WO2007002496A2 - Venturi duct for heat transfer - Google Patents
Venturi duct for heat transfer Download PDFInfo
- Publication number
- WO2007002496A2 WO2007002496A2 PCT/US2006/024633 US2006024633W WO2007002496A2 WO 2007002496 A2 WO2007002496 A2 WO 2007002496A2 US 2006024633 W US2006024633 W US 2006024633W WO 2007002496 A2 WO2007002496 A2 WO 2007002496A2
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- WO
- WIPO (PCT)
- Prior art keywords
- heat
- transfer
- venturi
- duct structure
- flow
- Prior art date
Links
- 239000012530 fluid Substances 0.000 claims abstract description 92
- 230000007246 mechanism Effects 0.000 claims description 7
- 239000002470 thermal conductor Substances 0.000 claims description 5
- 239000007787 solid Substances 0.000 claims description 3
- 238000000034 method Methods 0.000 claims 2
- 230000000694 effects Effects 0.000 abstract description 15
- 230000002269 spontaneous effect Effects 0.000 abstract description 2
- 239000007789 gas Substances 0.000 description 13
- 238000006243 chemical reaction Methods 0.000 description 6
- 230000007423 decrease Effects 0.000 description 4
- 230000006870 function Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 230000002349 favourable effect Effects 0.000 description 3
- 230000004907 flux Effects 0.000 description 3
- 230000002441 reversible effect Effects 0.000 description 3
- 230000002730 additional effect Effects 0.000 description 2
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- 238000007906 compression Methods 0.000 description 2
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- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000008450 motivation Effects 0.000 description 1
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Classifications
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- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D23/00—Control of temperature
- G05D23/19—Control of temperature characterised by the use of electric means
- G05D23/1919—Control of temperature characterised by the use of electric means characterised by the type of controller
- G05D23/192—Control of temperature characterised by the use of electric means characterised by the type of controller using a modification of the thermal impedance between a source and the load
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- 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
- F25B23/00—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect
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- 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
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- 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
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0011—Ejectors with the cooled primary flow at reduced or low pressure
Definitions
- the present invention relates to heat pumps, devices that move heat from a heat source to a warmer heat sink. More specifically, it relates to Bernoulli heat pumps.
- Heat engines are devices that move heat from a source to a sink. Heat engines can be divided into two fundamental classes distinguished by the direction in which heat moves. Heat spontaneously flows “downhill”, that is, toward lower temperatures. As with the flow of water, such "downhill” heat flow can be harnessed to produce mechanical work, as illustrated by internal-combustion engines, e.g.. Devices that move heat "uphill”, that is, toward higher temperatures, are called heat pumps. Heat pumps necessarily consume power. Refrigerators and air conditioners are examples of heat pumps. Most heat pumps work by varying the temperature of a working fluid 1 over a range that includes the temperatures of the source and sink. In this way heat can flow spontaneously from the source into the portion of the working fluid in which the temperature is below that of the source. Similarly, heat flows spontaneously into the sink from the portion of the working fluid in which the temperature is above that of the sink. The required temperature variation of the working fluid is commonly effected by compression and expansion of the working fluid.
- Bernoulli heat pumps accomplish the required working-fluid temperature variation by converting random molecular motion (reflected in the temperature and pressure of the fluid) into directed motion (reflected in macroscopic fluid flow).
- random and directed motion are particularly clear in the statistical distribution of molecular speeds. The random motion is the width of this distribution, whereas the directed flow is the mean on the same distribution.
- a fluid spontaneously converts random molecular motion into directed motion when the cross sectional area of a flow is reduced, as when the flow passes through a nozzle or Venturi.
- the coupled variation of the temperature, density and pressure with cross-sectional area is called the Bernoulli principle. Whereas compression consumes power, Bernoulli conversion does not.
- the energy-conserving character of Bernoulli conversion is the fundamental efficiency exploited by the Bernoulli heat pump.
- a conventional heat pump consists of four fundamental components: a compressor 4, and an expansion valve 7, a low-temperature heat exchanger 3 and a high-temperature heat exchanger 2.
- Figure 1 b shows that the Bernoulli heat pump combines the roles played by the expansion valve 7 and the low-temperature heat exchanger 8 into a Venturi 8 capable of heat transfer.
- a Bernoulli heat pump requires smaller pressure changes in a larger flux of working fluid.
- FIG. 1a is replaced by a fan or blower 9 in a Bernoulli heat pump (Fig. 1b).
- Fig. 1b Bernoulli heat pump
- Conventional heat pumps, Bernoulli heat pumps, heat exchangers, compressors, blowers and Venturis have all been widely discussed.
- the present invention describes a new structure for the efficient transfer of heat 3 into a fluid flowing through a Venturi. The importance of the invention is the improved efficiency it provides Bernoulli heat pumps.
- the discussion below describes the problems with prior art in this context which are addressed and solved by the present invention.
- Figures 2 and 3 provide a basis for comparing prior art involving the Bernoulli heat pump to the present invention.
- Figure 1 shows the coupled variation of the temperature, density, pressure, flow speed and cross-sectional area of a compressible gas undergoing so-called one-dimensional flow. There is nothing new or contentious about this well known and much studied phenomenon. The coupled variation of these properties of a flowing compressible fluid is reproduced here because it provides a succinct basis for the comparison of earlier efforts to exploit Bernoulli conversion with one another and with the present invention.
- specification of any one of the four covarying quantities implies the values for the remaining three.
- FIG. 1 Pressure is the product of temperature and density.
- Figure 2 shows the temperature, density, pressure and cross-sectional area implied by the (square of the) flow speed.
- the flow speed is labeled by the corresponding dimensionless Mach number.
- the linear decrease of the temperature with the square of the flow speed is a direct result of energy conservation, the conversion of random kinetic energy into directed kinetic energy. It is not surprising that the flow- speed scale over which the Bernoulli effect occurs is the Mach number, which is the ratio of the two speeds.
- the quantities shown in Fig. 1 are normalized to their values in the stationary gas.
- FIG. 2 shows immediately the relationship of US patent 3,049,891 to other inventions and to our invention.
- US patent 3,049,891 requires that the flow be supersonic (Mach number values greater than one).
- Figure 2 shows that the gas temperature is indeed lower for supersonic flow. But, Fig. 2 also shows that temperature reduction produced by subsonic flow is more than adequate for many practical purposes.
- the temperature scale in Fig. 2 is absolute. That is, at a flow speed of Mach 1 , for example, the gas temperature has decreased by 25%. If, for example, the temperature of the gas at rest is 70 degrees F, then the temperature near the neck of the Venturi at Mach 1 is ⁇ 60 degrees F below zero.
- Fig. 2 The second direct implication of Fig. 2 is that the power required to maintain highspeed flow in the Venturi neck can be substantial.
- the pressure near the Venturi neck is approximately half that at the Venturi entrance. If this pressure drop is not recovered by means of a diffuser (expanding portion of the Venturi), then the potential efficiency of the Bernoulli heat pump is reduced.
- efficiency requires the maintenance of laminar flow in the diffuser. This requirement translates directly into diffusers characterized by very gradual expansion, that is, very asymmetric Venturis (Venturis with very different converging and diverging sections).
- Fig. 2 shows that the inverse area passes through a maximum with increasing flow speed. This maximum is the basis of the Laval nozzle. Another implication of this maximum is that, considered as functions of distance along the Venturi axis, the temperature, density and pressure all exhibit narrow dips near the Venturi neck (the maximum of the inverse area). That is, Fig. 2 shows that, near Mach 1 , the temperature, density, and flow speed all vary significantly while the cross-sectional area varies little.
- the temperature, density and pressure all exhibit a strong dip at the neck of the Venturi.
- the variation of the temperature for a specific and much studied Venturi shape 11 is shown in Fig. 3.
- the variation of the temperature, density, pressure and flow speed along the Venturi axis is given (implicitly) by Fig. 2 by specifying the cross-sectional area as a function of distance along the axis of the Venturi.
- Figure 3 is obtained by taking the area variation of the cross-sectional area to be that of a so-called "toroidal critical-flow Venturi.
- the converging portion of the Venturi is a torus, and the diverging portion is a cone.
- the Venturi wall If the Venturi wall is thermally conducting outside the region of the dip shown in Fig. 3, then the Venturi wall provides a thermal path for heat transfer from elsewhere in the working-fluid flow to the cold neck of the same flow. That is, heat transferred to the neck portion of the working-fluid flow has come from elsewhere in same working-fluid flow, with no net benefit. While there is no benefit, there is a cost. Since the heat transferred to the working-fluid flow is the sum of the heat transferred from the heat-source flow (the desired effect) and that transferred from elsewhere in the working-fluid flow, we see that the desired heat transfer is directly reduced by heat transfer outside the dip. Restricting heat transfer between the working fluid and the Venturi wall to the region of the dip shown in Fig. 3 is a focus of the present invention. This restriction is not addressed in the earlier patents.
- the Nusselt effect is the enhancement of heat transfer at a fluid-solid interface by the convection provided by fluid flow. Because the flow speed vanishes at the interface, heat transfer into the working fluid from the solid depends on thermal conduction. But, the flow of the working fluid beyond the boundary layer sweeps away (convection) heat transferred into the boundary layer by conduction. Convection is generally much more effective than conduction. At flow speeds near Mach 1 , the Nusselt effect is large. For example, if the source of heat is a fluid flowing at a lower speed, then the area through which heat is transferred into the working fluid can be much smaller than the area through which heat is transferred out of the heat-source flow.
- the boundary layer is the region of a fluid that is flowing adjacent to the solid-fluid interface. Because the flow speed vanishes at the interface, the speed of the working-fluid flow must increase rapidly near the interface. The narrow region in which this increase occurs is called the boundary layer.
- the temperature gradient and therefore the conductive heat transfer are significantly enhanced where the boundary layer is thin.
- the thickness of the boundary layer is strongly affected by the gradient of the pressure along the direction of the working-fluid flow.
- the first of the two boundary-layer effects concerns the sign of the pressure gradient. It is well known that a so-called “adverse” (that is, positive) pressure gradient thickens the boundary layer.
- the pressure gradient is "adverse" in the diverging (diffuser) portion of the Venturi.
- the portion of the Venturi labeled "heat- transfer slice” in Figure 3 identifies the portion of the Venturi axis in which the conditions for heat transfer are favorable. These are all properties of the bulk of working-fluid flow. That is, the temperature axial pressure gradient are properties of the entire cross section of the working-fluid flow -- except for the thin boundary layer at the periphery of the cross section. The viscous losses occurring outside the region of the temperature dip represents costs devoid of benefits.
- a focus of the present invention is the exploitation of the properties of the thin section 10 of the Venturi axis labeled the "heat-transfer" in Fig. 3, without incurring the viscous losses associated with those portions of the Venturi lying outside the dip region of Fig. 3. There are thus five issues associated with the dip region of Fig. 3 that are not addressed in the prior art. These are:
- Bernoulli conversion is energy conserving (consumes no power)
- Bernoulli heat pump is not a perpetual-motion device. It consumes power in two ways.
- the power required to compensate for this entropy generation is proportional to the difference in temperatures at which heat is added and removed.
- the present invention is a structure that exploits the "heat-transfer” section identified in Fig. 3 and systems exploiting that structure.
- the structure is a Venturi designed specifically for effective transfer of heat into the fluid passing through the Venturi.
- the invention consists of two types of exploitation of the "heat-transfer" section. First, heat transfer is restricted to the heat-transfer section. Second, heat transfer within the heat-transfer section is maximized by the use of specialized fins within the heat-transfer section.
- the source of the heat transferred to the working fluid can be a flowing fluid, gas or liquid, or it can be nonfluid, as in the cas of heat-generating electrical components.
- the critical requirement is a thermal conductor connecting the heat source to the narrow portion of the Venturi axis designated in Fig. 3 as the "heat-transfer" section.
- the power consumed is reduced by making the divergence of the diffuser very gradual, with the objective of maintaining laminar flow.
- Venturis are staged to obtain either greater capacity or greater temperature difference.
- corrugation of the Venturi wall creates multiple "heat-transfer slices" within a single Venturi.
- the rate of heat transfer to the working fluid can be varied continuously by variation of the flow speed through the Venturi.
- systems based on the heat-transfer Venturi can be open or closed. That is, systems can exhaust the working fluid to which heat has been added, or circulate a working fluid optimized for heat transfer or other properties.
- systems based on the heat-transfer Venturi can be used to pump heat "downhill". That is, a heat source at a higher temperature than the working fluid when stationary will cool by conduction. Causing the working fluid to flow exploits the Nusselt effect and convection. Causing the working fluid to flow through a Venturi further enhances the cooling. Causing the working fluid to flow through a heat-transfer Venturi further enhances the cooling.
- the Bernoulli heat pump can be used for the purpose of heating or cooling.
- Fig. 1a shows the components of a conventional heat pump.
- Fig. 1b shows the components of a Bernoulli heat pump.
- Fig. 2 shows a graph of the coupled variation of the flow speed, temperature, density, pressure and cross-sectional area of a laminar flow of compressible gas.
- Fig. 3 shows a graph of the axial variation of the temperature within the Venturi revealing the "heat-transfer" section of the Venturi. The dashed curve is corresponding Venturi shape.
- Fig. 4 is a cross-sectional view of a heat-transfer Venturi according to an embodiment of the invention.
- Fig. 5a is a cross section of a rectangular Venturi taken through its "heat-transfer” section containing a grid of thermally conducting fins traversing the heat-transfer section of the Venturi according to an embodiment of the invention.
- Fig. 5b is a cross section of a non-rectangular Venturi taken through its "heat- transfer” section containing a grid of thermally conducting fins traversing the heat- transfer section of the Venturi according to an embodiment of the invention.
- Fig. 6a is a cross-sectional view of multiple heat-transfer Venturis staged in parallel in order to obtain increased capacity, according to an embodiment of the invention.
- Fig. 6b is a schematic view of multiple heat-transfer Venturis staged in serial in order to obtain increased capacity, according to an embodiment of the invention.
- Fig. 7 is a cross-sectional view of a Venturi containing a corrugated wall and multiple "heat-transfer J sections, according to an embodiment of the invention.
- Venturi a duct of varying cross-sectional area.
- the present invention provides an improved heat-transfer structure for use in a Bernoulli heat pump.
- Embodiments of the heat-transfer structure are illustrated in Figs. 4-7.
- the embodiments all exploit the "heat-transfer" section of a Venturi identified in Fig. 3.
- the heat-transfer section is exploited in two fundamental ways. First, heat transfer to the working fluid passing through the Venturi is restricted to the "heat-transfer" section. Second, heat transfer within the "heat-transfer" section is maximized by the introduction of thermally conducting fins that serve to increase the surface area available for heat transfer within the "heat-transfer" section of the Venturi.
- Figure 4 illustrates a first embodiment of the heat-transfer structure in the shape of an asymmetric Venturi 16 (Venturi possessing different shapes in the converging ad diverging sections).
- the working fluid undergoing Bernoulli conversion. Arrow length is intended to indicate flow speed, with longer arrows indicating higher speeds.
- the gas When the working fluid enters the Venturi 12, the gas is slowly moving, relatively warm and relatively dense.
- the cross-sectional area decreases the flow speed must increase in order to maintain a constant mass flux.
- the energy required for this increase in flow speed is, as shown in Fig. 2, obtained from the random kinetic energy manifest in temperature.
- the temperature decrease is proportional to the change in the square of the flow speed, that is, the Bernoulli effect.
- the flow speed increases until it reaches a maximum 13 at the minimum cross-sectional area.
- the axial variation of the flow speed is the mirror image of the variation of the temperature shown in Fig. 3.
- the cross-sectional area begins to increase in the diffuser portion of the Venturi, the flow speed decreases 14 as the gas proceeds to the Venturi exit 15, where the gas is warmed to the extent that heat has been transferred from the heat-source flow 17 through the thermally conducting material 18.
- the Venturi wall 16 is insulating everywhere outside of the "heat-transfer" section 10. In particular, this structure eliminates unwanted heat transfer into the "heat-transfer" section 10 of the working fluid from other regions of the working fluid.
- the heat source shown in Fig. 4 is a flowing fluid, chosen as an illustration.
- the nature of the heat source and its thermal coupling to the thermal conductor 17 is quite arbitrary. It is the restriction of heat transfer into the working fluid to the "heat- transfer" section 10 that is specific to this invention.
- the second fundamental component of this invention is the additional structures shown in the enlarged cross-sectional views of the "heat-transfer" section of the Venturi in Fig. 5.
- the "heat-transfer" section of the Venturi lies in the plane of the figure.
- heat transfer into the working fluid is increased by thermally conducting fins 19 extending from the Venturi wall 20 into the working-fluid flow.
- the use of fins to increase heat exchange is common. What is unusual here, beyond the context, is the limited extent of the fins in the direction of the flow, that is, parallel to the axis of the Venturi.
- the fins are confined to the "heat-transfer" section 10.
- the pattern of fins used is quite arbitrary.
- Figures 5a and 5b show fins extending across the Venturi, and intersecting to form a grid 19 within the "heat-transfer" section 10. Useful visualizations of the structure of such grids are provided by tennis rackets, apple corers and (planar) tea strainers. Figures 5a and 5b also serve to emphasize the arbitrariness of the cross-sectional shape of the Venturi. Many Venturis possess cylindrical symmetry, but this is not a requirement.
- thermally- conducting fins Another aspect of the invention is the cross-sectional shape of the thermally- conducting fins.
- Their cross-sectional shape is that of an airfoil, and is designed to minimize aerodynamic drag on the working-fluid flow by the fins.
- the normally larger component of drag, the so-called "pressure” component is rendered negligibly small by the aerodynamic cross-sectional shape of the fins.
- our thermally conducting fins need not provide lift and need not change their angle of attack. Thus, they can be thin and oriented along streamlines of the working-fluid flow to further reduce drag.
- arrays of fixed airfoils are often used to suppress turbulence in duct flow.
- Another degree of design freedom with regard to the grid elements is the variation of their cross section with distance from the Venturi wall. This degree of freedom represents a tradeoff between heat conductance and structural strength. Structural strength calls for increasing area with increasing distance from the Venturi wall. Heat conductance calls for the reverse. The appropriate balance depends on the material chosen for the grid element.
- multiple heat- transfer Venturis of the present invention can be configured in parallel to achieve greater capacity or in serial to achieve higher or lower temperatures. Such configurations are illustrated in Figs. 6a and 6b.
- the shape of the entire Venturi, especially the diffuser can be independently optimized to reduce drag and therefore the power required by the blower/fan mechanism 9 to maintain the working-fluid flow.
- the general requirement in this context is that, in order to maintain laminar flow, the expansion of the cross-sectional area in the diffuser portion of the Venturi must be very gradual.
- Laminar flow serves to minimize the largest component of aerodynamic drag, so-called pressure drag, leaving only the smaller component associated with viscous losses. The recovery of 95% of the pressure drop required to attain Mach 1 flow has been reported. Another design option concerns the flow speed at which the invention operates.
- Bernoulli heat pumps In contrast to traditional heat pumps based on a change of phase in the working fluid, the operating conditions of Bernoulli heat pumps can be readily and continuously varied. In particular, the flow speed, and therefore the temperature, of the heat-sink flow can be varied by changing the power provided to the blower that maintains the heat-sink flow.
- Bernoulli heat pumps including this invention, the rate of heat pumping is continuously variable, allowing startup transients and their inefficiencies to be effectively eliminated.
- the blower maintaining the working-fluid flow can be thermostatically controlled.
- a second virtue of continuous variation and control is the increase in thermodynamically allowed efficiency at smaller temperature differences. (Carnot efficiency is inversely proportional to the temperature difference across which heat is pumped.
- the present invention offers an efficiency gain associated with longer operation over a smaller temperature difference.
- Venturi a fluid-flow duct or channel structure whose cross-sectional area varies along its axis. The variation of the cross-sectional area along the duct axis possesses at least one local minimum. Although most Venturis contain a diffuser section in which the cross-sectional area increases along the axis, we include in our definition of Venturi nozzles in which the diffuser section is either short or nonexistent. This extension thus extends the applicability of the invention to applications in which power consumption is not critical.
- Working-Fluid a fluid whose temperature is varied locally so as to permit spontaneous heat flow into and out of the working fluid when the temperature of the heat source is below that of the sink.
- Working-fluid flow the flow of the working fluid through the Venturi structure.
- Cross section the area inside the closed curved formed by the intersection of the Venturi surface and a plane perpendicular to the Venturi axis.
- Heat-transfer section The portion of the Venturi near its neck lying between two planes perpendicular to the Venturi axis and characterized by low temperature, high flow speed and large negative axial pressure gradients. See Fig. 3.
- Fin a structure consisting of high thermal conductivity material extending from a thermally conducting surface into a fluid flow adjacent to that surface whose objective is to increase the surface area available for heat transfer between the surface and the fluid flow, while minimizing resistance to the flow.
- Diffuser A portion of a Venturi characterized by monotonically increasing cross-sectional area along the axis and flow direction.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Jet Pumps And Other Pumps (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/993,871 US20090183858A1 (en) | 2005-06-24 | 2006-06-23 | Venturi for Heat Transfer |
CA002613088A CA2613088A1 (en) | 2005-06-24 | 2006-06-23 | Venturi duct for heat transfer |
EP06773916A EP1899782A4 (en) | 2005-06-24 | 2006-06-23 | Heat transfer venturi |
JP2008518467A JP2008546984A (en) | 2005-06-24 | 2006-06-23 | Heat transfer venturi |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US69393405P | 2005-06-24 | 2005-06-24 | |
US60/693,934 | 2005-06-24 |
Publications (2)
Publication Number | Publication Date |
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WO2007002496A2 true WO2007002496A2 (en) | 2007-01-04 |
WO2007002496A3 WO2007002496A3 (en) | 2007-04-12 |
Family
ID=37595918
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/US2006/024633 WO2007002496A2 (en) | 2005-06-24 | 2006-06-23 | Venturi duct for heat transfer |
Country Status (7)
Country | Link |
---|---|
US (1) | US20090183858A1 (en) |
EP (1) | EP1899782A4 (en) |
JP (1) | JP2008546984A (en) |
KR (1) | KR20080025411A (en) |
CN (1) | CN101268430A (en) |
CA (1) | CA2613088A1 (en) |
WO (1) | WO2007002496A2 (en) |
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WO2013171744A1 (en) * | 2012-05-14 | 2013-11-21 | Merksamer Itzhak | Venturi refrigeration system |
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- 2006-06-23 EP EP06773916A patent/EP1899782A4/en not_active Withdrawn
- 2006-06-23 JP JP2008518467A patent/JP2008546984A/en active Pending
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
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US20090249806A1 (en) * | 2008-04-08 | 2009-10-08 | Williams Arthur R | Bernoulli heat pump with mass segregation |
US8281605B2 (en) * | 2008-04-08 | 2012-10-09 | Machflow Energy, Ing. | Bernoulli heat pump with mass segregation |
WO2013171744A1 (en) * | 2012-05-14 | 2013-11-21 | Merksamer Itzhak | Venturi refrigeration system |
Also Published As
Publication number | Publication date |
---|---|
EP1899782A4 (en) | 2012-04-25 |
US20090183858A1 (en) | 2009-07-23 |
JP2008546984A (en) | 2008-12-25 |
CA2613088A1 (en) | 2007-01-04 |
CN101268430A (en) | 2008-09-17 |
KR20080025411A (en) | 2008-03-20 |
WO2007002496A3 (en) | 2007-04-12 |
EP1899782A2 (en) | 2008-03-19 |
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