Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
  • F25B25/02—Compression-sorption machines, plants, or systems
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
  • F24D3/00—Hot-water central heating systems
  • F24D3/18—Hot-water central heating systems using heat pumps
• • 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
  • F25B37/00—Absorbers; Adsorbers
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
  • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
  • Y02B30/12—Hot water central heating systems using heat pumps

Definitions

• the invention relates to a two-component compression heat pump or refrigeration machine with a degasser and a resorber, which are interconnected to form a solution circuit in which a two-substance working medium, preferably formed by an ammonia / water mixture, is circulated, the degasser being supplied at a low pressure level gaseous working fluid component is expelled from thermal energy at a low temperature level and the resulting poor solution is conveyed to the resorber by increasing the pressure by means of a pump in a first line branch, where the gaseous working fluid component expelled in the degasifier after increasing its pressure to the resorber pressure by means of a compressor while removing the an increased temperature level, resorption heat is absorbed in the poor solution and the resulting rich solution returns to the degasser in a second line branch while reducing the pressure by means of a throttle device roms, and wherein in the sections of the first and second line branches located at the resorber pressure, a temperature changer is switched on, in which heat
• Two-component compression heat pumps or chillers operated with working fluid are used to a large extent, while in systems with low outputs, e.g. the mono- or bivalent heat pumps intended for heating single-family houses, the single-substance heat pumps operated with fluorohydrocarbons (Frigen) are used as working fluid become.
• fluorohydrocarbons fluorohydrocarbons
• the invention has for its object to provide a two-fluid compression heat pump or refrigeration machine, which provides a high performance figure even when designed for relatively low outputs, but within the cost framework for the production of single-component fluoro-hydrocarbons. Heat pumps.
• the resorber and / or the degasser is designed as a plate heat exchanger with at least one central plate, on the opposite flat sides of which are arranged at a distance and along the edges cover plates tightly connected to the middle plate each flow through at least one of the heat-exchanging media bar flow space is formed with connections provided at the opposite ends for the inlet and outlet of the heat-exchanging media and an inlet and outlet of gaseous expelled or supplied working medium component, and that the plate heat exchanger is arranged so inclined that the Inlet in the through-flow space to be flowed through for the purpose of absorption or degassing with the liquid solution is arranged higher than the outlet for the solution leaving this through-flow space.
• Plate heat exchangers are much cheaper to produce for the low capacities in question than the tube bundle heat exchangers used in large systems, without building too large.
• the inclined arrangement ensures that the rich solution to be degassed or the poor solution to be enriched by resorption of gaseous working fluid component within the heat exchanger flows through the natural gradient without a solution pump, the resulting flow rate - and thus also the heat exchanger performance - being chosen different angles of inclination can be changed or adapted to predetermined conditions without the plate heat exchanger itself having to be changed in construction or in dimensions.
• a holder or holders are provided for the plate heat exchanger forming the resorber or the degasser, in which or in which the respective plate heat exchanger can be fastened at different selectable inclination angles.
• the heat pump or chiller can thus be subsequently adjusted to different outputs or adapted to different conditions.
• the heat pump or refrigeration machine is to be manufactured with such increased performance that the single-plate heat exchangers are no longer sufficient, it is possible to stack two or more plate-type heat exchangers with their flat sides lying one on top of the other to form a resorber and / or degasifier of higher output, whereby the inlets and outlets of the flow spaces formed on both sides of the middle plate of each individual plate heat exchanger are connected in parallel.
• resorber or degassing units of higher performance can be created without the construction volume increasing inadmissibly.
• the flow velocity in the flow-through spaces can be relatively low in the case of heat pumps or refrigeration systems for small outputs, it is advisable, at least in the flow-through spaces intended for the flow of liquid solution, preferably in the form of a baffle in the respective space between the middle plate and the to arrange the respective flow space on the opposite side of the parallel cover plate arranged coarse metal mesh.
• this allows a uniform distribution of the flowing solution over the plate width and, on the other hand, the formation of a laminar one
• a heat pump designed in the manner according to the invention is intended to obtain useful heat at a higher temperature level from environmental heat contained in the ambient atmosphere, which heat is used to heat a liquid heating medium circulated in a heating circuit, the environmental heat contained in the ambient atmosphere being transferred to a heat exchanger Liquid heat transfer medium is transferred, which is circulated to the degasser and cooled there by heat exchange with the rich solution and then returned to the heat exchanger for re-heating by means of environmental heat, is provided in a preferred development of the invention that in the circuit between the heat exchanger and the degasser Instead of the normally used water-glycerine mixture, liquid two-fluid working fluid from the heat pump, i.e.
• the plate heat exchangers By designing the plate heat exchangers in such a way that the flow-through spaces are divided into separate partial flow-through spaces by partition walls which run in the direction of the fall line and are tightly connected to the middle and the respectively associated cover plate, and which can be flowed through with different flow media, into the plate heat exchangers Functions of the solution demonstration or other heat exchange functions are integrated, for which separate heat exchangers would have to be provided in the known heat pumps working with tube bundle heat exchangers as degassing or resorber units. In other words, complex heat pump circuits with which high performance figures can be achieved can be implemented without the design effort and thus the price increasing significantly.
• the heat pump is then designed, for example, in such a way that the upper throughflow area of the plate heat exchanger forming the resorber is divided into three parallel partial throughflow spaces, of which the two outer partial throughflow spaces each contain a subset of the gaseous working fluid component supplied by the compressor flow through high temperature, which then each pass through an opening in the intermediate wall to the central partial flow space, which is also flowed through by the poor solution, and that the associated lower flow space of the plate heat exchanger is divided into four parallel partial flow spaces, from which the two outer partial flow-through spaces are dimensioned in width corresponding to the two outer partial flow-through spaces of the upper flow-through space, while the two middle partial flow-through spaces as a whole Width of the middle partial flow space of the upper flow space, one of the middle partial flow spaces and the adjoining outer partial flow space connected in series through which the poor solution flowing in from the temperature changer flows before the poor solution in the middle partial Flow-through space of the upper flow-through space passes, while the other middle
• This construction enables not only the demonstration of the poor solution flowing from the temperature changer to the resorber, but also a subsequent heat exchanger for direct heat exchange with a partial amount of the gaseous working fluid component flowing from the compressor and another heat exchanger in which the remaining amount of the Compressor supplied gaseous working fluid the heating medium of the heating circuit is additionally heated in the resorber.
• a subdivision of the plate heat exchanger into a plurality of flow-through spaces is also advantageous on the degassing side, and a configuration is then expedient in which the upper flow-through space of the plate heat exchanger forming the degasser is divided into two partial flow-through spaces, of which a rich solution flows and gaseous working medium is expelled, which then passes through an opening in the intermediate wall into and flows through the second partial flow-through space before it is sucked off by the compressor, while the lower flow-through space is divided into three partial flow-through spaces, one of which is an outer partial flow-through space below of the partial flow-through space of the upper flow-through space through which the rich solution to be degassed is arranged, but in this case is narrower than this, so that a partial section of the middle partial flow-through space of the lower flow-through space n och runs below the remaining section of the first partial flow area of the upper flow area, while its second partial section runs below a partial section of the second partial section through which the gaseous working fluid component flows and the
• FIG. 1 shows a schematic circuit diagram of a two-material compression heat pump intended for heating a single-family home or a small apartment house by means of environmental heat;
• FIG. 2 shows a sectional view through the degasifier, designed as an obliquely inclined plate heat exchanger, of a two-component compression heat pump designed in the manner according to the invention, viewed in the direction of arrows 2-2 in FIG. 3b;
• 3a shows a sectional view of the degasser, seen in the direction of the arrows 3a-3a in FIG. 2;
• 3b shows a sectional view of the degasser, viewed in the direction of arrows 3b-3b in FIG. 2;
• FIG. 4a shows a sectional view of the degasser, seen in the direction of the arrows 4a-4a in FIG. 3b;
• 4b is a sectional view of the degasser, seen in the direction of arrows 4b-4b in FIG. 3a;
• Fig. 5 is a sectional view through the plate heat exchanger arranged at an incline trained resorber of a two-material compression heat pump designed in the manner according to the invention, seen in the direction of arrows 5-5 in FIG. 6b;
• FIG. 6a shows a sectional view of the resorber, seen in the direction of the arrows 6a-6a in FIG. 5;
• 6b shows a sectional view of the resorber, seen in the direction of the arrows 6b-6b in FIG. 5;
• FIG. 7a shows a sectional view of the resorber, seen in the direction of the arrows 7a-7a in FIG. 6b;
• FIG. 7b shows a sectional view of the resorber, seen in the direction of the arrows 7b-7b in FIG. 6a.
• FIG. 1 shows the basic circuit of an exemplary embodiment of a heat pump 10 designed in the manner according to the invention which will be used to generate thermal energy for heating a single-family house.
• the useful heat generated by the heat pump may be generated at a temperature level of slightly above 70 ° C, which makes it possible to heat circulated water from 40 ° C to 60 ° C in a central heating circuit.
• the heat source may be the heat energy contained in the room air within the single-family house to be heated, it being assumed that this energy is approximately at a temperature level of 20 ° C.
• the heat pump 10 thus works in recirculation mode.
• the heat pump 10 has a degasser 12, in which at a low pressure level p ⁇ of, for example, 1 bar by supplying heat energy at a low temperature level is expelled from a rich two-component working solution gaseous working component. If the preferred ammonia-water mixture is used as the working medium, ammonia is expelled in gaseous form from the solution in the degasifier 12.
• the low-temperature heat energy required to degas the rich solution is - as mentioned - taken from the room air of the house to be heated, ie it is available at around 20 ° C.
• the thermal energy is extracted from the room air in an air heat exchanger 14 and onto a liquid one
• Heat transfer medium i.e. a brine
• the working medium also used in the heat pump 10 is expedient, i.e. Ammonia-water mixture used, which is kept in line circuit 16 under increased pressure.
• the brine is thus heated in the air heat exchanger 14 - for example from -9 ° C to 16 ° C.
• gaseous working medium i.e.
• Heating of the water circulated in a central heating circuit 28 can be used.
• the water flowing to the resorber 22 from the heating circuit 28 at approximately 40 ° C. may be heated to approximately 60 ° C.
• the solution, which is rich again due to absorption of the gaseous working medium, is removed from the resorber 22 via a second line branch 30 while reducing the pressure to the pressure level PE is returned to the degasser 12 in a throttle element 32.
• a solution pump 34 is provided in the line branch 20, by means of which the pressure in the poor solution is increased from the pressure PE prevailing in the degasser to the resorber pressure PR.
• a temperature changer 36 is connected, which serves to transfer thermal energy from the rich solution flowing in the line branch 30 to the poor solution flowing in the line branch 20. If the rich solution leaving the resorber 22 has a temperature of approximately 42 ° C., it is possible to heat the poor solution flowing to the temperature changer 36 to a temperature of approximately 0 ° C. to approximately 40 ° C. To improve the performance figure of the heat pump 10 and to achieve further advantages, which will be explained in the following, additional heat exchangers are integrated in both the degasser and the resorber, which will be explained in more detail below.
• the line circuit 16 is connected to the line branch 30 via a line 38, in a region in which the latter is still under the increased absorber pressure PR. As a result, the brine circulated in the line circuit 16 is also kept at the increased absorber pressure.
• the rich solution cooled in the temperature changer 36 to approximately 12 ° C. is still cooled - still at the increased pressure PR, first in a demonstration 40 integrated in the degasifier before it is relaxed via the throttle element 32 and then finally at approximately -10 ° C. in the Degasser 12 enters.
• the poor solution in the degasser 12 which is heated to about 15 ° C. per se, is in the saturation range at the pressure pE of about 1 bar in the degasser, so that the risk cannot be excluded that it will be in the solution pump for the elimination of gaseous Working fluid in the form of bubbles and thus cavitation with the result of wear and damage to the solution pump 34 occurs when the poor solution flows directly from the degasser into the solution pump 34. For this reason, the poor solution is further cooled to about 0 ° C. in a heat exchanger section 44, which is also integrated in the degasser 12, by heat exchange with the gaseous working medium component. The occurrence of cavitation in the solution pump 34 due to the formation of bubbles from the poor solution is thus ruled out.
• the poor solution is heated to about 40 ° C. in the temperature changer 36 and therefore flows at this temperature into an
• Resorber 22 integrated demonstration 46 in which it is warmed up to about 65 ° C. by absorbing heat of absorption.
• the poor solution then flows further into a heat exchanger 48 integrated in the resorber 44, through which, on the other hand, a portion of the gaseous working fluid supplied by the compressor 26 at a temperature of 185 ° C. is supplied via a line branch 24a.
• the poor solution heats up to 71 ° C. At this temperature, the poor solution thus enters the resorber 22, into which, on the other hand, the partial amount of the gaseous working fluid component cooled in the heat exchanger 48 is introduced and resorbed in the poor solution, heat of absorption being generated.
• the remaining part of the gaseous working fluid component is not fed directly into the resorber via the line branch 24b, but first via one - again in the Resorber 22 integrated - heat exchanger 50, which on the other hand is flowed through by the water flowing through the heating circuit 28.
• the remaining part of the gaseous working fluid component is thereby also cooled down to approximately 85 ° C. and is then also resorbed in the poor solution while releasing heat of absorption.
• the resorption heat generated during the absorption of both partial quantities of the gaseous working medium component in the poor solution is transferred in the resorber to the water of the heating circuit 28 flowing to the resorber at 40 ° C., which heats up to about 57 ° C. before it enters the heat exchanger 50 continues to flow, in which it is then heated to 60 ° C. by the heat exchange with the second subset of the gaseous working medium component and can then flow in the heating circuit 28 to the radiators only shown schematically as heat consumers 52.
• FIGS. 2 to 4b The special configuration of the degasifier 12 of the heat pump 10 is shown in FIGS. 2 to 4b. It can be seen that the degasser 12 is designed as a plate heat exchanger, in which an upper and a lower throughflow space 66 are formed on both sides of a middle metal plate 60 by spaced cover plates 62 and 64, which are tightly connected along their edges to the middle metal plate , 68, which was created by an intermediate wall 70 tightly connected to the middle metal plate 60 on the one hand and the upper cover plate 62 into two upper partial flow-through spaces 72, 74 and by two parallel ones which were tight with the middle metal plate 60 on the one hand and the lower cover plate 64 on the other connected partitions 76, 78 are divided into three lower partial flow-through spaces 80, 82 and 84.
• an upper and a lower throughflow space 66 are formed on both sides of a middle metal plate 60 by spaced cover plates 62 and 64, which are tightly connected along their edges to the middle metal plate , 68, which was created by an
• the degassing device 12 is arranged in the heat pump 10 in the manner shown in FIG put on collection space 88 in the partial flow space 72 brought rich solution of the working fluid in the partial flow space 72 on the top of the middle metal plate 60 flows downwards into a collection space 90 for poor solution provided at the lower end, via a connection 92 the rich solution enters the collection space 88 and the poor solution from the collecting space 90 via the connection 94.
• a window 96 is provided in the intermediate wall 70, via which, when the rich solution on the top of the metal plate 60 flows down into the partial flow-through space 72, gaseous working fluid component passes into the partial flow-through space 74, flows through it in the downward direction and out of an am Bottom end provided port 98 is sucked to the compressor.
• the rich solution on the top of the metal plate 60 flows down into the partial flow-through space 72, gaseous working fluid component passes into the partial flow-through space 74, flows through it in the downward direction and out of an am Bottom end provided port 98 is sucked to the compressor.
• Partial flow chamber 80 is a connection 100, the serving as a heating medium and - as mentioned above - in the present case of a rich solution of the working medium also used in the circuit of the heat pump, a brine, which then flows through the partial flow chamber 80
• the partial flow-through space 80 is narrower than the partial flow-through space 72 arranged above it, so that heat from the brine serving as the heating medium only over a partial region of the width of the upper partial flow-through space 72 through the middle
• Metal plate 60 is passed. Below the remaining area of the partial flow-through space 72 is the partial flow-through space 82, which has connections 102 and 104 at its end, via which rich solution flowing in or out of the line branch 30 of the heat pump runs. The rich solution emerging from the connection 104 is then further demanded in a section of the line branch 30, in which the throttle element 32 is also arranged, before the line branch 30 opens into the connection 92 to the upper collecting space 88 for the rich solution.
• the partial flow-through space 82 which has connections 102 and 104 at its end, via which rich solution flowing in or out of the line branch 30 of the heat pump runs.
• the rich solution emerging from the connection 104 is then further demanded in a section of the line branch 30, in which the throttle element 32 is also arranged, before the line branch 30 opens into the connection 92 to the upper collecting space 88 for the rich solution.
• the partial flow-through space 82 is in turn dimensioned in such a way that it is still below that on the upper side of the partial metal flow chamber 74 formed in the middle metal plate 60, so that part of the rich solution flowing through the partial flow chamber 82 also transfers heat to the gaseous working fluid component flowing through the partial flow chamber 74.
• the partial flow-through space 84 which is finally provided and which also lies below the partial flow-through space 74 is flowed through by the poor solution emerging from the resorber, which enters and exits via the connections 106 and 108 before the poor solution in the line branch 20 the heat pump 10 reaches the solution pump 34.
• the heat-exchanging regions 40, 42 and 44 described in connection with FIG. 1 are designed to be integrated in the plate heat exchanger.
• a metal mesh 110 made of stainless steel or aluminum wire is arranged on the top and bottom of the middle metal plate 60, which on the one hand the flow of the solution over the width of the equalizes the respective partial flow channel and, on the other hand, prevents a laminar flow from being able to form in the flowing solution and thereby ensuring good heat transfer from the solution flowing in the respective partial flow space to the metal wall 60 or in the opposite direction.
• the resorber 22 is basically designed in a similar way to the degasser 12 as an obliquely inclined plate heat exchanger, in which on both sides of a central metal plate 120 through spaced cover plates 122, 124, which are tightly connected along their edges to the central metal plate, flow spaces 126, 128 are created, which in turn are divided into part flow-through spaces by partition walls, namely by two partition walls 130, 132 provided in the upper flow-through space 122 into three partial flow-through spaces 134, 136 and 138 and by three partition walls 140, 142 provided in the lower flow-through space 128. 144 into four lower partial flow spaces 146, 148, 150 and 152.
• the middle partial flow-through space 136 of the three upper partial flow-through spaces is supplied with poor solution via bores 154 from a collecting space 156, which flows to the lower collecting space 158, via windows 160 in the upper region of the intermediate walls 130, 132, gaseous working fluid component emerges from the two outer parts Flow-through spaces 138 and 134 into the middle partial flow-through space 136.
• the poor solution flowing in the central partial flow area resorbs the gaseous working fluid component entering through the windows 160, heat of absorption being generated and then rich solution collecting in the lower collecting space 158, which is discharged via the line branch 30.
• the gaseous working fluid component flows to the two outer partial flow-through spaces 138, 134 via the branch lines 24a and 24b from the compressor 26 of the heat pump 10.
• baffle plates 162 provided in the partial flow-through spaces 138, 134, each at a distance from and at an angle to one another, not only result in a swirling of the gaseous working fluid component flowing through, but also serve to separate any that may have been taken out of the compressor 26 Lubricating oil, which is droplet-shaped and can be discharged from the nozzle 164.
• the two partial flow-through spaces 146, 148, connected in series are successively flowed through by the water of the heating circuit 28, a window 166 in the intermediate wall 140 passing over the water supplied via the connection 168 from the partial flow-through space 146 to the partial flow-through space 148, from which it emerges again via the connection 170 into the heating circuit.
• the two other partial flow-through spaces 150, 152 which are also connected by a window 172, are connected in series from one another through which poor solution discharged from the line branch 20 via a connection 174 and a connection 176 flows, which solution flows out of the connection 176 into the upper collecting room 156 is continued.
• FIGS. 6a and 6b it can be seen from FIGS. 6a and 6b that the partition walls 130 and 132 in the upper flow-through space 126 are aligned with the partition walls 144, 140 in the lower flow-through space 128, i.e. that the upper partial flow spaces 134, 138 are aligned with the lower partial flow spaces 146, 152.
• FIGS. 6a and 6b also schematically indicate that the metal mesh 110 can be provided in the partial flow-through spaces through which liquid medium flows, in order to improve the heat transfer.
• FIG. 1 integrate additional heat exchanger functions.
• the dimensions of the plate heat exchangers shown in the drawing figures are, of course, only to be understood as schematic representations. In practice, the actual dimensioning of the partial flow-through spaces and the overlap of the upper and lower partial flow-through spaces must be calculated in accordance with the desired heat transfer between the heat-exchanging media.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Mechanical Engineering (AREA)
• Thermal Sciences (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Sorption Type Refrigeration Machines (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

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• 1988
  • 1988-03-12 DE DE3808257A patent/DE3808257C1/de not_active Expired
• 1989
  • 1989-02-06 WO PCT/EP1989/000109 patent/WO1989008805A1/de not_active Application Discontinuation
  • 1989-02-06 EP EP89902250A patent/EP0364515A1/de not_active Withdrawn
  • 1989-02-06 JP JP1502069A patent/JPH02503466A/ja active Pending

Non-Patent Citations (1)

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