US3732703A - Air conditioning plant for buildings - Google Patents

Air conditioning plant for buildings Download PDF

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Publication number
US3732703A
US3732703A US00157319A US3732703DA US3732703A US 3732703 A US3732703 A US 3732703A US 00157319 A US00157319 A US 00157319A US 3732703D A US3732703D A US 3732703DA US 3732703 A US3732703 A US 3732703A
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Prior art keywords
conduit
heat exchanger
air
heat
sectors
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US00157319A
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English (en)
Inventor
L Nordstrom
A Nilsson
M Nilsson
S Persson
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Rinipa AB
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Rinipa AB
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/001—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems in which the air treatment in the central station takes place by means of a heat-pump or by means of a 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
    • F25B2347/00—Details for preventing or removing deposits or corrosion
    • F25B2347/02—Details of defrosting cycles
    • F25B2347/021—Alternate defrosting
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/56—Heat recovery units

Definitions

  • This heat content may be tranferred back to the inlet air conduit by means of a heat pump having at least one heat exchanger in each conduit.
  • a major problem in an installation of that type is the need for defrosting the evaporating heat exchangers in the exhaust conduit.
  • This problem is solved by providing two heat exchanges in parallel in the exhaust conduit and arranged in such a manner that they will become operative alternately, one serving as evaporator, while the other is being defrosted.
  • the function of the two types of heat exchangers may be switched, whereby the exchanger in the inlet conduit, instead of working as a condensor, will serve as an evaporator, thereby to cool the incoming air.
  • the present invention relates to an air conditioning plant for buildings.
  • air-borne heat where the air is heated by means of a heat pump, it is possible to provide the desirable heating and ventilating in an easy and economic manner.
  • a very rapid adjustment of the temperature is obtained, and the inclusion of a heat pump means that a high rate of ventilation may be maintained without the use of the unreasonably large heat exchanger surfaces, which otherwise would have been necessary to obtain a high efficiency.
  • a heat pump is used for heating the air, it is possible, by simple means, and at a comparatively low cost to convert the plant to air-cooling purposes in order to obtain a satis factory indoor temperature during the summer.
  • the invention is applicable to a plant in which a first conduit conveys air to the building and a second conduit conveys at least a major part of the air to the building therefrom, and is characterized in a heat pump working with an evaporating fluid and comprising a compressor and at least one first heat exchanger operable as a condensor in connection with the first, inlet air conduit as well as at least two heat exchangers operable as evaporators in connection to the second exhaust conduit, and means alternately to bring the evaporating heat exchangers operable in connection with the exhaust conduit into and out of operation in step with the requirements for defrosting.
  • FIG. 1 shows schematically a first embodiment of the invention
  • FIG. 1 schematically shows the arrangement of an air conditioning plant for a building. Air is supplied to the building by way of a first conduit 12, and the major part of the air is evacuated from the building by way of a second conduit 16.
  • the conduit 16 is divided into two branch conduits 16a and 16b, respectively.
  • the air supplied to the building is heated in a heat exchanger 21 located in conduit 12, and this heat is largely extracted from the out-going air by means of heat exchangers a and 20b fitted into the exhaust branch conduits 16a and 16b.
  • These three heat exchangers form part of a heat pump working according to known principles, and on this occasion operating with an easily evaporable fluid, such as freon, or any similar fluid well known in connection with refrigerators.
  • This heat pump comprises a compressor 19 driven in any suitable manner and provided with governing means of known type including throttling valves 22a and 22b.
  • the pump draws fluid from the heat exchangers 200 or 20b, thereby cooling the out-going air, compresses the vapor and delivers it to heat exchanger 21, where it is condensed, thereby heating the in-coming air.
  • the heat exchanger further includes a main recipient 8 for the heat transferring fluid.
  • Each branch conduit 16a and 16b is provided with a butterfly valve 7a and 7b, respectively, and in the conduit from the recipient 8 to these heat exchangers there is a shut-off valve 6a and 6b, respectively.
  • the exhaust air butterfly valve 7a is open, which means that exchanger 20a is in operation, while exchanger 20b is being defrosted.
  • Fluid valve 60 is open and fluid valve 6b closed.
  • Defrosting is brought about by vapor, bled off by way of a conduit 5 from the high pressure side of the compressor 19 being transferred to the exchanger about to be defrosted.
  • a valve 4a and 4b to govern the flow of this defrosting vapor to the appropriate exchanger 20a or 20b, respectively.
  • the defrosting vapor becomes condensed in the heat exchanger and is, by way of a non return valve 3a and 3b, respectively, transferred to an auxiliary recipient 2a and 2b, respectively.
  • the latter is, by way of a shut-off valve a and 100b, respectively, as well as further non-return valves 101a and 101b connected to the inlet end of the heat exchanger.
  • a main shut-off valve 102a and 102b respectively, which is by passed by a branch conduit including a throttling member 103a and 10312 and an auxiliary shut-off valve 104a and b 1041; respectively.
  • valve 4b is open so high pressure vapor can pass through the heat exchanger thereby to melt the ice.
  • the water thus obtained may be conducted away by a drain l05b. While melting the ice the vapor is condensed in the heat exchanger and the fluid is collected in the auxiliary recipient 2b. Valves 100b, 102b and l03b are closed during this part of the operation.
  • valve 4b In order to bring this exchanger into operating condition, i.e., to bring the pressure and the temperature thereof to the same level as in exchanger 20a, which is about to be defrosted, valve 4b is closed and valves 100b and l03b are opened. Fluid can then pass from the auxiliary recipient to the inlet of the exchanger. While passing through the exchanger the fluid is evaporated, as the exchanger surfaces will reach room temperature a'short time after the ice has melted away. This arrangement is done in order to prevent liquid fluid from being drawn from the auxiliary recipient to the compressor, which would imply an apparent risk of damage.
  • valve 102b When the recipient is almost emptied the exchanger is ready for operation and valve 102b, as well as butterfly valve 7b in the exhaust air conduit may be opened. Simultaneously, butterfly valve 7a is closed, and as soon as the auxiliary recipient is completely empty valve 6b is opened to permit supply of fluid directly from the main recipient.
  • valve 6a pertaining to exchanger 200 has, of course, been closed and valve 4a opened so the defrosting of exchanger 20a can proceed as above described in connection with exchanger 10b.
  • the operation of the various valves may be brought about automatically by arbitrary means known in the art, and the time for starting the switching-over operation may be determined by means sensitive to the increasing pressure at the exchangers 20a and 20b, respectively, which is caused by a growing ice cover on the heat exchanger surfaces.
  • the plant above described is used to heat the incoming air. During the summertime it may be desirable instead to cool the air, and this can be arranged in a simple manner, basically by changing the direction of flow of the fluid. Evaporation will then occur in heat exchanger 21 and condensation in one of the exchangers 20a or 20b, respectively.
  • the supply from the compressor 19 to the heat exchanger 21, which during this working condition is serving as an evaporator, is shut of by means ofa valve 106.
  • the compressor 19 thus delivers the fluid via conduit 5 to one or both of heat exchangers a and 20b, which are serving as condensors and give off heat to the outlet air in conduits 16a and 1617.
  • the media is transferred from the condensors 20a and 20b to the recipients 2a and 2b respectively, and as the valves 100a and 100k respectively are closed, the fluid via conduits 107a and 107b respectively will be fed to the evaporating heat exchanger 21, which cools down the in-coming air flowing through conduit 12.
  • the valves 108a and 108b are open as well as a valve 109 provided in a by-pass-conduit 110, which connects the evaporator 21 with the suction side of the compressor 19.
  • valves 60, 6b, 102a, 102b, 104a, 104b, 100a and l00b are closed.
  • a building may include compartments of two basic types.
  • An ordinary appartment house first of all includes appartment, in which it is desirable to adjust the temperature individually in each room, and secondly sections, such as staircases, cellars and other common compartments, wherein a predetermined temperature is maintained In all these compartments a continous exchange of air is desirable.
  • FIG. 2 a building is schematically shown as a rectangular frame divided into three compartments, of which outer ones 10, are intended to denote apartments and each may include a number of rooms, each being provided with a mixing box of the type to be described below, as well as an intermediate compartment 11, which likewise may include a number of spaces such as cellars, a staircase and other common spaces, in which the requirements for adjustment of the temperature are not so great.
  • the plant comprises an air inlet conduit 12 provided with a fan 13, which draws in air from the atmosphere to the system.
  • the in-coming air is divided between two branch conduits I4 and IS.
  • the first mentioned conduit communicates with the compartments of type 10, as well as with compartments of type 11, while branch conduit 15 communicates with compartments of type 10 only.
  • the air is evacuated from the building by means of an exhaust conduit 16 provided with a fan 17. Branches 16a from the exhaust conduit reach into all compartments within the building, and the total amount of air supplied to the building will be evacuated through this conduit.
  • a counterflow heat exchanger 18 is mounted in the exhaust conduit, and the inlet branch conduit 15 is led through this heat exchanger.
  • This branch conduit basically conveys unheated air to the compartments for mixing with the heated air in the appartment in the manner to be described below.
  • this part of the air is slightly heated in heat exchanger 18.
  • This heating may be already effected at the still undivided air inlet conduit 12, whereby the amount of condensing in the heat exchanger proper is diminished.
  • the main heating of the air occurs in a heat pump 9, which in a well known manner, consists of a compressor 19, a first heat exchanger 20 located in the exhaust conduit 16, downstream of counterflow heat exchanger 18, and a second heat exchanger 21 located in the inlet branch conduit 14.
  • a throttling valve 22 for governing the flow of the heat transfer fluid.
  • the heat pump operates with an evaporating fluid of the type used in refrigerators, such as freon. This fluid is evaporated in exchanger 20, compressed in compressor 19 and condensed in exchanger 21, thereby heating the air flowing through branch conduit 14.
  • a branch 14a from this conduit is united with a branch 15a from the other air inlet branch conduit 15 in a mixing box 23 within each room of the compartments, in which it is desirable to adjust the temperature.
  • the amount of air passing through the inlet branch conduits is constant, and the temperature may be adjusted according to the occasional need.
  • a heat pump 9 of the above indicated type is that it is necessary occasionally to defrost the heat exchanger surfaces. It is, however, preferable to be able to provide a continous defrosting, partly in order to be able to withdraw as much as possible of the available heat content from the evacuated air without diminishing the heat transfer in the evaporator, and partly in order to prevent variations in the temperature of the in-coming air, when the heat exchanger is closed down for defrosting.
  • a continously working heat pump may, according to a development of the invention, be designed in such a manner that the heat exchangers 20 and 21 form parts of a rotating heat exchanger unit in which valves governing the supply and the withdrawal of heat transfer fluid are operated electrically, mechanically, pneumatically or hydraulically from the rotating unit.
  • FIGS. 3 A preferred embodiment of a rotating heat exchanger 9 is shown in FIGS. 3 5.
  • the in-coming air from branch conduit 14 passes the heat exchanger unit from below and upwards by way of an internal rotating distributor housing 25, while the evacuated air from conduit 16 passes the unit from above and downwards by way of an outer circular housing 26.
  • the heat exchanges are formed into a cylindrical drum 27, which is subdivided into a number of sector-shaped heat exchanger packages.
  • FIG. 4 shows 12 such sectors.
  • Each of these may include a number of pipe coils provided with external flanges.
  • Each package may work as a con denser and as an evaporator.
  • the coils are schematically indicated only and they will, on different occasions, be supplied with fluid from the high pressure side of the compressor, or deliver fluid to the low pressure side thereof, respectively.
  • the heat exchanger surfaces are stationary, whereas the inner housing for the in-coming air rotates and thereby evenly distributes the in-coming, as well as theout-going air over the heat exchanger packages.
  • the inner housing is, as is best shown in FIG. 5, provided with two radially extending, cowl-shaped arms, the downwardly open faces of which each has the same size as two sectors.
  • the in-coming and the out-going air will, in this manner, be evenly distributed over the front area of the heat exchanger unit.
  • two diametrically opposite exchanger packages always have the same function.
  • the top and the bottom portions of the outer and of the inner housing are mutually alike, and the top and bottom portions of the inner housing rotate synchronously.
  • the inner housing is provided with cover plates 28, which will extend over the sections about to switch from one function to the other.
  • the valves for switching from the high to the low pressure side are governed from the rotating part by mechanical, electrical, hydraulic or pneumatic means.
  • Throttling conduits 45 48 between the condensors and evaporators are schematically shown in the core of the heat exchanger drum. Each condensor will always supply the same evaporator with fluid. Possible throttling occurs in both directions whereby the number of connections may be reduced. The number of heat exchanger packages shall be sufficient to prevent detrimental influences in connection with the switching over of the valves.
  • the heat exchanger unit shown in FIG. 3 consists, as above mentioned, of twelve sectors, 31 42.
  • the rotating housing is provided with four cover plates 28.
  • the diametrically opposite sectors 31 and 32, as well as 37 and 38, operate in the position illustrated as evaporators, while sectors 34, 35 and 40, 41, respectively, operate as condensors.
  • Sectors 33, 36, 39 and 42 are simultaneously covered by the rotating plates 28.
  • the high pressure side of the compressor is, by way of a first annular conduit 43 encircling the unit, connected to every one of the sectors, and in the same manner the low pressure side of the compressor, by way of a second annular conduit 44, is connected to every sector.
  • branch conduits each of which is provided with a valve, governed by the rotating housing 25 in the manner indicated above.
  • FlG. 3 shows how, on the occasion illustrated, sectors 34, 35 and 40, 41 by way of valves 34H, 35H, 401-1 and 4111, respectively, are connected to annular conduit 43, while simultaneously sectors 31, 32, 37 and 38 by way of valves 31L, 32L, 37L and 38L, respectively, are connected to annular conduit 44.
  • Low pressure valves 36L and 42L are also open to drain the pertaining sectors 36 and 42.
  • the coil of sector 40 connected to annular conduit 43 is shown in full lines, as is a coil 51 in sector 37 connected to annular conduit 44.
  • These two coils are interconnected and in a similar manner high pressure vapor from the compressor will be conveyed to sectors 34, 35, 40 and 41 wherein it is condensed, whereupon the condensate is transferred to the pertaining sectors serving as evaporators.
  • Each sector will, in this manner, always supply the same sector with fluid.
  • the connecting conduits, which are operative in the present occasion, are shown in full lines, while the inoperative conduits are shown in dash lines.
  • Condensed fluid from sector 34 is thus by way of con duit 45 within the core transferred to sector 31, while condensed fluid from sector 35 by way of conduit 46 is transferred to sector 32.
  • sector 40 is connected to sector 37 by way of conduit 47, and sector 41 is connected to sector 38 by a further conduit 48.
  • a draining by opening two valves 36L and 42L, as the pertaining sectors 36 and 42, respectively, is each connected to one of the further covered sectors, viz 33 and 39.
  • coil 52 at sector 40 which is connected to annular conduit 44 and in turn is connected to a corresponding coil, not shown, in sector 31 is denoted by dash lines.
  • coil 53 at sector 37 which communicates with a coil, not shown, at sector 34 is denoted by dash lines.
  • Both coils at every sector may be interconnected at their inner or outer ends, respectively, but it is evident that it, in practice, may be necessary to provide a number of such coils in order to obtain the required heat exchange surface.
  • the number of sectors will have to be suited to the size of the plant, and the heat transfer is governed in the manner common with heat pumps.
  • Conduits 45 48 with the pertaining throttling valves (not shown) which divide the coils into a high pressure side and a low pressure side, respectively, may be located outside the exchanger unit.
  • the valves denoted by H and L in the annular conduits 43 and 44 preferably are mounted at a common panel.
  • An air conditioning plant for a building in which a first conduit conveys air to the building and a second conduit conveys at least a major part of the air supplied to the building therefrom, the improvement of a heat pump operating with an evaporating fluid, said pump comprising a compressor, at least one first heat exchanger operable as a condenser in connection with the first conduit, at least one heat exchanger operable as an evaporator in connection with the second conduit, and the evaporating and the condensing heat exchangers being formed into a cylindrical, rotating unit working on the general principle of a rotating regenerative heat exchanger, whereby said exchangers will switch position as well as function.
  • the exchanger unit comprises a stationary outer, cylindrical housing for the second conduit, an inner, rotatable housing subdivided into sectors, for the first conduit, and an intermediate, stationary cylindrical drum divided into a number of sector-shaped heat exchanger packages each designed to operate alternately as a condensor or as an evaporator.
  • An air conditioning plant for use in a building including compartments of two basic types having different requirements for heating, including a first conduit for conveying air to the building and a second conduit for conveying at least a major part of the air supplied to the building therefrom, the improvement of a heat pump operating with an evaporating fluid, said pump comprising a compressor, at least one first heat exchanger operable as a condenser in connection with the first conduit, at least one heat exchanger operable as an evaporator in connection with second conduit, said first conduit being divided into two branch conduits of which a first one is further subdivided into two branches to communicate with both types of compartments, the second branch conduit being connected to one of the types of compartments only, the second conduit evacuating both types of compartments having a first condensing heat exchanger in the first inlet branch conduit and a second evaporating heat exchanger in the second conduit, a branch from the second inlet branch conduit being united with a branch from the first branch conduit through a mixing box at the pertaining type of

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US00157319A 1970-06-29 1971-06-28 Air conditioning plant for buildings Expired - Lifetime US3732703A (en)

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Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2552459A1 (de) * 1974-11-28 1976-06-10 Schramel Dieter Mehrphasen-waermepumpenanlagen, insbesondere wasserkraft-waermepumpwerke und fern-waermepumpwerke
FR2336643A1 (fr) * 1975-12-22 1977-07-22 Atomenergi Ab Installation de transfert de chaleur entre une sortie et une entree d'air
US4123002A (en) * 1975-12-30 1978-10-31 Saunders Norman B Heating and ventilation system
US4182403A (en) * 1975-12-22 1980-01-08 Aktiebolaget Atomenergi Arrangement for transferring heat from the exhaust air leaving an enclosed volume to the input air supplied to said volume
US4205456A (en) * 1976-04-30 1980-06-03 Westinghouse Electric Corp. Heat pump arrangement and method for material drying system
US4232821A (en) * 1977-05-06 1980-11-11 Backlund Anders Daniel Heating and ventilation system
WO1981000147A1 (fr) * 1979-07-02 1981-01-22 Regenerator Corp Systeme de reduction d'oxygene et appareil de condensation avec degel automatique
US4313307A (en) * 1977-09-12 1982-02-02 Electric Power Research Institute, Inc. Heating and cooling system and method
US4316363A (en) * 1979-05-12 1982-02-23 Mckirdy Ian D Temperature control system
US4365480A (en) * 1978-09-05 1982-12-28 United Air Specialists, Inc. Process gas treating apparatus
US4928498A (en) * 1985-11-08 1990-05-29 Ewald Gossler Method and device for compression of gases
AT400972B (de) * 1985-11-08 1996-05-28 Gossler Ewald Verfahren und vorrichtung zum verdichten von gasen
US5771699A (en) * 1996-10-02 1998-06-30 Ponder; Henderson F. Three coil electric heat pump
US5839292A (en) * 1996-08-31 1998-11-24 Lg Electronics, Inc. Defroster for heat pump
US6626237B2 (en) * 2000-02-01 2003-09-30 Wartsila Technology Oy Ab Heat recovery apparatus and method of minimizing fouling in a heat recovery apparatus
US20150082824A1 (en) * 2013-09-24 2015-03-26 Walter Stark Low temperature cooling and dehumidification device with reversing airflow defrost for applications where cooling coil inlet air is above freezing
US9857123B2 (en) 2015-08-06 2018-01-02 John D. Mclaughlin System and method for defrosting a condensor without external heating
EP3453980A3 (fr) * 2017-08-14 2019-06-19 Ika-Air Oy Radiateur d'échangeur de chaleur, agencement de ventilation de bâtiment et procédé d'utilisation d'agencement de ventilation de bâtiment
US11867424B1 (en) 2020-03-05 2024-01-09 Apple Inc. Thermal control system

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Publication number Priority date Publication date Assignee Title
EP3086045A1 (fr) * 2015-04-24 2016-10-26 Zoppellaro S.r.l. Appareil et procédé de traitement d'air

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US3060698A (en) * 1961-07-06 1962-10-30 John V Felter Heat pump and method of operation
US3537274A (en) * 1968-10-18 1970-11-03 Alco Controls Corp Dual evaporator refrigeration system
US3572052A (en) * 1969-05-15 1971-03-23 Streater Ind Inc Ducted refrigeration unit

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US2496143A (en) * 1943-01-26 1950-01-31 Electrolux Ab Refrigeration apparatus
US2481348A (en) * 1946-08-21 1949-09-06 Trane Co Air-conditioning apparatus with defrosting means
US2581744A (en) * 1949-06-02 1952-01-08 William G Zimmerman Heating and cooling air conditioning system
US2763132A (en) * 1953-08-31 1956-09-18 Lawrence S Jue Dehumidifying apparatus
US2928255A (en) * 1957-04-04 1960-03-15 Borg Warner Heat pump systems
US2907178A (en) * 1957-10-04 1959-10-06 Borg Warner Air conditioning systems
US2978877A (en) * 1958-08-04 1961-04-11 Vilter Mfg Co Hot gas defrosting system with gravity liquid return for refrigeration systems
US2998710A (en) * 1959-06-05 1961-09-05 Melvin C Reese Heat pump
US3060698A (en) * 1961-07-06 1962-10-30 John V Felter Heat pump and method of operation
US3537274A (en) * 1968-10-18 1970-11-03 Alco Controls Corp Dual evaporator refrigeration system
US3572052A (en) * 1969-05-15 1971-03-23 Streater Ind Inc Ducted refrigeration unit

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2552459A1 (de) * 1974-11-28 1976-06-10 Schramel Dieter Mehrphasen-waermepumpenanlagen, insbesondere wasserkraft-waermepumpwerke und fern-waermepumpwerke
FR2336643A1 (fr) * 1975-12-22 1977-07-22 Atomenergi Ab Installation de transfert de chaleur entre une sortie et une entree d'air
US4119142A (en) * 1975-12-22 1978-10-10 Aktiebolaget Atomenergi Arrangement for transferring heat from the exhaust air leaving an enclosed volume to the input air supplied to said volume
US4182403A (en) * 1975-12-22 1980-01-08 Aktiebolaget Atomenergi Arrangement for transferring heat from the exhaust air leaving an enclosed volume to the input air supplied to said volume
US4123002A (en) * 1975-12-30 1978-10-31 Saunders Norman B Heating and ventilation system
US4205456A (en) * 1976-04-30 1980-06-03 Westinghouse Electric Corp. Heat pump arrangement and method for material drying system
US4232821A (en) * 1977-05-06 1980-11-11 Backlund Anders Daniel Heating and ventilation system
US4313307A (en) * 1977-09-12 1982-02-02 Electric Power Research Institute, Inc. Heating and cooling system and method
US4365480A (en) * 1978-09-05 1982-12-28 United Air Specialists, Inc. Process gas treating apparatus
US4316363A (en) * 1979-05-12 1982-02-23 Mckirdy Ian D Temperature control system
WO1981000147A1 (fr) * 1979-07-02 1981-01-22 Regenerator Corp Systeme de reduction d'oxygene et appareil de condensation avec degel automatique
US4928498A (en) * 1985-11-08 1990-05-29 Ewald Gossler Method and device for compression of gases
AT400972B (de) * 1985-11-08 1996-05-28 Gossler Ewald Verfahren und vorrichtung zum verdichten von gasen
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US9200829B2 (en) * 2013-09-24 2015-12-01 Walter Stark Low temperature cooling and dehumidification device with reversing airflow defrost for applications where cooling coil inlet air is above freezing
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Also Published As

Publication number Publication date
DE2131936A1 (de) 1972-01-05
CH534333A (de) 1973-02-28
FR2099991A5 (fr) 1972-03-17

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