EP0826935A2 - Heat pump - Google Patents
Heat pump Download PDFInfo
- Publication number
- EP0826935A2 EP0826935A2 EP19970202616 EP97202616A EP0826935A2 EP 0826935 A2 EP0826935 A2 EP 0826935A2 EP 19970202616 EP19970202616 EP 19970202616 EP 97202616 A EP97202616 A EP 97202616A EP 0826935 A2 EP0826935 A2 EP 0826935A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat pump
- plugs
- tubular member
- fluid
- working medium
- 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- Withdrawn
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
- F04B39/0011—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons liquid pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1401—Ericsson or Ericcson cycles
Definitions
- the present invention aims to obviate or at least to mitigate the above mentioned disadvantages.
- a magnetic liquid which preferably is constituted by an appropriate emulsion of iron oxide dust in an oil or ester.
- magnetic flux conducting bodies in the form of e.g. metal balls may be supplied thereto. Particularly these metal balls will have a diameter of about 10 to 30%, preferably about 20%, of the inner diameter of the tubular member.
- the force that can be generated by a magnetic field and thus the pressure difference that can be obtained over the fluid plugs in a tubular member, without the addition of the magnetic flux conducting bodies, is relatively low and amounts to a maximum of about 20 kPa.
- a large number of magnetic fluid plugs are present in series inside the tubular member, separated by gas bubbles of the working medium and all these plugs are driven simultaneously by the electromagnetically induced moving magnetic field. In such a manner a pressure difference of 300 to 400 kPa between compression and expansion can easily be achieved.
- a number of tubular members can be placed in parallel, if desired.
- An extra permanent magnet 17 can be located under the container 7 to allow the heat pump to operate in any orientation.
- Fig. 3 shows an example of a P-V diagram where isotherm compression of the gas bubbles between fluid plugs 10 takes place on the trajectory E-F, whereby heat is transferred from the gas to the environment. Thereupon the gas is lowered isochorically in temperature on a regeneration trajectory F-G, whereby the pressure decreases and whereby generated heat is transferred to the returning gas bubbles inside a regenerator. At the trajectory G-H heat is absorbed through the driven isotherm expansion of the gas bubbles of the working gas. A suitable working gas would be e.g. helium. Finally on the trajectory H-E the expanded returning gas bubbles are heated isochorically again to the original temperature in the regenerator where also the pressure increases to the original starting pressure.
- the central part of the wound tube functions as a regeneration section 24.
- the total system can be encapsulated inside a close housing similar to the system of fig. 2, filled with the working gas under an averaged pressure Pm of 2-3 MPa. At two positions in the loop of tube 18 the pressure will be equal to the average pressure Pm, where, if necessary, the forming of the fluid plugs 19 can be restored from a liquid container in a similar way as described for the system in fig. 2 or just by allowing the working gas to fill up the space between the fluid plugs 19.
- the fluid plugs are subjected to an additional acceleration by means of which a varying magnetic field is generated.
- This magnetic field may be used to generate an electric current in coils, which current may further be applied in the heat pump.
- the recovery of electrical energy leads to a system in which mainly an amount of energy has to be supplied equal to the frictional energy of the system, so that an ideal heat pump can be obtained.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Electromagnetic Pumps, Or The Like (AREA)
Abstract
A heat pump comprises a tubular member (6; 18)
forming a substantially closed loop with a compression and an
expansion section for a working medium. Each of said sections
cooperates with a heat exchanger (12, 16). In the operational
state at least two floating plugs (10; 19) of a magnetic
material are provided in the tubular member (6; 18), said
plugs (10; 19) enclosing a gas bubble and/or liquid sample of
the working medium. The heat pump further comprises
electromagnetic means along at least a part of said tubular
member (6; 18) for generating a moving magnetic field to
control the movement of the plugs (10; 19) in said tubular
member (6; 18). The plugs (10; 19) are formed by a magnetic
fluid.
Description
The present invention relates to a heat pump comprising
a tubular member forming a substantially closed loop with a
compression and an expansion section for a working medium,
each of said sections cooperating with a heat exchanger, in
which tubular member in the operational state at least two
floating plugs of a magnetic material are provided, said
plugs enclosing a gas bubble and/or liquid of the working
medium, the heat pump further comprising electromagnetic
means along at least a part of said tubular member for
generating a moving magnetic field to control the movement of
the plugs in said tubular member.
Such a heat pump is known from DE-A-3607976 and may be
used in e.g. household refrigerators. In said document the
plugs are formed by plungers, which have the disadvantage
that they are relatively heavy, induce vibrations, are noisy,
wear out, are difficult to regulate and have efficiency
losses because of friction and leakage of the working medium.
Other known heat pumps which may be used in e.g.
household refrigerators are based upon de so called Rankine
evaporation principle, where fluor-hydrogen compounds and
nowadays more environmental-friendly compounds are used as
heattransportmedia. The disadvantages of these systems is
that the "coefficient of performance (COP)", i.e. the amount
of removed heat divided by the required energy, for this
removal is rather low, varying from 1,2 to 1,4 at the
existing operating temperature-differences. A preferable COP
for a temperature-difference of about 30° C. in the order of
3 can be obtained by applying Stirling coolers, which however
are rarely used because of complexity and cost reasons. Also
in the latter type of heat pumps moving mechanical parts are
used with the above mentioned disadvantages.
The present invention aims to obviate or at least to
mitigate the above mentioned disadvantages.
Therefore, according to the invention, the heat pump as
described in the opening paragraph is characterized in that
the plugs are formed by a magnetic fluid. By applying such
plugs moving mechanical parts with the disadvantages thereof
are avoided. The term "magnetic fluid" is generally known and
relates to a fluid which is not magnetic of itself, but which
is a magnetic flux conducting fluid.
From the Dutch patent specification No. 31163, the
application of a liquid metal drivable by means of a movable
electromagnetic field and providing for the compression of a
working medium in a refrigerator is known per se. The
document however does not describe a heat pump of the type as
described in the opening paragraph.
The invention will now be described with reference to
the accompanying drawing wherein:
The principle of the heat pump according to the
invention is based upon the compression, the propulsion and
the expansion of a working medium, such as air or helium,
separated in a tubular member, such as a tube or pipe, by
means of magnetic fluid plugs, whereby these plugs are driven
by an electromagnetically induced moving magnetic field. The
diameter and the material of the tubular member is chosen in
such a way that the surface-tension of the magnetic fluid is
capable to separate the successive gas bubbles of the working
medium, so that the magnetic fluid plugs provide for an
appropriate sealing effect in the tubular member. Magnetic
fluids have been disclosed in e.g. US-A-5,147,573, US-A-5,064,550
and US-A-4,938,886 and are commercially available.
In the present invention a magnetic liquid is used which
preferably is constituted by an appropriate emulsion of iron
oxide dust in an oil or ester. However, in order to further
increase the flux density of the magnetic liquid and the
performance of the heat pump, according to the invention
magnetic flux conducting bodies in the form of e.g. metal
balls may be supplied thereto. Particularly these metal balls
will have a diameter of about 10 to 30%, preferably about
20%, of the inner diameter of the tubular member. With the
magnetic liquid according to the invention, i.e. with the
addition of magnetic flux conducting bodies, the sealing of a
working medium sample in the tubular member will be improved,
while the pressure difference over the fluid plugs can
further be increased.
Because of the effect that the commercially available,
so called super-paramagnetic fluids have relatively low
magnetic saturation values, the force that can be generated
by a magnetic field and thus the pressure difference that can
be obtained over the fluid plugs in a tubular member, without
the addition of the magnetic flux conducting bodies, is
relatively low and amounts to a maximum of about 20 kPa. To
obtain a larger pressure difference between compression and
expansion, in the heat pump according the invention a large
number of magnetic fluid plugs are present in series inside
the tubular member, separated by gas bubbles of the working
medium and all these plugs are driven simultaneously by the
electromagnetically induced moving magnetic field. In such a
manner a pressure difference of 300 to 400 kPa between
compression and expansion can easily be achieved. To increase
the total pumping volume a number of tubular members can be
placed in parallel, if desired.
In the embodiment of fig. 2 and as indicated in the P-V
diagram of the so called Ericssoncycle of fig. 1, for each
gas bubble between two fluid plugs the compression takes
place on the isotherm trajectory A-B, whereby heat is
transferred from the gas to the environment. Thereupon the
gas is lowered isobarically in temperature on the trajectory
B-C, whereby the volume decreases and the generated heat is
transferred to the returning gas bubbles inside a regenerator
as will be further explained below. At the trajectory C-D
heat is absorbed through isothermic expansion of the gas
bubbles of the working medium, e.g. by means of a magnetic
throttle. Finally on the trajectory D-A the expanded
returning gas bubbles are heated isobarically again to the
original temperature in the regenerator whereas also the
volume increases to the starting volume.
The embodiment schematically shown in fig. 2 includes a
closed circuit 1 largely provided by a tube 6 wherein the
working gas, e.g. air, is brought under an increased pressure
of about 2-3 MPa. For the induction of a moving magnetic
field statically mounted multiple pole shoes 2 and 3 are
located along an number of windings of the tube 6. On outer
pole shoes 2 and inner pole shoes 3 respectively coils 4 and
5 are wound and successively activated in e.g. four phases to
generate a circular moving magnetic field with a field
strength that is close to the saturation value of superparamagnetic
fluid plugs 10 provided in the tube 6. A first
section of tube 6 that is partly wound between the pole shoes
starts inside a container 7 containing a small volume of a
magnetic fluid 8, but just above the liquid level. When by
means of one or more coils 5 at the beginning of the tube 6 a
magnetic field is generated, then a certain amount of
magnetic liquid 8 will be sucked inside the tube 6 as
indicated at position 9, because the magnetic liquid tends to
fill areas with the highest magnetic flux density.
When in e.g. four phases the coils 4 and 5 are
successively activated, the tube 6 will be successively
filled with fluid plugs 10 and gas bubbles of the working
medium which is present in the container 7 above the fluid
level. For each winding of the tube 6 the fluid plugs 10 are
in phase, whereby all fluid plugs 10 inside the different
windings of the tube 6 and between the pole shoes 2 and 3 are
propelled, whereby a small increase of pressure inside the
gas bubble in front of each fluid plug 10 is induced. Because
a small compression of the gas bubbles takes place, also a
small correction of the relative distance between the pole
shoes 2 and 3 in relation to the tube 6 is necessary. This
can be achieved by decreasing the winding-pitch of the tube 6
between the poleshoes 2 and 3 or by changing the shape of the
tube 6 to reduce the surface of the bore of the tube 6 in
relation to the increase of pressure inside the tube 6.
Further, it may be noticed that is also possible to give the
pole shoes 2 and 3 a conical form, whereby the diameter of
the tube gradually increases.
During the compressioncycle of the gas bubbles in the
compression section of the tube 6 heat is transferred to the
"hot" side 11 of the heat pump through the pole shoes 2 and 3
and a heat exchanger 12. Via a, preferably isolated,
regenerator 13 the compressed gas bubbles together with fluid
plugs 10 are transferred to the "cold" side 14 of the heat
pump.
In the regenerator 13 heat from the gas bubbles and the
fluid plugs 10 is transferred to a return section of the tube
6 and to the returning gas bubbles and fluid plugs and is
used to bring the temperature thereof back to the level of
the "hot" side 11. At the "cold" side 14 a throttle
comprising in this embodiment a number of permanent magnets
16 is installed, by which a force is exerted on the magnetic
fluid plugs 10 to build up the required compression pressure.
It may be noticed that with such a throttle helium cannot be
used as working medium; therefore in this embodiment
preferably air is used as working medium. After the fluid
plugs 10 have passed the throttle, the working gas bubbles
expand in the expansion section of the tube 6 in accordance
with the pressure inside the closed system 1, whereby heat is
absorbed from the "cold" side through a heat exchanger 15.
After the returning gas bubbles and the magnetic fluid plugs
10 are warmed up inside the regenerator 13 the magnetic fluid
plugs 10 are dispensed into the container 7 where the fluid
is used to form new fluid plugs for further
compression/expansion cycles.
An extra permanent magnet 17 can be located under the
container 7 to allow the heat pump to operate in any
orientation.
Fig. 3 shows an example of a P-V diagram where isotherm
compression of the gas bubbles between fluid plugs 10 takes
place on the trajectory E-F, whereby heat is transferred from
the gas to the environment. Thereupon the gas is lowered
isochorically in temperature on a regeneration trajectory F-G,
whereby the pressure decreases and whereby generated heat
is transferred to the returning gas bubbles inside a
regenerator. At the trajectory G-H heat is absorbed through
the driven isotherm expansion of the gas bubbles of the
working gas. A suitable working gas would be e.g. helium.
Finally on the trajectory H-E the expanded returning gas
bubbles are heated isochorically again to the original
temperature in the regenerator where also the pressure
increases to the original starting pressure.
Fig. 4A and 4B schematically show another embodiment of
the heat pump in accordance with the invention wherein the
working gas follows the P-V diagram of fig. 3. This
embodiment is provided with a closed circuit tube 18, wherein
a working gas, e.g. helium, separated by magnetic fluid plugs
19, is brought under an increased pressure of about 2-3 MPa.
The induction of the moving magnetic fields takes place in a
similar way as shown in fig. 2 with statically mounted
multiple pole shoes 20 and 21. The tube 18 in this embodiment
is wound in two layers back and forth between the pole shoes
20 and 21. On the outer pole shoes 20 and the inner pole
shoes 21 respectively the coils 22 and 23 are wound and
successively activated in e.g. four phases to generate a
circular moving magnetic field with a field strength that is
close to the saturation value of the super-paramagnetic fluid
plugs 19. The central part of the wound tube functions as a
regeneration section 24. The total system can be encapsulated
inside a close housing similar to the system of fig. 2,
filled with the working gas under an averaged pressure Pm of
2-3 MPa. At two positions in the loop of tube 18 the pressure
will be equal to the average pressure Pm, where, if
necessary, the forming of the fluid plugs 19 can be restored
from a liquid container in a similar way as described for the
system in fig. 2 or just by allowing the working gas to fill
up the space between the fluid plugs 19.
For each winding of the tube 18 in both directions the
fluid plugs 19 are in phase, whereby all fluid plugs inside
the different windings of the tube 18 and between the pole
shoes 20 and 21 are driven in the expansion section 25.
Thereby in the "hot" compression section 26 a small increase
of pressure inside the gas bubble in front of each fluid plug
19 is induced. Because a small compression of the gas bubbles
takes place, also a small correction of the relative distance
between the pole shoes in relation to the fluid plugs 19 is
necessary, since the distance between the fluid plugs 19
remains constant. In the example system of fig. 4 this is
achieved e.g. by increasingly giving the tube 18 a more oval
shape between the pole shoes 20 and 21 in relation to the
increase of pressure inside the tube 18 in the compression
section 26. In this way the surface-area of the cross-section
of the tube 18 is gradually reduced in the compression
section, causing a pressure increase in the working gas
between the fluid plugs 19. It may be noticed that in this
embodiment the sum of the diameters of the tubes located
above each other is a constant.
During the isotherm compression cycle of the gas bubbles
heat is transferred to the "hot" side 26 of the heat pump.
Through the regenerator section 24 the compressed working gas
bubbles together with the fluid plugs 19 are also propelled
and transferred isochorically to the "cold" side 25 of the
heat pump. The heat content of the magnetic fluid plugs 19,
mainly consisting out of mineral oil or ester, also has to be
transferred inside the regenerator section 24.
In the regenerator section 24 heat of the working gas
and the fluid plugs 19 is transferred to the returning gas
bubbles and fluid plugs 19 and is used to bring the
temperature thereof to the level of the "hot" side 26.
Because of the isochoric cooling in the regenerator section
24 the pressure drops as indicated by trajectory F-G of fig.
3. At the "cold" side 25 driven isotherm expansion takes
place e.g. by changing the oval shape of the tube 18
gradually back to the original more round shape, by which a
force is induced on the magnetic fluid plugs 19 to achieve
the required expansion pressure. Due to the expansion, heat
is absorbed from the "cold" side 25 of the heat exchanger. On
the way to the compression side the returning gas bubbles and
the magnetic fluid plugs 19 are heated isochorically inside
the regenerator section 24, resulting in a pressure increase
as indicated by trajectory H-E of fig. 3.
Of cause modifications of the described system are
possible within the fundamentals of its working principle.
E.g. linear (in one or more rows) positioned pole shoes and a
more or less straight tubular member instead of circular or
helical positioned pole shoes or conical pole shoes and a
wound tubular member are possible. The moving magnetic field
can also be generated by means of permanent magnets in the
form of a rotor or by fixed permanent magnets, in which case
the tubular members have to be rotated. Also a different
throttle mechanism like a tube section of reduced diameter
can be used. Further there is a possibility to use a
combination of driven compression and expansion or
regeneration. Also a discontinuous up and down pumping
instead of a continuous closed loop pump system could be used
and a combination of an isochoric and an isobaric
regeneration. Instead of an ideal gas as a working medium,
gas mixtures or a non-condensing vapour, or even a condensing
vapour or liquid, could be used to increase the heat capacity
of the working medium.
Further it may be noticed that by the expansion of
the working medium the fluid plugs are subjected to an
additional acceleration by means of which a varying magnetic
field is generated. This magnetic field may be used to
generate an electric current in coils, which current may
further be applied in the heat pump. The recovery of
electrical energy leads to a system in which mainly an amount
of energy has to be supplied equal to the frictional energy
of the system, so that an ideal heat pump can be obtained.
Claims (21)
- Heat pump comprising a tubular member forming a substantially closed loop with a compression and an expansion section for a working medium, each of said sections cooperating with a heat exchanger, in which tubular member in the operational state at least two floating plugs of a magnetic material are provided, said plugs enclosing a gas bubble and/or liquid of the working medium, the heat pump further comprising electromagnetic means along at least a part of said tubular member for generating a moving magnetic field to control the movement of the plugs in said tubular member, characterized in that the plugs (10; 19) are formed by a magnetic fluid.
- Heat pump as claimed in claim 1, characterized in that the magnetic fluid is provided with magnetic flux conducting bodies in the form of e.g. metal balls with a diameter of about 10 to 30%, preferably about 20%, of the inner diameter of the tubular member (6; 18)
- Heat pump as claimed in claim 1 or 2, characterized in that the moving magnetic field is generated by means of successively positioned pole shoes (2, 3; 20, 21) which are electromagnetically energized successively in different phases.
- Heat pump as claimed in claim 3, characterized in that the pole shoes (2, 3; 20, 21) are positioned in a circular form.
- Heat pump as claimed in claim 4, characterized in that the tubular member (6; 18) containing the fluid plugs (10; 19) separated by gas bubbles and/or liquid of the working medium has been wound with one or more windings between the circular positioned pole shoes (2, 3; 20, 21), whereby in each winding the fluid plugs (10; 19) are driven in phase by means of the relevant electromagnetically driven pole shoes (2, 3; 20, 21).
- Heat pump as claimed in claim 4, characterized in that the pitch of the tubular member (6; 18) wound between the pole shoes (2, 3; 20, 21) decreases in relation to the increase of pressure inside the gas bubbles and/or liquid of the working medium between two fluid plugs (10; 19), whereby the relative position of the fluid plugs (10; 19) in relation to the pole shoes (2, 3; 20, 21) in front of the respective fluid plugs (10; 19) remains constant.
- Heat pump as claimed in claim 4, characterized in that the shape of the tubular member (6;18) is changed to reduce the surface of the bore of the tubular member (6;18) in relation to the increase of pressure inside the tubular member (6;18).
- Heat pump as claimed in claim 3, characterized in that the pole shoes (2, 3; 20, 21) are positioned linear, possibly in more than one row.
- Heat pump as claimed in any one of the preceding claims, characterized in that by the expansion of the working medium the fluid plugs (10; 19) are subjected to an additional acceleration by means of which a varying magnetic field is generated, the expansion section being provided with coils wherein an electric current is generated by said varying magnetic field, which current may further be applied in the heat pump.
- Heat pump as claimed in any one of the preceding claims, characterized in that the fluid plugs (10; 19) are driven in the compression section.
- Heat pump as claimed in any one of the claims 1-8, characterized in that the fluid plugs are driven in the expansion section.
- Heat pump as claimed in any one of the claims 1-8, characterized in that the fluid plugs (10; 19) are driven in both the compression section and the expansion section.
- Heat pump as claimed in any one of the preceding claims, characterized in that the pressure difference between compression and expansion is realized by means of a throttle in the expansion section.
- Heat pump as claimed in claim 13, characterized in that the throttle consists of a restriction in the tubular member (6; 18).
- Heat pump as claimed in any one of the claims 1-12, characterized in that the pressure difference between compression and expansion is realized by means of permanent magnets (16), located in a row along the tubular member (6; 18) and inducing a force on the fluid plugs (10) in front of the permanent magnets (16) and thus for each fluid plug (10) creating a pressure difference in the working medium in front of these fluid plugs (10).
- Heat pump as claimed in claim 12, characterized in that a linear or circular pumping system is used in which the working medium is transported isochorically instead of isobarically in the regenerator section (24) from the "hot" side (26) to the "cold" side (24) and vice versa.
- Heat pump as claimed in any one of the preceding claims, characterized in that a regenerator (13; 24) is provided to transfer the heat of the working medium and the fluid plugs (10; 19) transported from the "hot" side to the "cold" side of the heat pump to the working medium and the fluid plugs (10; 19) transported from the "cold" side to the "hot" side of the heat pump to minimise the heat leakage of the heat pump.
- Heat pump as claimed in any one of the preceding claims, characterized in that a number of tubular members (6; 18) is provided, located and working parallel to each other.
- Heat pump as claimed in any one of the preceding claims, characterized in that the heat pump is provided with a container (7) for a magnetic fluid.
- Heat pump as claimed in claim 19, characterized in that the heat pump is provided with one or more permanent magnets (17) located at the container (7), the said one or more permanent magnets (17) preventing the fluid to drop out of the container (7) such that the heat pump can operate in any orientation.
- Heat pump as claimed in any one of the preceding claims, characterized in that a two-phase working medium is used and an additional cooling capacity is obtained from the evaporation phase change of the working medium.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NL1003887A NL1003887C2 (en) | 1996-08-27 | 1996-08-27 | Heat pump without moving mechanical parts. |
NL1003887 | 1996-08-27 |
Publications (1)
Publication Number | Publication Date |
---|---|
EP0826935A2 true EP0826935A2 (en) | 1998-03-04 |
Family
ID=19763419
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19970202616 Withdrawn EP0826935A2 (en) | 1996-08-27 | 1997-08-26 | Heat pump |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0826935A2 (en) |
NL (1) | NL1003887C2 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006081055A1 (en) * | 2005-01-26 | 2006-08-03 | Sullair Corporation | Torus geometry motor system |
DE102004004370B4 (en) * | 2004-01-29 | 2008-02-07 | Kraußer, Raimund | Cooling-compression control unit for heat engines |
GB2565578A (en) * | 2017-08-17 | 2019-02-20 | Edwards Ltd | A pump and method of pumping a fluid |
CN110631398A (en) * | 2019-09-03 | 2019-12-31 | 刘桓 | Heat pipe type ball plug magnetic induction power device |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3607976A1 (en) | 1986-03-11 | 1987-10-01 | Juergen Schoenell | Pump |
US4938886A (en) | 1988-02-08 | 1990-07-03 | Skf Nova Ab | Superparamagnetic liquids and methods of making superparamagnetic liquids |
US5064550A (en) | 1989-05-26 | 1991-11-12 | Consolidated Chemical Consulting Co. | Superparamagnetic fluids and methods of making superparamagnetic fluids |
US5147573A (en) | 1990-11-26 | 1992-09-15 | Omni Quest Corporation | Superparamagnetic liquid colloids |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL31163C (en) * | ||||
DE41129C (en) * | E. schergen in Lacken, Brüssel | Spiral pump, can also be used as a motor | ||
US2434705A (en) * | 1944-09-09 | 1948-01-20 | Henry W Jarrett | Gas compressor |
GB1408236A (en) * | 1972-01-31 | 1975-10-01 | Battelle Development Corp | Method and positive-displacement engine for converting one form of energy into another form of energy |
US4197715A (en) * | 1977-07-05 | 1980-04-15 | Battelle Development Corporation | Heat pump |
DE3229239C2 (en) * | 1982-08-05 | 1986-12-18 | Helmut 2420 Eutin Krueger-Beuster | Peristaltic pump |
FR2666627B1 (en) * | 1990-09-06 | 1994-12-02 | Norbert Zimmermann | FLOATING PISTON PUMP. |
-
1996
- 1996-08-27 NL NL1003887A patent/NL1003887C2/en not_active IP Right Cessation
-
1997
- 1997-08-26 EP EP19970202616 patent/EP0826935A2/en not_active Withdrawn
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3607976A1 (en) | 1986-03-11 | 1987-10-01 | Juergen Schoenell | Pump |
US4938886A (en) | 1988-02-08 | 1990-07-03 | Skf Nova Ab | Superparamagnetic liquids and methods of making superparamagnetic liquids |
US5064550A (en) | 1989-05-26 | 1991-11-12 | Consolidated Chemical Consulting Co. | Superparamagnetic fluids and methods of making superparamagnetic fluids |
US5147573A (en) | 1990-11-26 | 1992-09-15 | Omni Quest Corporation | Superparamagnetic liquid colloids |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004004370B4 (en) * | 2004-01-29 | 2008-02-07 | Kraußer, Raimund | Cooling-compression control unit for heat engines |
WO2006081055A1 (en) * | 2005-01-26 | 2006-08-03 | Sullair Corporation | Torus geometry motor system |
US8274184B2 (en) | 2005-01-26 | 2012-09-25 | Sullair Corporation | Torus geometry motor system |
GB2565578A (en) * | 2017-08-17 | 2019-02-20 | Edwards Ltd | A pump and method of pumping a fluid |
CN110631398A (en) * | 2019-09-03 | 2019-12-31 | 刘桓 | Heat pipe type ball plug magnetic induction power device |
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