EP4198418A1 - Procédé de pompe à chaleur et agencement de pompe à chaleur - Google Patents

Procédé de pompe à chaleur et agencement de pompe à chaleur Download PDF

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Publication number
EP4198418A1
EP4198418A1 EP21020642.1A EP21020642A EP4198418A1 EP 4198418 A1 EP4198418 A1 EP 4198418A1 EP 21020642 A EP21020642 A EP 21020642A EP 4198418 A1 EP4198418 A1 EP 4198418A1
Authority
EP
European Patent Office
Prior art keywords
compression
temperature level
heat pump
heat
working medium
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.)
Withdrawn
Application number
EP21020642.1A
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German (de)
English (en)
Inventor
Heinz Bauer
Martin Kamann
Thomas Widl
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.)
Linde GmbH
Original Assignee
Linde GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Linde GmbH filed Critical Linde GmbH
Priority to EP21020642.1A priority Critical patent/EP4198418A1/fr
Priority to PCT/EP2022/025514 priority patent/WO2023110141A1/fr
Publication of EP4198418A1 publication Critical patent/EP4198418A1/fr
Withdrawn legal-status Critical Current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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • 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
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine 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
    • 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
    • F25B2400/12—Inflammable refrigerants
    • 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
    • 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
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
    • 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
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel

Definitions

  • the present invention relates to a heat pump method and a heat pump arrangement.
  • Closed circuit compression heat pumps are used to raise heat Qu from a lower temperature level Tu (heat source) to an upper temperature level To (heat sink). This requires work.
  • the ratio Qo/W of the heat Qo that can be used at To to the work W is also known as the coefficient of performance (COP).
  • COP coefficient of performance
  • the temperature difference To-Tu is also referred to as ⁇ TLift.
  • the present invention sets itself the task of improving known heat pump methods and heat pump arrangements.
  • pressure level and "temperature level” to characterize pressures and temperatures, which is intended to express that pressures and temperatures in the respective Explained method or a corresponding arrangement does not have to be used in the form of exact pressure or temperature values.
  • pressures and temperatures typically vary within certain ranges, which are, for example, ⁇ 10% around an average value.
  • Pressure and temperature levels can be in disjunctive ranges or in ranges that overlap. In particular, pressure levels include unavoidable or expected pressure losses. The same applies to temperature levels.
  • saturated is intended below to denote the increase in the degree of saturation of a working medium in a heat pump circuit that is not yet in a saturated state, that is to say it is overheated. In embodiments of the invention, this is achieved in particular by withdrawing a vapor phase from a container, cooling it and at least partially or completely liquefying it, and then at least partially feeding it back into the same container.
  • an “injection” is intended to refer to the introduction of a liquid medium into one or between a plurality of compressor stages of a multi-stage centrifugal compressor.
  • One or more nozzles are used here, which finely atomize (nebulize) the liquid medium in order to ensure that it is converted into the gaseous state as quickly as possible.
  • the overheating caused by the compression can in particular be reduced by a corresponding saturation of the compressed working medium. This can prevent the heat sink from being at least partially subjected to an undesirably high temperature. This is particularly advantageous, for example, when boiling loaded amine in the regeneration column of an amine scrubber.
  • Amine scrubbing is a commonly used chemical process to separate carbon dioxide, hydrogen sulfide and other acidic gases from gas mixtures.
  • the amine scrubbing is based on the principle of chemisorption. With amine scrubbing, comparatively high purities can be achieved even at relatively low pressures. The selectivity is also typically higher than with physisorption.
  • An amine wash typically becomes light alkaline aqueous solutions of amines (mostly ethanolamine derivatives) are used as detergents, which chemically absorb acid gases reversibly, releasing heat of reaction. To regenerate the loaded detergent, the chemical equilibrium is reversed at high temperature (use of thermal energy) and low pressure, and the bound acid gases are thus removed from the detergent.
  • Embodiments of the present invention can use, in particular, the loaded detergent as a heat sink, which can be heated in this way, but which is already at a comparatively high temperature before it is heated.
  • the temperature at the bottom of the regeneration column is determined by the fact that essentially water mixed with amines is evaporated. At least atmospheric pressure results in a bottom temperature of more than 120 °C. A high-temperature heat pump is therefore advantageously used for heating.
  • Embodiments of the present invention thus relate to a method which includes a corresponding amine wash.
  • the present invention creates a (high-temperature) heat pump method with an upper temperature level To of typically more than 120° C. and a COP value of typically more than 2.5.
  • the heat is largely released isothermally at the upper temperature level To, so that excessive heating of the heat sink can be avoided. Excessive heating must be avoided, since the amines used degrade at higher temperatures, i.e. change their chemical properties by changing the molecular structure. It can lead to local damage to the amines, even if the bottom temperature remains at the boiling point.
  • the present invention proposes a heat pump method in which a working medium is subjected to evaporation using a heat source at a lower temperature level Tu and then to compression and condensing using a heat sink at an upper temperature level To, the working medium after evaporation and is subjected to overheating before compression, with a temperature increase caused by compression being limited by injection into the compression, and with the working medium being subjected to saturation after compression and before liquefaction at the upper temperature level To becomes.
  • the superheating of the vaporized working medium takes place in particular in a counterflow heat exchanger against working medium liquefied at high pressure, the suction temperature of a compressor used for compression being in particular at most 10 K, preferably at most 5 K, below the upper temperature level To.
  • the lower temperature level is in particular 10 to 60.degree.
  • the upper temperature level To is in particular at least 115°C, in particular at least 120°C.
  • the method proposed in a corresponding embodiment of the present invention is a high-temperature heat pump method mentioned at the outset, which is particularly advantageous for certain purposes, such as the amine scrubbing mentioned.
  • the upper temperature level To can be up to 140° C., in particular up to 130° C., for example.
  • An inlet temperature level in the compression, i.e. a compressor used here, is in particular at most 10 K, further in particular at most 5 K below the upper temperature level To.
  • an inlet pressure level of the compressor used can be in particular 1.5 to 5 bar, an outlet pressure level in particular 20 to 50 bar.
  • the temperature increase brought about by the compression can be limited by the injection, in particular to a temperature level of at most 180° C. Such a limitation makes it possible to avoid excessive heating, for example if a loaded detergent in an amine wash is used as a temperature sink.
  • the injection can be performed using a part of the working fluid that is before the vaporization and before the superheating of one of the superheating and after the Compression fed remainder diverted, expanded, and fed to one or more intermediate stages of compression in the compression.
  • the corresponding working medium used for the injection can be fed back into the circuit and is used further in this way.
  • the injection can take place in particular in a multi-stage manner.
  • an arrangement can be used, as in the EP 3 505 767 B1 is described.
  • a particularly advantageous embodiment is in the European Patent Application No. 20176585.6 described by the applicant in connection with a surge limit control (engl. Surge Control).
  • the injection provided in one embodiment of the present invention can also take place using one or more nozzles.
  • the nozzle or at least one of the plurality of nozzles can have an outlet which is arranged in a return bend between different compressor stages of a multi-stage centrifugal or turbo compressor.
  • the nozzle or at least one of the plurality of nozzles or at least one line connected thereto can have thermal insulation.
  • the nozzle or at least one of the plurality of nozzles or at least one line connected thereto can have a degassing device.
  • the nozzle or at least one of the several nozzles can be operated with a pressure difference of 2 to 10 bar, in particular 7 bar.
  • a vapor blockage can result from the working fluid to be injected escaping in the supply line to the injection nozzle.
  • the liquid working medium passes through areas with higher temperatures. Since this is not necessarily supercooled, corresponding outgassing can occur. Only a small part of the vapor formed can pass through the injection nozzle. If the evaporation rate is higher than the maximum possible vapor flow in the nozzle, no more liquid can pass through the nozzle. This can lead to insufficient atomization and evaporation.
  • a thermal insulation can be designed in particular in the form of a double-walled construction of a line section with an intermediate space which can in particular be evacuated.
  • the thermal insulation can be Configurations extend as far as technically possible in the direction of the injection point to reduce the heat flow and thus the risk of vapor locks.
  • Degassing can be carried out in particular using a line which is arranged, for example, coaxially inside or outside the line through which the working medium to be injected is conducted. In this way, the cold gas formed by evaporation can preferably be fed to the compressor.
  • Another fundamentally possible alternative is supercooling of the liquid to be injected, so that evaporation and thus the formation of vapor bubbles can be avoided.
  • a compressor can be used for the compression, which is designed as a single-shaft turbo compressor or screw compressor. Screw compressors are particularly suitable for smaller arrangements, whereas (multi-stage) single-shaft turbo compressors, in particular of the type just explained, are used in particular for larger arrangements.
  • a heat pump method includes, in particular, that the saturation is carried out using a container from which a vapor phase is removed at the top, at least partially liquefied in a heat exchanger thermally coupled to the heat sink, and fed back into the container.
  • a heat pump method is proposed in which the container is designed to be empty or equipped with bases and/or packing.
  • empty containers have advantages in terms of weight and cost, while internals promote the establishment of equilibrium.
  • the heat pump method comprises a start-up operating mode and a follow-up operating mode carried out after the start-up operating mode, the working medium in the follow-up operating mode being subjected to saturation at the upper temperature level To and the working medium in the start-up operating mode being at least partially used after compression a further heat sink at an intermediate temperature level Tm between the lower temperature level Tu and the upper temperature level To is cooled.
  • a cooler can be provided which can dissipate the heat generated during compression at a mean temperature level Tm below the upper temperature level To.
  • an associated container can be combined with the container explained above in connection with the saturation.
  • the additional heat sink can be thermally coupled to a start-up cooler.
  • the lower temperature level Tu is at least partially lowered in the start-up operating mode, in that a heating medium at the lower temperature level Tu is first passed through the start-up cooler and then through a heat exchanger used for evaporating the working medium.
  • the start-up cooler is also used to lower the lower temperature level Tu at least temporarily.
  • the heat source can be a condensing refrigerant of a refrigeration circuit or can include such a refrigerant whose heat of condensation at the lower temperature level Tu is at least partially used for evaporating the working medium.
  • the embodiment explained above with a temporary lowering of the lower temperature level Tu can be advantageous, since the condensation conditions of the cooling medium can be improved in this way.
  • a working medium that has a critical temperature that is at least 20° C. or 30° C. above the upper temperature level To.
  • the working medium can in particular have one or more components which is or are selected from n-butane, i-pentane, n-pentane, cyclobutane and cyclopentane.
  • the heat source can be a condensing refrigerant and/or a regenerated amine from an acid gas scrubber or can comprise a corresponding medium.
  • a suitable heat source in the form of the regenerated detergent
  • a suitable heat sink in the form of the loaded detergent
  • a heat pump arrangement which is set up to subject a working medium to evaporation using a heat source at a lower temperature level Tu and then to compression and condensation using a heat sink at an upper temperature level To is also the subject of the present invention.
  • a corresponding heat pump arrangement comprises means which are set up to subject the working medium to overheating after evaporation and before compression, to limit a temperature increase caused by compression by injection into the compression, and the working medium after compression and before condensation to be subjected to saturation at the upper temperature level To.
  • such a heat pump arrangement has a control device which is designed to switch between the start-up and the subsequent operating mode as required, for example according to a fixed switching pattern, on the basis of a sensor signal or on request.
  • a heat pump method is illustrated in the form of a greatly simplified process flow diagram and is denoted overall by 100 .
  • the figure also serves to explain a corresponding heat pump arrangement. If method steps are explained below, the corresponding explanations for components of the arrangement apply in the same way and vice versa. With regard to the abbreviations and variables used below, reference is also made to the explanations given at the beginning.
  • a liquid working medium supplied to it via a line L1 with a valve V1 is available at a first (lower) pressure level against a heat source or a heating medium which is available at a lower temperature level Tu is, evaporated.
  • the vaporized working medium is fed via a line L2 to a countercurrent heat exchanger E3 and is subjected there to superheating against liquefied working medium present at a second (higher) pressure level in a line L3.
  • the superheated working medium is fed to a compressor C1 via a line L4 and removed from it via a line L5.
  • the compressed working medium is liquefied, with a vapor phase being withdrawn from the container D1 via a line L6 and in the heat exchanger E2 against a heat sink or a cooling medium which is available at an upper temperature level To, at least partially liquefied and returned to container D1 via line L7.
  • the container D1 serves to saturate the compressed working medium from the line L5 with the liquid from the condenser E2, which gives off heat Qo at To to the heat sink.
  • a liquid phase is removed from the container D1 via the already mentioned line L3 and further cooled in the countercurrent heat exchanger E3 while the vaporized working medium is overheated in line L2.
  • an inlet temperature level of compressor C1 is at most 10 K, preferably at most 5 K, below upper temperature level To.
  • the superheated working medium is compressed in the compressor C1 to an outlet pressure level which corresponds at least to the boiling pressure of the working medium at the temperature To of the heat sink.
  • the overheating caused by the compression is reduced by the saturation of the compressed working medium in the container D1. This can prevent the heat sink from being at least partially subjected to an undesirably high temperature. This is, for example, when boiling loaded amine in the regeneration column of a carbon dioxide scrubber is an important criterion for the selection of the process.
  • the overheating of the working medium before compression enables an efficient process with a COP value > 2.5.
  • the temperature increase in the compressor C1 can be limited to ⁇ 180 °C by injecting supercooled working medium via a line L8 with a valve V2.
  • a cooler E4 can be provided, which can dissipate the heat generated during the compression at an average temperature level Tm below the upper temperature level To.
  • An associated container D2 can optionally be combined with the container D1 or connected to the cooler E4 in the manner explained, the working medium being fed to the container D2 via a line L9 with a valve V3 and being removed from this via a line L10.
  • the start-up cooler E4 can also be used to lower the upper temperature level (To) at least temporarily.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
EP21020642.1A 2021-12-16 2021-12-16 Procédé de pompe à chaleur et agencement de pompe à chaleur Withdrawn EP4198418A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP21020642.1A EP4198418A1 (fr) 2021-12-16 2021-12-16 Procédé de pompe à chaleur et agencement de pompe à chaleur
PCT/EP2022/025514 WO2023110141A1 (fr) 2021-12-16 2022-11-16 Procédé de pompe à chaleur et agencement de pompe à chaleur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21020642.1A EP4198418A1 (fr) 2021-12-16 2021-12-16 Procédé de pompe à chaleur et agencement de pompe à chaleur

Publications (1)

Publication Number Publication Date
EP4198418A1 true EP4198418A1 (fr) 2023-06-21

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EP21020642.1A Withdrawn EP4198418A1 (fr) 2021-12-16 2021-12-16 Procédé de pompe à chaleur et agencement de pompe à chaleur

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EP (1) EP4198418A1 (fr)
WO (1) WO2023110141A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008130357A1 (fr) * 2007-04-24 2008-10-30 Carrier Corporation Système de compression de vapeur de réfrigérant et procédé d'opération transcritique
US20140053597A1 (en) * 2012-01-18 2014-02-27 Panasonic Corporation Refrigeration cycle apparatus
EP3502587A1 (fr) * 2017-02-21 2019-06-26 Mitsubishi Heavy Industries Thermal Systems, Ltd. Système de fluide frigorigène pourvu d'un échangeur de chaleur à contact direct, et procédé de commande de système de fluide frigorigène
EP3505767B1 (fr) 2017-12-27 2021-06-23 Mitsubishi Heavy Industries Compressor Corporation Compresseur centrifuge et procédé de modification d'un compresseur centrifuge

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008130357A1 (fr) * 2007-04-24 2008-10-30 Carrier Corporation Système de compression de vapeur de réfrigérant et procédé d'opération transcritique
US20140053597A1 (en) * 2012-01-18 2014-02-27 Panasonic Corporation Refrigeration cycle apparatus
EP3502587A1 (fr) * 2017-02-21 2019-06-26 Mitsubishi Heavy Industries Thermal Systems, Ltd. Système de fluide frigorigène pourvu d'un échangeur de chaleur à contact direct, et procédé de commande de système de fluide frigorigène
EP3505767B1 (fr) 2017-12-27 2021-06-23 Mitsubishi Heavy Industries Compressor Corporation Compresseur centrifuge et procédé de modification d'un compresseur centrifuge

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
ARPAGAUS CORDIN ET AL.: "High temperature heat pumps: Market overview, state of the art, research status, refrigerants, and application potentials", ENERGY, vol. 152, 2018, pages 985 - 1010, XP085393430, DOI: 10.1016/j.energy.2018.03.166

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