam yield.
  • the excess steam results from the effective liquid condensate surface in the mixer nozzle, which is a targeted Optimization of the pressure levels in the jet pump area enables (see Fig. 1).

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Jet Pumps And Other Pumps (AREA)

Abstract

Un processus de fonctionnement d'une thermopompe à compression pourvue d'un évaporateur, d'un compresseur (1) d'un condensateur (2) et d'une pompe à jet de liquide chaud (4, 5) servant de dispositif de détente pour le réfrigérant condensé, prévoit que deux pompes à jet de liquide chaud (4, 5) sont alimentées par intermettence avec le condensat, que les deux mélanges vapeur-liquide produits sont maintenus à des pressions différentes, que la portion de vapeur du mélange vapeur-liquide maintenue à la pression la plus élevée est conduite au côté admission du compresseur (1) et que la portion de vapeur du mélange vapeur-liquide maintenue à la pression la plus basse est conduite à la pompe à jet de liquide chaud (5) à la pression la plus élevée, que la portion de liquide du mélange vapeur-liquide à la pression la plus élevée est amenée dans la portion de liquide du mélange vapeur-liquide à la pression la plus basse, que la portion de liquide du mélange vapeur-liquide à la pression la plus basse est conduite par l'intermédiaire d'un dispositif de détente iso-enthalpique à l'évaporateur et que la vapeur ainsi obtenue est amenée à la pompe à jet de liquide chaud (4) à la pression la plus basse.

Claims (12)

  1. Procédé de fonctionnement d'une thermopompe à compression avec un évaporateur, un compresseur (1), un condenseur (2) et deux pompes à jet de liquide chaud (4, 5) comme dispositifs de détente pour le fluide de refroidissement condensé qui sont alternativement soumises, par intermittence, à l'admission du condensat, dans lequel
    - les deux mélanges vapeur-liquide se produisant lors de la détente sont maintenus à des pressions différentes,
    - la partie vapeur du mélange vapeur-liquide à la pression supérieure est amenée au côté d'aspiration du compresseur (1) et la partie vapeur du mélange vapeur-liquide à la pression inférieure est amenée à la pompe à jet de liquide chaud (5) à la pression supérieure,
    - la partie liquide du mélange vapeur-liquide à la pression supérieure est introduite dans la partie liquide du mélange vapeur-liquide à la pression inférieure, et
    - la partie liquide du mélange vapeur-liquide à la pression inférieure est amenée par une détente iso-enthalpique à l'évaporateur et la vapeur qui se produit est amenée à la pompe à jet de liquide chaud (5) à la pression inférieure.
  2. Procédé selon la revendication 1, caractérisé en ce que le jet de liquide (14) du condensat est décomposé, par une tuyère de détente (12) des pompes à jet de liquide chaud (4, 5), en plusieurs jets individuels dont la position angulaire, pour conférer un mouvement rotatif avec concentration centripète du jet de liquide (14′) par rapport à l'axe de tuyère, vu dans la direction du jet, présente une composante orientée tangentiellement et une composante orientée radialement vers l'intérieur.
  3. Procédé selon la revendication 2, caractérisé en ce que le jet de liquide (14′) est formé et concentré par des jets individuels disposés en spirale.
  4. Procédé selon l'une des revendications 1 à 3, caractérisé en ce que la vapeur amenée au compresseur (1) est séchée par la chaleur de surchauffe du fluide de fonctionnement.
  5. Procédé selon l'une des revendications 1 à 4, caractérisé en ce qu'une régulation de la largeur de bande de la température se fait en modifiant les intervalles de temps lors de la soumission des pompes à jet de liquide chaud à l'admission de condensat.
  6. Thermopompe à compression avec évaporateur, compresseur (1), condenseur (2) et deux pompes à jet de liquide chaud (4, 5) comme dispositifs de détente pour le fluide de refroidissement condensé, et avec un dispositif (3) destiné à soumettre les pompes à jet de liquide chaud (4, 5) alternativement, par intermittence, à l'admission du condensat, dans laquelle :
    - les deux mélanges vapeur-liquide se produisant lors de la détente présentent, chacun, une pression différente,
    - le côté d'aspiration du compresseur (1) reçoit la partie vapeur du mélange vapeur-liquide à la pression supérieure et la pompe à jet de liquide chaud (5) à la pression supérieure reçoit la partie vapeur du mélange vapeur-liquide à la pression inférieure,
    - la partie liquide du mélange vapeur-liquide à la pression supérieure est introduite dans la partie liquide du mélange vapeur-liquide à la pression inférieure, et
    - l'évaporateur reçoit la partie liquide du mélange vapeur-liquide à la pression inférieure par une détente iso-enthalpique et la pompe à jet de liquide chaud (4) à la pression inférieure reçoit la vapeur qui se produit lors de l'évaporation.
  7. Thermopompe à compression selon la revendication 6, caractérisée en ce que chaque pompe à jet de liquide chaud (4, 5) présente une tuyère de détente consistant en une tuyère à jets multiples (12), qui, par des canaux de tuyère (16) orientés radialement vers l'intérieur, décompose le jet de fluide (14, 14′) en plusieurs jets individuels, tous les canaux de tuyère (16) de la tuyère à jets multiples (12) étant inclinés radialement vers l'intérieur et tangentiellement et la position angulaire des jets individuels présentant, par rapport à l'axe de tuyère, vu dans la direction du jet, une composante orientée tangentiellement et une composante orientée radialement vers l'intérieur.
  8. Thermopompe à compression selon la revendication 7, caractérisée en ce que des orifices d'entrée (18) des canaux de tuyère (16) sont disposés sur la surface enveloppe conique intérieure (24) de la tuyère à jets multiples (12).
  9. Thermopompe à compression selon la revendication 7 ou 8, caractérisée en ce que les orifices d'entrée (18) des canaux de tuyère (16) sont disposés, en vue de dessus, en spirale dans la zone périphérique de la tuyère à jets multiples (12).
  10. Thermopompe à compression selon la revendication 9, caractérisée en ce que l'inclinaison tangentielle des canaux de tuyère (16) s'étend en direction d'une distance décroissante entre les orifices d'entrée (18) disposés en spirale.
  11. Thermopompe à compression selon l'une des revendications 8 à 10, caractérisée en ce que la tuyère à jets multiples (12) présente, dans une zone exempte de canaux de tuyère (16), un cône intérieur (20) en saillie par rapport à l'orifice d'entrée de tuyère (22).
  12. Thermopompe à compression selon la revendication 11, caractérisée en ce que le cône intérieur (20) est disposé de manière excentrique et induit un courant en forme de spirale du condensat pénétrant dans les orifices d'entrée (18).
EP90905521A 1990-04-10 1990-04-10 Processus de fonctionnement d'une thermopompe a compression et thermopompe a compression Expired - Lifetime EP0523035B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90905521T ATE112843T1 (de) 1990-04-10 1990-04-10 Verfahren zum betreiben einer kompressionswärmepumpe, sowie kompressionswärmepumpe.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP1990/000570 WO1991015722A1 (fr) 1990-04-10 1990-04-10 Processus de fonctionnement d'une thermopompe a compression et thermopompe a compression

Publications (2)

Publication Number Publication Date
EP0523035A1 EP0523035A1 (fr) 1993-01-20
EP0523035B1 true EP0523035B1 (fr) 1994-10-12

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ID=8165475

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90905521A Expired - Lifetime EP0523035B1 (fr) 1990-04-10 1990-04-10 Processus de fonctionnement d'une thermopompe a compression et thermopompe a compression

Country Status (4)

Country Link
EP (1) EP0523035B1 (fr)
DE (1) DE59007469D1 (fr)
DK (1) DK0523035T3 (fr)
WO (1) WO1991015722A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6410775B1 (en) 1995-06-07 2002-06-25 La Jolla Pharmaceutical Company APL immunoreactive peptides, conjugates thereof and methods of treatment for APL antibody-mediated pathologies
US5874409A (en) * 1995-06-07 1999-02-23 La Jolla Pharmaceutical Company APL immunoreactive peptides, conjugates thereof and methods of treatment for APL antibody-mediated pathologies
EP0954531A1 (fr) * 1996-06-06 1999-11-10 Lajolla Pharmaceutical Company PEPTIDES IMMUNOREACTIFS PAR RAPPORT AUX aPL, LEURS CONJUGUES ET PROCEDES DE TRAITEMENT DES PATHOLOGIES DEPENDANTES DE L'ANTICORPS aPL
DE102005011807A1 (de) 2004-03-26 2005-10-13 Ebm-Papst St. Georgen Gmbh & Co. Kg Verfahren und Anordnung zur Kühlung eines Substrats, insbesondere eines Halbleiters

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2790595A (en) * 1950-09-20 1957-04-30 Metallgesellschaft Ag Steam jet apparatus
CH342583A (de) * 1956-06-21 1959-11-30 Rawyler Ernst Nach dem Prinzip der Wärmepumpe arbeitende Dampferzeugungsanlage
US3694107A (en) * 1970-11-19 1972-09-26 Nash Engineering Co Ejector apparatus and method of utilizing same
US3670519A (en) * 1971-02-08 1972-06-20 Borg Warner Capacity control for multiple-phase ejector refrigeration systems
DE3622743A1 (de) * 1986-07-07 1988-01-21 Ruhrgas Ag Waermepumpe
SE464319B (sv) * 1988-02-05 1991-04-08 Teknovia Ab Vaetskedriven straalpump
DE3834302A1 (de) * 1988-10-08 1990-04-12 Karl Friedrich Vedder Verfahren zum mehrstufigen, effizienteren waermepumpen mittels kompressormaschinen mit vorgeschalteten heissfluessigkeitsstrahlern fuer hohe waermenutzungstemperaturen

Also Published As

Publication number Publication date
WO1991015722A1 (fr) 1991-10-17
DE59007469D1 (de) 1994-11-17
EP0523035A1 (fr) 1993-01-20
DK0523035T3 (da) 1995-04-18

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