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
  • 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
  • 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
  • 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
  • F25B13/00—Compression machines, plants or systems, with reversible cycle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
  • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
  • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
• • 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
  • F25B2400/13—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
  • 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
  • F25B2400/23—Separators

Definitions

• the invention relates to a heat pump device according to the preamble of patent claim 1.
• a heat pump device of the type mentioned is known from JP 2001 153482 A.
• This consists inter alia of a compressor (in particular screw compressor), which is followed by a condenser (also called a condenser), in turn, a refrigerant collector (also called refrigerant tank) is connected downstream.
• the refrigerant collector is connected to the intermediate injection of refrigerant into the compressor with this via a refrigerant line.
• the refrigerant collector nachge ⁇ a controllable expansion valve, which in turn is followed by an evaporator, in turn, the already mentioned compressor is connected downstream.
• the refrigerant circuit of JP 2001 153482 A therefore corresponds ei ⁇ nem very classic refrigeration cycle, but added to the refrigerant collector for intermediate injection of refrigerant in the compressor.
• the invention has for its object to further improve a politicianspumpenvor ⁇ direction of the type mentioned.
• the limits of use or the efficiency of such a heat pump device should be even more expanded or increased.
• a controllable expansion valve is arranged and that the refrigerant line depending on the setting of the expansion valve during the loading ⁇ operation of the heat pump device above and / or below the refrigerant level ausmündende Has refrigerant inlet.
• the heat ⁇ pump device is characterized in particular by the fact that can be adjusted via the expansion valve, the refrigerant level in the refrigerant collector, wherein the refrigerant inflow opening is formed so that it depending on the setting of the expansion ⁇ onsventils either above and / or below the refrigerant ⁇ tel mirror is formed ausmündend.
• the proviso "and / or” means that the refrigerant line is formed with its cold ⁇ medium inflow either either so that the refrigerant inflow either opens above or below the refrigerant level, or that the refrigerant additive Flow opening is formed so that it opens both above and below the refrigerant level, which incheswei ⁇ se may be realized by a correspondingly large refrigerant inlet or by a plurality of refrigerant inflow at the guided into the refrigerant collector refrigerant line.
• the heat pump device In contrast to the heat pump device mentioned above, it is thus possible in the heat pump device according to the invention to supply optionally pure refrigerant vapor, liquid refrigerant or even refrigerant wet steam to the compressor.
• state of aggregation the refrigerant is injected into the compressor can be determined via the controllable Ex ⁇ expansion valve and thus on the refrigerant level in the cold ⁇ means collector.
• liquid refrigerant offers, as mentioned above, the ability to cool the compressor to lower the hot gas ⁇ temperature and thus expand the limits of use.
• a heat pump device in which a comparatively small part of the refrigerant coming from the condenser is branched off and led to the decoupling voltage via a controllable expansion valve to which a heat exchanger (so-called economizer) is connected downstream to transfer heat between the small, already relaxed some of the refrigerant and the rest of kom from the condenser ⁇ Menden refrigerant.
• a heat exchanger so-called economizer
• the expanded refrigerant can be injected to the compressor, wherein festle ⁇ gene can be over the setting of the expansion valve, which physical state (liquid, vapor or wet vapor) has the injected refrigerant.
• Ver ⁇ equal to the described inventive solution in comparison to the refrigerant collector
• harnesseconomiser is required in the solution according to EP 1965154 Bl.
• FIG. 1 is a basic embodiment of the invention
• FIG 2 is an enlarged view of the refrigerant collector according to Figure 1;
• Figure 3 shows the embodiment of Figure 1 with a
• Figure 4 shows an embodiment with a Sauggastagetau ⁇ shear in the refrigerant collector and a 4/2-Wegeum- switching valve
• FIG 5 is an enlarged view of the refrigerant collector according to Figure 4.
• FIG. 6 shows a heat pump device according to the prior art
• the heat pump devices shown in Figures 1, 3, 4 and 6 consist in a known manner from a compressor 1, in particular a so-called screw or Scrollverdich- ter, which is followed by a condenser 2, which is particularly preferably designed as a plate capacitor.
• This condenser is a refrigerant collector 3 (also called high pressure collector) downstream, which is connected to the intermediate injection of refrigerant in the compressor 1 with this via a refrigerant line 4 ⁇ .
• this intermediate injection serves the purpose of improving the efficiency of the heat pump device. tion or to expand the application limits of the heat pump device.
• the refrigerant collector 3 is shown enlarged for better understanding.
• a From ⁇ section 7 of the refrigerant pipe 4 in the refrigerant collector 3 is arranged.
• the refrigerant inflow opening (s) 6 is (are) arranged on the section 7 of the refrigerant line 4.
• the section 7 is tubular and in particular formed as a U-shaped piece of pipe.
• the section 7 also has a vertical extension direction and an open line end 8.
• the ⁇ of fene conduit end 8 forming at least one of the Kälteschzu ⁇ flow openings 6 and is preferably always located, during operation of the heat pump apparatus of the above refrigerant Spie ⁇ gels.
• a plurality of superimposed refrigerant ⁇ inlet openings 6 are provided at section 7.
• the refrigerant collector 3 connected to the expansion valve 5, during the operation of the heat pump ⁇ device opening below the refrigerant level Refrigerant supply port 9 has.
• the refrigerant enters the Kältemit ⁇ telsammler 3.
• the refrigerant collector 3 a 10 ver ⁇ -bound to a second electronically controllable (and reversible working) expansion valve, during operation of the heat pump apparatus below the refrigerant level opening out refrigerant discharge ⁇ connection 11 has.
• this refrigerant discharge port 11 the refrigerant to the second expansion valve 10 is consider ⁇ leads.
• This liquid refrigerant mixes it with the incoming through the üb ⁇ membered refrigerant inflow opening 6 refrigerant vapor into a refrigerant wet steam. Finally, to flood the refrigerant receiver 3 completely, so adjust such a refrigerant level in which all the refrigerant inflow ports ⁇ 6 are positioned in the liquid refrigerant, it would be at the compressor to a fully liquid intermediate Injection, which, as explained, especially desirable ⁇ is worth if you want to cool the compressor.
• a further preferred feature of the invention Lö ⁇ solution consists again with reference to Figures 2 and 5 in that the refrigerant collector exhibiting 3 by at least one through opening 12, in particular oriented vertically arranged partition member 13 and the partition wall (preferably a perforated plate, metal mesh or the like) is formed divided into a first and a second chamber 14, 15, wherein in the first chamber 14, the refrigerant supply port 9 opens and wherein the first chamber 14 of the refrigerant discharge port 11 goes off.
• the flow in the first chamber 14 is highly turbulent.
• the proviso of the separating element 13 leads to a calming of the refrigerant in the second chamber 15, in which the portion 7 of the refrigerant line 4 is arranged, which in turn is favorable for the desired precise adjustment of the ratio zwi ⁇ 's liquid and vapor refrigerant.
• the refrigerant collector 3 a two ⁇ tes electronically controllable expansion valve 10 nachgeschal ⁇ tet which is in turn connected to an evaporator 16 to the compressor 1 (in particular finned evaporator) connected downstream.
• a further specifics ⁇ derheit the solution according to the invention is that a refrigerant-carrying and heat-exchanging with the refrigerant in the refrigerant collector 3 line 17 is disposed in the first chamber 14 of the refrigerant receiver 3, the one hand to the volatilization ⁇ fer 16 and on the other hand connected to the compressor 1. This line 17 forms together with the refrigerant collector.
• a (preferably bi-directional) filter 18 also called Fil ⁇ tertrockner
• a (preferably bidirectionally operating) filter 19 is also between the second expansion valve 10 and the evaporator 16 is arranged.
• gaseous refrigerant is brought to a higher pressure level via the compressor 1, supplied to the condenser 2 via the 4/2-way switching valve, where it is completely condensed and undercooled.
• the liquid Käl ⁇ testoff passes through the filter 18 and then passes the ex ⁇ pansionsventil 5 in which it ge ⁇ is brought to a lower pressure level. In this case, a part of the refrigerant passes into the gas ⁇ shaped state.
• the refrigerant is then fed to the cold ⁇ means collector 3, which is divided into two areas.
• the refrigerant supply port 9 of the Kälteschsamm ⁇ toddlers 3 the refrigerant is very turbulent due to the high speed Strömungsge ⁇ .
• the refrigerant flows via passage opening 12 flows to the separator 13 (see Figure 2) in the traffic area of the coolant collector 3 (chamber 15), where the liquid portion due to gravity un ⁇ th settles.
• the refrigerant inflow opening 6 which ends in the upper region of the coolant collector 3, exclu ⁇ Lich gaseous refrigerant is sucked in and the insects ⁇ spraying of the compressor 1 is supplied.
• the liquid Kältemit ⁇ tel is supplied to the expansion valve 10, via which the pressure on evaporation pressure level is reduced. A part of the refrigerant ⁇ means goes over it in the gaseous state.
• the refrigerant enters the evaporator 16, where it is completely evaporated and overheated.
• the refrigerant is finally fed to the compressor 1 via the 4/2-way switching valve. The cycle closes.
• the solution according to FIG. 4 differs finally from that according to FIG. 3 in that there takes place a heat transfer from the warmer refrigerant in the refrigerant collector 3 to the colder refrigerant in the coil via a pipe coil (line 17) (keyword: suction gas superheating).
• line 17 keyword: suction gas superheating
• the gaseous portion of the refrigerant in the refrigerant ⁇ collector partially or completely condensed, whereby the ratio of liquid to gas increases.
• the line 17 ver ⁇ runs from the evaporator 16 via the 4/2-way valve to the first chamber 14 and from there directly to the compressor first

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• 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)
• Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Priority Applications (4)

Applications Claiming Priority (2)

Publications (2)

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ID=47826781

Family Applications (1)

Country Status (6)

Cited By (1)

Families Citing this family (2)

Citations (5)

Family Cites Families (3)

• 2012
  • 2012-02-09 DE DE102012101041A patent/DE102012101041A1/de not_active Withdrawn
• 2013
  • 2013-01-30 PL PL13707538T patent/PL2812638T3/pl unknown
  • 2013-01-30 EP EP13707538.8A patent/EP2812638B1/de active Active
  • 2013-01-30 WO PCT/DE2013/100033 patent/WO2013117187A2/de not_active Ceased
  • 2013-01-30 ES ES13707538.8T patent/ES2669223T3/es active Active
  • 2013-01-30 DK DK13707538.8T patent/DK2812638T3/da active

Patent Citations (5)

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