EP0299947A1 - Wärmepumpe - Google Patents

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Publication number
EP0299947A1
EP0299947A1 EP88890129A EP88890129A EP0299947A1 EP 0299947 A1 EP0299947 A1 EP 0299947A1 EP 88890129 A EP88890129 A EP 88890129A EP 88890129 A EP88890129 A EP 88890129A EP 0299947 A1 EP0299947 A1 EP 0299947A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
oil
evaporator
heat pump
expansion valve
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.)
Withdrawn
Application number
EP88890129A
Other languages
German (de)
English (en)
French (fr)
Inventor
Karl Steinkellner
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0299947A1 publication Critical patent/EP0299947A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements

Definitions

  • the invention relates to a heat pump with a refrigerant circuit running via a compressor, a condenser, an expansion valve and an evaporator, the evaporator being arranged essentially vertically and consisting of a preferably underground pipeline forming a downward and then an upward leading refrigerant line .
  • the invention is therefore based on the object of eliminating these deficiencies and creating a heat pump of the type described at the outset which, even with the use of vertical evaporators of the largest dimensions, ensures a trouble-free, functionally reliable operation in a rational manner.
  • the invention solves this problem in that at least one oil separator is integrated in the upward leading refrigerant line of the evaporator, which has a deflection point located above an oil collector with a passage for the refrigerant which is dependent on the fill level of the oil collector.
  • These oil separators allow the separated or separated oil droplets to be taken along in stages so that the oil remains in the evaporator and the associated dangers are eliminated.
  • the oil is carried along with the refrigerant vapor from the oil separator to the oil separator, excess oil being collected in the respective oil separators after the corresponding height differences have been overcome and then conveyed on step by step.
  • the oil separator can be designed in any suitable manner per se, but there is a particularly expedient construction if the oil separator consists of an intermediate floor of the pipeline which forms a raised axial overflow nozzle and an overflow nozzle which overlaps with its edge to below that Extending deflection hood exists. With simple structural measures, it comes through the intermediate floor and the deflection hood to the oil collector and the deflection point, the remaining clear cross-section between the hood edge and the oil collecting at the intermediate floor determining the respective passage for the refrigerant flow and influencing the entrainment of the precipitated oil droplets by the refrigerant flow.
  • the refrigerant circuit can be controlled from the outset in such a way that proper flow through the evaporator is ensured without major fluctuations in the oil content in the refrigerant flow at the evaporator outlet.
  • a heat pump 1 using the geothermal heat essentially comprises at least one compressor 2, a condenser 3, an expansion valve 4 and one or more evaporators 5, a ring line 6 permitting a self-contained refrigerant circuit.
  • the evaporation heat absorbed by the evaporating refrigerant directly from the bottom in the evaporator 5 is pumped up by the compressor 2 and is released as condensation heat in condenser 3 by the condensing refrigerant via a heat exchanger 3a to a consumer (not shown).
  • the refrigerant condensate then passes through a collector 7 and a refrigerant dryer 8 to the expansion valve 4, in which it is expanded, and then flows back to the evaporator 5.
  • lubricant enters the refrigerant circuit, which is separated from the refrigerant shortly after the compressor 2 by an oil separator 9 and is returned to the compressor 2 via an oil expansion tank 10.
  • oil separator 9 Due to the necessary lubrication of the compressor 2, lubricant enters the refrigerant circuit, which is separated from the refrigerant shortly after the compressor 2 by an oil separator 9 and is returned to the compressor 2 via an oil expansion tank 10.
  • oil separator 9 Due to the necessary lubrication of the compressor 2, lubricant enters the refrigerant circuit, which is separated from the refrigerant shortly after the compressor 2 by an oil separator 9 and is returned to the compressor 2 via an oil expansion tank 10.
  • oil separator 9 Due to the necessary lubrication of the compressor 2, lubricant enters the refrigerant circuit, which is separated from the refrigerant shortly after the compressor 2 by an oil separator 9 and is returned to the compressor 2 via an oil expansion tank 10.
  • oil or lubricant components make up the entire refriger
  • the evaporator 5 is arranged vertically and essentially consists of a U-shaped pipeline 11, which has a leg leading a downward refrigerant train 11a and the other Leg forms an upward leading refrigerant cable 11b. Since the specific evaporates when the refrigerant evaporates Volume changes, the cross section of the upward refrigerant line 11b is correspondingly larger than that of the downward refrigerant line 11a, so that the flow conditions are adapted to the changes in state of the refrigerant.
  • the oil separators 12 consist of an intermediate floor 13 of the pipeline 11, which forms a raised axial overflow nozzle 13a and serves as an oil collector 13b in the circumferential area around this nozzle 13a together with the wall of the pipeline 11.
  • the overflow nozzle 13a is covered by a deflection hood 14, which extends with its edge 14a to below the outlet mouth of the nozzle 13a and results in a deflection point for the refrigerant which causes the oil to fail.
  • the refrigerant flowing up through the overflow nozzle 13a is deflected by the deflection hood 14 and continues to flow through the remaining space between the deflection hood 14 and the wall of the pipeline 11.
  • an underground evaporator has already been successfully tested, which extends 60 m deep into the ground and which has an oil separator at intervals of 12 meters, which maintains the oil content in the refrigerant circuit and prevents the oil from accumulating inside the evaporator.
  • a pressure switch 15 is installed in the ring line 6 and, in order to be able to adjust the flow and pressure conditions within the evaporator 5 to the conditions favorable for oil entrainment, the expansion valve 4 is dependent on the pressure difference before and after the evaporator 5 operated.
  • other control devices and additional units for monitoring the refrigerant circuit and for improving the efficiency can also be used for the heat pump 1, and neither the evaporator 5 itself nor the oil separator 12 are restricted to special constructions.

Landscapes

  • 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-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Central Heating Systems (AREA)
EP88890129A 1987-07-15 1988-05-25 Wärmepumpe Withdrawn EP0299947A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT1787/87 1987-07-15
AT178787A AT387650B (de) 1987-07-15 1987-07-15 Waermepumpe

Publications (1)

Publication Number Publication Date
EP0299947A1 true EP0299947A1 (de) 1989-01-18

Family

ID=3520963

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88890129A Withdrawn EP0299947A1 (de) 1987-07-15 1988-05-25 Wärmepumpe

Country Status (6)

Country Link
EP (1) EP0299947A1 (fi)
JP (1) JPH02500997A (fi)
AT (1) AT387650B (fi)
FI (1) FI891164A0 (fi)
NO (1) NO891066D0 (fi)
WO (1) WO1989000666A1 (fi)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4952527A (en) * 1988-02-19 1990-08-28 Massachusetts Institute Of Technology Method of making buffer layers for III-V devices using solid phase epitaxy
MY150162A (en) * 2007-01-18 2013-12-13 Earth To Air Systems Llc Multi-faceted designs for a direct exchange geothermal heating/cooling system

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR615785A (fr) * 1926-05-07 1927-01-15 Landskrona Gjuteri Aktiebolag Perfectionnements dans les machines réfrigérantes
GB352528A (en) * 1930-04-07 1931-07-07 Lightfoot Refrigeration Compan Improvements in or relating to evaporator coils for refrigerating apparatus
GB699568A (en) * 1951-09-20 1953-11-11 Gen Electric Improvements relating to compression refrigerating systems
GB725925A (en) * 1953-11-02 1955-03-09 Svenska Turbinfab Ab Device for controlling the flow of liquid refrigerant to the compressor of a refrigerating plant
US3438218A (en) * 1967-09-13 1969-04-15 Dunham Bush Inc Refrigeration system with oil return means
US3837177A (en) * 1973-11-01 1974-09-24 Refrigeration Research Suction accumulator
US4199960A (en) * 1978-10-26 1980-04-29 Parker-Hannifin Corporation Accumulator for air conditioning systems
DE2931485A1 (de) * 1979-08-03 1981-02-05 Rudolf Oetjengerdes Verfahren und vorrichtung zum gewinnen von heiz- und gebrauchswasserwaerme mittels kaeltemittelverdampfer im erdreich, in verbindung mit einer waermepumpenanlage
BE887276A (nl) * 1981-01-29 1981-05-14 Bruyn Bernard De Warmtepomp
BE890012A (nl) * 1981-08-19 1981-12-16 Dammekens Jozef Warmtepomp of warmtegenerator
US4530219A (en) * 1984-01-30 1985-07-23 Jerry Aleksandrow Self-regulated energy saving refrigeration circuit
US4573327A (en) * 1984-09-21 1986-03-04 Robert Cochran Fluid flow control system

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4557115A (en) * 1983-05-25 1985-12-10 Mitsubishi Denki Kabushiki Kaisha Heat pump having improved compressor lubrication
SE446286B (sv) * 1984-08-27 1986-08-25 Bengt Thoren Vermepump med strypanordningar fordelade utmed forangarens ror
US4551990A (en) * 1984-10-18 1985-11-12 Honoshowsky John C Oil return apparatus for a refrigeration system

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR615785A (fr) * 1926-05-07 1927-01-15 Landskrona Gjuteri Aktiebolag Perfectionnements dans les machines réfrigérantes
GB352528A (en) * 1930-04-07 1931-07-07 Lightfoot Refrigeration Compan Improvements in or relating to evaporator coils for refrigerating apparatus
GB699568A (en) * 1951-09-20 1953-11-11 Gen Electric Improvements relating to compression refrigerating systems
GB725925A (en) * 1953-11-02 1955-03-09 Svenska Turbinfab Ab Device for controlling the flow of liquid refrigerant to the compressor of a refrigerating plant
US3438218A (en) * 1967-09-13 1969-04-15 Dunham Bush Inc Refrigeration system with oil return means
US3837177A (en) * 1973-11-01 1974-09-24 Refrigeration Research Suction accumulator
US4199960A (en) * 1978-10-26 1980-04-29 Parker-Hannifin Corporation Accumulator for air conditioning systems
DE2931485A1 (de) * 1979-08-03 1981-02-05 Rudolf Oetjengerdes Verfahren und vorrichtung zum gewinnen von heiz- und gebrauchswasserwaerme mittels kaeltemittelverdampfer im erdreich, in verbindung mit einer waermepumpenanlage
BE887276A (nl) * 1981-01-29 1981-05-14 Bruyn Bernard De Warmtepomp
BE890012A (nl) * 1981-08-19 1981-12-16 Dammekens Jozef Warmtepomp of warmtegenerator
US4530219A (en) * 1984-01-30 1985-07-23 Jerry Aleksandrow Self-regulated energy saving refrigeration circuit
US4573327A (en) * 1984-09-21 1986-03-04 Robert Cochran Fluid flow control system

Also Published As

Publication number Publication date
AT387650B (de) 1989-02-27
FI891164A (fi) 1989-03-10
NO891066L (no) 1989-03-13
FI891164A0 (fi) 1989-03-10
WO1989000666A1 (en) 1989-01-26
ATA178787A (de) 1988-07-15
NO891066D0 (no) 1989-03-13
JPH02500997A (ja) 1990-04-05

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