WO2019043009A1 - Pompe à chaleur comprenant un système de refroidissement intermédiaire fermé et procédé servant à pomper de la chaleur ou procédé servant à fabriquer la pompe à chaleur - Google Patents

Pompe à chaleur comprenant un système de refroidissement intermédiaire fermé et procédé servant à pomper de la chaleur ou procédé servant à fabriquer la pompe à chaleur Download PDF

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Publication number
WO2019043009A1
WO2019043009A1 PCT/EP2018/073143 EP2018073143W WO2019043009A1 WO 2019043009 A1 WO2019043009 A1 WO 2019043009A1 EP 2018073143 W EP2018073143 W EP 2018073143W WO 2019043009 A1 WO2019043009 A1 WO 2019043009A1
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WO
WIPO (PCT)
Prior art keywords
condenser
heat exchanger
liquid
heat pump
heat
Prior art date
Application number
PCT/EP2018/073143
Other languages
German (de)
English (en)
Inventor
Oliver Kniffler
Original Assignee
Efficient Energy 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 Efficient Energy Gmbh filed Critical Efficient Energy Gmbh
Priority to GB2002457.6A priority Critical patent/GB2579928B/en
Publication of WO2019043009A1 publication Critical patent/WO2019043009A1/fr

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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
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled 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—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/072—Intercoolers therefor
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems

Definitions

  • the present invention relates to heat pumps and more particularly to heat pumps having a multi-stage compressor and intermediate cooling.
  • Fig. 5 shows a heat pump, as it can be used for example for heating.
  • the heat pump comprises an evaporator 100, a compressor 110, a condenser 120 and an expansion valve 130.
  • working fluid is vaporized and fed via an intake passage 1 12 to the compressor, which is exemplified here as a piston compressor.
  • Compressed working steam is then fed via an ejection line 1 14 in the condenser 120.
  • the condenser 120 the compressed from the compressor 1 10 working vapor liquefied.
  • the circuit is closed by an expansion valve 130, which is to expand the working fluid at the condenser outlet from the high condenser pressure to the low evaporator pressure.
  • a heat exchanger is arranged with a closed line, which is shown at 102, above it runs a liquid, the z. B. brings heat from the environment. Due to the heat introduced into the evaporator 100, the working liquid evaporates in the evaporator, whereby heat is removed from the liquid in the heat exchanger 02 and thus cooled working fluid is led out of the evaporator via the heat exchanger.
  • the condenser also has a heat exchanger 122. In the heat exchanger 122 heat introduced by the liquefaction process in the condenser 120 out of the condenser, and indeed to cooler, which may be, for example, a radiator. The working fluid cooled in the radiator is then fed back into the heat exchanger 122, which is located in the condenser 120.
  • European Patent EP 2 281 155 discloses a vertically arranged heat pump in which an evaporator and a condenser as well as a gas area extending between the evaporator and the condenser are present.
  • the condenser is arranged above the evaporator in an operating Aufzeiques the heat pump.
  • the compressor comprises a first compressor stage, an intermediate cooling and a second compressor stage. Energy taken from the superheated working steam after the first compressor stage by the intercooler is used to heat a service water tank to a temperature that is above the temperature in the condenser.
  • a return channel For the return of the medium, a return channel is provided, wherein a first stage of the return channel has nozzle openings in the bottom wall of the condenser, so that liquefied working fluid, which is in the vicinity of such a nozzle opening, due to the pressure difference between the condenser bottom and spraying the intercooler into the intercooler.
  • the sprayed-in liquid medium is then collected in a bulge of the intercooler to be transported from there into the evaporator through a second section of the return channel.
  • a similar spraying technique can be used through nozzle openings, as again there is a pressure difference between the gas channel and the evaporation space in the evaporator.
  • European patent EP 2 016 349 discloses a heat pump which uses water as the working fluid and in which a multi-stage compressor is provided, the multi-stage compressor having a first turbomachine and an nth (last) turbomachine.
  • an intercooler is used, which has a heat exchanger for domestic water heating.
  • the turbomachines are designed as a radial compressor with a rotating wheel, the wheel is a slow-speed Radial, a medium radial wheel, a Halbaxialrad or an axial gear or a propeller can be.
  • a turbomachine with a radial wheel is used.
  • For intercooling one or more heat exchangers are provided for domestic water heating.
  • heat exchangers are designed to cool the gas heated (and compressed) by a previous turbomachine.
  • the heat of enthalpy of entrainment is usefully used to increase the efficiency of the entire compaction process. It is thus removed heat from the compressed water vapor to service water to higher temperatures than z. B. 40 ° C to heat.
  • refrigerant for example water
  • a closed intercooling cool the superheated steam only to saturated steam, if there are sufficiently supercooled large areas for the heat transported. If cold water is provided for this, the power is introduced unfavorably into the system on the cold water side and must be provided as additional cooling capacity.
  • JPH 06257890 discloses a heat pump that uses water and is performed in cooling and heating with the same apparatus. To produce chilled water or ice, part of the water is evaporated and the rest of the water is cooled. The vapor produced by evaporation is compressed in several stages, and then enters a condenser coupled to a cooling tower.
  • US Pat. No. 3,665,724 discloses a heating and cooling apparatus with a multi-stage centrifugal compressor. The latent heat of a coolant is released along with the heat of compression via a cooling tower.
  • the object of the present invention is to provide an improved heat pump concept with intercooling that deals more efficiently with existing resources.
  • a heat pump according to claim 1 a method for pumping heat according to claim 18 or a method for producing a heat pump according to claim 19.
  • the present invention is based on the finding that the reaching of the saturated steam temperature after a compressor stage is eliminated. Although this increases the compressor capacity of the downstream stage due to the less favorable starting conditions. But it can with the cooling liquid, ie the return of the area to be heated, a heat exchanger to cool the superheated working fluid to near the cooling water temperature, which is provided for example by the roof or from the area to be heated, cool. This produces no water vapor, which would have to be compacted with the downstream stage, but a large part of the superheat enthalpy is already as heat output to the cooling system, ie z. B. the waste heat system when using a heat pump as a cooling or refrigerating machine or the heating system when using a heat pump as a heater dispensed.
  • an intercooler with a heat exchanger is used, which is arranged in the vapor space, and a heat exchanger input and a heat exchanger Output.
  • the heat exchanger inlet or the heat exchanger outlet is connected to a condenser inlet or condenser outlet for directing condenser coolant in a circuit through both the condenser and the heat exchanger during operation of the heat pump.
  • the condenser is an open condenser, in that the water from the intermediate heat exchanger is used directly to condense into this water compressed working steam from the second compressor stage.
  • the condenser is a "closed" condenser, meaning that in the condenser there is a closed line between the condenser inlet and the condenser exit. tion, so again a heat exchanger is arranged, which ensures that the flowing medium in the heat exchanger does not come into direct contact with the condensed in the condenser compressed working steam, but only in thermal contact.
  • the heat exchanger of the intercooler which implements a closed intercooling, is carried out continuously with the heat exchanger in the condenser.
  • the line of the heat exchanger extends either initially through the intermediate cooling and further through a partition wall into the pressure range of the condenser stage.
  • first the return of the area to be heated can be fed into the heat exchanger in the condenser to then run from there into the heat exchanger in the intercooler.
  • the two heat exchangers are continuously designed to a certain extent as a single heat exchanger, going to a line of this heat exchanger the partition wall between the vapor space of the insectsüh- lungs Colour and the condenser Passes through the region of the condenser.
  • an implementation can also be used in which the heat exchangers in the condenser and in the intercooler outside the heat pump volume are connected to each other, so that then no passage through the partition in the pressure range of the downstream stage is necessary.
  • FIG. 1 shows a preferred embodiment of a heat pump with closed intermediate cooling and connection to the return from the area to be heated; an alternative embodiment of the present invention, wherein the return from the area to be heated is passed first through the condenser and then through the intercooler; an alternate embodiment of the present invention wherein the return from the area to be heated is first passed through the intercooler and then through the condenser heat exchanger;
  • Fig. 4 shows an embodiment of the present invention, wherein the heat exchanger in the intercooler within the heat pump with the heat exchanger in Condenser is connected, so that a line of heat transfer! Pass through the partition wall to the higher pressure stage;
  • FIG. 6 shows a schematic representation of a compressor stage with suction mouth, radial wheel and guide space
  • Fig. 7 is a tabular overview of various modes in which the heat pump is operable.
  • the compressor comprises a first compressor stage 31, a steam chamber 32 and a second compressor stage 33. It should be noted that the present invention does not the use of only two levels is limited, but may include the use of three, four, five or even more levels. In any case, between at least two stages of the plurality of stages of the compressor motor, the vapor space 32 is arranged, in which an intercooler 40 is arranged.
  • the evaporator can be coupled to a region 50 to be cooled, and the condenser can be coupled to a region 60 to be heated.
  • the evaporator 10 is designed to evaporate working fluid.
  • Working fluid is provided for example via a connection 1 1 for a return from the area to be cooled.
  • This liquid provided via the connection 11 is warmer than the liquid which is dispensed from the evaporator via a connection 12 to a passage to the area to be cooled from the evaporator.
  • the heat, which has been brought into the evaporator via the connection for the return, is guided by the vaporized working steam via a suction line 13 into the first stage 31 of the compressor 30.
  • the vaporized working steam is compressed in the first stage, and the compressed working steam enters the steam chamber 32. There, the compressed working steam is cooled to reduce its typically occurring overheating.
  • the working steam which has meanwhile been cooled by the intercooler 40, is then recompressed and then brought into the condenser 20 via a discharge line 24.
  • the condenser comprises a condenser inlet 21 and a condenser outlet 22.
  • the intercooler 40 comprises a heat exchanger, the one Heat exchanger input 41 and a heat exchanger output 42 has.
  • heat exchanger input 41 or the heat exchanger output 42 to the condenser inlet 21 or the condenser outlet 22 is connected to the operation of the heat pump coolant for the condenser in a circuit by both the condenser 20 and by the heat exchanger in the Conduct intercooler 40.
  • the condenser may be an open condenser, so that the condenser cooling liquid is the liquid into which the compressed working steam supplied from the discharge line 24 is directly condensed.
  • the condenser may be a closed condenser, so that in the condenser there is also a heat exchanger with a conduit through which the cooling fluid for the condenser flows, but with the situation in the condenser 20 only thermal contact, but no direct media contact.
  • the liquid fed into the condenser via its inlet 21 serves as the cooling liquid for the condenser, because this liquid, regardless of whether it is used directly for condensing or whether it is separated from the working steam by a line, ie a closed line Line is disconnected, is used.
  • the heat pump has a port 61 for connecting the trace for the area to be heated 60.
  • the heat pump also has a port 62 for connecting the return of the area to be heated.
  • the inlet 41 of the heat exchanger in the intercooler is connected to the connection 62 for the return from the area to be heated.
  • the output 42 of the heat exchanger is connected to the condenser inlet 21.
  • the condenser outlet 22 is connected to the connection for the trace to the area to be heated.
  • Fig. 1 further shows a heat exchanger 710 and a mixer or switch 720.
  • the heat exchanger 710 and the mixer / switch 720 are optionally present.
  • the switch is controllable to bridge in the position 1, the heat exchanger 710, and to integrate in position 2, the heat exchanger full 710.
  • the mixer / switch and the heat exchanger can also be present in the embodiments of the other figures 2a to 4, although it is not shown.
  • the port 62 of the area to be heated is connected to a first input of the heat exchanger, and is the first output with connected to the intercooler input 41.
  • the 2nd input is connected to the output 2 of the heat exchanger and the 2nd output is connected to the input 1 1 of the evaporator 10.
  • the second output is also the output 2 of the switch 720 coupled.
  • Fig. 1 further shows an evaporator circuit interface 1 1, 12 for introducing liquid to be cooled into the heat pump and for discharging cooled liquid from the heat pump, a condenser circuit interface 21, 22 for introducing liquid to be heated in the heat pump and for discharging heated liquid from the heat pump, wherein the condenser circuit interface is coupled to the intercooler (40), a controllable heat exchanger, the z. B.
  • heat exchanger 710 is implemented as the combination of heat exchanger 710 and switch / mixer 720, for controllably coupling the evaporator circuit interface and the condenser circuit interface; and a controller 730 for controlling the controllable heat exchanger (710, 720) depending on an evaporator circuit temperature (TV or TWK) in the evaporator circuit interface or a condenser circuit temperature (TK or TWW) in the condenser circuit interface.
  • TV or TWK evaporator circuit temperature
  • TK or TWW condenser circuit temperature
  • the heat exchanger 710 is connected between the intercooler inlet 41 and the port 62 for the area to be heated.
  • the warm side of the mixer in FIG. 1 is connected between the intercooler output 42 and the condenser inlet 21.
  • the warm side of the mixer is connected between the intercooler outlet 42 and the port 61 for the trace to the area to be heated, or between the condenser outlet 22 and the intercooler inlet 41.
  • the controller 730 is designed to prevent cooling of the liquid to be cooled by the liquid to be heated using the controllable heat exchanger preferably consisting of the heat exchanger 710 and the mixer or switch 720, if a condenser circuit temperature of the liquid to be heated is greater than is an evaporator circuit temperature of the liquid to be cooled, or to prevent cooling of the liquid to be cooled by the liquid to be heated using the controllable heat exchanger and depending on a required cooling power to make a speed control of Radial alrads a compressor in the heat pump, if a condenser - Circulation temperature of the liquid to be heated is greater than a Verdampfernikank- is the temperature of the liquid to be cooled, or to activate a cooling of the liquid to be cooled by the liquid to be heated using the controllable heat exchanger, when a condenser circuit temperature of the liquid to be heated is smaller than an evaporator circuit temperature of the liquid to be cooled, or to a cooling of to activate liquid to
  • FIGS. 2 and 3 show an implementation in which the heat exchanger 43 in the intercooler 40 is shown in more detail as a continuous line.
  • a further heat exchanger 23 is shown in the condenser 20 as a closed heat exchanger, which ensures that in the line of the heat exchanger 23, the cooling liquid is running, but that cooling liquid does not come into contact with the compressed working steam, so not in one direct contact via the steam supplied from the line 24, but only in thermal contact with the steam or with liquefied working fluid present in the condenser to dissipate heat from the condenser.
  • FIG. 3 shows an implementation similar to FIG. 1, namely that the cooling liquid, which is supplied via the connection for the return 62 from the area to be heated 60, first passes through the heat exchanger 43 and then the heat exchanger 23.
  • Fig. 2 shows an alternative implementation, in which the return from the area 60 to be heated is first passed via the connection 62 for the return from the area to be heated in the heat exchanger 23 via the inlet 21, and then out of the heat exchanger 23 via its output 22 into the inlet 41 of the heat exchanger 43, in the vapor space between the two compressor stages 31 is guided, and from there via the port 61 in the area to be heated 60. It can be seen that the flow direction of the cooling liquid, which is cooled in the area to be heated 60, in Fig. 2 opposite to the flow direction the cooling liquid in Fig. 3 is.
  • the inlet 41 of the heat exchanger is connected to the condenser return 22.
  • the output 42 of the heat exchanger 23 of the intercooler 40 is connected to a port 61 for a trace to the area to be heated.
  • the condenser inlet 21 of the condenser heat exchanger 23 is connected to the return line 62 from the area 60 to be heated.
  • the condenser may be an open condenser, in which the compressed working steam condenses directly into the liquid which also runs in the heat exchanger 43 of the intercooler 40.
  • the condenser inlet 21 and the condenser outlet 22 are connected within the condenser through an intermediate line, so that a liquid in the line is medially separated from a working fluid liquefied in the condenser 20, but is in thermal contact.
  • a wall 59 is arranged between the condenser space, ie the space into which the discharge line 24 opens, and the dam f 32.
  • a line of the heat exchanger 43 of the intercooler or a line of the heat exchanger in the condenser passes through the wall 59 in the embodiment shown in FIG. 4 inside the heat pump.
  • both the heat exchanger 43 in the intercooler 40 and the heat exchanger 23 in the condenser directly coupled with each other.
  • either the condenser outlet 22 or the condenser inlet 21 is thus connected to the heat exchanger outlet 42 or the heat exchanger inlet 41. Therefore, in Fig.
  • the respective heat exchanger inputs / outputs are each provided with two reference numerals, because the definition of whether the input is an input or an output, depends on which direction the cooling liquid flows, so whether the cooling liquid from the area to be heated via the terminals 61, 62 communicates with the heat pump, either first in the intercooler 40 and the heat exchanger 43 flows through the intercooler 40, as shown in Fig. 1 and in Fig. 3, or whether the liquid first flows through the heat exchanger 23 in the evaporator and then only through the intercooler, as shown in Fig. 2. Therefore, the connections between the outputs of the heat exchanger cascade from the heat exchangers 43 and 23 in Fig. 4 are shown in dashed lines. It should be noted, however, that typically only one of the two configurations will be used in actual implementations of the heat pump.
  • Fig. 4 also shows a first throttle or a first expansion valve 61 between the vapor space 32 of the intermediate cooling and the evaporator 10.
  • a second throttle is schematically drawn, which is also drawn at 62 as an expansion valve, and by the Condenser space 20 of the condenser 20 is connected to the evaporator 10 in order to achieve a return to working fluid to ensure the complete circuit.
  • a droplet separator is shown, which is arranged between the evaporator 10 and the first compressor stage 31.
  • an optional droplet separator 72 is provided, which is arranged in the vapor space between the first compressor motor 31 and the second compressor motor 33.
  • a control is shown in Fig. 4 at 80, through which the two-stage compressor can be controlled to run the heat pump in single-stage operation, if the requirements are not particularly high, and then the heat pump when the Requirements are high, to run in two-stage operation.
  • FIG. 6 shows a schematic representation of a motor of a compressor stage 31 or 33.
  • FIG. 6 shows a compressor stage with a suction mouth 91, a radial wheel 92, a motor 93 and a guide space 94 in order to compress steam.
  • the centrifugal compressor of Fig. 6 is used in the first stage 31, the steam sucked in via the suction port 91 comes from the evaporator, and the steam discharged via the guide space 94 flows into the vapor space 32
  • the steam sucked in via the suction mouth passes out of the steam space and has been cooled by the intercooler 40, and is the steam is output from the Leitraum 94, the steam, which is finally fed into the condenser 20 and is liquefied there to give its energy to the condenser and ultimately to the cooling liquid, which run via the condenser outlet 22 in the area to be heated 60 can.
  • a large part of the superheat enthalpy is thus already delivered as heat output to the cooling water system, ie to the circuit which runs through the area 60 to be heated.
  • condensation on the heat exchanger 43 can take place. It is preferred therefore to provide a throttle 63 to bring this condensate into the evaporator.
  • the second throttle 62 is provided to provide a two-stage operation for a closed system.
  • the system has an open component, since in the single-stage operation over a range of the condensate of the throttle 63 is supplied and should first be collected in advance.
  • the cooling liquid and the condensate of the downstream stage are returned via the throttle 64 in the evaporator, where then takes place, the closing of the circuit. It is preferred that the water in the second throttle 62 does not touch the heat exchanger 43, since otherwise it would cool the cooling water in the heat exchanger by evaporation.
  • a further (shown in dashed lines in Fig. 4) throttle 65 between the condenser 20 and the vapor space 32 may be present, which is supplemented by the throttle 63 between the vapor space 32 and the evaporator 10.
  • the throttles are designed such that the intercooler 40 in the vapor space 32 does not come into contact with liquid from the throttles.
  • the cooling water flows first through the downstream stage, so by the Verfiüssiger and then by the intermediate cooling of the first stage, then the temperature thereof and thus the distance to S attd at the pfte perat ur in the intercooler.
  • the condensation chamber after the stage are partially shared, and so the heat exchanger surface in the intermediate cooling and the single-stage operation can be again reduced slightly.
  • the droplet separator 72 may also be omitted, since the heat exchanger 43 provides for slight overheating. This will not produce drops in this area when the second stage is active.
  • the start of the second stage is critical if the steam has previously condensed in the Swisskühiung and this is damp when starting. Then drops of water can be caused by the lowering of the suction pressure by boiling and the mist eliminator 72 is at least temporarily necessary, this can be avoided by a slow start of the second stage.
  • Fig. 7 shows a tabular compilation of various modes, the z. B. with a two-way switch 720 and the heat exchanger 710, as has been shown in Fig. 1, can be effected.
  • the free cooling is active, Furthermore, the controllable heat exchanger flows from both sides, so it is active.
  • the compressor both stages is deactivated, ie switched off. Control of the temperature can be achieved, for example, by controlling the condenser-side pump contained in a condenser circuit interface. If it is determined that the temperature of the cooled liquid is less than a set temperature, the pump can be throttled.
  • the pump can be turned faster again.
  • a fan which is typically present in the area to be heated 60, can also be rotated faster or slower in order to achieve more or less cooling power.
  • the free cooling is also active.
  • the compressor is also active in a first stage, and if necessary in the second stage, and a regulation of the temperature which is fed into the data center or into the area to be cooled can be effected in that the Speed of the radial wheel in the first stage of the compressor is controlled, the second stage is switched on, and / or the radial wheel is controlled in the second stage in its speed. If a higher cooling capacity is required, the speed is increased and / or the second stage is switched on. If, on the other hand, a lower cooling capacity is required, the speed of the radial wheel is reduced and / or the second stage is switched off.
  • the temperatures are greater than 16 ° C, for example.
  • the controllable heat exchanger is deactivated, ie switched inactive, and it can be a cooling power control again via the speed of the radial wheel.
  • this mode ie in the warm temperature range, however, no free cooling is active.
  • a controllable short circuit between the output or the condenser circuit and the input or the evaporator circuit of the heat pump device can be achieved.
  • a partial load operation for example, there may be the situation that the control would go without the special mode with controllable short circuit to an on-off timing, which for various reasons is not advantageous.
  • the special mode with controllable short circuit is activated, which is detected for example by a specific frequency of clocking. If a too high frequency of clocking is detected, then the controllable short circuit is activated, so a typically smaller part, that is a part less than 50% of the flow rate in the corresponding first or second path of the heat exchanger unit is fed and with the other (typically larger ) Share at the output of the heat exchanger unit combined again.
  • this mixing effect may be controlled according to the implementation, eg from 1% / 99% control to 51% / 49%. - Control.
  • the major portion of the flow pass the heat exchanger element 710 and only the minor portion of the flow pass through the heat exchanger element 710, as previously noted, allowing the smaller flow fraction to be controllable from 0 to 50%, as appropriate Execution of the mixer.
  • a heat exchanger and a three-point switch are installed.
  • the three-point switch can be on the Be installed cold water side or the hot water side and is to unlock the flow through the heat exchanger or lock.
  • water as a refrigerant offers the advantage for free cooling plus that the volume flow and the pressure ratio can be adjusted by a speed-controlled centrifugal compressor, thus creating a nearly ideal operating point of the system in a wide range of applications can be achieved with small cooling capacities below 50 kW.
  • water from e.g. B. 20 ° C cooled to 16 ° C although other temperatures are possible, such as a cooling to 20 ° C from a higher temperature of 26 ° C.
  • it is always achieved that the cooling capacity is achieved with the least possible expenditure of energy to a temperature level, depending on the outside temperature, the output to the environment again.
  • the compression refrigeration system is switched on with power control to provide the missing part, for example 3 ° C or 50% power. If the outside temperatures continue to rise and the cooling water reaches temperatures of, for example, 25 ° C and more, virtually no more energy can be transferred through the heat exchanger. The entire cooling capacity must now be provided by the compression refrigeration machine. If the cooling water temperatures continue to rise, in this range above 26 ° C, the three-way switch must block the flow through the heat exchanger at least on one side, otherwise the cooling system would have to provide even more cooling capacity than required by the application.
  • control ie whether the heat exchanger is flowed through or not, depends only on the temperatures TWW and TWK; namely, when the temperature TWW is less than TWK, the heat exchanger unit is flowed through. If the temperature in the evaporator is greater than the flow temperature on the cold water side or customer side, the compressor must work. On the other hand, if the temperatures in the free cooling mode are below the required customer temperature, in this case 16 ° C, the fan can be on the roof and finally the pumps can be throttled. LIST OF REFERENCE NUMBERS

Abstract

L'invention concerne une pompe à chaleur, comprenant un évaporateur (10) servant à évaporer du liquide de travail, un condenseur (20) servant à condenser de la vapeur de travail compactée, un compresseur (30) pourvu d'un premier étage (31) de compresseur, d'un deuxième étage (33) de compresseur et d'un espace de vapeur (32) entre le premier étage (31) de compresseur et le deuxième étage (33) de compresseur ; et un refroidisseur intermédiaire (40) pourvu d'un échangeur de chaleur (43), qui est disposé dans l'espace de vapeur (32) et qui comporte une entrée (41) d'échangeur de chaleur et une sortie (42) d'échangeur de chaleur. L'entrée (41) d'échangeur de chaleur ou la sortie (42) d'échangeur de chaleur est reliée à une entrée de compresseur (21) ou à une sortie de compresseur (22) afin d'acheminer, lors du fonctionnement de la pompe à chaleur, du liquide de refroidissement pour le condenseur (20) dans un circuit à la fois à travers le condenseur (20) et à travers l'échangeur de chaleur (43).
PCT/EP2018/073143 2017-08-30 2018-08-28 Pompe à chaleur comprenant un système de refroidissement intermédiaire fermé et procédé servant à pomper de la chaleur ou procédé servant à fabriquer la pompe à chaleur WO2019043009A1 (fr)

Priority Applications (1)

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GB2002457.6A GB2579928B (en) 2017-08-30 2018-08-28 Heat pump with closed intermediate cooling and method for pumping heat or method for producing the heat pump

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DE102017215198.6 2017-08-30
DE102017215198.6A DE102017215198A1 (de) 2017-08-30 2017-08-30 Wärmepumpe mit geschlossener Zwischenkühlung und Verfahren zum Pumpen von Wärme oder Verfahren zum Herstellen der Wärmepumpe

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WO2019043009A1 true WO2019043009A1 (fr) 2019-03-07

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PCT/EP2018/073143 WO2019043009A1 (fr) 2017-08-30 2018-08-28 Pompe à chaleur comprenant un système de refroidissement intermédiaire fermé et procédé servant à pomper de la chaleur ou procédé servant à fabriquer la pompe à chaleur

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DE (1) DE102017215198A1 (fr)
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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3665724A (en) 1970-07-13 1972-05-30 Carrier Corp Heating and cooling refrigeration apparatus
EP2016349A1 (fr) 2006-04-04 2009-01-21 Efficient Energy GmbH Pompe a chaleur
EP2281155A1 (fr) 2008-04-01 2011-02-09 Efficient Energy GmbH Pompe à chaleur agencée verticalement et procédé de fabrication de cette pompe à chaleur agencée verticalement
WO2013125215A1 (fr) * 2012-02-23 2013-08-29 川崎重工業株式会社 Machine de réfrigération

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE229824C (fr) *
DE475674C (de) * 1925-01-17 1929-04-30 Bbc Brown Boveri & Cie Kreiselverdichter fuer Kaeltemaschinen
US3165905A (en) * 1962-08-15 1965-01-19 Trane Co Refrigerating machine including an economizer
JPH06257890A (ja) * 1993-03-04 1994-09-16 Nkk Corp ヒートポンプ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3665724A (en) 1970-07-13 1972-05-30 Carrier Corp Heating and cooling refrigeration apparatus
EP2016349A1 (fr) 2006-04-04 2009-01-21 Efficient Energy GmbH Pompe a chaleur
EP2281155A1 (fr) 2008-04-01 2011-02-09 Efficient Energy GmbH Pompe à chaleur agencée verticalement et procédé de fabrication de cette pompe à chaleur agencée verticalement
WO2013125215A1 (fr) * 2012-02-23 2013-08-29 川崎重工業株式会社 Machine de réfrigération

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GB2579928A (en) 2020-07-08
GB202002457D0 (en) 2020-04-08
DE102017215198A1 (de) 2019-02-28
GB2579928B (en) 2022-03-30

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