WO1997003326A1 - Rotating heat pump - Google Patents
Rotating heat pump Download PDFInfo
- Publication number
- WO1997003326A1 WO1997003326A1 PCT/NO1996/000180 NO9600180W WO9703326A1 WO 1997003326 A1 WO1997003326 A1 WO 1997003326A1 NO 9600180 W NO9600180 W NO 9600180W WO 9703326 A1 WO9703326 A1 WO 9703326A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- evaporator
- condenser
- heat pump
- compressor
- pump according
- Prior art date
Links
- 239000002826 coolant Substances 0.000 claims abstract description 55
- 239000007788 liquid Substances 0.000 claims abstract description 43
- 230000006835 compression Effects 0.000 claims abstract description 23
- 238000007906 compression Methods 0.000 claims abstract description 23
- 238000009833 condensation Methods 0.000 claims abstract description 14
- 230000005494 condensation Effects 0.000 claims abstract description 14
- 238000001704 evaporation Methods 0.000 claims abstract description 8
- 230000008020 evaporation Effects 0.000 claims abstract description 8
- 239000003570 air Substances 0.000 claims description 56
- 238000001816 cooling Methods 0.000 claims description 21
- 230000008878 coupling Effects 0.000 claims description 8
- 238000010168 coupling process Methods 0.000 claims description 8
- 238000005859 coupling reaction Methods 0.000 claims description 8
- 238000007789 sealing Methods 0.000 claims description 8
- 125000006850 spacer group Chemical group 0.000 claims description 7
- 239000012080 ambient air Substances 0.000 claims description 6
- 230000005672 electromagnetic field Effects 0.000 claims 1
- 238000000034 method Methods 0.000 description 9
- 230000008569 process Effects 0.000 description 8
- 239000007789 gas Substances 0.000 description 5
- 230000001105 regulatory effect Effects 0.000 description 5
- 238000009413 insulation Methods 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 3
- 230000033001 locomotion Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000005381 potential energy Methods 0.000 description 3
- 230000032258 transport Effects 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 239000001273 butane Substances 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- IJDNQMDRQITEOD-UHFFFAOYSA-N n-butane Chemical compound CCCC IJDNQMDRQITEOD-UHFFFAOYSA-N 0.000 description 2
- OFBQJSOFQDEBGM-UHFFFAOYSA-N n-pentane Natural products CCCCC OFBQJSOFQDEBGM-UHFFFAOYSA-N 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 239000004411 aluminium Substances 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000018044 dehydration Effects 0.000 description 1
- 238000006297 dehydration reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000001035 drying Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000004941 influx Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000005399 mechanical ventilation Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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
- F25B3/00—Self-contained rotary compression machines, i.e. with compressor, condenser and evaporator rotating as a single unit
Definitions
- the invention concerns a heat pump with a closed cooling medium circuit for transport of heat from one air flow to another, comprising an evaporator provided in one air flow for evaporation of a cooling medium, a compressor for compression of the vaporiform cooling medium, a condenser provided in the second air flow for condensation of the cooling medium, and a return system for condensed cooling medium from the condenser to the evaporator.
- Heat pumps for transfer of heat from one air flow to another are used, amongst other places, in houses, where heat can be transferred from air which is extracted via a ventilation system to air which is drawn in from outside to be discharged inside the house.
- heat pumps it is also possible to transfer heat from the outdoor air to the indoor air.
- Heat pumps work with a liquid cooling medium which is passed between the vapour and the liquid phase, thus permitting heat to be transferred from a colder air flow to a warmer air flow.
- Current heat pumps work well as long as the air from which the heat is taken is relatively warm, usually over 5-6°C, but the efficiency is reduced as soon as the temperature drops.
- the object of the invention is to develop completely new heat pump solutions which work efficiently at low outdoor temperatures which, e.g., occur during winter in Scandinavia, and which have a simple design which provides low manufacturing costs, a high degree of reliability and a long working life.
- the heat pumps according to the present invention consist in principle of a rotating part, a fan casing which encloses the rotating part, insulation which is placed on the outside of the fan casing in order to insulate against heat loss, the formation of condensation and noise from the rotating part, and an outer casing.
- the heat pumps according to the present invention work according to an approximate Carnot process. This is achieved by passing the cooling medium from the condensation stage to the evaporation stage through a return system which comprises one or more tubes or bores which contain separated restrictions, with the result that when the condensed medium flows through it undergoes an expansion and total or partial evaporation after it has passed the restrictions, with subsequent condensation between the restrictions.
- the restrictions are preferably in the form of plugs with grooves or holes, separated by spacers.
- the compressor works according to the liquid ring principle, but differs from standard liquid ring compressors in that the compressor housing also rotates, preferably with the same number of revolutions as the compressor's impeller, since in the present invention it is the liquid ring which transfers the motive power from the compressor housing to the compressor's impeller.
- the liquid ring compressor which is employed in the invention is preferably designed without valves, and can be designed for one stage, two or more stages. With, e.g., butane as the cooling medium it is appropriate to provide a compression in two stages.
- the working medium in the liquid ring an oil is used which does not mix with the cooling medium employed, which has greater specific weight than the cooling medium, and which has suitable viscosity at those temperature ranges in which the heat pump is working.
- the heat pump according to the present invention has a rotating compressor housing, where it is the rotation which establishes the liquid ring, thus permitting an oil with relatively high viscosity to be used as the working medium in the liquid ring without any increase in the power consumption on this account.
- the advantage of the relatively high viscosity is that a further improvement is obtained in the sealing conditions between the rotating and stationary parts in the compressor part compared to the sealing conditions in a conventional liquid ring compressor.
- the heat pump according to the present invention is best suited for small units with a heat output from 1-2 kW and up to approximately 10 kW, and is primarily intended for installation in detached houses, flats in blocks of flats, as well as shops, small business premises and industrial premises, etc., but it can also be employed in a number of other areas such as, e.g., for dehydration of air/gases, heat transfer between two air/gas flows, and, e.g., as a unit in cold-storage rooms, refrigerated display cabinets and drying rooms. They may also be used as pure air conditioning units, e.g. in shops and office premises. Since they are of a compact design, they will also cover a building's requirements for mechanical ventilation in a very economical fashion.
- the heat pumps have the same cross section regardless of size, while the length will vary depending on the size.
- the cross section will be approximately 306 x 306 mm for all types, while, e.g., the length for a 2 kW unit will be approximately 900 mm, and for a 4 kW unit approximately 1400 mm.
- Fig. la is a longitudinal section through the rotating part of the heat pump, i.e. the fan casing, insulation and outer casing are not illustrated.
- Fig. lb is a cross section A-A through the compressor part.
- Fig. lc is a cross section B-B through the compressor part.
- Fig. Id is a cross section C-C through the compressor part.
- Figs. 2a and b are a cross section through evaporator and condenser.
- Fig. 2c illustrates various alternatives for coupling inlet and outlet connectors to evaporator and condenser.
- Fig. 3 is a view of a heat pump where the movement of air over evaporator, compressor housing and condenser is illustrated.
- the rotating heat pump illustrated in fig. 1 consists of a central through-going shaft 1, driven by a motor which is not shown and which is permanently installed and forms a mounting for the evaporator part 27, the compressor part, indicated by its housing 17, and the condenser part 28.
- the compressor's impeller is mounted by ball bearings 9 on an intermediate shaft 2, thus allowing the impellers to rotate freely about the centre of the intermediate shaft.
- the number of impellers is determined by the number of compression stages to be used. In the embodiment illustrated in fig. 1 a two-stage compression is shown, with two impellers 3 A and 3B.
- the heat pump is filled with a cooling medium, which may be butane, and a working medium in the form of an oil which does not mix with the cooling medium, which has greater specific weight than the cooling medium and which has a suitable viscosity.
- a cooling medium which may be butane
- a working medium in the form of an oil which does not mix with the cooling medium, which has greater specific weight than the cooling medium and which has a suitable viscosity.
- the housing 17 rotates, drawing the working medium along in the rotation, with the result that, due to the centrifugal force, the working medium forms a liquid ring 43, which in turn draws the impellers along during the rotation.
- the impellers consist of a hub with radial wings, which together with the liquid ring will define closed spaces 44.
- the centre of the intermediate shaft 2 is displaced by a distance e from the centre of the shaft 1, and provided that the intermediate shaft 2 rotates at a different speed from the impellers 3A, 3B, the impellers will rotate eccentrically about the shaft 1 , with the result that the closed spaces 44 vary in size as the impellers rotate.
- This variation in size of the closed spaces 44 generates forces which attempt to compress cooling medium which is located in the space, while at the same time the forces also attempt to cause the intermediate shaft 2 to rotate at the same speed as the impellers, i.e. the same speed as the compressor housing and the shaft 1.
- the compressor's capacity, and thereby the heat pump's capacity by altering the intermediate shaft's speed, which will be discussed in more detail later.
- the intermediate shaft is at rest or rotates at a diffe ⁇ rent speed from the impellers.
- annular chambers 4, 5, 6 On the intermediate shaft 2, on each side of the impellers 3A, 3B, there are permanently mounted closed annular chambers 4, 5, 6 which form reservoirs for the cooling medium vapour during the compression.
- the annular chambers 4, 5, 6 are provided on each side with port openings 41, 42 which form inlets to and outlets from the individual impellers.
- Annular chamber 4 will contain cooling medium vapour with vapour pressure corresponding to the evaporator pressure
- annular chamber 5 will contain cooling medium vapour with vapour pressure which is formed after the first stage compression
- annular chamber 6 will contain cooling medium vapour with vapour pressure which is formed after the second stage compression.
- the compressed cooling medium vapour flows from annular chamber 6 through a not shown radially provided outlet to an axial bore bl in the intermediate shaft 2, through a radial bore b2 in the shaft 1, on through an axial bore in the shaft 1 and out through radial openings 45 in the shaft 1, to condensation in the condenser 28.
- seals 11 are provided between sealing surfaces on the shaft 1 and the intermediate shaft 2.
- the intermediate shaft 2 consists of an eccentric central section and a centric part at each end, mounted in ball bearings 10. At each end of the intermediate shaft 2 on the eccentric part there is a permanently mounted counterweight 7.
- the counterweight 7 balances the laterally directed forces which act on the intermediate shaft due to the eccentric rotation of the impellers.
- the annular chamber 5 has a radial tube b3 whose inlet is submerged in the liquid ring.
- oil from the liquid ring will be passed into the radial tube b3 through an axial bore b4 in the intermediate shaft 2, and on to lubrication of the ball bearings 9 and 10.
- oil from the liquid ring will be passed to the contact-free seals 11, where the oil acts as seal oil.
- the intermediate shaft 2 has an axial bore b5 which forms a passage for the through-going shaft 1.
- the contact- free seals 1 1 are produced by providing on each side of a cylindrical section on the shaft 1 which forms the inlet for the seal oil helical grooves in the shaft 1 with direction of pitch adapted to the direction of rotation. As the stationary intermediate shaft 2 and the rotating shaft 1 rotate about each other the grooves will generate a thrust which forces oil against the gas pressure against which the seal is intended to act, and together with the grooves this thrust will prevent leakage of gas through the seals.
- the ball bearings 10 at each end of the intermediate shaft 2 are mounted in an end gable 12 against the condenser and an end gable 13 against the evaporator.
- the end gable 12 forms a watertight wall between the condenser and the compressor part, while the end gable 13 has 6 openings blO which form inlets from the evaporator to the compressor part.
- Two covers 29 A form the termination of the compressor part against the evaporator and the condenser respectively, and are welded to the end gables 12 and 13.
- the cover 29 A against the condenser is also welded to the shaft 1 after it has been passed into place through the bore b5 in the intermediate shaft 2.
- the three annular chambers 4, 5, 6 have an external diameter which is slightly larger than the internal diameter of the liquid ring, with the result that the three annular chambers project slightly into the liquid ring.
- slits are formed which are in the form of contact-free gap seals, where one sealing surface is provided with helical grooves whose direction of pitch is adapted to the direction of rotation.
- the compression heat is removed due to the fact that the rotating compressor housing 17 has cooling fins 36 on the outside and is cooled by air.
- the cooling fins 36 can either be provided as radial, helical or axial cooling fins.
- the cooling fins 36 should preferably be axial as illustrated in figs. 1 and 3. With axial cooling fins 36, see fig. 3, the cooling air flows in over the compressor housing 17 at the end which abuts against the evaporator 27, indicated by C.
- the air intake is pe ⁇ endicular to the heat pump's longitudinal axis, and takes place in the extension of the air intake 33 to the evaporator 27.
- axial cooling fins 36 there are also provided in the compressor housing 17 six axial bores b6 diametrically located above one another, as illustrated in fig. 1. In the six bores there are located one or more separated restrictions in the form of plugs 19, separated by spacers 20.
- the outer surface of the plugs is provided with grooves, which can either be helical or axially linear.
- the length of the plugs 19 together with the depth of the grooves and the number of grooves in the individual plugs 19 can vary.
- the spacers 20 have a smaller diameter than the plugs 19, with the result that between each of the plugs 19 there is formed an annular cavity, and the length of the spacers 20 and thereby also the length of the annular cavity created can vary.
- each end the six bores b6 have an end plug 21 which forms a gas-tight seal of the bores b6 against the atmosphere.
- a circular flange on the end gable 12 there are provided six radial holes b7 which form a passage from the condenser to the annular cavities in the bores b6.
- radial bores b8 which run from the annular cavity in the bores b6 towards the heat pump's centre axis to six axially located tubes 22.
- the tubes 22 are anchored at one end to the end gable 13, and at the other end, inside the evaporator 27, provided with a 90 degree bend 24 which ends in nozzles 25 with outlet in a plane perpendicular to the heat pump's centre axis, directed towards the heat pump's direction of rotation (not shown in fig. 1).
- the bores b7, b6 with the plugs 19, spacers 20, bores b8, tubes 22, bends 24 and nozzles 25 form the return system for cooling medium condensate from the condenser 28 to the evaporator 27.
- the return systems In fig. 1 there are illustrated six return systems, but the number may be more or less depending on the size of the heat pump. However, the return systems must be provided in such a manner along the circumference of the compressor housing 17 that they do not create an imbalance and additional mechanical forces due to the rotation.
- the cooling medium in the cooling processes is brought from a state under high pressure in the condenser to a state under low pressure in the evaporator.
- a Carnot process which theoretically is the best process which can be achieved, and which is considered to be unattainable in practice, during this lowering of pressure the cooling medium gives up its enthalpy as useful work.
- this enthalpy difference is not given up as useful work, but is released during expansion and evaporation of the cooling medium as the cooling medium passes a choke valve at the inlet to the evaporator.
- the cooling medium Compared to a Carnot process the cooling medium hereby obtains a reduced capacity to absorb heat in the evaporator, and the efficiency becomes correspondingly lower than what it could have been if it had been possible to produce a cooling process which acted as a Carnot process.
- cooling medium condensate In its passage through the grooves in one of the plugs 19 the cooling medium condensate undergoes a lowering of pressure, thus causing it to expand and evaporate.
- the cooling medium vapour which is formed has a higher temperature than the plug 19 and the walls in the bore b6, which results in enthalpy in the form of heat being given up from the cooling medium vapour to the walls, and on to the compressor's housing. This emission of enthalpy in turn results in the cooling medium vapour condensing in the cavity behind the plug, and returning to condensate.
- the cooling medium has thereby undergone one stage in the multi-stage expansion and condensation.
- the condensate flows on in the return system, expands and evaporates once again as it passes through the grooves in the next plug, condenses again in the cavity behind the plug, and continues in this manner until at the end of the bore b6 it has undergone a multi-stage expansion and condensation.
- the enthalpy difference is passed from the compressor's housing to an ambient air flow as useful heat.
- the flow through bore b6 is two-phased since the rotation separates gas and liquid due to the difference in specific weight, and will take place the whole time during cooling with the same cooling air from the extended air inlet 33 which passes over compressor housing 17 and removes heat from the compressor's liquid ring, i.e. the enthalpy difference between the condenser's and the evaporator's condensate is transferred as heat to the same cooling air which cools the liquid ring, and leaves the heat pump as hot air together with the rest of the hot air from the condenser through the extended air outlet 38, and continues to be used for heating purposes.
- the illustrated plugs 19 with the spacers 20 are a preferred embodiment of separated restrictions in order to provide a multi-stage expansion with subse ⁇ quent condensation of the cooling medium during its flow from the condenser to the evaporator, but it is obvious that a number of other designs of these separated restrictions are also possible.
- the plugs 19 can have holes instead of external grooves, or separated narrowings in the actual bores b6 can replace the plugs and the distance pieces.
- the cooled condensate passes through the radial bores b8 where it receives an additional lowering of pressure and cooling when it meets the centrifugal field created by the rotation, and is then led into the axially located tube 22 in the evaporator 27 where the condensate emits further heat to the surrounding cooling medium vapour in the evaporator.
- the directions of flow of the cooling medium in the tubes 22 is turned via a 90 degree bend to directions perpendicular to the heat pump's centre axis, whereupon the cooling medium flows out through nozzles 25 oppositely directed to the heat pump's direction of rotation, with the result that any reaction force from the outflow can also help to reduce the amount of energy necessary to maintain the rotation of the heat pump.
- the evaporator 27 and the condenser 28 are each made of aluminium tubes which preferably have the same diameter, but different lengths.
- the end which faces the compressor part is smoothed for welding to the end gables 12 and 13. At the opposite end they are welded to the circular end covers 29 B.
- the evaporator tube 27 with the end cover 29 B, and the condenser tube 28 with the end cover 29 B are each passed in over the shaft 1 from its own side to abutment against the end gables 12 and 13.
- the evaporator tube 27 is welded with a circumferential weld seam against the end gable 13 at one end, and with a circumferential weld seam between the end cover 29 B and the shaft 1 at the other end.
- the condenser tube 28 is welded with a circumferential weld seam against the end gable 12 at one end, and with a circumferential weld seam between the end cover 29 B and the shaft 1 at the other end.
- Figs. 2a and b are radial cross sections through the evaporator and the condenser, with the fan casing, insulation and outer casing also illustrated.
- the inlet and outlet connectors for the air for evaporator and condenser are illustrated at an angle of 270° and 360° to each other, but it is clear that a number of other configurations are also possible. With different combinations of inlet connectors for evaporator and condenser the heat pumps will be able to cover all possible installation alternatives, some of which are illustrated in fig. 2c.
- Fig. 3 is a view of the heat pump where the inlet and outlet connectors are provided at an angle of 180° to each other both for evaporator and condenser.
- Both evaporator and condenser are equipped with circular fins 30 as illustrated in figs. 1,2, and 3, where in a preferred embodiment grooves 31 are pressed in the fins, with the result that in combination with the circular fan casing 32, and the tangential position of air inlet 33 and air outlet 34 for the evaporator 27, or air inlet 37 and air outlet 38 for the condenser 28, illustrated in figs. 2a and b, they create a fan function which transports air over the evaporator and the condenser respectively when the heat pump rotates.
- separate fans are not necessary for transport of air over the evaporator and condenser, as is required with conventional heat pumps with stationary heat exchangers.
- This fan function arises as a result of the fact that the air in the fan casing 32 is set in vigorously circulating motion when the evaporator 27 and the condenser 28 with the fins 30 and the pressed grooves 31 rotate.
- the energy per mass unit which the air receives will consist of three parts, viz.:
- the air flow over the evaporator 27 and the condenser 28 with the circular fins 30 and the grooves 31 is substantially two-dimensional, which gives less air noise than the three-dimensional flow which normally occurs with conventional fan systems.
- the grooves 31 on the circular fins 30 may have different shapes, and thus they can either be, e.g., bent forward, bent backward or straight radial as illustrated in figs. 2a and b. When the circular fins 30 rotate at high speed ice and frost particles will not build up on the fins and straight radial grooves are therefore considered to be the most favourable design.
- the number and length of the grooves on each of the circular fins 30 can vary, while the depth of the grooves will be slightly less than the distance between two neighbouring fins.
- Fig. 1 illustrates how the circular fins 30 are attached to the evaporator tube 27 and the condenser tube 28.
- the circular fins 30 have a flanged section 35 which abuts against the evaporator tube 27 and the condenser tube 28.
- the flanged section 35 has holes b9 located along the circumference as illustrated in fig. 1.
- the circular fins 30 with the flanged part 35 are shrunk on to the evaporator tube 27 and the condenser tube 28, and secured mechanically by filling weld deposit in the holes b9 on the flanged part 35.
- the flanged part 35 provides a large contact surface with good heat transmission conditions, ensures equal spacing between the circular fins 30 and provides a good mechanical attachment for the circular fins 30 on the evaporator/condenser tubes.
- the rotating part of the heat pump is provided with two ball bearings (not shown) which in turn are mounted in end gables in the fan casing 32.
- the shaft is driven directly via a not shown coupling by a not shown electrical motor located on the condenser side.
- the air passage for cooling air over the motor is provided in such a manner that, after having taken up the motor heat, the cooling air enters the air outlet 38 from the condenser, and is mixed with the hot air therefrom, the motor heat thus also being exploited for heating purposes (not shown).
- the capacity of the rotating heat pumps according to the present invention can be regulated by altering the speed of the motor, which in principle can be performed in three different ways:
- Capacity regulation can also be performed by regulating the rotation speed of the intermediate shaft.
- the free-running impellers 3A, 3B will attempt to cause the intermediate shaft 2 to rotate at the same speed as the compressor housing 17 and the shaft 1. Maximum compression is therefore achieved when the intermediate shaft is kept at rest, and no compression is achieved when the intermediate shaft rotates freely at the same rotational speed as the compressor housing and the shaft.
- the non-return devices can be in the form of elastic sleeves or stockings placed on the outside of the condenser's outlet openings 45. During compression of the cooling medium vapour an elastic stocking of this kind will be lifted from the shaft 1 and admit cooling medium vapour into the condenser through the openings 45. When compression ceases the stocking will cover the outside of the shaft 1 and prevent backflow of cooling medium vapour.
- the non-return devices can also be in the form of non-return valves located inside the axial bore in the shaft 1, either as separate non-return valves or integrated into the actual shaft.
- the intermediate shaft 2 is extended inside the evaporator 27 for the attachment of magnetic or magnetizable sections internally located in relation to the evaporator or the condenser.
- these magnetic or magnetizable sections are designed as a permanent magnetic ring 52, which is attached to a hub 51 which in turn is attached to the extension of the intermediate shaft.
- the magnetic coupling between the internal and external magnets generates a holding moment which will keep the intermediate shaft at rest as long as the torque which the impellers exerts on the intermediate shaft is lower than the holding moment.
- the magnetic coupling can be regulated by attaching the external permanent magnetic ring 53 in an axially displaceable, non-rotatable holder 54, since an axial displacement of the external permanent magnetic ring 53 will increase the distance between the internal and the external permanent magnetic ring in such a manner that the resulting magnetic field is weakened.
- the magnetic coupling can also be regulated if the external, stationary, adjustable magnetic field is an electromagnetically adjustable field.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Central Heating Systems (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Other Air-Conditioning Systems (AREA)
- Air-Conditioning For Vehicles (AREA)
- Compressor (AREA)
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DK96923107T DK0838011T3 (en) | 1995-07-13 | 1996-07-12 | Rotating heat pump |
CA002226939A CA2226939C (en) | 1995-07-13 | 1996-07-12 | Rotating heat pump |
EP96923107A EP0838011B1 (en) | 1995-07-13 | 1996-07-12 | Rotating heat pump |
DE69606302T DE69606302T2 (en) | 1995-07-13 | 1996-07-12 | ROTATING HEAT PUMP |
US08/973,836 US5901568A (en) | 1995-07-13 | 1996-07-12 | Rotating heat pump |
AT96923107T ATE189051T1 (en) | 1995-07-13 | 1996-07-12 | ROTATING HEAT PUMP |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NO952792A NO300186B1 (en) | 1995-07-13 | 1995-07-13 | Heat pump with closed refrigerant circuit for transporting heat from one air stream to another |
NO952792 | 1995-07-13 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1997003326A1 true WO1997003326A1 (en) | 1997-01-30 |
Family
ID=19898390
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/NO1996/000180 WO1997003326A1 (en) | 1995-07-13 | 1996-07-12 | Rotating heat pump |
Country Status (8)
Country | Link |
---|---|
US (1) | US5901568A (en) |
EP (1) | EP0838011B1 (en) |
AT (1) | ATE189051T1 (en) |
DE (1) | DE69606302T2 (en) |
DK (1) | DK0838011T3 (en) |
ES (1) | ES2144756T3 (en) |
NO (1) | NO300186B1 (en) |
WO (1) | WO1997003326A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2000004327A2 (en) * | 1998-07-16 | 2000-01-27 | Jon Ahn | Air-conditioner with condenser/evaporator housed in fans |
WO2008018812A1 (en) * | 2006-08-07 | 2008-02-14 | Veniamin Iakovlevich Veinberg | Power converter |
ES2389432A1 (en) * | 2009-09-18 | 2012-10-26 | Tomás GANUZA ERRAZQUIN | Rotary refrigerating system. (Machine-translation by Google Translate, not legally binding) |
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AU2002250128A1 (en) * | 2001-02-20 | 2002-09-04 | Thomas E. Kasmer | Hydristor heat pump |
US6886528B2 (en) * | 2002-04-16 | 2005-05-03 | Richard G. James | Rotary machine |
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MY147654A (en) * | 2002-11-13 | 2012-12-31 | Deka Products Lp | Pressurized vapor cycle liquid distillation |
EP2476471B1 (en) | 2002-11-13 | 2016-07-27 | DEKA Products Limited Partnership | Liquid distillation with recycle of pressurized vapor |
US8511105B2 (en) | 2002-11-13 | 2013-08-20 | Deka Products Limited Partnership | Water vending apparatus |
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- 1996-07-12 AT AT96923107T patent/ATE189051T1/en active
- 1996-07-12 DE DE69606302T patent/DE69606302T2/en not_active Expired - Lifetime
- 1996-07-12 DK DK96923107T patent/DK0838011T3/en active
- 1996-07-12 US US08/973,836 patent/US5901568A/en not_active Expired - Lifetime
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WO2000004327A2 (en) * | 1998-07-16 | 2000-01-27 | Jon Ahn | Air-conditioner with condenser/evaporator housed in fans |
WO2000004327A3 (en) * | 1998-07-16 | 2000-06-22 | Jon Ahn | Air-conditioner with condenser/evaporator housed in fans |
WO2008018812A1 (en) * | 2006-08-07 | 2008-02-14 | Veniamin Iakovlevich Veinberg | Power converter |
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Also Published As
Publication number | Publication date |
---|---|
NO300186B1 (en) | 1997-04-21 |
NO952792L (en) | 1997-01-14 |
NO952792D0 (en) | 1995-07-13 |
ATE189051T1 (en) | 2000-02-15 |
EP0838011A1 (en) | 1998-04-29 |
US5901568A (en) | 1999-05-11 |
ES2144756T3 (en) | 2000-06-16 |
DE69606302D1 (en) | 2000-02-24 |
DE69606302T2 (en) | 2000-08-24 |
EP0838011B1 (en) | 2000-01-19 |
DK0838011T3 (en) | 2000-07-10 |
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