WO2018178169A1 - Pompe à chaleur et procédé permettant de faire fonctionner une pompe à chaleur - Google Patents

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

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Publication number
WO2018178169A1
WO2018178169A1 PCT/EP2018/057956 EP2018057956W WO2018178169A1 WO 2018178169 A1 WO2018178169 A1 WO 2018178169A1 EP 2018057956 W EP2018057956 W EP 2018057956W WO 2018178169 A1 WO2018178169 A1 WO 2018178169A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
bypass line
heat pump
evaporator
heat
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.)
Ceased
Application number
PCT/EP2018/057956
Other languages
German (de)
English (en)
Inventor
Mark Reissig
Florian REISSNER
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.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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 Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to CN201880022852.7A priority Critical patent/CN110520683B/zh
Priority to KR1020197031796A priority patent/KR102344187B1/ko
Priority to DK18716943.8T priority patent/DK3583365T3/da
Priority to EP18716943.8A priority patent/EP3583365B1/fr
Priority to JP2019551521A priority patent/JP7074969B2/ja
Publication of WO2018178169A1 publication Critical patent/WO2018178169A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F25B30/00—Heat pumps
    • 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
    • F25B40/02—Subcoolers
    • 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
    • F25B40/06—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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for condensers
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for expansion valves or capillary tubes
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/13—Economisers
    • 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
    • F25B2600/00—Control issues
    • F25B2600/23—Time delays
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves

Definitions

  • the invention relates to a heat pump with a Flu ⁇ id Vietnameselauf in which circulates a working fluid.
  • the fluid ⁇ circuit comprises at least one evaporator for transferring heat energy from a heat source to the fluid, a current ⁇ from subsequent compression unit for compressing the Flu ⁇ ids, at least one downstream subsequent condenser for releasing heat energy of the fluid to a heat sink on hö ⁇ Herem temperature level as the heat source, and a downstream expansion unit for expansion of the fluid.
  • the heat pump also comprises a first bypass line with at least ⁇ least a bypass valve so that the fluid circuit downstream of the compressor unit and upstream of the condenser, the compressor unit can be fluidically connected to the fluid circuit downstream of the evaporator and upstream.
  • the invention also relates to a method for operating a heat pump, wherein a fluid is continuously conducted in a fluid circuit and in this case thermal energy is transferred from ei ⁇ ner heat source to the fluid in an evaporator, wherein the fluid at least partially evaporated and the fluid subsequently compacted becomes.
  • the Flu ⁇ id is for the delivery of thermal energy to a heat sink at a higher temperature level than the heat source at least in part ⁇ as liquefied and subsequently expanded to cool, whereby a first partial stream of fluid in a partial load operation of the fluid circuit after compression and prior to liquefaction, a first bypass line is branched off and the fluid circuit downstream of the evaporator and before Ver ⁇ seal is supplied again.
  • thermal energy that is, heat
  • the fluid with the absorbed thermal energy is adjusted by a compressor to an elevated Druckni ⁇ veau and then liquefied at an elevated compared to egg ⁇ ner evaporation temperature liquefaction temperature.
  • it is expanded, causing it to lower its temperature again.
  • the efficiency of a heat pump (narrow coefficient of performance. COP) by means of a power ⁇ number measured, whereby the coefficient of performance is given by the reciprocal best efficiency of a Carnot process.
  • the figure of merit corresponds to the quotient from benefit to expense. If the heat pump used for heating the heat sink, this corresponds to the output transmitted to the heat sink quantity of heat Q W arm ge ⁇ divided by the amount of work W MECH of the compressor. The larger the difference in magnitude (temperature lift) between the evaporating and condensing temperature of the fluid, the lower the efficiency of the heat pump.
  • the mass flow, the temperature level and the temporal availability of the heat source is almost constant in order to be able to resort to a constant efficiency and performance of the heat pump.
  • the heat pump is operated with waste heat from industrial processes, fluctuations in the three parameters can occur.
  • the heat pump must travel at partial load in order to be able to use as much heat as possible from the heat source.
  • a reduced volume flow of vaporized fluid flows out of the evaporator.
  • Includes the compressor unit of the heat pump piston or screw compressor according to the displacement principle, such heat pumps of the prior art are adapted in part-load operation, for example by adjusting the rotational ⁇ number of compressors to the reduced volume flow of the evaporated fluid.
  • a bypass line with at least one bypass valve for adapting the operation of heat pumps to a reduced volume flow of the fluid flowing from the evaporator, so that the fluid circuit downstream of the Verdich ⁇ ter unit and upstream of the condenser fluidly with the Fluid circuit downstream of the evaporator and upstream of the Ver ⁇ denser unit is connectable.
  • the bypass valve can be adjusted of the air passing through the compressor unit Volu ⁇ volume flow.
  • the temperature of the suction gas (fluid in the inlet region of the compressor unit) is also increased by the partial flow flowing through the bypass line and thus also the temperature of the compressed gas (fluid at the outlet of the compressor unit).
  • the invention has for its object to provide a heat pump of the type mentioned above and a method for operating such a heat pump, in which / the heat pump has an extended in the direction of low heat source power area of the partial load operation.
  • a heat pump of the aforementioned type characterized in that a second bypass line is included with with ⁇ stuffs for metering the flow rate, wherein by means of the second bypass line, a liquid phase of the Flu ⁇ ids in the first bypass line and / or downstream of the evaporator and upstream of the compressor unit in the fluid circuit can be introduced.
  • the heat pump according to the invention is adapted for use in the inventive method it ⁇ .
  • the fluid flowing via the second bypass line is mixed with the fluid flowing through the first bypass line and evaporates in this case.
  • the temperature of the first partial flow is lowered from the compressed gas temperature to a lower mixing temperature.
  • the second partial flow branched off via the second bypass line which would actually be conducted into the evaporator without being interrupted, is evaporated according to the invention by means of the first partial flow without the heat source having to be used for this purpose.
  • the mixing takes place be ⁇ preferably within the first bypass line by the second bypass line opens into the first bypass line.
  • the mixing can also take place within the fluid circuit downstream of the evaporator and upstream of the compressor unit by opening both bypass lines in this area in the fluid circuit and the partial flows there vermis ⁇ rule before entering the compressor unit.
  • This alternative variant is particularly suitable if the fluid circuit downstream of the evaporator via ei ⁇ nen detour to the compressor and a correspondingly long Distance in this area of the fluid circuit for Vermi ⁇ tion of the two partial flows is available.
  • the two bypass lines comprise at least one valve for the partial load operation in the case of the first bypass line and means for metering the flow rate in the case of the second bypass line.
  • the means for metering the flow rate of the second bypass line may be, for example, a pump and / or a valve.
  • the valves or the pump can be adjustable and / or controllable and / or regulated and, for example, controlled and / or controlled by a control ⁇ er / control device of a heat pump comprising the heat pump system.
  • the volume flows and their relationship to each other can be selected in partial load operation of the heat pump to each other so that the fluid at the beginning, during and at the end of the compression is at least saturated vapor to superheated.
  • This ver ⁇ avoid when using turbo compressors slugging at the compressor.
  • the volume flows and their relationship to each other can be chosen so zuei ⁇ in the partial load operation of the heat pump that a material or gas-dependent maximum temperature at the end of the compression is not exceeded. This avoids decomposition of the fluid and verhin ⁇ changed material damage in the compressor unit, due to high temperatures.
  • the heat pump Due to the inventive design of the heat pump, the heat pump can be operated in part-load operation with higher volume flow and is thus particularly suitable for expanding the partial load range in heat pumps with at least one turbo compressor.
  • a turbo compressor In a turbo compressor is to pay attention to a sufficiently high volume flow at the respective operating point of the turbo compressor, which should not be below a ⁇ operating point-dependent minimum flow rate so that the flow to the pressure side of the compressor back does not collapse.
  • a control / regulating unit be provided which adjusts the volume flow through the bypass lines and the ratio of the two partial flows to each other in part-load operation that a material- or gas-dependent maximum temperature is not exceeded at the end of the compression and the heat pump at too low heat source performance is switched off.
  • in partial load of the heat pump can this be made in combination with a rotation speed adjustment and / or control and / or regulation of the compressor ⁇ operation.
  • turbocompressors alternatively or additionally, a combination with a setting and / or control and / or regulation of the angle of attack of guide vanes can be made.
  • the compressor unit comprises at least one compressor, wherein the compressor is a turbo compressor.
  • This embodiment of the invention is particularly suitable for heat pumps in industrial applications in the power range of more than 500 kW.
  • a greater volume flow through the bypass lines is in the partial load ⁇ operation of the heat pump in relation to the state of the art allows, so that an operating point-dependent minimum volumetric flow can be maintained in an inventive heat pump with at least one turbo-compressor only at lower heat source services anymore.
  • the expansion unit comprises at least two expansion devices connected in series, wherein a separator for separating a gas and liquid phase is interposed between the two expansion devices, wherein the second bypass line is fluidly connected to a trained for the accumulation of the liquid phase portion of the separator.
  • the expansion device may be a throttle.
  • a throttle has a constriction of the flow path, so that the fluid expands due to the reduced pressure during fürströ ⁇ mens of the constricted portion.
  • the cross section of the throttle can be adjustable.
  • the arranged between the two expansion devices separator is used to improve the efficiency of the heat pump by the istadose ⁇ ne gaseous phase is at least partially supplied to the fluid circuit between two compression steps.
  • the second bypass line is fluidly connected to a trained for the accumulation of the liquid phase region of the separator.
  • the separator may comprise a pressure vessel for separating the gas and liquid phases.
  • the gaseous phase of the fluid accumulates in an upper region, wherein in this region the gaseous fluid can be sucked in via a feed line from the at least one compressor.
  • the second bypass line may, for example, branch off from the lower region of the pressure vessel.
  • a further advantageous embodiment of the invention can provide that the second bypass line is fluidly connected to a flooded area of the evaporator during operation.
  • This embodiment of the invention is also suitable for heat pumps without separator.
  • the heat mepumpe comprises means for overheating the fluid flowing from the evaporator to a heat exchanger, which is formed such that it thermally from the condenser strö ⁇ Mendes fluid before entry into the expansion unit from connecting the evaporator fluid before entering the compressor unit, the first bypass line downstream of the heat exchanger into the fluid circuit and the second By ⁇ pass line into the first bypass line or also downstream of the heat exchanger opens into the fluid circuit.
  • This embodiment of the invention enables the use of high temperature fluids with a positive slope of the tau line in a temperature versus entropy diagram.
  • the fluid both in full and part-load currency rend not in a state portion of the fluid to ge ⁇ long, in which there is drop formation and thus to damage from drop impact in the compressor unit, the fluid must be overheated before entering the compressor unit.
  • the degree of overheating can be designed by means of the surface of the heat exchanger for full load operation.
  • the two bypass lines can einmün ⁇ example in the output range of the heat exchanger in the fluid circuit.
  • a heat source with an external power supply can be switched, which is arranged and designed to transfer heat to the fluid in Fluid Vietnamese ⁇ run downstream of the heat exchanger and upstream of the compressor unit.
  • Another object of the invention is to provide a method of the type mentioned at the beginning of operating a heat pump suits ⁇ ben with which a lower heat source in the direction of power extended the range of the partial load operation is enabled.
  • ge ⁇ dissolves in a method of the type a ⁇ initially mentioned for operating a heat pump that branched off from the fluid circuit after the partial Verflüssi ⁇ supply and upstream of the evaporator via a second bypass line, a liquid part-stream with the first partial flow is mixed before compaction.
  • the fluid flowing via the second bypass line is mixed with the fluid flowing via the first bypass line.
  • Line flowing fluid mixed and evaporated here.
  • the temperature of the first partial flow is lowered from the compressed gas temperature to a lower mixing temperature.
  • the branched off via the second bypass line second partial flow which would be unabgabzweigt actually conducted into the evaporator is evaporated according to the invention by means of the first partial flow without the heat source would have to be used for this purpose.
  • the mixing preferably takes place within the first by-pass line.
  • the liquid partial flow can be conducted into the first bypass line, for example, by opening the second bypass line in the first bypass line.
  • the mixing can also be done additionally or alternatively within the fluid circuit downstream of the evaporator and before the compression of the fluid by the liquid substream additionally or alternatively in the fluid circuit downstream of the evaporator and before the compression is passed, for example by the second bypass line additionally Alternatively, it enters the fluid circuit in this area.
  • the heat pump can be and is therefore particularly suitable for extending the partial load range in heat pumps with at least ei ⁇ nem turbo compressor at partial load with a higher volume flow be ⁇ exaggerated.
  • a turbo compressor should be taken to a sufficiently high volume flow at the respective operating point of the turbo compressor, the Do not fall a ⁇ be operating point-dependent minimum flow rate should th so that the flow to the pressure side of the compressor back does not collapse.
  • the ratio of the first and second partial flow is adjusted and / or controlled and / or regulated, that the fluid at the beginning, during and at the end of the compression at least saturated vapor to superheated .
  • This embodiment of the invention prevents damage to liquid in the compressor, in particular in the case of a heat pump with at least one turbocompressor.
  • at least one valve may be provided in the case of the first bypass lines and, in the case of the second bypass line, means for metering the flow rate, for example a pump and / or a valve.
  • the valves or the pump can be adjustable and / or controllable and / or controllable and can be controlled and / or regulated, for example, by means of a control / regulating device.
  • the adjustment and / or control and / or regulation of the volume flow can be made according to an embodiment of the invention in combination with a speed setting and / or control and / or control of the compressor.
  • a combination with an adjustment and / or control and / or regulation of the angle of attack of guide vanes can additionally be carried out according to this exemplary embodiment.
  • the ratio of the first and second partial flow is adjusted and / or controlled and / or regulated that a material or gas-dependent maximum temperature is not exceeded at the end of the compression.
  • This embodiment of the invention is suitable for the operation of heat pumps with a heat source, the power varies widely and temporarily makes the operation of the heat pump in réellebe ⁇ rich the operating range of the heat pump required.
  • the design prevents decomposition of the fluid and material damage in the at least one compressor used for compression due to excessive temperatures.
  • the volume flow of the first and second partial Streams adjusted and / or controlled and / or gere ⁇ gel is that a dependent of the operating point of the compressor ⁇ giger minimum volume flow is not exceeded.
  • This embodiment of the invention is particularly suitable when using a heat pump with at least one turbocompressor for carrying out the method.
  • liquid partial flow is conducted into the first bypass line and / or into the fluid circuit downstream of the evaporator and before the compression.
  • This embodiment of the invention allows a mixing of the two partial flows in the first bypass line and / or within the fluid circuit downstream of the evaporation ⁇ fers and prior to compaction.
  • the mixing preferably takes place within the first by-pass line.
  • the liquid partial flow can be conducted into the first bypass line, for example, by opening the second bypass line in the first bypass line.
  • the mixing can also be done additionally or alternatively within the fluid circuit downstream of the evaporator and before the compression of the fluid by the liquid substream additionally or alternatively in the fluid circuit downstream of the evaporator and before the compression is passed, for example by the second bypass line additionally Alternatively, it enters the fluid circuit in this area.
  • a further advantageous embodiment of the invention can provide that the heat pump is operated with a high-temperature fluid whose tau line essentially has a positive slope in a temperature-over-entropy diagram and thermal energy of the fluid circuit after liquefaction and before expansion onto the fluid is transmitted downstream of the evaporator and before compression, so that the fluid is overheated at the beginning, during and after the compression, wherein the part-flow operation, the first partial flow or alternatively both partial flows are supplied to the transmission of the heat energy to the fluid circuit.
  • the advantageous embodiment of the invention enables operation of the heat pump with high-temperature fluids, which have such a pitch of the dew line and therefore must be overheated prior to compression to avoid damage to the compressor.
  • the transfer of heat energy can be done by means of a heat exchanger.
  • a degree of overheating can be set. For example, this can be chosen such that both at full load and at partial load, the fluid after compression is in a state that maintains a safe distance (temperature difference) to the dew line.
  • the expansion takes place in at least two expansion steps, wherein at least between two expansion steps a gas phase of the
  • Fluid is separated from a liquid phase of the fluid, and the liquid partial stream is diverted from the liquid phase.
  • the information to be between two expansion steps separating a gas phase from a liquid phase serves to IMPROVE ⁇ tion of the efficiency of the heat pump by the istadose ⁇ ne gaseous phase is at least partially fed into the fluid circuit between the two compression steps.
  • the separated liquid phase which would otherwise be completely supplied to the evaporator, is partially branched off via the second bypass line as a second partial flow.
  • liquid substream can also be considered advantageous for the liquid substream to be branched off from a flooded area of the evaporator.
  • This embodiment of the invention is also suitable for the operation of heat pumps without separator.
  • FIG. 2 schematically shows a temperature-over-entropy diagram of the fluid R134a with a state progression during the fluid circuit of a heat pump according to the prior art illustrated in FIG. 1, FIG.
  • FIG. 3 is a schematic diagram of a temperature-over-entropy diagram of a fluid having a tau line with a substantially positive gradient and a marked course of the fluid when passing through the fluid circuit of a heat pump according to the prior art shown in FIG.
  • FIG. 4 schematically shows a fluid circuit of a heat pump according to a first embodiment of the invention
  • Fig. 5 shows schematically a flow chart of a method according to a third embodiment of the OF INVENTION ⁇ dung.
  • Figure 1 shows schematically a fluid circuit 21 of a heat pump 12 according to the prior art.
  • the fluid 2 is conveyed in egg ⁇ ner flow direction 11 through the heat pump 12.
  • An evaporator 10 vaporizes the fluid while absorbing heat. meenergy the heat source 4, so that it assumes a vapor state 1.
  • the fluid 2 enters a compressor unit 7, which includes a compressor 7 a, and is compressed to a compression state 3.
  • the compression state 3 it flows into a condenser 8 with release of heat energy to the heat sink 20 and is converted into a condensed state ⁇ 5, and finally expanded in an expansion unit 9 with an expansion device 9a.
  • the fluid 2 assumes an expansion state 6, wherein it is in turn supplied to the evaporator 10 in this state.
  • the fluid is therefore continuously fed during the operation of the heat pump 12 according to the direction of flow 11 through the heat pump 12, and takes this in the evaporation in the evaporator 10, heat of the heat source 4 and outputs during liquefaction in the Ver ⁇ liquid 8 heat energy at a higher temperature level than that of the heat source 4 to the heat sink 20 from.
  • Figure 2 shows a temperature-over-entropy diagram 23, which according to the image plane to the right, ie on the abscissa axis entropy 14 and on the image plane up to, ie on the ordinate axis, a temperature 13 represents ⁇ represents.
  • the temperature versus entropy diagram 23 provides both a vapor line 18, a boiling point 19, as well as different ⁇ Liche aggregate states of a fluid.
  • the dew line 18 is adjacent a gas phase 15 of a 2-phase region 16 from where the 2-phase region 16, the Fluid is present in both liquid and gaseous state.
  • the boiling line 19 delimits the 2-phase region 16 from a liquid phase 17.
  • the ⁇ is asked temperature versus entropy diagram 23 shows a vapor line 18 a fluid with essentially negative sti ⁇ supply.
  • thermodynamic states of the fluid which the fluid assumes when passing through the fluid circuit of a heat pump according to the prior art shown in FIG. ⁇ out starting from the vapor state 1, according to the Strömungsrich- tion 11 achieved by compression of the compression state 3.
  • the compression state 3 is located within the Gaspha ⁇ se 15, which is why the compressor in an embodiment as a turbo compressor no damage from liquid slugging in a row of droplet formation in the fluid would take 7a.
  • the connecting line Darge ⁇ provided between the individual states are shown as straight connecting lines in Figure 2 and Figure 3, but may also deviate from this ideal path.
  • the condensed state 5 is set by the condenser 8, wel ⁇ cher is on the boiling line.
  • FIG. 3 shows, analogously to FIG. 2, a temperature-over-entropy diagram 24, but for a different fluid.
  • the course of the boiling line 19 and the tau line 18 of the fluid adjoin a strongly overhanging 2-phase region 16, so that the dew line 18 has a substantially positive slope. If such a fluid fen Vietnamese pipe, a pipe, a pipe, or a pipe, or a pipe, or a pipe, or a pipe, or a temperature-over-entropy diagram 24, but for a different fluid.
  • the course of the boiling line 19 and the tau line 18 of the fluid adjoin a strongly overhanging 2-phase region 16, so that the dew line 18 has a substantially positive slope. If such a fluid fen Vietnamese- the fluid circuit of the heat pump is provided in ⁇ figure 1 according to the prior art, the compression state is within the 3 2-
  • FIG. 4 schematically shows a fluid circuit 28 of a heat pump 26 according to a first embodiment of the OF INVENTION ⁇ dung.
  • a compressor unit 7 with two compressors 7a, 7b are arranged in the flow direction on egg ⁇ nen evaporator 10 following.
  • the compressors 7a and 7b are arranged in series and can be keptbil ⁇ det as a turbo compressor.
  • Downstream of the compressor unit 7 28 includes the fluid circulation ⁇ a condenser 8 and subsequently a Expan ⁇ sion unit 9 with two series-arranged Expansionsvor- directions 9a, 9b.
  • the expansion device 9a and / or 9b may be formed as a throttle or, for example, as an expansion valve.
  • the fluid circuit 28 of the heat pump 26 also summarizes at ⁇ overheating of the evaporator 10 flowing fluid Removing means 34 with a heat exchanger 32.
  • the heat exchanger 32 is formed such that it thermally flowing out of the condenser 8 fluid before entry into the expansion unit 9 with the out of the evaporator 10 strö ⁇ Menden fluid before entry into the compressor unit 7 nects.
  • the means 34 comprise an additional selectable heater 38 which is heated with an exter ⁇ NEN energy source 40th
  • the heat pump 26 includes a first bypass line 42 with a bypass valve 43, so that the fluid circuit 28 downstream of the compressor unit 7 and upstream of the Verflüssi ⁇ gers 8 fluidly with the fluid circuit 28 downstream of Ver ⁇ steamer 10 and upstream of the compressor unit 7 is connected and a second bypass line 45.
  • the second bypass line comprises means 46 for metering the flow rate, which are designed as a valve 47.
  • the second bypass line 45 branches off from the separator 30 and opens into the ers ⁇ th bypass line 42 so that a branched 45 from the separator 30 by means of the second bypass line copessigpha- se of the fluid in the first bypass line 42 can be introduced.
  • the second bypass line 45 could branch off from a flooded area 49 instead of the separator. This alternative course of the second bypass line is not shown in the figure.
  • the ratio of the partial flows flowing in the partial load operation via the bypass lines can be reduced by means of the valve.
  • the means for metering a flow rate in such a manner turned provides ⁇ and / or controlled and / or regulated in that the fluid at the beginning (the vapor state lb), during (Verdichtungszu ⁇ stand 3a and 3b) and at the end of the compaction (stand Verdichtungszu- 3c) at least saturated vapor is overheated and to a material or gas-dependent maximum temperature at the en ⁇ de densification (compaction state 3c) is not exceeded ⁇ th.
  • the heat pump 26 according to the invention makes it possible to operate the heat pump at lower heat source outputs.
  • the illustrated embodiment allows the use of a high temperature fluid with positive slope of the dew line in conjunction with a high coefficient of performance.
  • FIG. 5 shows schematically in a flow chart an exemplary embodiment of the inventive method, wherein in a preparatory process step VS1 for operation of the heat pump selected is a fluid having a dew line with positive in Wesentli ⁇ chen pitch in a print-on-enthalpy diagram and used.
  • a preparatory step VS2 the superheating of the fluid is selected in the fluid circuit in such a way - for example, medium-interpretation means of the heat exchange surface - that the distance to the vapor line at the compressor-end point of at least 10K, 10K insbeson ⁇ particular amounts to 20K.
  • a control / regulation unit is provided with data for a partial load operation, in particular, which maximum temperature of the compressed gas is to be maintained and which operating point-dependent minimum volume flows in the compressor unit are to be maintained.
  • a process step in a starting phase of the VS4 Be ⁇ drive the heat pump overheating of a heating fluid ⁇ device is switched on.
  • a step VS5 heat energy from a heat source to a fluid in one Is transferred evaporator, wherein the fluid at least partially vaporizes ⁇ .
  • the fluid is superheated after the transfer of the heat energy and before the compression, and heat energy of the fluid leaving the condenser is removed before expansion and the fluid leaving the evaporator is transferred before compression.
  • step VS7 the fluid is subsequently compressed in a first compression step.
  • a method step VS8 the compressed fluid is compressed in a second compression step.
  • the fluid for dispensing Wär ⁇ meenergy to a heat sink at a higher temperature level is liquefied in the heat source at least partially.
  • the fluid is expanded to cool in a first expansion step.
  • a gas phase of the fluid is separated from a liquid phase of the fluid and the gaseous fluid is at least partially supplied to the fluid between at least two compression steps.
  • the fluid is ex- pandiert in a second expansion step, and is again supplied to the vaporizer and circulating in the fluid circuit of the heat pump fluid continuously kon ⁇ the method steps VS5 passes to VS12.
  • step VS13 and VS14 is continuously repeated.
  • a first partial flow of the fluid may be diverted via a first bypass line and the fluid circuit fed back downstream of the evaporator and before the compression, and from the fluid circuit after the partial liquefaction and upstream of the evaporator from the fluid circuit ⁇ running after compaction and prior to liquefaction branched off via a second bypass line, a liquid second partial flow and mixed with the first partial flow.
  • step VS14 is checked whether all the conditions of process step VS13 can be met ak ⁇ tulle. If not, the heat pump is turned off in step VS15 due to low power of the heat source. If so, is repeated VS13 process ⁇ step.

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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)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

L'invention concerne une pompe à chaleur (12, 26) comprenant un circuit de fluide (21, 28) comportant au moins un évaporateur (10), une unité compresseur (7) située en aval, au moins un condenseur (8) situé en aval et une unité de détente (9) située en aval, et une première conduite de dérivation (42) comportant au moins une soupape de dérivation (43), de telle sorte que le circuit de fluide en aval de l'unité compresseur (7) et en amont du condenseur (8) puisse être relié fluidiquement au circuit de fluide en aval de l'évaporateur (10) et en amont de l'unité compresseur (7). La pompe à chaleur comprend une plage de fonctionnement à charge partielle élargie en direction d'une puissance de source de chaleur plus faible. À cet effet, la pompe à chaleur comprend une deuxième conduite de dérivation (45) dotée de moyens de dosage du débit (46), une phase liquide du fluide pouvant être introduite dans la première conduite de dérivation (42) au moyen de la deuxième conduite de dérivation.
PCT/EP2018/057956 2017-03-31 2018-03-28 Pompe à chaleur et procédé permettant de faire fonctionner une pompe à chaleur Ceased WO2018178169A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN201880022852.7A CN110520683B (zh) 2017-03-31 2018-03-28 热泵和用于运行热泵的方法
KR1020197031796A KR102344187B1 (ko) 2017-03-31 2018-03-28 열 펌프 및 열 펌프를 작동시키기 위한 방법
DK18716943.8T DK3583365T3 (da) 2017-03-31 2018-03-28 Fremgangsmåde til drift af en varmepumpe
EP18716943.8A EP3583365B1 (fr) 2017-03-31 2018-03-28 Procédé permettant de faire fonctionner une pompe à chaleur
JP2019551521A JP7074969B2 (ja) 2017-03-31 2018-03-28 ヒートポンプ及びヒートポンプの運転方法

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017205484.0A DE102017205484A1 (de) 2017-03-31 2017-03-31 Wärmepumpe und Verfahren zum Betreiben einer Wärmepumpe
DE102017205484.0 2017-03-31

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WO2018178169A1 true WO2018178169A1 (fr) 2018-10-04

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JP (1) JP7074969B2 (fr)
KR (1) KR102344187B1 (fr)
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DE (1) DE102017205484A1 (fr)
DK (1) DK3583365T3 (fr)
WO (1) WO2018178169A1 (fr)

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DE102020130063A1 (de) 2020-11-13 2022-05-19 CTS Clima Temperatur Systeme GmbH Temperieranlage und Verfahren zum Betreiben einer Temperieranlage
DE102024102689B3 (de) * 2024-01-31 2025-06-05 Man Energy Solutions Se Verfahren und Steuergerät zum Betreiben einer Wärmepumpe unter Stabilisierung einer Netzfrequenz eines elektrischen Stromnetzes

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EP2068096A1 (fr) * 2006-09-11 2009-06-10 Daikin Industries, Ltd. Dispositif de réfrigération
US20120011866A1 (en) * 2009-04-09 2012-01-19 Carrier Corporation Refrigerant vapor compression system with hot gas bypass
US20150285539A1 (en) * 2014-04-04 2015-10-08 Johnson Controls Technology Company Heat pump system with multiple operating modes
EP3144603A1 (fr) * 2015-09-16 2017-03-22 Heatcraft Refrigeration Products LLC Système de refroidissement à faible charge de température

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JPS5022364Y2 (fr) * 1971-06-15 1975-07-05
JP2684845B2 (ja) * 1990-11-30 1997-12-03 ダイキン工業株式会社 空気調和装置の運転制御装置
JPH0490857U (fr) * 1990-12-03 1992-08-07
JP2005257237A (ja) * 2004-03-15 2005-09-22 Sanyo Electric Co Ltd 冷凍装置
JP4859480B2 (ja) 2006-02-21 2012-01-25 三菱重工業株式会社 ターボ冷凍機およびその制御装置ならびにターボ冷凍機の制御方法
EP2147264B1 (fr) * 2007-04-24 2019-01-16 Carrier Corporation Système de compression de vapeur de réfrigérant
US9810464B2 (en) * 2012-04-27 2017-11-07 Mitsubishi Electric Corporation Air-conditioning apparatus with low outside air temperature mode
DE102013210175A1 (de) * 2013-05-31 2014-12-18 Siemens Aktiengesellschaft Wärmepumpe zur Verwendung von umweltverträglichen Kältemitteln

Patent Citations (4)

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Publication number Priority date Publication date Assignee Title
EP2068096A1 (fr) * 2006-09-11 2009-06-10 Daikin Industries, Ltd. Dispositif de réfrigération
US20120011866A1 (en) * 2009-04-09 2012-01-19 Carrier Corporation Refrigerant vapor compression system with hot gas bypass
US20150285539A1 (en) * 2014-04-04 2015-10-08 Johnson Controls Technology Company Heat pump system with multiple operating modes
EP3144603A1 (fr) * 2015-09-16 2017-03-22 Heatcraft Refrigeration Products LLC Système de refroidissement à faible charge de température

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Publication number Publication date
CN110520683A (zh) 2019-11-29
EP3583365B1 (fr) 2022-06-08
JP2020512519A (ja) 2020-04-23
DE102017205484A1 (de) 2018-10-04
EP3583365A1 (fr) 2019-12-25
CN110520683B (zh) 2021-12-21
KR20190130158A (ko) 2019-11-21
DK3583365T3 (da) 2022-08-29
KR102344187B1 (ko) 2021-12-30
JP7074969B2 (ja) 2022-05-25

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