EP0190319B1 - Machine frigorifique ou pompe a chaleur et pompe a jet pour celle-ci - Google Patents

Machine frigorifique ou pompe a chaleur et pompe a jet pour celle-ci Download PDF

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Publication number
EP0190319B1
EP0190319B1 EP85904230A EP85904230A EP0190319B1 EP 0190319 B1 EP0190319 B1 EP 0190319B1 EP 85904230 A EP85904230 A EP 85904230A EP 85904230 A EP85904230 A EP 85904230A EP 0190319 B1 EP0190319 B1 EP 0190319B1
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EP
European Patent Office
Prior art keywords
jet pump
heat
condensate
wall arrangement
jet
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.)
Expired
Application number
EP85904230A
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German (de)
English (en)
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EP0190319A1 (fr
Inventor
Michael Laumen
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M LAUMEN THERMOTECHNIK GmbH
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M LAUMEN THERMOTECHNIK GmbH
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Priority to AT85904230T priority Critical patent/ATE43900T1/de
Publication of EP0190319A1 publication Critical patent/EP0190319A1/fr
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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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/06—Compression machines, plants or systems with non-reversible cycle with compressor of jet type, e.g. using liquid under pressure
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof

Definitions

  • the invention relates to a refrigeration machine or heat pump according to the first part of claim 1, and to a jet pump according to the first part of claim 15, which is particularly suitable for use here.
  • Chillers in which compression is carried out in a jet pump without a compressor, have been widely described in the literature. An example of this in connection with a cooling system in chemical process engineering is explained, for example, in the journal “Heat Pumps 1978, 161, 168, from which the invention is based.
  • Low-pressure water vapor from an evaporation condenser is used as motive steam for a jet pump in the form of a steam jet compressor and sucks from a trickle evaporator. Water vapor is then condensed in a condenser and fed to a throttle device in the form of a standpipe. From there, on the one hand, the. for the formation of the propellant vapor provided portion in the evaporation condenser and on the other hand a return of the portion provided for the formation of the suction vapor via a heat exchanger in which heat is supplied to the condensate to the evaporator.
  • the condensate In the evaporator, the condensate is only partially evaporated and the non-evaporated portion of the condensate is recirculated to the circuit.
  • the evaporation energy is taken in the evaporator from the elevated temperature of the condensate supplied, so that the non-evaporated condensate leaves the evaporator at a low temperature.
  • a refrigerator which works with a jet pump as a compressor.
  • the refrigerant liquefied in a condenser is expanded or throttled by means of a porous wall or with a plurality of porous walls which are arranged in the evaporator of the heat pump.
  • the evaporation of the liquid refrigerant penetrating the porous wall takes place in this known refrigerator in the manner of a trickle evaporator in a space below the porous wall arrangement, which is connected on the suction side to the jet pump.
  • jet compressors of such refrigeration machines or heat pumps work optimally only closely around the design point of the jet pump, i. H. react to changes in pressure or temperature conditions with a drastic deterioration in the delivery number.
  • the object of the present invention is therefore to provide a refrigeration machine or heat pump or jet pump of the type specified in the preamble of claims 1 and 15, respectively, in which the delivery number of the jet compressor is considerably improved and at the same time a compact design is ensured.
  • the evaporator is formed by a wall made of porous material such as sintered metal, over the thickness of which there is a pronounced pressure drop when the suction vapor is sucked in by the propellant.
  • the porous wall acts as a throttle device.
  • the suction power of the blowing agent on the downstream side of the wall results in a pressure dependent on the throttling effect of the wall, which in any case falls below the evaporation pressure at the given temperature of the condensate.
  • a further decrease in this pressure is counteracted by the evaporation of the condensate, so that there is a dynamic equilibrium between the pressure which arises and the amount of condensate evaporated, since a further decrease in pressure would lead to increased steam generation.
  • the temperature of the porous material of the wall drops, so that it becomes a heat source and to the inflowing condensate results in an enlarged, for a given chiller essentially the maximum possible corresponding temperature difference, which favors the heat transfer of the heat of vaporization from the heat source or the condensate to the porous material.
  • good thermal conductivity of the material of the wall for example metal, this results in a largely uniform temperature over the thickness of the wall and therefore also in the case of evaporation which occurs only in the region of the downstream side, a sharp decrease in temperature of the upstream side of the wall exposed to the condensate, as well as on any surface through which heat enters the wall.
  • the steam generated on the downstream side of the wall arrangement is immediately located in the suction chamber of the jet pump, so that large-volume pipes and flow losses are largely avoided and a compact design can be achieved.
  • the mass flow resulting from the given efficiency of the jet pump and the temperature of the generated steam can be adjusted by dimensioning the consistency and the thickness of the wall arrangement, that is to say by choosing its throttling effect.
  • a certain throttling effect results in the minimum possible achievable suction pressure and thus minimum steam temperature.
  • a further increase in the throttling effect from this optimal point would only lead to a reduction in the mass flow, which is generally not desirable.
  • a reduction in the throttling effect leads to an increase in the mass flow when the temperature of the steam generated increases, which can be aimed for in some operating states.
  • the wall arrangement can thus consist of a plurality of layers or layers of a porous material of different consistency and optionally also of a plurality of spaced-apart individual walls, which can have a different consistency over their thickness and in comparison with one another.
  • the space between adjacent walls is particularly suitable, for example, for removing non-evaporated condensate in the case of circulation cooling.
  • the energy required for the evaporation is supplied via a heat-conducting connection between the wall arrangement and a heat source.
  • the wall arrangement encloses the suction space of the jet pump on the circumference and in particular approximately concentrically to its central axis of the jet pump, i. H. the propellant or mixing nozzle is arranged, a compact design with the largest possible evaporator area is made possible.
  • the wall arrangement is flowed through essentially radially from the outside inwards, as a result of which the wall arrangement encloses the suction chamber with a small diameter by means of a corresponding structural design and can thus be arranged as close as possible to the coldest point of the refrigerator. This also minimizes the so-called "dead space".
  • a throttle device is known in particular for refrigeration machines, in which the liquid refrigerant is expanded when it passes through a highly heat-conductive porous wall, which inevitably evaporates part of the liquid condensate. Because the wall is a good heat conductor, so much heat is absorbed from the environment that freezing of the throttle device is prevented.
  • the heat source according to claim 2 is a medium surrounding the jet pump, such as air in a closed room, heat can be removed directly from this closed room.
  • a medium surrounding the jet pump such as air in a closed room
  • heat can be removed directly from this closed room.
  • a medium surrounding the jet pump such as air in a closed room
  • heat can be removed directly from this closed room.
  • Such a variant is therefore particularly suitable as an integrated power and evaporator part for cold rooms such as refrigerators or freezers, the wall arrangement being quite simple inside space of the refrigerator is arranged.
  • An improvement in the heat transfer between the surrounding medium and the porous material results according to claim 3 by sheathing the wall arrangement with fins to enlarge the heat exchange surfaces, wherein the sheathing according to claim 4 can be produced particularly advantageously as an extruded piece cut to length.
  • the condensate can be introduced without problems even when the generated steam is drawn off on the side of the porous material opposite the casing in that, according to claim 5, the condensate is formed by forming corresponding channels in the casing and / or in the porous material the area of the porous material covered by the jacket is supplied.
  • the heat source can also be formed by a heat transfer medium which is guided in a metallic pipe coil and is in contact with the wall arrangement by means of surface-side installation or completely or partially embedded. Even in the case of a heat-conducting connection to a heat source via a closely fitting sheathing, such a coil could in principle be embedded in the porous material of the wall to use the heat of a heat transfer medium.
  • such a coil is advantageously arranged on the surface of the wall arrangement opposite the exit of the vapor from the porous material - possibly with a few pipe turns also at a distance from this surface - in a prechamber which is sealed off from the surroundings and in which the condensate is also present, so that a heat transfer from the coil to the condensate can take place before the condensate enters the upstream surface of the wall arrangement; In this way, pre-evaporation can already be achieved and condensate in the form of wet steam can be supplied to the wall arrangement.
  • the pipe coil can be arranged according to claim 7 when the wall arrangement is divided into a plurality of individual walls in a corresponding number of levels in the spaces between such walls and through which the heat transfer medium flows in such a way that there is a heat exchange between the liquid or in the evaporation condensate and the heat transfer medium in countercurrent.
  • Such an arrangement of pipe coils in the gap between adjacent individual walls' has the advantage of a more straightforward production compared to a basically conceivable embedding of the pipe coil in corresponding planes inside the porous material.
  • the heat in the pipe coil which can be the medium to be cooled, for example, can be removed from the heat at low temperature differences and thus under the most favorable exergetic conditions with optimal heat transfer conditions.
  • evaporation can also be carried out using the circulation method, in particular if a heat source connected to the wall arrangement in a thermally conductive manner is not available or is not to be used, or if the amount of heat required for full evaporation is not introduced by means of an additional heat transfer medium.
  • the only source of heat that can be used is the condensate itself, the large surface area of the porous material acting like a trickle evaporator.
  • a plurality of jet pumps can be connected in series, the mixed steam of an upstream jet pump serving either as a propellant - series connection - or as suction steam - cascade connection. - of the subsequent jet pump (claims 11 and 12). If more than two jet pumps are connected in series, the circuit can be implemented partly as a series connection and partly as a cascade connection.
  • the series connection according to claim 11 enables optimal use of the impulse of the propellant, as is known per se from WO 80/02 863 for vacuum technology; the nozzles of the jet pumps connected in series are matched to one another in such a way that the greatest possible pulse utilization of the propellant is achieved.
  • the pressure of the mixed steam of a jet pump can be used in a subsequent jet pump without having an adverse effect on the function of the jet pump, although the temperature and pressure reduction of the previous jet pump can no longer be fully achieved in the following jet pump.
  • each jet pump switched in this way receives the full propellant pulse.
  • a jet pump arrangement can be achieved which, compared to the temperature difference achievable with one stage between the suction space and mixed steam outlet, can produce a significantly increased temperature difference, in that the mixed steam pressure rises within the jet pump arrangement, so that after a plurality of stages at the outlet the arrangement has a high mixed steam pressure which enables condensation at high temperature.
  • cooling to low temperatures for example -10 ° C.
  • condensation for example in a hot environment, must take place at a high temperature of, for example, 40 ° C.
  • a particularly advantageous further development of the cascade circuit described consists in assigning a separate coolant to each jet pump or each specific group of jet pumps, which can be connected in series or cascade connection, and the separate cooling circuits thus formed within the cascade arrangement of the jet pumps to a certain extent to be connected in series so that the evaporator of the downstream jet pump is in heat exchange with the condenser of the upstream jet pump.
  • the downstream jet pump can be located in the area of the evaporator a heat exchange in a double phase change take place in such a way that the refrigerant to be evaporated extracts at least part of its heat of vaporization from the refrigerant to be condensed and this condenses in the process.
  • the two different refrigerants in the separate cooling circuits can serve different cooling purposes at different temperature levels.
  • Claim 9 relates to an advantageous development of a refrigeration machine or heat pump with a jet pump as a compressor, the jet pump having a plurality N of nozzles arranged one behind the other, which are assigned to N-1 jet pump stages connected in series.
  • the mixed steam from an upstream jet pump stage is used as motive steam for the subsequent jet pump stage.
  • the optimal ratio of suction gas quantity to propellant gas quantity is only met for the design point of the jet pump, - in the case of the multi-stage jet pump, due to the jet pump stages connected in series, there is a delivery area in which the optimal ratio of suction gas quantity to the amount of propellant gas significantly improved with increasing suction pressure or decreasing condensation pressure.
  • the ratio of suction gas quantity to propellant gas quantity can be optimized for a desired design area and not only for one design point by specifying the nozzle spacings, nozzle lengths of the nozzle inlet and outlet cross sections. Due to the equivalence of the switching of the individual jet pump stages of such a multiple ejector with the switching of individual jet pumps explained in connection with claim 11, the circuit examples explained for chillers or heat pumps can be transferred accordingly.
  • the nozzles of the individual jet pump stages advantageously have a diverging flow channel in the outlet-side nozzle end, with which the impulse of the mixed steam is converted into a pressure increase.
  • a jet pump which starts in the first part from a jet pump, as is known for example from US-A-2 044 811.
  • a driving nozzle and a mixing nozzle are arranged one behind the other within a common casing.
  • driving steam By Be Impact of the driving nozzle with driving steam creates a suction effect in the space between the driving nozzle and the mixing nozzle - the suction chamber.
  • the disadvantage here is that with these known jet pumps, integration into the evaporator and / or throttle device of a refrigerator or heat pump in the jet pump is only possible with a considerable enlargement of the component.
  • the characteristic features of claim 15 enable the integration of three components, namely the actual jet pump, the evaporator and the throttle device, in one component.
  • An additional advantage of such a jet pump is the filter function of the porous wall with which, for example, oil particles can be extracted from the suction flow.
  • a jet pump in the function as a fractional filter.
  • porous material as a metallic material with good heat conduction and in particular as a sintered metal is advantageous.
  • Fig. 1 shows the basic scheme of a refrigeration cycle according to the present invention.
  • a jet pump 1 with the integrated evaporator 2 made of porous material is driven by motive steam from the steam generator 4.
  • the mixed steam generated in the jet pump is condensed in the condenser 3 and part of this condensate is fed back to the evaporator 2.
  • the other part of this condensate is conveyed back into the propellant generator 4 via the liquid pump 5.
  • the drive energy Oex is fed to the steam generator 4, the heat of condensation is removed from the condenser 3 and the heat 0 0 necessary for the evaporation of the refrigerant is supplied to the evaporator 2.
  • the liquid refrigerant penetrates into the evaporator 2 made of porous material and changes to the gaseous state on the large inner surface of the porous material.
  • the liquid refrigerant is throttled by the condenser pressure P e to the pressure P o prevailing in the suction chamber of the jet pump.
  • the heat Q o necessary for the evaporation of the refrigerant can be introduced into the porous material by heat conduction or , in a special embodiment, can be removed directly from the liquid refrigerant.
  • the temperature that can be achieved in the capillary evaporator can be considerably lower than the temperature that results from the pressure P o prevailing in the suction frame of the jet pump.
  • This effect of lowering the pressure in capillary systems has already been established in connection with absorption processes. See also the Refrigeration Technology Manual by Rudolf Planck, Volume 7, Absorption Chillers by Dr. Ing. Wilhelm Niebergall, page 246, Springer-Verlag 1959. Therefore, if the heat exchange on the cold side of the refrigerator is carried out via the sintered metal, these low temperatures can be used technically. The refrigerant used is thus cooled significantly below the temperature that would result from the pressure conditions in the suction chamber.
  • Another effect that the temperature in Moving the capillary system downwards is probably a Joule / Thomson effect when the vaporized gas emerges from the capillary system and probably also a Venturi effect in the capillaries due to the suction gas flowing quickly at a 90 ° angle to the capillary outlet.
  • FIG. 2 shows a longitudinal section of an embodiment of the jet pump 1.
  • a blowing agent for example steam
  • a suction chamber 13 is arranged between the driving nozzle 11 and the mixing nozzle 12.
  • a vacuum P o is generated in the suction chamber 13 in the known manner by the propellant jet.
  • Condensate is fed via lines 14 and 15 to a storage space 16 and 17, respectively, and from there to a wall arrangement 18 in the radially outer region.
  • the wall arrangement 18 is closely surrounded on its outside by a metallic sheathing 19 which projects into the wall arrangement 18 with lamellae 20 and projects into the surrounding atmosphere with lamellae 21.
  • the fins 20 and 21 serve as heat exchange surfaces.
  • channels 22 are provided between the casing 19 and the outer region of the wall arrangement 18, which are formed by a corresponding shape or recess both on the inside of the casing 19 and on the outer circumference of the wall arrangement 18.
  • the channels 22 can be formed solely in the area of the casing 19 or the wall arrangement 18, openings being also possible in the area of the wall arrangement 18 in the area on the surface thereof.
  • the wall arrangement 18 consists of porous material, in the example of sintered metal, and is permeable to the liquid condensate at least in its surface layers.
  • condensate When condensate is supplied through the lines 14 and 15 via the voda spaces 16 and 17, it thus reaches the channels 22, which are arranged in a plurality distributed over the circumference of the wall arrangement 18, and from there penetrates into the sintered metal of the wall arrangement essentially uniformly 18 a.
  • the wall arrangement 18 serves as a throttle for the flow of the condensate, so that a pressure drop occurs in the region of the thickness of the wall arrangement 18, the pressure in the region of the downstream surface 23 of the wall arrangement 18 reaching the suction pressure Po .
  • evaporation of the condensate inevitably occurs, which leaves the surface 23 as steam and is supplied to the propellant jet.
  • the thermal energy required for the evaporation is introduced into the porous material by heat conduction via the fins 21, the casing 19 and the fins 20. In this case, heat is extracted from the surroundings of the fins 21. This heat extraction results in the desired cooling capacity.
  • the wall arrangement is designed as an elongated part with the same cross section, namely outer slats 21 and inner slats 20. Therefore, the casing can be expediently made available as an extruded piece cut to length.
  • FIG. 4 illustrates another embodiment of a jet pump, designated 24, for a refrigeration machine according to the invention.
  • the jet pump 24 in turn has a driving nozzle 11a, a suction chamber 13a with the pressure p o and a mixing nozzle 12a.
  • a wall arrangement 18a made of porous material is also provided.
  • a jacket for heat conduction is not provided close-fitting on the outer circumference of the wall arrangement 18a, but the wall arrangement 18a is surrounded by an annular prechamber 25 and sealed off from the environment in a liquid-tight manner.
  • Condensate is introduced into the prechamber 25 via a line 14a and from there is applied to the outer circumference of the wall arrangement 18a.
  • the condensate enters the surface area of the wall arrangement 18a which is permeable to condensate, evaporates there, exits as steam at the downstream surface 23a and is supplied to the propellant jet.
  • the heat required for evaporation is removed from the surroundings by heat conduction and supplied to the wall arrangement 18, in the case of the embodiment according to FIG. 4 the heat is supplied via a heat transfer medium in a line 26, which in the Area of the wall arrangement 18a is present as a highly conductive, that is metallic pipe coil 27 and closely surrounds the outer circumference of the wall arrangement 18a.
  • a heat transfer medium in a line 26 which in the Area of the wall arrangement 18a is present as a highly conductive, that is metallic pipe coil 27 and closely surrounds the outer circumference of the wall arrangement 18a.
  • a rapid temperature compensation takes place in the area of the wall arrangement 18a, so that the heat removed for evaporation inside the wall arrangement 18a leads to a strong cooling of the outer circumference of the wall arrangement 18a as well.
  • a wall arrangement 18b can also consist of a plurality of individual walls, in the example case two walls 28 and 28a. Between the two walls 28 and 28a and on their outer sides, heat can be transferred to a coil 29 which is arranged in several layers or levels 29a, 29b and 29c.
  • the direction of flow of the condensate or of the evaporating condensate illustrated by arrows in FIG. 5 illustrates that initially the foremost plane 29a of the pipe coil comes into contact with the condensate, and this can already pre-evaporate to a certain extent.
  • a further plane 29d of the pipe coil can also be arranged at a distance in front of the wall arrangement 18b, which only serves to preheat or pre-evaporate the condensate.
  • the actual evaporation then takes place in the first wall 28 of the wall arrangement 18b in the manner already explained, wherein a large part of the condensate may pass into vapor form.
  • the heat transfer medium first flows through the plane 29d, which is in the area with the highest temperature, and exits in the area of plane 29c, which is in the area with the lowest temperature, so that there are always minimal temperature differences.
  • 6 to 11 show different circuits for a refrigeration machine according to the invention in a circuit diagram, whereby jet pumps of the basic type according to FIG. 4 (with prechamber 25 and heat exchange) are always used via a heat transfer medium, unless expressly stated otherwise.
  • the diagrams also show the phase in which the medium is present, (1) denoting the liquid phase and (v) the gaseous phase.
  • the pressures p and heat flows Q or energy are entered in the diagrams in the usual manner with the usual indices, so that the circuit diagrams are largely self-explanatory and are therefore only dealt with in the following to be explained in particular.
  • FIG. 6 and 7 show a further embodiment, designated 50, of a jet pump for a refrigeration machine or heat pump according to the invention.
  • FIG. 6 shows a longitudinal section of this embodiment of the jet pump 50 and
  • FIG. 7 shows a section perpendicular to the plane designated by I-I in FIG. 6.
  • the jet pump 50 consists of a plurality of jet pump stages connected in series. Four nozzles 51, 52, 53, 54 arranged one behind the other each form the jet pump stages I, II and 111 in pairs.
  • the individual jet pump stages are separated from one another in a gas-tight manner by two boundary walls 55. Suction spaces 56, 57 and 58 of the respective jet pump stages are arranged between two nozzles.
  • the suction spaces 56, 57 and 58 are each surrounded by wall arrangements 39, 40 and 41 made of porous material, which are enclosed by a good heat-conducting jacket 42 enveloping the entire jet pump.
  • Liquid refrigerant is supplied via, for example, four condensate feeds 43, 44, 45 and 46, which are arranged in recesses in the wall arrangements 39, 40, 41 and / or the casing 42, and reaches the wall arrangements 39, 40 and 41 through openings 47 in the condensate feeds the respective jet pump stages.
  • the condensate feed could also be designed, for example, in such a way that in the individual jet pump stages the respective wall arrangement 39, 40, 41, annularly surrounding lines, are connected to the condensate feeds 43, 44, 45 and 46.
  • Another option would be to guide the condensate feed in a spiral around the wall arrangements of the individual jet pump stages.
  • a non-return valve 48 is arranged in the flow direction of the condensate.
  • the heat necessary for the evaporation of the condensate is supplied directly from the environment via the heat-conducting jacket 42.
  • the casing 42 as in the embodiment according to FIGS. 2 and 3, could also be provided with lamellae.
  • the casing 42 could also be designed as a double casing through which a heat transfer medium is passed, by means of which the heat necessary for the evaporation of the condensate is supplied or the cooling capacity is removed. It would also be possible to wrap the casing 42 with a coil, in which a heat transfer medium medium circulated.
  • the mixed steam formed in the third nozzle 53 in turn serves as motive steam for the third jet pump stage 111, in which condensate is evaporated from the wall arrangement 41 at a pressure P o3 which is higher than the pressure P o2 , so that finally the fourth emerges at the outlet Nozzle 54 mixed steam with the condenser pressure P e is present.
  • the arrangement of four nozzles is of course only an example.
  • the evaporation temperature of the condensate also increases in the respective jet pump stages. If the cooling capacity is dissipated by a heat transfer medium, this is advantageously conducted in countercurrent from the third to the first jet pump stage. If the supplied heat transfer medium has a temperature which is below the evaporation temperatures in the jet pump stages II and III or if the temperature of the heat-conducting jacket 42 drops below these temperatures, then the non-return flaps 48 close due to the pressure ratios which can thus be achieved in the jet pump, so that the jet pump stages II and III are no longer supplied with condensate.
  • a refrigeration machine or heat pump according to the invention equipped with such a jet pump regulates itself automatically according to the circumstances on the evaporator side.
  • the lowest suction steam pressure, but also the lowest heat flow, is reached; as the number of nozzles increases or from jet pump stage to jet pump stage, evaporation pressure and thus the evaporation temperature in the porous wall arrangements 39, 40, 41 as well as mass and heat flow in the respective jet pump stage .
  • the nozzle inlet diameter d e By calculating the nozzle inlet diameter d e, the nozzle exit diameter d a, the nozzle lengths 1 and the nozzle distances a from the thermodynamic characteristics of the desired Auslege Schemees and the refrigerant used can be optimized to blowing amount of steam, the ratio of Saugdampf-.
  • the nozzle geometry can also be advantageously adapted to the throttling action of the wall arrangements 39, 40 and 41. This results in a significant improvement in the part-load behavior of the refrigeration machine or heat pump according to the invention.
  • the improved efficiency with multi-ejectors results in a propellant gas requirement that is reduced by approximately 25%.
  • the combination of the integrated sintered metal evaporator and the multi-ejector thus enables a steam jet pump which, based on the end operating point, saves around 25% in operating costs and has automatic control over a wide temperature range with a continuously improving ratio of suction gas to propellant gas towards the upper end of the design range.
  • the economy of a refrigeration machine or heat pump equipped with such a multijector increases considerably.
  • wall arrangements 39 to 41 can also be designed in accordance with the embodiment shown in FIG. 5. All of the options for guiding the heat transfer medium further mentioned in the explanation of the embodiments according to FIG. 4 are also possible in the embodiment according to FIG. 6.
  • the embodiment according to FIG. 8 differs from that according to FIG. 1 essentially in that the condensate line 6 does not release the condensate in the antechamber 25 like the condensate line 14a, but rather the condensate initially in the sense of the heat transfer medium in line 26 in contact-free heat exchange is guided with the evaporator and thereby undergoes pre-cooling. Via a line 6a, the pre-cooled, still liquid condensate is fed to an external evaporator 30 which works in direct evaporation, in which heat is supplied and the condensate is evaporated, the amount of heat required for this corresponds to the useful output of the chiller.
  • the vaporous refrigerant is then fed to the pre-chamber 25 via a line 6b and released in the pre-chamber 25 in a manner similar to that in the case of the condensate line 14a in FIG. 4.
  • the condensate line 14a_ releases liquid condensate or already vaporous refrigerant in the prechamber 25.
  • liquid condensate is introduced into the pre-chamber 25 via the condensate line 14a and fed to the evaporator 2.
  • the evaporator 2 or the wall arrangement 18a may not be able to absorb significant amounts of heat by conduction or in any other way in the example.
  • the thermal energy required for evaporation is only available in the form of the energy content of the condensate. This removes heat from the condensate as evaporation begins, with the inner surface of the porous material acting like a trickle evaporator.
  • the condensate which has passed into the vapor phase arrives in the propellant stream in the manner explained, while unevaporated, cooled condensate remains.
  • refrigeration machines are realized in which a plurality of two jet pumps are connected in series in the example.
  • a cold-side circuit with internal heat exchange is shown.
  • any other variant of the heat exchange for example according to FIGS. 9 or 10, can be implemented accordingly.
  • a first jet pump 24 with a driving nozzle 11 a, suction chamber 13 a and mixing nozzle 12 a is provided, the outlet of the mixing nozzle 12 a being connected to the driving nozzle 11 a of the downstream jet pump 24.
  • the mixed steam of the upstream jet pump thus serves as a propellant for the downstream jet pump 24.
  • the pressure at the outlet of the mixing nozzle of the first jet pump 24 can again be used accordingly, albeit using a lower pulse, so that the suction pressure Po1 of the upstream jet pump 24 is lower than the suction pressure p a2 of the downstream jet pump 24.
  • the liquid heat transfer medium in line 6c finally reaches the heat exchanger 30, where direct evaporation takes place.
  • the vaporous heat transfer medium is fed via a line 6d, which is branched, to the prechambers 25 of the two jet pumps 24 via a check valve 34.
  • Complete evaporation takes place to form saturated steam from the wet steam introduced in line 6a (or in FIG. 8 and further 6b) or generated at least in the region of tube coil 27. If necessary, the condensate can be moistened further, thus increasing the energy extracted by evaporation, as is explained in more detail in connection with FIG. 5.
  • a second external evaporator 30 can be connected in the manner shown in dashed lines in FIG. 11, the arrangement being such that each evaporator 30 is assigned to one of the jet pumps 24, so that there is normally no flow in the region of the non-return valve 34 is present.
  • each of the evaporators operates in the power range of the associated jet pump 24. If only one evaporator 30 is connected to both jet pumps 24 in the manner explained above, this can be in the entire area Po1 and p o2 can be regulated, while maintaining the optimum efficiency of the propulsion jet pulse.
  • the live steam propellant generator 4 serving as a propellant in the example can be found at different pressure levels, as is additionally illustrated in dashed lines in FIG. 12.
  • a connection between the first blowing agent generator 4 and the Driving nozzle of the first jet pump 24 is closed by a schematically illustrated shut-off device 35, this line, which is only required when both jet pumps 24 are operated by a single propellant generator 4, can of course also be omitted entirely in the case of two propellant generators 4.
  • the jet pump 24 forming the last stage is connected to the propellant generator 4 which generates the highest propellant pressure in order to achieve the highest possible back pressure at the associated mixing nozzle 12a.
  • this may be the propellant generator 4 shown with solid lines.
  • the heating medium output of the propellant generator 4 illustrated with solid lines can in turn be connected to the heating medium input of the propellant generator 4 shown in dashed lines, so that it works at a lower pressure and is connected to the upstream jet pump 24.
  • the further training on the cold side there are no differences from the embodiment according to FIG. 9, so that reference can be made to this for further details.
  • the cascade circuit according to FIG. 12 is also used in principle, but both jet pumps work with different refrigerants.
  • the first jet pump 24 is assigned a cooling circuit, designated overall by 36, which instead of the usual condenser 3 has a condenser 37 which is explained in more detail below, but otherwise works according to the embodiment according to FIG. 8.
  • a cooling circuit 38 is assigned to the downstream jet pump 24, which corresponds in principle to the embodiment according to FIG. 9, wherein a circulation method according to FIG. 10 can also be used instead of the embodiment according to FIGS. 8 and 9.
  • the condenser 37 is in heat exchange with the evaporator 2 of the downstream jet pump 24, that is to say releases the heat of condensation to the downstream evaporator 2.
  • the refrigerants in the cooling circuits 36 and 38 must be selected differently, in such a way that the refrigerant of the cooling circuit 36 assigned to the upstream jet pump 24 has a condensation temperature which is approximately the same or higher at the pressure prevailing at the outlet of the upstream jet pump 24 than the evaporation temperature of the refrigerant in the cooling circuit 38 of the downstream jet pump 24 at its suction pressure p o , so that the heat required for evaporation of the refrigerant in the circuit 38 can be obtained from the condensation of the refrigerant from the circuit 36 in the region of the condenser 37.
  • the jet pump 24 according to FIG. 4, with a wall arrangement 18a made of sintered metal concentrically surrounding the central axis in the manner of a sleeve, is not only outstandingly suitable for use in all the circuits shown for refrigeration machines or heat pumps, but also has its own meaning; For example, another medium can be sucked through the sintered metal instead of a refrigerant and the filter effect of the sintered metal or another porous wall can be used to filter out substances from this medium, as explained in more detail in the introduction.
  • a particular advantage of the refrigeration machine or heat pump according to the invention is that the integration of the evaporator or the integration of several jet pump stages in a jet pump results in a very compact design.
  • maintenance is also simplified since, apart from a liquid pump and non-return valves, no moving parts are required.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Jet Pumps And Other Pumps (AREA)

Abstract

Machine frigorifique ou pompe à chaleur avec pompe à jet (1) en tant que compresseur, où l'évaporateur du circuit de la machine frigorifique ou de la pompe à chaleur est incorporé dans la pompe à jet (1). Dans le cas le plus simple, ceci est obtenu en montant dans la conduite d'admission une paroi (18, 39, 40, 41) constituée en un matériau poreux, par exemple du métal fritté, et qui exerce une action de régulation entre la pression du condenseur et la pression d'évaporation et sur la grande surface interne de laquelle a lieu l'évaporation simultanée du milieu de travail. L'alimentation en chaleur d'évaporation résulte du fait que seule une partie du milieu de travail liquide arrivant du condenseur (3) est évaporée, et que d'autre part de la chaleur peut être alimentée de l'extérieur via des échangeurs de chaleur (21, 27). Des circuits de machine frigorifique ou de pompe à chaleur ayant une pompe à jet de ce type (1, 24, 30) peuvent également être conçus avec plusieurs étages de sorte qu'un échange de chaleur interne peut s'effectuer de plusieurs manières. Les compresseurs à jet (1) utilisés peuvent également inclure des pompes à jet avec une multitude de buses (31, 32, 33, 34) situées les unes derrière les autres et formant une multitude d'étages de pompes à jet connectées en série.

Claims (17)

1. Machine frigorifique ou pompe à chaleur, comprenant :
un organe de compression constitué par un éjecteur (1 ; 24 ; 50) qui comprend un ensemble de buses (11, 12 ; 11a ; 12a ; 51, 52, 53, 54) et une chambre d'aspiration (13 ; 13a ; 56, 57, 58),
un condenseur (3 ; 37) placé en aval de l'éjecteur, un évaporateur (2) relié à l'éjecteur et dans lequel peut être produite de la vapeur d'aspiration à basse tension destinée à être aspirée par le fluide moteur et introduite dans la chambre d'aspiration (13 ; 13a ; 56, 57, 58) de l'éjecteur (1 ; 24 ; 50), et un dispositif d'étranglement destiné à agir sur le condensat, agencé en amont de la chambre d'aspiration (13 ; 13a ; 56, 57, 58) de l'éjecteur et présenté sous la forme d'un dispositif à paroi (18 ; 18a; 39, 40, 41) en matière poreuse, dont la surface (23 ; 23a) située en aval forme au moins une partie de la limite de la chambre d'aspiration (13 ; 13a ; 56, 57, 58) de l'éjecteur (1 ; 24 ; 50), dont les bords latéraux sont fermés à joint étanche aux liquides, et dans lequel au moins les couches superficielles amont de la première paroi (28) ou de l'unique paroi du dispositif à paroi (18 ; 18a ; 18b ; 39, 40, 41), considéré dans le sens de l'écoulement du condensat, sont d'une constitution perméable au condensat, caractérisée en ce que
le dispositif à paroi (18 ; 18a; 39, 40, 41) forme l'évaporateur, de sorte que l'évaporateur (2) constitue au moins une partie du dispositif d'étranglement,
en ce que le dispositif à paroi (18 ; 18a ; 39, 40, 41) est constitué par une matière poreuse faite d'une matière métallique comme, en particulier, un métal fritté,
en ce que le dispositif à paroi (18 ; 18a; 18b ; 39, 40, 41) entoure circonférentiellement la chambre d'aspiration (13 ; 13a ; 56, 57, 58) de l'éjecteur (1 ; 24 ; 50) et au moins partiellement le dispositif à buses (11, 12 ; 11a, 12a ; 51, 52, 53, 54), et est en particulier disposé concentriquement à l'axe médian de l'éjecteur (1 ; 24 ; 50), et
en ce que le dispositif à paroi (18 ; 18a; 18b ; 39, 40, 41) en matière poreuse est relié, par une liaison de transmission de la chaleur, à une source de chaleur qui fournit de l'énergie thermique à un niveau de température qui est supérieur à la température de vaporisation du condensat à la pression qui règne sur la surface aval (23 ; 23a ; 23b) du dispositif à paroi (18 ; 18b ; 39, 40, 41).
2. Machine frigorifique selon la revendication 1, caractérisée en ce que la source de chaleur est constituée par un milieu qui entoure l'éjecteur (1 ; 50), tel que de l'air ou de l'eau, et en ce qu'il est prévu, comme liaison conductrice de la chaleur, une enveloppe métallique (19 ; 42) du dispositif à paroi (19 ; 39, 40, 41) en contact étroit avec ce dispositif.
3. Machine frigorifique selon la revendication 2, caractérisée en ce que l'enveloppe (19 ; 42) est munie de lamelles (21 et 20 respectivement), extérieures, immergées dans le milieu, et/ou intérieures, immergées dans le dispositif à paroi (18 ; 39,40,41).
4. Machine frigorifique selon la revendication 3, caractérisée en ce que les lamelles (20, 21) de l'enveloppe (19 ; 42) s'étendent dans la direction longitudinale de cette enveloppe et l'enveloppe (19 ; 42) est constituée par une pièce filée à la presse, possédant la même section transversale en tous points et coupée à longueur.
5. Machine frigorifique selon une des revendications 2 à 4, caractérisée en ce qu'on fait passer le condensat dans des canaux (22 ; 43, 44, 45, 46) formés dans la matière de l'enveloppe (19; 42) et/ou dans la matière du dispositif à paroi (18 ; 39, 40, 41), à l'intérieur des couches superficielles de ce dispositif qui sont perméables au condensat.
6. Machine frigorifique selon une des revendications 1 à 5, caractérisée en ce que la source de chaleur est constituée par un milieu caloporteur qu'on fait passer dans une conduite (6 ; 6c ; 26), en ce qu'il est prévu, comme liaison conductrice de la chaleur, la paroi de la conduite qui est constituée par un serpentin tubulaire métallique (27 ; 27a), qui est en contact avec le dispositif à paroi (18a ; 18b), et en ce que le serpentin tubulaire (27 ; 27a) est agencé dans une chambre collectrice (25) isolée de l'environnement.
7. Machine frigorifique selon la revendication 6, caractérisée en ce que le serpentin tubulaire (27a) est agencé dans une pluralité de plans (29a ; 29b ; 29c), le long de parois distinctes (28, 28a) du dispositif à paroi (18b), et est parcouru par le milieu caloporteur des plans situés en amont (29a ; 29b) vers les plans situés en aval (29b ; 29c).
8. Machine frigorifique selon une des revendications 1 à 7, caractérisée en ce que, dans la région du dispositif à paroi (18a; 18b), débouche une conduite d'évacuation du liquide (32) au moyen de laquelle le condensat non vaporisé peut être renvoyé dans le circuit en passant par un échangeur de chaleur extérieur (33).
9. Machine frigorifique ou pompe à chaleur selon une des revendications précédentes, caractérisée en ce que l'éjecteur (1 ; 24 ; 50) présente une pluralité N de buses (51, 52, 53, 54) disposées l'une à la suite de l'autre, qui forment N - 1 étages éjecteurs (I, II, III) connectés en série, la vapeur mélangée issue d'un étage éjecteur amont servant de vapeur motrice pour un étage éjecteur aval.
10. Machine frigorifique selon la revendication 9, caractérisée en ce que les extrémités côté sortie des buses de la pluralité des buses (51, 52, 53, 54) présentent un canal d'écoulement divergent.
11. Machine frigorifique selon une des revendications 1 à 8, caractérisée en ce qu'une pluralité d'éjecteurs (1 ; 24 ; 50) sont connectés l'un à la suite de l'autre de telle manière que la vapeur mélangée d'un éjecteur situé en amont serve de fluide moteur pour l'éjecteur situé en aval.
12. Machine frigorifique selon une des revendications 1 à 8, caractérisée en ce qu'une pluralité d'éjecteurs (1 ; 24 ; 50) sont connectés l'un à la suite de l'autre de telle manière que la vapeur mélangée d'un éjecteur situé en amont serve de vapeur d'aspiration pour l'éjecteur situé en aval.
13. Machine frigorifique selon une des revendications 9 à 12, caractérisée en ce qu'on fait passer un milieu à refroidir à contre-courant à travers le groupe d'éjecteurs (1 ; 24; 50) ou d'étages éjecteurs (I, I1, III) connectés les uns à la suite des autres, de telle manière qu'il soit mis en relation d'échange de chaleur, tout d'abord avec le condensat ou le condensat en vaporisation du dernier éjecteur (1 ; 24 ; 50) aval du groupe ou le dernier étage éjecteur (I, II, III) aval et, en dernier lieu, avec le condensat ou le condensat en vaporisation du premier éjecteur (1 ; 24 ; 50) du groupe amont, ou le premier étage éjecteur (I, II, III) amont.
14. Machine frigorifique selon la revendication 13, caractérisée en ce que chaque éjecteur (1 ; 24 ; 50) possède son propre circuit de réfrigération (36 ; 38) contenant son propre fluide frigorigène, les fluides frigorigènes étant différents les uns des autres, en ce sens que le fluide frigorigène de l'éjecteur (1 ; 24 ; 50) situé en amont se condense, à sa pression de vapeur mélangée, à une température qui est au moins très légèrement supérieure à la température de vaporisation du fluide frigorigène de l'éjecteur (1 ; 24 ; 50) situé en aval à sa température d'aspiration, et en ce que le condenseur (37) prévu pour le fluide frigorigène de l'éjecteur situé en amont est en relation d'échange de chaleur avec le dispositif à paroi (18a ; 18b) de l'éjecteur (1 ; 24 ; 50) situé en aval.
15. Ejecteur, notamment pour une machine frigorifique ou une pompe à chaleur selon au moins une des revendications 1 à 14, comprenant :
une buse de fluide moteur (11 ; 11a ; 51, 52, 53) et une buse de mélange (12; 12a; 52, 53, 54) qui sont disposées l'une à la suite de l'autre dans une enveloppe commune (19 ; 42), et
une chambre d'aspiration (13 ; 13a; 56, 57, 58) qui s'étend entre la buse de fluide moteur (11 ; 11a ; 51, 52, 53) et la buse de mélange (12 ; 12a ; 52, 53, 54), à l'intérieur de l'enveloppe (19 ; 42), caractérisée par
un dispositif à paroi (18; 18a ; 18b ; 39, 40, 41) disposé à l'intérieur de l'enveloppe (19 ; 42), qui entoure circonférentiellement la chambre d'aspiration (13 ; 13a ; 56, 57, 58) et au moins en partie les buses de fluide moteur et de mélange (11 ; 12 ; 11a ; 12a ; 51, 52, 53, 54), et qui est en particulier disposée concentriquement à l'axe médian des buses de fluide moteur et de mélange (11, 12; 11a, 12a; 51, 52, 53, 54), au moins les couches superficielles radialement extérieures du dispositif à paroi (18, 18a; 18b ; 39, 40, 41) étant d'une constitution perméable aux liquides,
un dispositif (14, 15 ; 14a ; 43, 44, 45, 46) servant à acheminer un fluide frigorigène liquide sur une face du dispositif à paroi (18 ; 18a; 18b ; 39, 40, 41) qui est la plus éloignée de la chambre d'aspiration, et
une conduite (27 ; 27a) destinée à conduire un fluide caloporteur, qui est noyée au moins partiellement dans le dispositif à paroi (18 ; 18a ; 18b ; 39, 40, 41), de sorte que le dispositif à paroi (18 ; 18a ; 18b ; 39, 40, 41) peut être relié à une source de chaleur.
16. Ejecteur selon la revendication 15, caractérisé en ce qu'il comprend une pluralité N de buses (51, 52, 53, 54) disposées l'une à la suite de l'autre, qui forment N - 1 étages éjecteurs (I, II, III) connectés en série, la vapeur mélangée issue d'un étage éjecteur situé en amont servant de vapeur motrice pour un étage situé en aval.
17. Ejecteur selon la revendication 15 ou 16, caractérisé en ce que la matière poreuse est une matière métallique, notamment un métal fritté.
EP85904230A 1984-08-24 1985-08-23 Machine frigorifique ou pompe a chaleur et pompe a jet pour celle-ci Expired EP0190319B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85904230T ATE43900T1 (de) 1984-08-24 1985-08-23 Kaeltemaschine bzw. waermepumpe sowie strahlpumpe hierfuer.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843431240 DE3431240A1 (de) 1984-08-24 1984-08-24 Kaeltemaschine bzw. waermepumpe sowie strahlpumpe hierfuer
DE3431240 1984-08-24

Publications (2)

Publication Number Publication Date
EP0190319A1 EP0190319A1 (fr) 1986-08-13
EP0190319B1 true EP0190319B1 (fr) 1989-06-07

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US (1) US4748826A (fr)
EP (1) EP0190319B1 (fr)
JP (1) JPS62500045A (fr)
DE (2) DE3431240A1 (fr)
WO (1) WO1986001582A1 (fr)

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Also Published As

Publication number Publication date
DE3570915D1 (en) 1989-07-13
WO1986001582A1 (fr) 1986-03-13
US4748826A (en) 1988-06-07
DE3431240A1 (de) 1986-03-06
EP0190319A1 (fr) 1986-08-13
JPS62500045A (ja) 1987-01-08

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