EP3097370B1 - Wärmepumpe mit vorratsbehälter - Google Patents

Wärmepumpe mit vorratsbehälter Download PDF

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Publication number
EP3097370B1
EP3097370B1 EP15702673.3A EP15702673A EP3097370B1 EP 3097370 B1 EP3097370 B1 EP 3097370B1 EP 15702673 A EP15702673 A EP 15702673A EP 3097370 B1 EP3097370 B1 EP 3097370B1
Authority
EP
European Patent Office
Prior art keywords
working fluid
condenser
heat pump
working
fluid
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.)
Active
Application number
EP15702673.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3097370A1 (de
Inventor
Vladimir Danov
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 Energy Global GmbH and Co KG
Original Assignee
Siemens AG
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 filed Critical Siemens AG
Publication of EP3097370A1 publication Critical patent/EP3097370A1/de
Application granted granted Critical
Publication of EP3097370B1 publication Critical patent/EP3097370B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression 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
    • F25B45/00—Arrangements for charging or discharging 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
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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 device and a method for regulating a fluid level of a working fluid of a heat pump.
  • working fluids In refrigerating machines, in particular in heat pumps, fluids are typically used as working media (working fluids).
  • the working fluid circulates within a working circuit of the heat pump.
  • the working fluid is typically introduced into the working circuit of the heat pump when the heat pump is started up for the first time and the heat pump is thus filled.
  • the working cycle of the working fluid is closed during the operation of the heat pump.
  • the working fluid of the heat pump circulates within a closed working circuit.
  • no influence can be exerted on the working cycle of the working fluid, in particular on a temperature profile of the working fluid.
  • Any leaked working fluid is topped up solely during maintenance work on the heat pump, which is usually carried out once a year.
  • the heat pump is not in operation during maintenance work.
  • heat pumps transfer the heat absorbed by a heat source to a heat sink.
  • fluctuations in the temperature of the heat sink as well as the Temperature of the heat source.
  • Known heat pumps can only react inadequately to temperature fluctuations in the heat sink and / or the heat source.
  • the efficiency (coefficient of performance; COP) of the heat pump is reduced by such temperature fluctuations, depending on the application.
  • the present invention is therefore based on the object of enabling a heat pump to be adapted to temperature fluctuations in a heat sink.
  • the device comprises a storage tank and a heat pump, which heat pump has at least one condenser, an expansion valve, an evaporator and a compressor, the heat pump comprising a working circuit for a circulating working fluid, the storage tank being arranged with respect to the working circuit between the condenser and the evaporator and the reservoir for regulating a fluid level of the working fluid in the condenser comprises a piston.
  • the fluid level of the working fluid in the condenser of the heat pump can advantageously be regulated.
  • the fluid level of the working fluid in the condenser of the heat pump is regulated by the piston, for example by a translational movement of the piston in the storage container.
  • the device according to the invention enables the fluid level to be regulated during operation of the heat pump.
  • a height or a level of the fluid column (liquid column) of the working fluid in the condenser can be used as a measure of the fluid level.
  • condensed working fluid collects at the bottom of the condenser, the condensed working fluid being supercooled in the condenser by the thermal contact with a heat sink.
  • the fluid level is given by the height of the liquid column of the working fluid accumulated in the condenser.
  • the subcooling of the working fluid can thus be regulated by increasing or decreasing the fluid level. According to the invention, it is possible to react to temperature fluctuations in the heat sink by regulating the subcooling of the working fluid in the condenser. In other words, the subcooling of the working fluid in the condenser can be adapted to the temperature fluctuations of the heat sink, the adaptation being carried out in such a way that the heat pump always works as efficiently as possible.
  • heat pumps known from the prior art have non-controllable undercooling of the working fluid, since the fluid level in the condenser is approximately constant. An adaptation to the temperature fluctuations of the heat sink consequently does not take place according to the prior art.
  • the fluid level by regulating the fluid level, it is possible to react directly to fluctuations in the heat sink and / or a heat source by regulating the subcooling of the working fluid.
  • Increased subcooling of the working fluid can be advantageous here, since the enthalpy difference in the condenser is increased by the increased subcooling of the working fluid. This advantageously increases the coefficient of performance (COP) and consequently the efficiency of the heat pump.
  • COP coefficient of performance
  • Another advantage of the invention is that large temperature fluctuations of the heat source and / or the heat sink can be regulated by means of a small change in the amount of fluid in the working fluid. As a result, it is possible to dispense with an oversized filling quantity of the working fluid within the working circuit of the heat pump.
  • overheating of a suction gas can advantageously be regulated via the undercooling of the working fluid.
  • the fluid level of the working fluid in the condenser of the heat pump is regulated by means of a piston, whereby the subcooling of the working fluid is regulated and consequently the efficiency of the heat pump is improved in the event of temperature fluctuations in the heat sink.
  • a working fluid circulating within a working circuit of the heat pump is condensed by means of a condenser, expanded by means of an expansion valve, evaporated by means of an evaporator and compressed by means of a compressor, the working fluid increasing with respect to the working circuit between the condenser and the evaporator a storage container is passed, wherein a fluid level of the working fluid in the condenser is regulated by means of a piston of the storage container.
  • the fluid level of the working fluid in the heat pump can be regulated by means of a translational movement of the piston.
  • the storage container which comprises a piston, is fluidly coupled to the heat pump via an outlet and inlet valve, the outlet valve being arranged between the condenser and the expansion valve and the inlet valve between the expansion valve and the evaporator with respect to the working circuit.
  • Working fluid is thus advantageously conducted to the storage container after the condenser and before the expansion valve. This is advantageous because the working fluid has a high pressure after the condenser and before the expansion valve. It is consequently possible to remove large amounts of working fluid from the working circuit of the heat pump during a short period of time and to conduct it to the storage tank.
  • the working fluid of the heat pump is temporarily stored in the storage tank in its liquid state.
  • the working fluid is introduced into the storage container preferably with the outlet valve open and the inlet valve closed.
  • the fluid level is regulated by increasing and / or reducing the storage volume (volume that is available for the working fluid in the storage container) by means of a linear displacement of the piston. By increasing the storage volume, more working fluid can consequently be received in the storage container, so that the fluid level in the condenser is reduced and there is less undercooling of the working fluid.
  • a storage container which is designed as a hydraulic cylinder is particularly preferred here.
  • the storage container can advantageously be realized in a technically simple manner by a hydraulic cylinder, preferably by a double-acting hydraulic cylinder.
  • a pressure within the hydraulic cylinder of at most 20 MPa is preferred here.
  • the said valves each include a further expansion valve and a check valve.
  • the fluid level can be regulated by means of the piston of the working fluid if a fluid level threshold value of the working fluid in the condenser is exceeded or not reached. Since the fluid level of the working fluid in the condenser is positively correlated with the subcooling of the working fluid, the subcooling of the working fluid is advantageously controlled by regulating the fluid level. If a certain fluid level, which for example corresponds to the fluid level threshold value, is exceeded, the working fluid may be excessively undercooled. As a control, the fluid level of the working fluid must therefore be reduced. In the opposite case, if the fluid level falls below the threshold value, the fluid level of the working fluid in the condenser can be increased by regulating, so that the desired increased subcooling of the working fluid is established.
  • the fluid level of the working fluid is regulated if a temperature threshold value of the working fluid is exceeded or not reached.
  • the temperature of the working fluid in the condenser is typically indirectly proportional to the fluid level of the working fluid in the condenser. At a high fluid level, there is a high level of subcooling and thus a low temperature of the working fluid, while at a low fluid level there is a higher temperature and thus less subcooling of the working fluid.
  • the temperature of the working fluid is consequently advantageously measured within the condenser of the heat pump.
  • FIG. 1 shows a device 1 which comprises a heat pump 4 and a storage tank 2, the heat pump 4 having a condenser 6, an expansion valve 8, an evaporator 10 and a compressor 12.
  • the heat pump 4 is fluidly coupled to the storage container 2 via an outlet valve 18 and an inlet valve 20 via a working fluid 24 of the heat pump 4.
  • the working fluid 24 circulates in the heat pump 4 in a working circuit 42.
  • the reservoir 2 is designed as a hydraulic cylinder 2 and comprises a piston 14.
  • a control of a storage volume 30 of the hydraulic cylinder 2 takes place here via a straight movement of the piston 14, the straight movement in Figure 1 is illustrated by the directional arrows 32, 33.
  • a first partial volume 30, which is available to the working fluid 24 in the hydraulic cylinder 2 is increased (directional arrow 33) or decreased (directional arrow 32) by means of the linear movement of the piston 14.
  • the working fluid 24 condensed in the condenser 6 is introduced into the hydraulic cylinder 2 with respect to the working circuit 42 or with respect to a direction of the working circuit 42 after the condenser 6 and before the expansion valve 8.
  • the working fluid 24 is advantageously introduced into the hydraulic cylinder 2 upstream of the expansion valve 8, so that the working fluid 24 is introduced into the hydraulic cylinder 2 under high pressure, for example in the range from 10 MPa to 20 MPa. Due to the increased pressure, large Quantities of working fluid 24 can be removed from the working circuit 42 of the heat pump 4 and introduced into the hydraulic cylinder 2 in only a short time. In other words, the mass flow of the working fluid 24 in the outlet valve 18 is increased by the increased pressure.
  • further expansion valves 21 and check valves 22 are provided for the outlet and inlet valves 18, 20.
  • the outlet valve 18 is closed and the inlet valve 20 is opened.
  • the Working fluid 24 is pressed out of the hydraulic cylinder 2 by a straight movement - indicated by the directional arrow 32.
  • the return of the working fluid 24 takes place with respect to the working circuit 42 preferably downstream of the expansion valve 8 at a low pressure level. In this way, the working fluid 24 can advantageously be made to evaporate directly.
  • the device 1 shown makes it possible to regulate the fluid level of the working fluid 24 in the condenser 6 of the heat pump 4, so that the subcooling of the working fluid 24 in the condenser 6 can be regulated.
  • Working fluids known from the prior art for example R134a and / or R245fa, can be used as working fluids 24 can be used.
  • Working fluids containing at least one of the substances 1,1,1,2,2,4,5,5,5-nonafluoro-4- (trifluoromethyl) -3-pentanones (trade name Novec TM 649), perfluoromethylbutanone, 1 -Chloro-3,3,3-trifluoro-1-propene, cis-1,1,1,4,4,4-hexafluoro-2-butenes and / or cyclopentane.
  • the use of R134a, R400c and / or R410a can also be provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
EP15702673.3A 2014-02-27 2015-01-21 Wärmepumpe mit vorratsbehälter Active EP3097370B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014203578.3A DE102014203578A1 (de) 2014-02-27 2014-02-27 Wärmepumpe mit Vorratsbehälter
PCT/EP2015/051138 WO2015128122A1 (de) 2014-02-27 2015-01-21 Wärmepumpe mit vorratsbehälter

Publications (2)

Publication Number Publication Date
EP3097370A1 EP3097370A1 (de) 2016-11-30
EP3097370B1 true EP3097370B1 (de) 2020-09-23

Family

ID=52450063

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15702673.3A Active EP3097370B1 (de) 2014-02-27 2015-01-21 Wärmepumpe mit vorratsbehälter

Country Status (8)

Country Link
US (1) US20160370044A1 (zh)
EP (1) EP3097370B1 (zh)
JP (1) JP2017510781A (zh)
KR (2) KR20180021935A (zh)
CN (1) CN105899890B (zh)
CA (1) CA2940740A1 (zh)
DE (1) DE102014203578A1 (zh)
WO (1) WO2015128122A1 (zh)

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US10830515B2 (en) * 2015-10-21 2020-11-10 Mitsubishi Electric Research Laboratories, Inc. System and method for controlling refrigerant in vapor compression system
CN105485991B (zh) * 2016-01-04 2018-07-24 珠海格力电器股份有限公司 一种变容压缩机系统及控制方法、空调
CN105650926B (zh) * 2016-03-21 2018-12-07 珠海格力电器股份有限公司 冷媒循环系统及具有其的空调器
WO2018076364A1 (zh) * 2016-10-31 2018-05-03 合肥华凌股份有限公司 制冷装置
KR20180135882A (ko) * 2017-04-01 2018-12-21 이동원 냉매 저장수단을 구비한 히트펌프
DE102017206547A1 (de) * 2017-04-19 2018-10-25 Robert Bosch Gmbh Verfahren zum Befüllen eines Rohrleitungskreislaufs einer Wärmepumpe mit einem Kältemittel, Behälter dafür und Wärmepumpe
CN107763890B (zh) * 2017-09-26 2020-04-24 国网浙江省电力公司杭州供电公司 一种基于高压储液罐控制的高温热泵系统及控制方法
KR20190117344A (ko) 2018-04-08 2019-10-16 이동원 냉매 저장 탱크를 구비한 히트펌프
EP3839382B1 (en) * 2019-12-19 2023-09-27 Carrier Corporation Refrigeration system and method for operating a refrigeration system
DE102022100918A1 (de) 2022-01-17 2023-07-20 Schaeffler Technologies AG & Co. KG Aktive Füllmengensteuerung von Kfz-Kältemittelsystemen

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Also Published As

Publication number Publication date
CN105899890A (zh) 2016-08-24
US20160370044A1 (en) 2016-12-22
CA2940740A1 (en) 2015-09-03
KR20180021935A (ko) 2018-03-05
KR20160129029A (ko) 2016-11-08
CN105899890B (zh) 2018-10-23
WO2015128122A1 (de) 2015-09-03
EP3097370A1 (de) 2016-11-30
DE102014203578A1 (de) 2015-08-27
JP2017510781A (ja) 2017-04-13

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