JPH05118704A - Absorption cycle heat machine - Google Patents

Abstract

PURPOSE: To obtain an improvement in an efficiency of a heat exchange crossing a thickness of a plate for forming a part of an absorption cycle heat machine. CONSTITUTION: In the absorption cycle heat machine comprising a rotary assembling having a steam generator, a condenser, an evaporator and an absorber, a layer 200 of a thermal structure for improving an efficiency of a heat exchange crossing a disc is provided by increasing a surface area on an inner surface of a wall 116 of the disc of at least the absorber.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION The present invention relates to a rotary heat exchange device in which heat transfer between two media, at least one of which is in liquid phase, is achieved through the thickness of a plate which is driven to rotate.

One example of such a device is disclosed in prior European patent application 327030, which relates to a rotary absorption cycle heat pump, which heats a volatile fluid element and an absorbent liquid thereto. A vapor generating section, a condensing section, interconnected to provide a fluid flow path,
It has a rotating assembly that includes an evaporator and an absorber. In European Patent Application No. 327030, heat exchange between a heat-donating fluid and a heat-receiving liquid (eg, water) in the condensing and absorbing portions results in the respective wall thicknesses associated with the condensing and absorbing portions. Achieved across. The heat receiving liquid flows through a chamber bounded on both sides by the walls of the condenser and the absorber, which chamber is flooded with the heat receiving liquid.

It is an object of the present invention to provide improved efficiency of heat exchange across the thickness of rotating plates forming part of a rotary heat exchange device.

According to the present invention, it includes a vapor generating section, a condensing section, an evaporating section and an absorbing section interconnected to provide a circulating fluid flow path for volatile fluid components and absorbent liquid thereto. A rotating assembly having means for delivering heat to and / or from the inner surface of at least one of the generally radially extending walls of the generator, condenser, absorber and evaporator. Then, the means discharges the fluid to the inner surface at a location radially inward so that the fluid flows as a thin-film liquid radially outwardly across the inner surface by the action of centrifugal force. A heat conducting structure attached thereto for making good thermal contact therewith, said heat conducting structure having an array of elements distributed radially and circumferentially across said inner surface; An element inside the thin film liquid flow The degree of protrusion of the thermal structure projecting from the outer surface to provide a surface that deflects the flow of liquid as it flows radially outward across the substrate is substantially greater than the thickness of the thin film. , An absorption cycle thermomachine is provided. In use, for a liquid having a given viscosity and density, the thickness of the liquid film can be controlled by selecting the rotational speed of the plate and the rate of liquid supply to the plate. The fluid supplied to the inner surface may be in the vapor phase, which condenses when discharged onto the one surface and then flows across the plate as a thin film liquid.

Desirably, the thermal structure is such that it increases the effective surface area of the surface to which it is attached by a factor of at least 3, preferably at least 10, in a direction orthogonal to said inner surface. The protrusion from this is 5m
m, preferably 10 mm.

In order to avoid "blinding" of the thermal structure by the liquid and to facilitate the access of the vapor to the interior of the thermal structure, the thermal structure is conveniently at least 80%, more preferably at least 80%. , Having a porosity of at least 90%.

[0007] Preferably, the thermal structure is provided on the inner surface of the absorber.

Conveniently, the thermal structure is formed to increase the mixing of the fluids supplied to said inner surface. Thus, the vapor phase refrigerant should be absorbed by the liquid phase absorbent at the wall of the absorber, in the case of the absorber enhancing the mixing of the refrigerant and the absorber with the centrifugal forces that occur during rotation of the assembly. It would be particularly convenient if the thermal structure had such a shape.

The elements can be in the form of metal fins, or
It may consist of strands or filaments of a layer of metal mesh or metal gauze, such as Expamet®, bonded to said one side of the plate.

Preferably, the element is constituted by a strand or filament of porous metal foam, such as manufactured under the trade name Retimet, joined to said one side of the plate. For more information on reclaimed metal foam, see Filtration and Separation (Filtration
and Separation) Reference is made to a paper entitled "Porous Metal Foams" by HABray in the May 6, 1973 issue.

When the element consists of a metal mesh, a metal gauze or a metal foam, the layers of material can be joined to the plate by vacuum brazing or diffusion bonding, in this way the good between the strands or filaments and the plate. Thermal contact is achieved.

When the thermal structure consists of strands or filaments, the strands or filaments are desirably joined at the intersections between them, in this way good heat transfer from one strand or filament to the next. Contact occurs. In fact, said elements of the thermal structure have a high fin efficiency, which can be achieved by the selection of a suitable thermally conductive material with an effective fin length which is not large relative to the fin thickness.

Desirably, the layer of material is bonded to said inner surface on only one side of the layer, the other side of the layer being free.

The invention has particular application in dual effect machines, where the generator / condenser and / or the absorber / evaporator consist of two stages, eg generator / condenser. Is a first stage consisting of a primary generating part and an intermediate condensing part, and a second stage consisting of an intermediate generating part and a primary condensing part.
And stages. Similarly, the absorber / evaporator may consist of a primary evaporator and an intermediate absorber and an intermediate evaporator and a primary absorber. Such a dual effect machine is disclosed in detail in the prior art EP 149353, the disclosure of which is hereby incorporated by reference. Thus, an absorption cycle thermomachine as defined above has at least one internal surface of the primary and / or intermediate components (ie, generator, condenser, absorber and evaporator) as described above. It can consist of a dual-effect machine with structure.

According to a special aspect of the invention, the absorption cycle thermomechanical machine as defined above comprises a dual effect machine, wherein the generator / condenser section comprises a primary generator section and an intermediate condenser section. And a second stage from the intermediate generator and the primary condenser, the inner surface of the absorber comprises a thermal structure as described above, the thermal structure preferably having the form of a porous metal foam.

Where the evaporator / absorber comprises two stages, a primary evaporator and an intermediate absorber, and an intermediate evaporator and a primary absorber, preferably at least the primary absorber is as described above. With a good thermal structure.

Examples of rotary thermomechanical machines of the type relevant to the present invention are the conventional European patents 119776 and 149.
353 and European Patent Application No. 327230.

In such a rotary thermal machine, when the condensed fluid is transferred from the condensing means associated with the high pressure zone to the vaporizing means, a large pressure difference is generated between the vapor generating means (which is the high pressure zone) and the vaporizing means. Means (this is the low pressure zone)
During, it must exist and be maintained.

As disclosed in European Patent Application No. 327230, this can be achieved and maintained by a restriction in the form of a U-tube extending between the steam generating means and the peripheral edges of the vaporizing means and rotating with the machine. The maximum pressure difference is determined by the height of the liquid cylinder (liquid column) in the U pipe.

The machine specifically shown in European Patent Application No. 327230 is a single-effect machine, in which each cycle of the flow of working fluid through the machine is
Steam generation and steam condensation occur once in the generating means.
Typically, in such single-effect machines, the pressure prevailing in the steam generation / condensation zone is of the order of 0.3 bar absolute and the pressure prevailing in the vaporization section is of the order of a few millibar absolute.

European Patent No. 149353 discloses a double-effect machine in which steam generation and condensation in the high pressure zone occur in two steam generation / condensation section stages. In a dual effect machine, the pressure dominating the high side of the machine tends to be higher than it would be for a single effect machine. For example, in the first steam generator / condenser stage, the pressure is typically on the order of 3.0 bar absolute, and in the second steam generator / condenser stage, this is typically 0.3 bar absolute. In other words, the pressure difference to be maintained can be quite large for a dual effect machine. European Patent Application No. 32723
When a U-tube restrictor deployment such as that disclosed in No. 0 is used to isolate the high and low pressure zones from each other, the increased pressure differential results in a double effect machine (or, if desired, a single effect machine). In the case of a one-effect machine), it could be accommodated by extending the U-tube radially outwards. However, this has the disadvantage of increasing the overall radial dimension of the machine. Similarly, in the case of a single-effect machine, for example, when it is desired to reduce the radial dimension of the machine in order to achieve a compact design, the U-leg of the U-leg is provided while providing a suitable throttle to maintain the pressure differential. To the extent that the length can be reduced,
There are limits.

According to another aspect of the invention, at least two zones containing working fluid at different pressures during operation of the machine and a U-tube throttle for transferring the working fluid from the high pressure zone to the low pressure zone. A rotary thermomechanical machine, comprising:
A pipe throttle communicates with each zone at a position radially inward from the outer circumference of each zone, and a working fluid is collected from a region radially outward of the high-pressure zone to radially inward the U-tube throttle. A rotary thermomechanical machine is provided, characterized in that means for feeding to the high temperature zone are provided. By these means, the effective length of each leg of the U-tube can exceed the radial dimension of said area without overly protruding beyond the circumference of the area interconnected thereby.

Desirably, the legs of the U-tube throttle extend radially outward beyond the circumference of the area interconnected thereby, so that the portion of the U-tube interconnecting the legs is of said area. Located outside. However, according to the invention, it is possible to lengthen the legs of the U-tube inwardly of the zone, so that, as is conceivable, in appropriate circumstances, the U-tube throttle may be placed in the circumference of said zone. Can be accommodated as a whole.

The rotary heat machine can be a single-effect machine, in which the high-pressure zone is constituted by the vapor-generating / condensing stage and the low-pressure zone is constituted by the vaporizing / vapor-absorbing stage.

If the thermal machine is a dual effect machine with two steam generating / condensing and evaporating section stages, each having a different pressure, the U-tube throttling means and associated collecting and feeding means are Providing for a pressure difference between two steam generator / condenser stages and / or for a pressure difference between a low pressure steam generator / condenser stage and an evaporator stage. it can.

The collecting and feeding means is preferably rotationally restrained, disposed in a high pressure zone, with passage means having an inlet located radially outward and an outlet located radially inward. The inlet is immersed in the rotating working fluid in the peripheral passages of the high pressure zone during operation of the machine, and the outlet is for the working fluid collected from the passages to the outer periphery of the high pressure zone. Discharge into the U-tube at a position radially inward of.

Desirably, the thermo-machine has a heat transfer wall separating at least some of the different stages of the machine from each other, and external heating and / or cooling sources and / or The transfer wall extends in the radial direction of the axis of rotation of the thermomechanical machine, and heat transfer between different stages and / or between said stage and an external source takes place through the thickness of said wall.

In a preferred embodiment of the present invention, the machine has a rotatably mounted assembly, which assembly generally radially extending walls forming a primary steam generating section and an intermediate condensing section, respectively. A first high pressure section with a second intermediate pressure section with a generally radially extending wall forming an intermediate steam generating section and a primary condensing section, and a wall forming an evaporation section and an absorption section; A third low pressure zone, generally radially extending walls of the absorber, and a first throttle means provided between the first zone and the second zone;
A second throttling means provided between the zone and the third zone, wherein the machine is further characterized in that at least one of the throttling means is located radially inward of the outer circumference of the respective zone. The working fluid radially inwardly for collecting the working fluid from the peripheral region of the high pressure area of the two areas interconnected by the U tube and to the low pressure area. Means for delivering to the U-tube in said high pressure area.

Preferably, the one diaphragm means is constituted by a first diaphragm means.

The second throttling means can likewise have a U-tube, in which case the pressure difference is between the first section and the second section.
Since it has a tendency to be somewhat smaller than exists between the zones, the U-tube can reach these zones at a location near the outer perimeters of the second and third zones, so
No means for collecting and directing the working fluid radially inward is required.

In the machine disclosed in European Patent Application No. 327230, heat transfer between the condensing and absorbing parts of the machine and the external source of the heat exchange fluid, eg the water to be heated, is of the condensing and absorbing parts. Achieved by a chamber disposed therebetween and rotatable with the assembly, fluid is supplied to the chamber via an annular passage in the rotary drive shaft portion of the assembly.
The disadvantage of this arrangement is that the heat exchange fluid should be supplied via a special seal and is operated with the fluid supply circuit completely flooded so that the heat exchange efficiency is not as high as desired. If not, measures should be taken to improve the heat exchange efficiency, and a mesh should be prepared on such surface, for example to increase the effective area of the surface in contact with the heat exchange fluid. is there.

In order to provide an alternative form of heat exchange arrangement for achieving heat exchange between a fluid circulating inside a rotary heat machine and an external heat receiving and / or heat supplying fluid, the present invention is provided. According to another aspect of the invention, a vapor generating section, a condensing section, an evaporating section and an absorbing section are interconnected to provide a circulating fluid flow path for the volatile fluid component and the absorbent liquid thereto. In an absorption cycle thermomachine having a rotating assembly for receiving heat and / or supplying heat to the outer surface of at least one generally radially extending wall of the generator, condenser, absorber and evaporator. Means are provided for delivering the fluid of said means, at a radially inward position, for ejecting the fluid to such an outer surface so that this fluid traverses said outer surface as a thin film liquid under the action of centrifugal force. Radial direction It flows in the direction, it is provided which is characterized in.

Although the heat-receiving or heat-supplying fluid normally takes the form of a liquid when discharged onto the outer surface of the wall, the fluid has a gaseous nature and condenses when discharged onto the wall. Then flowing as a thin film liquid is not excluded. For example, when the machine is used for thermal deformation, the intermediate-grade heat supplied to the generator can be in the form of water vapor, which condenses when in contact with the outer surface of the wall of the generator and then the liquid. Flows across the surface as a thin film of.

The outer surface through which the thin film liquid flows can be conveniently treated to aid in the retention of a continuous film of liquid along it. Such treatments, which can be achieved chemically, for example by etching or physically, for example by sandblasting, are generally directed to giving the surface an overall fine roughness.

The machine can be a dual effect machine, comprising a generator / condenser and / or absorber / evaporator in two stages, eg the generator / condenser is a primary generator and an intermediate condenser. And a second stage consisting of an intermediate generation section and a primary condensation section.
Similarly, the absorber / evaporator can consist of primary and intermediate absorbers and intermediate and primary absorbers. Such a dual effect machine is disclosed in detail in the prior art EP 149353, the disclosure of which is hereby incorporated by reference.

If the means are arranged to deliver heat exchange liquid to two or more of the outer surfaces, the liquid can be drawn from different sources. Typically, the liquid supplied to the evaporation section is withdrawn from a different source than the liquid supplied to the absorption section and / or the condensation section. The absorber and condenser can comprise liquids from a common source, or each can comprise liquids from separate sources. If the condenser and absorber are supplied with heat exchange liquid from a common source, the liquid can be supplied to the outer surfaces of the condenser and absorber either in parallel or in series. For example, if a series feed is employed, the heat exchange liquid may be fed to one of the outer surfaces of the condenser or evaporator and collected at the outer diameter of that outer surface, and then radially inward. Can be transferred to another outer surface and then collected at a location outside the latter outer surface in the radial direction.

In one embodiment of the invention, the condensing portion and the absorbing portion are bounded by generally radially extending walls in spaced-apart relation with each other, said means extending between the opposing walls. A liquid supply passage, which has a discharge opening near the wall for discharging heat exchange liquid to each wall at a location radially inward, each of the condensing section and the absorbing section. Providing an annular collection passage near the radially outer location of the outer surface to collect the liquid after it has flowed as a thin film across each surface.

Only examples of the present invention are described below with reference to the drawings.

A dual effect machine is illustrated in FIG. 1 and can be operated to achieve heat pumping, cooling or thermal deformation, depending on an external heating / cooling source interacting with the machine. .. For the moment, the machine will be described with respect to its use in heat pump mode. The working aqueous solution is used in the evaporation section
V, absorber AB, a pair of solution heat exchangers 30 and 32, generator / condenser assembly (which consists of a primary steam generator PG, an intermediate condenser IC, an intermediate generator IG and a primary condenser PC). The circuit is circulated so as to be returned to the evaporation section EV around a circuit that is hermetically sealed. The working solution consists of a mixture of evaporable components such as water (as refrigerant) and an absorbent for water (for example a mixture of alkali hydroxides as disclosed in EP 208427). The evaporation portion EV is limited by the convex dish-shaped wall 34, and the condensed refrigerant is discharged to the inner surface thereof. The condensed refrigerant flows from the primary condenser PC to the U-tube throttle 3
6 is discharged from the open end of the leg 38 of the diaphragm 36, which travels through 6 (which rotates with the machine) and ends at a position near the axis of the rotary drive axis S of the machine. The rotation axis S is
It is rotatably driven by a driving member D which is reversible and whose speed can be changed.

The refrigerant discharged to the inner surface of the wall 34 of the evaporation portion spreads as a thin film due to the action of centrifugal force and flows toward the annular passage 40 on the outer periphery of the evaporation portion EV, where the refrigerant that has not evaporated is collected. And is circulated through a stationary tube 42 arranged in the manner of a Pitot tube and returned for discharge to the evaporator wall 34 at a location radially inward. Excess refrigerant accumulated in passage 40 is scooped by stationary tube 50, which acts as a Pitot tube, and sent to the area of the machine's absorber where the refrigerant rich solution in annular passage 52 Mix.

Some of the refrigerant, as it flows from the legs 38 or tubes 42 and then across the inner surface of the wall 34,
It vaporizes by exchanging heat with the flow of liquid flowing across the outer surface of the wall 34, which acts as a source of low quality heat. This liquid, which may be water, is expelled at a radially inward position from a passage 44 that is stationary in the wall 34, so that the water spreads as a thin film under the action of centrifugal force, across the wall 34 and radially outwardly. It flows towards a channel 46 from which it is picked up by a stationary tube 48 arranged in the manner of a Pitot tube. The refrigerant vapor produced as a result of heat exchange across the thickness of the wall 34 travels axially towards the absorber AB where it is sprayed onto the inner surface of the wall 56 via the stationary tube 54. When in contact with the absorbent, it is recombined with the absorbent. The heat of formation of the solution is transferred to the load, which will be described later, through the wall 56.

The produced working solution, which is rich in refrigerant, is collected in the annular passage 52 and, due to its kinetic energy, rotates with the tubes 42 and 50 (as detailed in European Patent Application No. 327230). (Forms part of a pitot pumping deployment 62 constrained with respect to) via stationary tubes 58 and 60 into an annular chamber 64 and from there via tubes 66 and 68 which rotate with the machine. It is sent to the heat exchange section 30 where it exchanges heat with the refrigerant-depleted working solution from the annular passage 70 associated with the intermediate generation section IG. The refrigerant-rich solution then passes through the second solution heat exchange section 32, where the tube 72 from the annular passage 74 associated with the primary generator PG.
And heat exchange with the refrigerant-depleted working solution, which is transported via 72a. This transfer is performed by the pump 6
Achieved by a rotation-constrained pitot pump 76 that operates in a manner similar to 2. The tube 72a is constrained from rotating, but the tube 72a rotates with the rotating structure of the machine.

After passing through the heat exchange section 32, the refrigerant-rich solution is sent via the tube 79 to the annular passage 80, where it is skimmed by the tube 82 forming part of the pitot pump 76 and the wall 84. Is discharged. The opposite side of the wall 84 is heated by the radiant amount 86 of the burner 88, which is supplied with gas and contained in the high-grade heat in the form of radiant energy from the radiant amount 86 and in the products of combustion. And generate heat. The hot flue gas from the burner 88 flows over the outer surface of the primary generator wall 84, which is shielded by the housing 90, passes around the heat exchange sections 30 and 32, and then through the annular slot 92. Exhausted and in these heat exchanges the heat is further
It is delivered by heat exchange with the fluid flowing in the heat exchange sections 30 and 32. The refrigerant-rich solution that impinges on the walls 84 of the primary generator, as it flows radially outward, is heated by heat exchange across the wall thickness, causing evaporation of the water component. The reduced constituents, which consist of absorbent and non-evaporated water, flow across the face of the wall 84 and ultimately the heat exchange section 3.
2 and 30, the intermediate generator IG and the annular passage 94, for picking up in the annular passage 74 for transfer back to the absorber, in the annular passage 94 by a pipe 96 forming a part of the pitot pump 62. The wall 5 of the absorber
6 is delivered to tube 54 for discharge. The resulting pressure in the area surrounding the primary generator PG and the intermediate condenser IC as a result of evaporation of the refrigerant is typically 3.0.
Absolute degree of bar.

The evaporated component contacts the wall 98 common to the intermediate condenser section IC and the intermediate generation section IG, where
As a result of heat exchange with the cooled refrigerant-depleted solution on the IG side of the wall 98, the refrigerant vapor on the IC side is
It condenses and flows radially outward into the annular passage 100. The fluid supplied to the IG side of the wall 98 is supplied from the passage 74 to the pipe 7
2, 72a, 102 and 104, the tube 104 forms part of a rotationally restrained pitot pump 106 arranged to operate in a manner similar to the pumps 62 and 76. .. The refrigerant-depleted solution from the passages 74 passes through the heat exchange section 32 in a heat exchange relationship with the relatively cooled refrigerant-rich solution withdrawn from the absorption section, and thus is relatively cool, and thus of the wall 98. It absorbs heat from the water vapor on the IC side and produces the desired condensation. The solution in which the refrigerant supplied to the intermediate generation part IG is reduced is
The heat transfer across the wall 98 produces more water vapor, which proceeds to the one-cooling condenser PC and is condensed.

The condensed refrigerant collected in passage 100 is scooped by tube 108 forming part of pitot pump 76 and annular passage 10 near the axis of rotation of the machine.
Transferred to 9. From the passage 109, the condensed refrigerant constitutes one leg of the U-tube throttle 112 that rotates together with the machine.
0 to send radially outward. The other leg 114 of the throttle 112 sends the condensate into an area of low pressure (typically on the order of 0.3 bar absolute) surrounding the IG and PC. The legs 114 are folded back (as shown at 115) so that the condensate is delivered to a point near the axis of rotation and then radially outward along the section 115 to discharge into the wall 116. This condensate is collected in the intermediate generation part I.
Together with the condensate derived from the refrigerant vapor generated in G, it flows radially outwardly across the wall 116 in a heat exchange relationship with the load described below. The condensed refrigerant is collected in the annular passage 118, and the stationary pipe 120, the rotating pipe 122,
It is sent to the evaporation section EV via the U-tube throttle 36 and the tube 38. A tube 120 immersed in the passage 118 forms part of the pitot pump 106.

A portion of the condensate supplied to the passage 118 can be continuously recirculated by a tube (not shown) that can form part of the Pitot pump 106 and discharged to the wall 116 at a point near the axis of rotation. As can be seen, the throttles 36 and 112 are within the limits of the housing 90, which should always have a certain diameter to accommodate the heat exchange parts 30 and 32 located on the outside. , PG
A cylinder height can be provided that exceeds the radial dimensions of / IC and IG / PC. According to this method, the diaphragm 36
And 112 allow a substantial pressure differential to be maintained during the differential pressure zones of the assembly.

The refrigerant-depleted solution discharged by tube 104 to the IG side of wall 98 achieves further evaporation as it flows radially outward across the surface of wall 98 (as previously described). , The solution remaining after evaporation remains in the passage 13
0, where it is routed by stationary tubing 132 into the annular passage 70, from where the pipe 134 rotating with the assembly, the heat exchange section 30 and the tubing 136 rotating with the assembly, of the wall 56. It is sent to the passage 94 for discharge to the AB side, and thus rich in refrigerant as described above.

The above-mentioned assembly is mounted as a unit so as to rotate about the axis of the shaft structure S driven by the motor D. The shaft structure S serves to rotatably mount the pitot pumps 62, 76 and 106 which are gravity or magnetically restrained from rotating with the shaft as disclosed in EP 327230.

At the outer surfaces of the AB and PC walls 56 and 116, heat exchange takes place between the fluid in the AB and PC sections and the fluid forming the heat-receiving load, and heat transfer to the load is accomplished by the primary condenser PC. In the case of, the refrigerant is condensed, and in the case of the absorbing portion AB, it is extracted from the condensed refrigerant. The load consists of a fluid, eg water circulating around a central heating system, which is delivered by stationary tubes 138, 140 to the outer surface of walls 56 and 116 at a point located radially inward so that centrifugal force In action, it flows radially outward as a thin film and collects in annular passages 142, 144, where it is skimmed by stationary tubes 146, 148 which form part of the circuit through which the fluid making up the load flows.

If desired, the fluid provided by tubes 138 and 140 may flow in a common circuit,
It may flow in another circuit. For example, if the heat receiving fluid is water flowing around the central heating circuit, the collection tube 146 can be connected in series with the supply tube 140.

It is worth noting that the heat-receiving fluid is provided in a non-overflow method, in contrast to the arrangement disclosed in EP 327230, which has the advantage that a thin film of the heat-receiving fluid is provided on the heat transfer surface. , Which results in improved heat transfer characteristics. Also, this technique is less sensitive to problems that occur when the fluid is dirty compared to overflow techniques (such as EP 327230).

According to the present invention, at least the inner surface of the wall 116 has a heat conducting structure (thermal structure) attached thereto. Referring to FIG. 2, the thermal structure is formed of a layer 200 of porous metal foam bonded to the outer surface of the wall 116 only on one side, the other side of the layer 200 being free and unsupported. Porous metal foams consist of Retimet metal foams, which are materials with good thermal conductivity and high surface area per unit volume. Layer 200
The layer 200 is bonded to the wall 116 by vacuum brazing or diffusion bonding to ensure good thermal contact between the and the wall 116, which will also have good thermal conductivity. The thickness of layer 200, i.e. its depth in the direction parallel to the axis of rotation of the machine, is significantly greater than the thickness of the liquid film (preferably at least by a magnitude) so that the film forms layer 200. It follows a tortuous path that extends three-dimensionally through the layers, i.e., radially, circumferentially and axially as it flows across the strands or filaments.

Typically, the layer of reclaimed metal has a thickness of 0.
It is on the order of 5 cm thick and its specific area is on the order of 25 cm ⁻¹ , which provides an area enhancement factor of the order of 12.5 compared to the area of a single plane surface.

In addition to wall 116 with layer 200, other walls of the assembly, such as the interior surfaces of walls 34, 56 and 84, can be provided with layers of material for the same purpose in the same manner. In the example shown, the working solution is illustrated as being sent from the absorber AB to the primary generator PG and then returned via the intermediate generator IG. However, within the scope of the invention, various variants are possible, for example the working solution can be sent first from the absorber to the intermediate generator and then returned via the primary generator, or , Split, 2
As one component, one can be sent to the primary generator and the other to the intermediate generator. In such variations, the configuration of the pumping arrangement will differ from that shown in the illustrated embodiment, for which the form of pumping required for such alternative embodiments will be readily apparent to those skilled in the art. Therefore, it will not be described here.

The illustrated embodiment has been described with respect to using the machine in a heat pump mode. It can also be used as a heat distortion device, for example, both the evaporation section and the primary generation section can be supplied with medium-grade heat, the primary condensation section can provide a low-grade heat output, and the absorption section Can provide a useful grade of heat output.

Referring to FIG. 3, this includes European Patent Application No. 327, the disclosure of which is incorporated herein by reference.
A diaphragm arrangement similar to that employed in the single effect machine illustrated in No. 230 is shown diagrammatically. Area 210
Represents a high pressure zone in which the refrigerant evaporates from the working solution (comprising refrigerant and absorbent) at wall 212 and condenses at wall 214, and U-tube throttle 216.
Via low pressure zone 218, where the cycle's evaporation and absorption mechanism takes place. The axis of rotation of the assembly is shown at 220. As can be seen, the maximum pressure difference that can be maintained for a given speed of rotation of the machine is
It is governed by the cylinder height h of the working solution. In general, the pressure difference that can be maintained is given by the equation ΔP = 1/2 · dw ² (x ² −y ² ), where d is the density of the liquid forming the cylinder,
w is the rotational speed of the assembly, and x and y are the outer diameter and inner diameter of the cylinder.

As shown in FIG. 4, the sustained pressure differential can be significantly increased without unduly increasing the extent to which the U-tube projects radially outward beyond the perimeter of zones 210 and 218. .. To achieve this, U tube 21
The six legs 222, 224 are extended to terminate near the axis 220 and provided with a pumping arrangement 216 for collecting the working solution at the outer periphery of the zone 210, which pumps the working solution radially inward. And is transferred into U-tube 216 and then to section 218. Pump action deployment 2
26 operates on the Pitot principle and comprises a tube which is constrained from rotating and collects rotating fluid around the circumference of the zone 210, so that the liquid can be obtained without the need for a separate drive source for the pump. The kinetic energy of the fluid is used to drive the radial inward.

In FIG. 5, a dual-effect machine is illustrated, which relies on an external heating / cooling source interacting with the machine to operate to achieve heat pumping, cooling or thermal deformation. it can. For this purpose, limiting the machine when used in the heat pump mode, it is described below. The working aqueous solution includes an evaporation part EV, an absorption part AB, a first solution heat exchange part 230, a second solution heat exchange part 252, and a primary steam generation part P.
G, intermediate condenser IC, intermediate generator IG, primary condenser PC
It circulates so as to be returned to the evaporation section EV around a circuit that is hermetically sealed provided with. The working solution consists of a mixture of evaporable components such as water (as a refrigerant) and a mixture of absorbents for water such as alkaline hydroxides as disclosed in EP 208427. Evaporator EV has European Patent Application No. 32723.
A number of angularly spaced elliptical cross-section tubes 23 generally constructed according to the teachings of No. 0 and mounted on wall 233.
2 in which the primary condenser PC to U-tube throttle 2
The condensed refrigerant traveling via 34 is distributed by the distributor 2 (detailed in European Patent Application No. 327230).
This distribution device 236 injects water from the area surrounding the evaporation section EV and the absorption section AB by means of a pipe 23.
Collect by 7. In the evaporator tube 232 some of the water is ambient air (or other source of low quality heat).
The vapor generated by heat exchange with the stream of
When it comes into contact with the absorbent sprayed onto the wall 242 through 40, it is recombined with the absorbent. The generated heat of the solution is transferred via the wall 242 to a load as described below.

The resulting water-rich working solution is passed through the annular passage 24.
4 (European Patent Application No. 32723)
Via a tube 246 which forms part of a rotationally constrained pitot pumping arrangement 248 detailed in No. 0).
Transferred to the solution heat exchange section 230, where heat exchange with the water-reduced working solution from the annular passage 250 associated with the intermediate generation section IG is performed. The water-rich solution then proceeds to the second solution heat exchange section 252, where
From the annular passage 254 to the pipe 253 associated with the primary generator PG
And heat exchange with the water-reduced working solution transferred via line 253a is achieved, and such transfer is accomplished by pump 248.
Is accomplished by a pitot pump 256 constrained for rotation that operates in the same manner as. Tube 253 is constrained from rotating, while tube 253a rotates with the rotating structure of the machine.

After passing through the heat exchange section 252, the water-rich solution passes into the annular passage 257 where it is picked up by the pipe 258 forming part of the pitot pump 256 and discharged onto the wall 260. The opposite side of the wall 260 is the radiant dose 26 of the burner 246 which is supplied with gas to produce high quality heat in the form of radiant energy from the radiant dose 262.
2 and the heat contained in the combustion products. Hot flue gas from burner 264 flows across the outer surface of primary generator wall 260, which is shielded by housing 266, and passes around heat exchange sections 230 and 252 before passing through annular slot 268. Exhausted through
In these heat exchange sections 230 and 252, further heat is released by the flue gas in heat exchange with the fluid flowing through the heat exchangers 230 and 252.

The water-rich solution impinging on the wall 260 of the primary generator, as it flows radially outward, is heated by heat exchange across the wall thickness, causing evaporation of the water component. The reduced constituents of absorbent and non-evaporated water flow across the face of wall 260 and are collected in annular groove 254, via heat exchange sections 252 and 230, intermediate generation section IG and annular passage 268. It is then transported back to the absorber and, in the annular passage 268, is scooped by the pipe 271 forming part of the pitot pump 248 and sent to the pipe 240 for discharge into the absorber wall 242. The resulting pressure in the area surrounding the primary generator PG and the intermediate condenser IC as a result of water evaporation is typically on the order of 3.0 bar absolute.

The evaporated component is eventually the intermediate condenser IC
And a wall 270 common to the intermediate generator IG where the water vapor on the IC side condenses as a result of heat exchange with the cooled water-reduced solution on the IG side of the wall 270, An annular passage 272 radially outwardly
Flow to. The fluid supplied to the IG side of the wall 270 is supplied from the passage 254 to the pipes 253, 253a, 274 and 276.
And the pipe 276 is connected to the pump 2
It forms part of a rotationally constrained pitot pump 278 that is arranged to operate in a manner similar to 48 and 256. The water-depleted solution from the passages 254 passes through the heat exchange section 252 in heat exchange relationship with the relatively cooled water-rich solution withdrawn from the absorber, so that it is relatively cold and, therefore, the walls. Heat is taken from the water vapor on the IC side of 270 to produce the desired condensation. Intermediate generation part I
The water-depleted solution supplied to G further generates steam due to heat transfer across the wall 270, which proceeds to the primary condenser PC and condenses. The condensed water that collects in the passage 272 forms a part of the pitot pump 256, and the pipe 2
Scooped by 80 and transferred to an annular passage 282 near the machine axis of rotation. Tube 28 in this embodiment
0 is the corresponding portion of tube 226 in FIG. Condensed water is channeled radially outward from passage 282 by a tube 284 that forms one leg of a U-tube throttle 286 that rotates with the machine. The other leg 288 of the throttle 286 routes the condensate into a low pressure zone (typically on the order of 0.3 bar absolute) surrounding the IG and PC. The condensate is fed to a point near the axis of rotation and discharged to the wall 290 so that it is radially outwardly in the annular passage 292 with the condensate drawn from the water vapor produced in the intermediate generator IG. The flow then flows via the U-tube throttle 234, the passage 238 and the distributor 236 to the evaporator EV.

A part of the condensate supplied to the passage 292 is
It is continuously recirculated by a tube 294 forming part of the pitot pump 278. As can be seen, the throttle 286 is within the limits of the housing 266, which in each case should have a diameter to accommodate the heat exchangers 230 and 252 located on the outside. Can provide cylinder heights that exceed the radial dimensions of the PG / IC and IG / PC areas.

It should be noted that the tubes 253a and 274 are noted.
And the heat exchange section 252 is also arranged to act as a U-tube throttle in the manner described with reference to FIG. In this case, the working fluid used consists of the refrigerant-depleted solution sent by the pipe 253 to the pipe 253a, where the refrigerant-depleted solution (assuming that the absorbent is a mixture of hydroxides as described above). ) Due to its high specific gravity, the tube height required to maintain the pressure differential is somewhat smaller than in the case of the throttle 286, which means that the tubes 253a and 2
The length of 74 can be correspondingly shortened as shown,
Means

The above-mentioned assembly is attached as a unit for rotating about the axis of the shaft structure S driven by the motor D. The shaft structure is solid part 296
And a hollow section consisting of a pair of concentric inlet and outlet tubes 298 and 300 for delivering the fluid medium to be heated through the chamber 302 defined by the walls 242 and 290 associated with the absorber AB and the primary condenser PC, respectively. And the chamber 302 is partitioned in the middle so that the heat-receiving fluid is flowed first across the wall 290 of the primary condenser and then over the wall 242 of the absorber. Outlet pipe 300
Sent through. In addition to this, the shaft structure is provided with a pitot pumping arrangement 248, via a bearing assembly, respectively.
Helps mount 256 and 278 so that the pump can remain stationary, while the remaining mechanical components rotate with the shaft structure.

In the illustrated embodiment, the invention has been described with respect to a dual effect generator / condenser. However, as can be seen, the invention also relates to a machine having a single effect generator / condenser and a single effect absorber / evaporator (as described in European patent application 327230), or to a European patent. It can be applied to a multi-effect machine such as that described in No. 149353.

[Brief description of drawings]

FIG. 1 is an axial sectional view of a rotary absorption heat machine according to the present invention.

FIG. 2 is an enlarged schematic view showing a heat conductive layer material bonded to a certain surface of a machine.

FIG. 3 is a diagram showing the shape of a U-tube diaphragm which is already known in the industry.

FIG. 4 is a schematic view of a U-tube throttle arrangement according to the present invention.

5 is an axial cross-sectional view of a machine incorporating a U-shaped aperture arrangement of the shape shown in FIG.

[Explanation of symbols]

 AB Absorbing part EV Evaporating part IC Intermediate condensing part IG Intermediate generating part PC Primary condensing part PG Primary generating part

Front Page Continuation (71) Applicant 591040096 Kyaradan Myra Limited Limited United Kingdom. Jiel 52.5 EP. Gloster Shear. Cheltenham. Clamwell Road (street address and other not shown) (72) Inventor Terence Leslie Winington United Kingdom. Gloucester Shear. Jacobs Knorr Burley. Hillside House (No. and other not shown) (72) Inventor Robert Larton United Kingdom. Gloucester Shear. Chayar Thong Kings Cheltenham. Haywards Road. 37 (72) Inventor Colin Ramshio United Kingdom. Checker. Noley Woolington. The Spinay. Four

Claims (10)

[Claims] 1. A rotating assembly including a steam generating section, a condensing section, an evaporating section and an absorbing section interconnected to provide a circulating fluid flow path for a volatile fluid component and an absorbent liquid thereto. Means for delivering heat to and / or from the inner surface of at least one of the generally radially extending walls of the generator, condenser, absorber and evaporator. However, due to the action of centrifugal force, as a thin film liquid, the fluid is discharged to the inner surface at a location radially inward so that the fluid flows outward in the radial direction across the inner surface. Having a heat conducting structure attached to it in contact, said heat conducting structure comprising:
Having an array of elements distributed radially and circumferentially across the inner surface, the elements deflecting the flow of the thin film liquid as it flows radially outward across the inner surface. Projecting from the outer surface to provide a surface to
An absorption cycle thermomachine, wherein the degree of protrusion of the thermal structure is substantially greater than the thickness of the thin film. 2. The machine of claim 1 wherein the thermal structure increases the effective surface area of the surface to which it is attached by a factor of at least 3. 3. The machine of claim 1 wherein the thermal structure increases the effective surface area of the surface to which it is attached by a factor of at least 10. 4. The machine according to claim 1, wherein the projection of the thermal structure is only 10 mm from the inner surface in a direction orthogonal to the inner surface. 5. The machine according to claim 1, wherein the protrusion of the thermal structure is only 5 mm from the inner surface in a direction orthogonal to the inner surface. 6. Machine according to claim 1, wherein the thermal structure has a porosity of at least 80%. 7. The machine according to claim 1, wherein the thermal structure is provided on the inner surface of the absorber. 8. The machine according to claim 1, wherein the element is constituted by strands or filaments of porous metal foam, metal mesh or metal gauze. 9. The method of claim 8 wherein the porous metal foam, metal mesh or metal gauze is bonded to the plate by vacuum brazing or diffusion bonding to achieve good thermal contact between the strands or filaments and the plate. Machine described. 10. Machine according to claim 8 or 9, wherein said porous metal foam, metal mesh or metal gauze is bonded to said inner surface on only one side of the layer, the other side of the layer being free.