WO2014191237A1 - Wärmepumpe zur verwendung von umweltverträglichen kältemitteln - Google Patents
Wärmepumpe zur verwendung von umweltverträglichen kältemitteln Download PDFInfo
- Publication number
- WO2014191237A1 WO2014191237A1 PCT/EP2014/060081 EP2014060081W WO2014191237A1 WO 2014191237 A1 WO2014191237 A1 WO 2014191237A1 EP 2014060081 W EP2014060081 W EP 2014060081W WO 2014191237 A1 WO2014191237 A1 WO 2014191237A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- temperature
- heat pump
- compressor
- working fluid
- pressure
- Prior art date
Links
Classifications
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- 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
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- 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
- 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
- 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
- F25B49/022—Compressor control 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
- 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
- F25B2400/01—Heaters
-
- 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
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
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- 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
- F25B2600/02—Compressor control
- F25B2600/027—Compressor control by controlling pressure
- F25B2600/0272—Compressor control by controlling pressure the suction pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/19—Refrigerant outlet condenser temperature
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
Definitions
- the present invention relates to heat pumps and the use of refrigerant therein.
- the use of a refrigerant in a heat pump is characterized by the so-called temperature lift.
- the tempera ⁇ turlift is the difference between the condensation and Ver ⁇ steaming temperature.
- the temperature lift thus means how much the heat source is raised in the temperature level to be used at the heat sink.
- the figure 1 is shown for comparison conductedung the problem of the phase boundary line of a geeig ⁇ Neten environmentally friendly refrigerant, which is characterized by a greatly overhanging dew line.
- a heat pump process for a temperature elevation of 50 Kelvin from 75 ° C evaporation temperature to 125 ° C condensation temperature is shown.
- the compression endpoint In order to operate a heat pump with such a cold ⁇ medium, the compression endpoint must maintain a minimum distance from the dew line to still be in the gas phase region. If the temperature lift in ⁇ play, at 20 Kelvin, that the condensation temperature be as low as 95 ° C, as shown in Figure 3, the compression end point would thus lie within the phase boundary line in the mixed phase region. This would lead to fluid sluice conditions in the compressor and prevent stable operation of the heat pump.
- the heat exchanger described which, as illustrated graphically in Figure 2, by supercooling the condensate from to ⁇ stand 4 to state 5, it transmits heat produced on the stand to ⁇ 7 and so overheat the suction gas before compression.
- the distance from state 4 to state 5 and the distance from state 7 to state 1 is the same enthalpy difference, as can be seen from the pressure-enthalpy diagrams 1 to 4.
- the approach with the internal heat exchanger is not suitable for every temperature lift.
- a tempera ⁇ turlift of, for example, 20 Kelvin
- the amount of heat that can provide the internal heat exchanger for the overheating of the suction gas is not enough and the compression end point is problematically again within the phase boundary line.
- the heat pump according to the invention comprises a compressor, a condenser, an internal heat exchanger, an expansion valve, an evaporator and a control device which is designed to bring the temperature of the working fluid at the outlet of the compressor to a predeterminable minimum distance, above the dew point.
- the Temperaturmindestab- was refers to the working fluid at constant pressure and is in particular at least one Kelvin, prior ⁇ preferably at least 5 Kelvin. This has the advantage that in order ⁇ world friendly not distinguish toxic safe working media, which often th through very specific thermodynamic Eigenschaf- such as a very low Taulinienste Trent of less than 1,000 (kg K 2) / kJ in the temperature-entropy diagram, are used and a steady state stable heat pump operation is possible.
- a control device which is designed to bring the temperature of the working fluid at the outlet of the compressor to a predeterminable minimum distance, above the dew point.
- the Temperaturmindestab- was refers to the working fluid at constant pressure and is in particular at least one Kelvin
- Control device a temperature control device which is designed to increase the temperature of the working fluid at the inlet of the compressor.
- the temperature ⁇ turregel shark is a pipe heater which is so arranged be- see the internal heat exchanger and the compressor, that gas flowing from the internal heat exchanger to the compressor working fluid by means of the heating pipe
- the temperature control device is designed such that it regulates the pipeline heating via the temperature of the working fluid at the compressor outlet. Depending on the temperature measured by the temperature control means at the compressor output, the Rohr Obershei ⁇ wetting is turned on or off or varied in its temperature.
- the pipeline heating can thus start briefly, for example, in fluctuating heat sources or réellesenketemperaturen or be in continuous operation. This has the advantage of compensating for a too low temperature lift.
- the temperature limit for the temperature lift depends on used refrigerant, or working fluid.
- the temperature lift depends on various properties and parameters of the heat pump.
- the temperature control device comprises a bypass line with a valve which connects the high-pressure region at the outlet of the compressor with the low pressure region at the inlet of the compressor, that the working fluid flowing from the internal heat exchanger to the compressor by means of the
- Bypass line traceable hot gas is overheatable.
- the temperature control device is in particular so diverse ⁇ tet that they pass through the valve of the
- Compressor output controls This embodiment also has to control the advantage for temperature lift, which would end up in the two-phase region without an additional A ⁇ access in the heat pump process to the compression end ⁇ point so that the heat pump with the used working fluid can be stably operated in a stationary state.
- the bypass valve used may be, for example, a thermostatic or an electronically controlled valve.
- the control device is a pressure regulating device, which is configured to lower the pressure of the working fluid at the inlet of the compressor.
- the Druckre ⁇ gel device in particular comprise an automatic expansion valve, which is arranged as an expansion valve in the heat pump cycle between the internal heat exchanger and the evaporator.
- An automatic expansion valve is a pure evaporator pressure control valve by means of which it is ⁇ possible to adjust the evaporation temperature and therefore the evaporation pressure.
- a higher pressure ratio P rat i o may be generated between the pressure side after the com pressor ⁇ and the low pressure side upstream of the compressor become. Because the compressor has to implement a higher pressure ratio PRATIO, a higher-pressure gas ⁇ temperature T 2 is generated at the compressor outlet. The higher the pressure ratio Pratio / the higher the temperature T 2 of the
- T 2 and i is the isentropic exponent ⁇ , the tem- peratures to and upstream of the compressor and the PRATIO Druckver ⁇ ratio of the gas pressures after and before the compressor.
- the pressure upstream of the compressor can also be lowered.
- an additional heating power is in this case an additional
- This embodiment has the advantage of being able to dispense with ⁇ additional heating elements and temperature control devices and to require no additional components in the heat pump for stationary operation by replacing the expansion valve by the automatic expansion valve.
- an automatic expansion valve in the heat pump has the added benefit represent a criz Wenn- ness for the application, that the temperature ⁇ turlift is not below a limit temperature, but well above the limit temperature. If the temperature lift is just too far above it, the pressure gas temperature T 2 after the compressor would also be very far above the minimum distance to the dew point to be maintained. This can result in a further problem if, for example, the compressor has an upper temperature limit.
- Such an upper temperature limit of use of a compressor may be due, for example, to the thermal stability of the lubricants or to excessive expansion for close fits in the compressor. Due to the automatic expansion valve, however, the pressure in the evaporator can also be increased to such an extent that Beitsfluid only slightly overheated or even partially evaporated.
- the embodiment with the automatic expansion valve at a temperature lift above the limit ⁇ temperature has the additional advantage due to the pressure increase to increase the overall efficiency of the heat pump, as by reducing the temperature difference in the evaporator, the pressure ratio decreases and a lower
- Compressor performance is demanded. At the same time the density of the fluid increases, thus increasing the power density in the com pressor ⁇ . In addition, an increased service life of the compressor can be ensured by the lower Druckgastempera ⁇ tur.
- the heat pump preferably comprises a working fluid which, in the temperature-entropy diagram, has a pitch of the dew line below 1000 (kg K 2 ) / kJ.
- the advantage of the ⁇ A set of such a working fluid is located in its projectingforementioned and safety properties. For example, as such, working fluids of the family of
- Fluoroketones be used. Particularly advantageous therefrom are the working fluids Novec649 (dodecafluoro-2-methylpentan-3-one) and Novec524 (decafluoro-3-methylbutan-2-one).
- Novec649 has a dew point slope of 601 (kgK 2 ) / kJ
- Novec524 has a dew point slope of 630 (kgK 2 ) / kJ
- another suitable example is R245fa (1,1,1,3,3-pentafluoropropane) which has a slope in the TS plot of 1653 (kgK 2 ) / kJ, the slope being given for a saturation temperature of 75 ° C, respectively.
- a working fluid is used in a heat pump, which has a slope in the vapor line at the tempera ture ⁇ -entropy diagram of less than 1,000 (kg K 2) / kJ.
- the temperature of a working fluid after the grain Pression to a predetermined minimum distance, in particular of a Kelvin, brought about the dew point.
- Figure 1 shows a logarithmic pressure-enthalpy diagram of a new working medium and thus driven ⁇ nen heat pump process with 50 Kelvin temperature lift
- FIG. 1 shows the heat transfer through the internal
- Figure 3 illustrates a logarithmic pressure-enthalpy diagram of the working medium as in Figure 1 with a heat pump process ⁇ with 20 Kelvin temperature lift.
- Figure 4 illustrates a logarithmic pressure-enthalpy diagram of the working medium as in Figure 1 with a heat pump process ⁇ with 60 Kelvin temperature lift.
- Figure 5 shows a flow diagram of a heat pump with Rohrlei ⁇ tung heating
- Figure 6 is a flow diagram of a heat pump with hot gas bypass
- Figure 7 shows a flow diagram of a heat pump with automatic ⁇ schem expansion valve.
- FIGS. 1 to 4 show pressure-enthalpy diagrams in which the pressure p is plotted on a logarithmic scale.
- the isotherms IT and dotted the isentropes IE are shown in dashed lines.
- the temperatures to the isotherms IT in degrees Cel sius, the entropy values to the isentropes IE in kJ / (kg-K) given.
- the continuous curve is drawn in each case the phase boundary line of a new PG working medium beispielswei ⁇ se is the fluid Novec649. This has a critical point at 169 ° C.
- the tau line would be tilted by 601 (kgK 2 ) / kJ in the temperature-entropy diagram.
- Another suitable example of a working medium is Novec524 with a critical point at 148 ° C.
- a heat pump process WP is additionally drawn in dashed lines.
- ge ⁇ be reached via a compression state to the point 2 or 3, which coincide in purely theoretical considerations and are named in the following only as state of step 2.
- the state point 4 is reached.
- the route from state point 7 back to starting point 1 is an overheating of the working medium.
- the heat pump process WP shown has an evaporation temperature at 75 ° C and a Kondensa ⁇ tion temperature at 125 ° C, ie a temperature lift of 50 Kelvin.
- the enthalpy is reduced by the same amount during the subcooling as it is increased in the case of overheating.
- the distance of the condition 2 of the dew line TL in the heat pump process WP, ie the temperature ⁇ turdifferenz state 2 is to its dew point at the same pressure 10 Kelvin.
- the example values for the transferred heat output Q IH x through the internal heat exchanger IHX refer to a capacitor output of 10 kW. In these examples, therefore, with a small temperature lift of 20 Kelvin, not enough heat can be transferred to maintain a minimum distance of, for example, 5 Kelvin for this system. At a temperature lift of 60 Kelvin, however, the transferred heat Qi H x of the internal heat exchanger IHX is sufficient for the minimum distance. The temperature lift of 60 Kelvin is so above the limit temperature lift for this system.
- the limit temperature lift is 37 Kelvin. If, for example, Novec524 were used as the working fluid with otherwise identical parameters, the limit temperature lift would be 31 Kelvin.
- FIGS. 5 to 7 show embodiments of heat pumps 10 with different control options for the use of new work equipment.
- heat pump processes WP can nevertheless still be operated stably stationary with too ge ⁇ ringem temperature lift below the limit temperature lifts.
- the capacitor power for example, is 10 kW.
- FIGS. 5 and 6 show two alternative temperature controls. In these cases, the heat pump 10 is operated with a conventional expansion ⁇ onsventil 14, which may be, for example, a thermostatic or an electronically controlled expansion valve 14.
- This expansion valve 14 controls the flow of the working fluid and the superheat after the evaporator 15.
- a pipe heater 20 is disposed around the pipe section between the internal heat exchanger 13 and the compressor 11 around.
- the working medium flowing therein can be heated. How much the pipe heater 20, the working fluid in the state 1 is heated over the temperature T 2 at state 2, that is regulated at the output of the compressor 11. Additionally the temperature T is there 2 ge ⁇ measure and an adjustment to a minimum distance of the temperature ⁇ the heater turned on or off or its heating power is lowered or raised.
- the temperature control means 30 shown in Figure 6 includes a hot gas bypass 31, the compressed gas from the pressure side 2 of the compressor 11 to the suction side 1 of the compressor 11 to-back leads and so by means of the hot compressed gas heats the suction gas wei ⁇ ter.
- the increase in the temperature ⁇ of the suction gas is limited by a bypass valve 31, which in turn is regulated by the temperature T 2 in state 2.
- the valve 31 may be a thermostatically or electronically controlled valve 31.
- the additional power required for this temperature control 30 is, for example, 0.58 kW, which is an additional compressor output in an isentropic pressure and temperature increase.
- FIG. 7 shows an alternative embodiment for controlling the temperature 30, namely a regulation via the suction gas pressure:
- an automatic expansion valve 40 ie a pure evaporator pressure regulating valve
- the pressure of 1.96 bar are lowered to 1.35 bar so as to maintain the minimum distance of 5 Kelvin.
- example ⁇ an additional compressor capacity at isentropic Pressure and temperature increase by the compressor 11 of 0.45 kW necessary.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Compressor (AREA)
Abstract
Description
Claims
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DK14727748.7T DK3004754T3 (en) | 2013-05-31 | 2014-05-16 | Heat pump for use of environmentally friendly refrigerants |
KR1020157036851A KR101907978B1 (ko) | 2013-05-31 | 2014-05-16 | 환경 친화적인 냉매를 사용하기 위한 열 펌프 |
CN201480038694.6A CN105358920B (zh) | 2013-05-31 | 2014-05-16 | 用于使用环境兼容的制冷剂的热泵 |
EP14727748.7A EP3004754B1 (de) | 2013-05-31 | 2014-05-16 | Wärmepumpe zur verwendung von umweltverträglichen kältemitteln |
US14/894,676 US11473819B2 (en) | 2013-05-31 | 2014-05-16 | Heat pump for using environmentally compatible coolants |
PL14727748T PL3004754T3 (pl) | 2013-05-31 | 2014-05-16 | Pompa ciepła do stosowania z przyjaznymi dla środowiska czynnikami chłodniczymi |
CA2913947A CA2913947C (en) | 2013-05-31 | 2014-05-16 | Heat pump for using environmentally compatible coolants |
JP2016515716A JP6328230B2 (ja) | 2013-05-31 | 2014-05-16 | 環境親和性のある冷媒を利用するためのヒートポンプおよびその運転方法ならびに動作流体の使用 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013210175.9A DE102013210175A1 (de) | 2013-05-31 | 2013-05-31 | Wärmepumpe zur Verwendung von umweltverträglichen Kältemitteln |
DE102013210175.9 | 2013-05-31 |
Publications (1)
Publication Number | Publication Date |
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WO2014191237A1 true WO2014191237A1 (de) | 2014-12-04 |
Family
ID=50884354
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2014/060081 WO2014191237A1 (de) | 2013-05-31 | 2014-05-16 | Wärmepumpe zur verwendung von umweltverträglichen kältemitteln |
Country Status (10)
Country | Link |
---|---|
US (1) | US11473819B2 (de) |
EP (1) | EP3004754B1 (de) |
JP (1) | JP6328230B2 (de) |
KR (1) | KR101907978B1 (de) |
CN (1) | CN105358920B (de) |
CA (1) | CA2913947C (de) |
DE (1) | DE102013210175A1 (de) |
DK (1) | DK3004754T3 (de) |
PL (1) | PL3004754T3 (de) |
WO (1) | WO2014191237A1 (de) |
Cited By (4)
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KR20190125434A (ko) * | 2017-03-14 | 2019-11-06 | 지멘스 악티엔게젤샤프트 | 열 펌프 및 열 펌프 작동 방법 |
KR20190130158A (ko) * | 2017-03-31 | 2019-11-21 | 지멘스 악티엔게젤샤프트 | 열 펌프 및 열 펌프를 작동시키기 위한 방법 |
DE102018125411A1 (de) * | 2018-10-15 | 2020-04-16 | Vaillant Gmbh | COP-optimale Leistungsregelung |
US11473819B2 (en) | 2013-05-31 | 2022-10-18 | Siemens Energy Global GmbH & Co. KG | Heat pump for using environmentally compatible coolants |
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AT514476A1 (de) * | 2013-06-17 | 2015-01-15 | Lenzing Akiengesellschaft | Polysaccharidfaser und Verfahren zu ihrer Herstellung |
DE102014200820A1 (de) | 2014-01-17 | 2015-07-23 | Siemens Aktiengesellschaft | Verfahren zur Herstellung eines wenigstens eine Wärmeübertragungsfläche aufweisenden Wärmetauschers |
BR112017001637B1 (pt) * | 2014-07-29 | 2023-04-11 | Siemens Energy Global GmbH & Co. KG | Aparelho e método para secar matéria-prima de secagem, e planta industrial para fabricar matériaprima |
EP3239626A1 (de) | 2016-04-27 | 2017-11-01 | PLUM spólka z ograniczona odpowiedzialnoscia | Verfahren zur wärmepumpenbetriebssteuerung |
DE102017216361A1 (de) * | 2017-09-14 | 2019-03-14 | Weiss Umwelttechnik Gmbh | Verfahren zur Konditionierung von Luft |
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- 2014-05-16 KR KR1020157036851A patent/KR101907978B1/ko active IP Right Grant
- 2014-05-16 EP EP14727748.7A patent/EP3004754B1/de active Active
- 2014-05-16 PL PL14727748T patent/PL3004754T3/pl unknown
- 2014-05-16 US US14/894,676 patent/US11473819B2/en active Active
- 2014-05-16 CN CN201480038694.6A patent/CN105358920B/zh not_active Expired - Fee Related
- 2014-05-16 DK DK14727748.7T patent/DK3004754T3/en active
- 2014-05-16 WO PCT/EP2014/060081 patent/WO2014191237A1/de active Application Filing
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US11473819B2 (en) | 2013-05-31 | 2022-10-18 | Siemens Energy Global GmbH & Co. KG | Heat pump for using environmentally compatible coolants |
KR20190125434A (ko) * | 2017-03-14 | 2019-11-06 | 지멘스 악티엔게젤샤프트 | 열 펌프 및 열 펌프 작동 방법 |
KR102355349B1 (ko) * | 2017-03-14 | 2022-01-26 | 지멘스 악티엔게젤샤프트 | 열 펌프 및 열 펌프 작동 방법 |
KR20190130158A (ko) * | 2017-03-31 | 2019-11-21 | 지멘스 악티엔게젤샤프트 | 열 펌프 및 열 펌프를 작동시키기 위한 방법 |
KR102344187B1 (ko) | 2017-03-31 | 2021-12-30 | 지멘스 악티엔게젤샤프트 | 열 펌프 및 열 펌프를 작동시키기 위한 방법 |
DE102018125411A1 (de) * | 2018-10-15 | 2020-04-16 | Vaillant Gmbh | COP-optimale Leistungsregelung |
EP3640565A1 (de) | 2018-10-15 | 2020-04-22 | Vaillant GmbH | Cop-optimale leistungsregelung |
Also Published As
Publication number | Publication date |
---|---|
KR20160014033A (ko) | 2016-02-05 |
US11473819B2 (en) | 2022-10-18 |
PL3004754T3 (pl) | 2019-06-28 |
DK3004754T3 (en) | 2019-01-28 |
US20160102902A1 (en) | 2016-04-14 |
CA2913947A1 (en) | 2014-12-04 |
CA2913947C (en) | 2018-03-13 |
EP3004754A1 (de) | 2016-04-13 |
EP3004754B1 (de) | 2018-10-24 |
KR101907978B1 (ko) | 2018-10-15 |
DE102013210175A1 (de) | 2014-12-18 |
JP2016520187A (ja) | 2016-07-11 |
CN105358920A (zh) | 2016-02-24 |
CN105358920B (zh) | 2018-05-04 |
JP6328230B2 (ja) | 2018-05-23 |
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