EP2321592B1 - Pompe à chaleur ou machine frigorifique et procédé permettant de faire fonctionner une pompe à chaleur ou une machine frigorifique - Google Patents

Pompe à chaleur ou machine frigorifique et procédé permettant de faire fonctionner une pompe à chaleur ou une machine frigorifique Download PDF

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Publication number
EP2321592B1
EP2321592B1 EP09782642A EP09782642A EP2321592B1 EP 2321592 B1 EP2321592 B1 EP 2321592B1 EP 09782642 A EP09782642 A EP 09782642A EP 09782642 A EP09782642 A EP 09782642A EP 2321592 B1 EP2321592 B1 EP 2321592B1
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EP
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Prior art keywords
coolant
heat
pump
displacement compressor
fluid displacement
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EP09782642A
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German (de)
English (en)
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EP2321592A1 (fr
Inventor
Klaus Ramming
Michael Deichsel
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AGO GmbH Energie und Anlagen
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AGO GmbH Energie und Anlagen
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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • F01K27/005—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for by means of hydraulic motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating 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
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers

Definitions

  • the invention relates to a method for operating a heat pump or chiller, in which a refrigerant is compressed by means of a liquid piston compressor, then cooled and then expanded and vaporized in a next step and finally fed back to the liquid piston compressor.
  • the invention relates in terms of device technology, a heat pump or chiller.
  • Heat pump or chiller processes have been part of the well-known state of the art for quite some time.
  • the use of liquid piston compressors attempts to realize an isothermal compression of the refrigerant in the closed loop process.
  • the compression space can be given generously sized and structurally very free surfaces to optimize heat transfer since there is no sealing problem when using a fluid as a "piston".
  • liquid-piston compressors can achieve a nearly isothermal compression.
  • Another advantage of a liquid piston compressor is the fact that a phase transition in the compression from the vapor to the liquid state for such devices is unproblematic, since the liquid piston can take no "mechanical” damage even in so-called "liquid shocks".
  • a prerequisite for the functioning of a liquid piston compressor is the use of immiscible fluids.
  • the invention has for its object to develop a method for operating a heat pump or chiller so that the efficiency of the process is further increased.
  • the same object is the present invention in device-technical terms with respect to a heat pump and chiller based.
  • the above object starting from a method of the type described above, achieved in that heat of the cooled after compression refrigerant is transferred to the refrigerant before it is fed back to the liquid piston compressor and thus the cycle is closed and that the refrigerant is expanded in an engine having an operative connection to a hydraulic pump (31) by means of which a hydraulic fluid of the liquid piston compressor (2) is pumpable.
  • This advantage has an effect, in particular, on heat pumps or refrigerating machines which are operated in the transcritical range, for example with CO 2 as refrigerant.
  • the critical temperature of CO 2 is 31 ° C. Above this temperature, no phase change to the liquid phase out is more possible, so that there is no ability of the refrigerant to release heat at the same temperature alone due to the phase change.
  • CO 2 is at a very high level End temperature must be compressed, so that in the further course of the cycle, the waste heat can be delivered to a heat source with a specified temperature. The heat to be released in this case comes solely from the cooling of the hot gas and not from a phase change.
  • the refrigerant is alternately compressed by two liquid piston compressors, each having a working space whose common working fluid is reciprocated alternately from the working space of one liquid piston compressor into the working space of the other liquid piston compressor. In this way, a homogenization of the mass flow in the remaining process steps can be achieved.
  • a further increase in continuity can be achieved by temporarily storing the refrigerant in a high pressure accumulator after it has cooled and transferred further heat to the vaporized refrigerant.
  • the refrigerant may already be present during cooling during the compression and / or subsequent transfer of heat to the vaporized refrigerant and / or during the subsequent cooling partially - condense.
  • a further significant increase in efficiency can be achieved in the process in question by the fact that the refrigerant after cooling and the heat transfer to the reheated refrigerant under work in an engine, in particular an expansion pump or an expansion turbine, is relaxed before it evaporates again or is heated.
  • the previously unexploited expansion work can be used with the help of a relaxation machine.
  • the expansion work gained by the expansion machine can be advantageously used to pump the liquid used as working fluid into the liquid piston.
  • the pumping work to be applied during the refrigerant compression is hereby reduced and the power requirement of the hydraulic pump or the hydraulic work to be performed by it is reduced.
  • the heat should be removed from the refrigerant during the compression in the liquid piston compressor so that the compression takes place isothermally.
  • the heat dissipated from the compressor by means of a separate heat transfer medium from the heat of a heat sink, i. for example, to a consumer in the form of underfloor heating, or otherwise provided as process heat at a low temperature level, wherein the heat transfer medium is further heated after heating in the liquid piston compressor in the gas cooler for the refrigerant.
  • the object of the invention is achieved by a heat exchanger, by means of which heat from the transcritical, the cooler leaving the refrigerant to the heater leaving the refrigerant is transferable.
  • the pressure reducing means is an engine, in particular, an expansion pump or expansion turbine, which is arranged between the radiator and the heater.
  • the expenditure on equipment is particularly low when a free-piston pump with self-switching valves is used as the expansion pump.
  • FIG. 5 schematically illustrated heat pump / chiller 1 has in the cycle of the refrigerant (here: CO 2 ) a liquid piston compressor 2, a gas cooler 3 / condenser an internal heat exchanger 4, a high-pressure accumulator 5, an expansion pump 42, a Low-pressure accumulator 7, an evaporator 8 and check valves 9 to 12 on.
  • the refrigerant here: CO 2
  • a liquid piston compressor 2 a liquid piston compressor 2
  • gas cooler 3 / condenser an internal heat exchanger 4
  • a high-pressure accumulator 5 an expansion pump 42
  • a Low-pressure accumulator 7 an evaporator 8 and check valves 9 to 12
  • the following process takes place in the form of a cycle through the aforementioned components and the interconnecting lines:
  • the isothermally compressed CO 2 in the liquid piston compressor is fed via a line 13 to the gas cooler 3, in which condensation may occur depending on the compression end temperature of the refrigerant. Due to the comparatively low critical temperature of CO 2 (31 ° C.), however, condensation typically does not take place either during the compression or in the downstream gas cooler 3 / "condenser", that is to say the wet steam area is not reached in these process steps.
  • the refrigerant passes from the inner heat exchanger into a high-pressure accumulator 5, from which it passes through a line 16 to the expansion pump 42, in which an ideal isentropic expansion of the refrigerant takes place, which occurs during the expansion in the wet steam area.
  • the expanded refrigerant enters the low-pressure accumulator 7, from where it passes through a line 18 into the evaporator and evaporates there under heat absorption. Subsequently, the refrigerant is conducted via a line 18 to the already mentioned inner heat exchanger 4 and heated there before it flows back via the line 19 back to the liquid piston compressor 2.
  • the liquid piston compressor 2 has two cylinders 20, 21 each defining a working space, which are connected in parallel to each other. From the line 19 branches off the inflow line 22 of the cylinder 20, in which the check valve 10 is arranged, which allows only an influx into the cylinder 20. Via the line 23, in which there is only one outflow permitting check valve 9, the refrigerant passes from the cylinder 20 into the conduit 13 and thus back into the gas cooler 3 / condenser.
  • Cylinder 21 is connected via a conduit 24 serving for the inflow to the conduit 19 and via the conduit 25 serving for the outflow to the conduit 13
  • the check valves 11 and 12 allow only an inflow or outflow of the refrigerant.
  • hydraulic lines 24 and 25 are connected, which open into a respective working chamber 26, 27 formed by the interior of the cylinders 20, 21.
  • a respective working chamber 26, 27 formed by the interior of the cylinders 20, 21.
  • the hydraulic fluid is selected so that it is neither miscible nor dissolved in the refrigerant.
  • the hydraulic lines 24 and 25 lead to a four-way hydraulic valve 28, from which in turn depart two hydraulic lines 29, 30 which are connected to the suction or pressure side of a hydraulic pump 31.
  • a four-way hydraulic valve 28 From which in turn depart two hydraulic lines 29, 30 which are connected to the suction or pressure side of a hydraulic pump 31.
  • now hydraulic fluid pressure is removed from one of the two cylinders 20, 21 and pumped under pressure into the other of the two cylinders 20, 21, whereby in the latter cylinder a compression stroke is performed, whereas in the other cylinder, the vaporized and preheated refrigerant is sucked.
  • Both cylinders 20, 21 are surrounded on their outer side by a double jacket 32 to 33 and provided in their interior with a heat exchanger bundle 34, 35.
  • the double shells 32 to 33 or heat exchanger bundles 34, 35 are connected to discharge lines 36, 37 and supply lines 38, 39.
  • the heated during the compression process heat transfer medium is passed after passing a located in the respective switching position three-way valve 39 from a circulation pump 40 to a consumer 41, which may be, for example, a floor heating or a consumer of process heat at low temperature level. From the consumer, the cooled heat transfer medium reaches the gas cooler 3, from which it is already preheated, in order subsequently to be returned to the liquid piston compressor 2, where it is reheated in the course of the isothermal compression of the refrigerant and its circuit thus closes.
  • the heat transfer medium is depending on the switching position of the three-way valve 39 each only by those cylinders 20 and 21st in which the isothermal compression of the refrigerant is taking place. Alternatively, both cylinders are constantly flowed through.
  • the heat pump / chiller 1 has an expansion pump 42.
  • the refrigerant taken from the high-pressure accumulator 5 is expanded by means of the expansion pump 42 designed as a free-piston pump before the expanded refrigerant is returned to the low-pressure accumulator and the process via the evaporation, preheating to condensation temperature, isothermal compression and cooling runs identically as in FIG. 5 ,
  • FIG. 3 illustrates how the refrigerant from point A is isothermally compressed to point B.
  • the idealized, horizontally extending line AB intersects the wet-steam line 43, whose section on the right of the maximum 44 is referred to as a dew-line 45 and whose section 46 on the left of the maximum 44 is referred to as a boiling line. From the intersection point 47 between tau line 45 and line AB, the refrigerant is thus in the post-vaporized area.
  • the refrigerant in the internal heat exchanger 4 is isobarically cooled along boiling line 46 until point C is reached.
  • the expansion pump 42 the refrigerant is now polytropically expanded and thus reaches point D with a correspondingly reduced temperature.
  • throttling via an expansion valve FIG. 5
  • FIG. 5 Without expansion pump, that is, throttling via an expansion valve ( FIG. 5 ) is dashed along the the point D 'reached, which is characterized by a greater entropy - due to the isenthalic relaxation.
  • FIGS. 1 and 3 show the cycles with R 134 A as the refrigerant form the Figures 2 and 4 a comparison of the processes when using CO 2 as a refrigerant. It is clear that by the internal heat exchanger 4, the relaxation of a lower temperature level (point C ') starts, as is the case in b' without internal heat exchanger.
  • point C ' For CO 2 as a refrigerant, neither the in FIG. 2 illustrated process according to the prior art still in the in FIG. 4 process according to the invention during the isothermal compression reaches the wet steam area.
  • the line A'-B 'and the line a'-b' are located above the wet steam line of CO 2 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (10)

  1. Procédé d'exploitation d'une pompe à chaleur ou d'une machine frigorifique (1), lors duquel un agent réfrigérant est comprimé au moyen d'un compresseur de liquide à pistons (2) puis refroidi et éventuellement condensé et ensuite expansé et dans une étape suivante, il est évaporé et finalement reconduit dans le compresseur de liquide à pistons (2), caractérisé en ce que de la chaleur de l'agent réfrigérant pré-refroidi après la compression est transférée sur l'agent réfrigérant évaporé avant que ce dernier ne soit reconduit vers le compresseur de liquide à pistons (2), ce qui achève le circuit du processus et en ce que l'agent réfrigérant est détendu dans une machine motrice, qui est en liaison active avec une pompe hydraulique (31), au moyen de laquelle un fluide hydraulique du compresseur de liquide à pistons (2) peut être pompé.
  2. Procédé selon la revendication 1, caractérisé en ce que le compresseur de liquide à pistons (2) comporte deux espaces de travail séparés et en ce que l'agent réfrigérant est compressé alternativement dans l'un des deux espaces de travail, dont le fluide hydraulique commun est pompé en va-et-vient alternativement de l'un des espaces de travail (26, 27) dans l'autre espace de travail (26, 27).
  3. Procédé selon l'une quelconque des revendications précédemment citées, caractérisé en ce que l'agent réfrigérant est temporairement stocké dans un accumulateur haute pression (5) après avoir été refroidi et avoir transféré de la chaleur supplémentaire sur l'agent réfrigérant évaporé.
  4. Procédé selon l'une quelconque des revendications précédemment citées, caractérisé en ce qu'après l'expansion, l'agent réfrigérant est stocké temporairement dans un accumulateur basse pression (7) avant d'être évaporé consécutivement.
  5. Procédé selon l'une quelconque des revendications précédemment citées, caractérisé en ce que lors du refroidissement et/ou du transfert de chaleur sur l'agent réfrigérant évaporé et/ou pendant la compression, l'agent réfrigérant se condense.
  6. Procédé selon l'une quelconque des revendications précédemment citées, caractérisé en ce qu'après le refroidissement et le transfert de chaleur sur l'agent réfrigérant évaporé, l'agent réfrigérant est détendu sous rendement effectif dans une machine motrice, notamment une pompe d'expansion (42) ou une turbine d'expansion, avant d'être évaporé ou réchauffé.
  7. Procédé selon l'une quelconque des revendications précédemment citées, caractérisé en ce que pendant la compression dans le compresseur de liquide à pistons (2), de la chaleur est retirée de l'agent réfrigérant, de telle sorte que la compression s'effectue de manière isotherme et en ce que la chaleur évacuée de l'agent réfrigérant au moyen d'un milieu caloporteur séparé est conduite vers un dissipateur thermique, après l'échauffement dans le compresseur de liquide à pistons (2), le milieu caloporteur étant encore échauffé dans le radiateur (3) pour l'agent réfrigérant.
  8. Pompe à chaleur ou machine frigorifique (1) avec un compresseur de liquide à pistons (2) pour la compression d'un agent réfrigérant sous restitution de chaleur à un milieu caloporteur matériellement séparé de l'agent réfrigérant, un radiateur (3) pour baisser la température de l'agent réfrigérant compressé, un évaporateur (8) pour l'évaporation de l'agent réfrigérant détendu, ainsi que des conduits reliant les composants précédemment cités, de telle sorte que l'agent réfrigérant puisse être conduit dans le circuit et transféré sur l'agent réfrigérant quittant l'évaporateur avec un agent caloporteur au moyen duquel de la chaleur de l'agent réfrigérant quittant le radiateur peut être transférée sur l'agent réfrigérant quittant l'évaporateur, caractérisée en ce que le dispositif d'abaissement de la pression est une machine motrice, notamment une pompe d'expansion (42) ou une turbine d'expansion qui est placée entre le radiateur (3) et l'évaporateur (8) et qui est en liaison active avec une pompe (31) au moyen de laquelle un fluide hydraulique peut être pompé dans compresseur de liquide à pistons (2).
  9. Pompe à chaleur ou machine frigorifique (1) selon la revendication précédemment citée, caractérisée en ce que la pompe d'expansion (4) est une pompe à pistons libres avec des soupapes à déclenchement automatique.
  10. Pompe à chaleur ou machine frigorifique (1) selon l'une quelconque des revendications 8 et 9, caractérisée par une liaison active, notamment un couplage mécanique entre la machine motrice active pendant la détention de l'agent réfrigérant et une pompe hydraulique (31), à l'aide de laquelle un fluide hydraulique peut être pompé dans un espace de travail du compresseur de liquide à pistons (2).
EP09782642A 2008-09-10 2009-09-04 Pompe à chaleur ou machine frigorifique et procédé permettant de faire fonctionner une pompe à chaleur ou une machine frigorifique Active EP2321592B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008041939A DE102008041939A1 (de) 2008-09-10 2008-09-10 Verfahren zum Betreiben einer Wärmepumpe oder Kältemaschine bzw. einer Kraftmaschine sowie Wärmepumpe oder Kältemaschine und Kraftmaschine
PCT/EP2009/061496 WO2010029027A1 (fr) 2008-09-10 2009-09-04 Pompe à chaleur ou machine frigorifique et procédé permettant de faire fonctionner une pompe à chaleur ou une machine frigorifique

Publications (2)

Publication Number Publication Date
EP2321592A1 EP2321592A1 (fr) 2011-05-18
EP2321592B1 true EP2321592B1 (fr) 2011-12-28

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Country Status (4)

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EP (1) EP2321592B1 (fr)
AT (1) ATE539304T1 (fr)
DE (1) DE102008041939A1 (fr)
WO (2) WO2010029027A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104005801A (zh) * 2013-02-25 2014-08-27 宝山钢铁股份有限公司 一种低压蒸汽差压发电系统及其回用蒸汽背压控制方法
CN104005801B (zh) * 2013-02-25 2015-12-09 宝山钢铁股份有限公司 一种低压蒸汽差压发电系统及其回用蒸汽背压控制方法

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ATE539304T1 (de) 2012-01-15
WO2010029020A1 (fr) 2010-03-18

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