EP2392881B1 - Heat exchanger for phase converting coolant with horizontal distribution and collection pipe - Google Patents
Heat exchanger for phase converting coolant with horizontal distribution and collection pipe Download PDFInfo
- Publication number
- EP2392881B1 EP2392881B1 EP10164993A EP10164993A EP2392881B1 EP 2392881 B1 EP2392881 B1 EP 2392881B1 EP 10164993 A EP10164993 A EP 10164993A EP 10164993 A EP10164993 A EP 10164993A EP 2392881 B1 EP2392881 B1 EP 2392881B1
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- European Patent Office
- Prior art keywords
- heat exchanger
- tube
- refrigerant
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- 239000002826 coolant Substances 0.000 title 1
- 239000003507 refrigerant Substances 0.000 claims abstract description 84
- 239000007788 liquid Substances 0.000 claims abstract description 39
- 238000000926 separation method Methods 0.000 claims description 13
- 238000005259 measurement Methods 0.000 claims 1
- 238000004781 supercooling Methods 0.000 claims 1
- 239000007789 gas Substances 0.000 description 40
- 239000003921 oil Substances 0.000 description 34
- 238000005057 refrigeration Methods 0.000 description 7
- 230000008901 benefit Effects 0.000 description 6
- 239000012071 phase Substances 0.000 description 6
- 239000010726 refrigerant oil Substances 0.000 description 6
- 238000012546 transfer Methods 0.000 description 6
- 238000013461 design Methods 0.000 description 5
- 239000007792 gaseous phase Substances 0.000 description 4
- 230000010354 integration Effects 0.000 description 4
- 239000000203 mixture Substances 0.000 description 4
- 238000001816 cooling Methods 0.000 description 3
- 238000007872 degassing Methods 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000005191 phase separation Methods 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000007791 liquid phase Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000013517 stratification Methods 0.000 description 1
Images
Classifications
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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
- F25B39/00—Evaporators; Condensers
-
- 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
- F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B9/00—Auxiliary systems, arrangements, or devices
- F28B9/02—Auxiliary systems, arrangements, or devices for feeding steam or vapour to condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B9/00—Auxiliary systems, arrangements, or devices
- F28B9/08—Auxiliary systems, arrangements, or devices for collecting and removing condensate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/02—Centrifugal separation of gas, liquid or oil
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/03—Suction accumulators with deflectors
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
-
- 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
- F25B39/028—Evaporators having distributing means
-
- 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05341—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
Definitions
- the invention relates to a multi-flow heat exchanger for a refrigerant circuit.
- Generic heat exchangers are used for example as a condenser or evaporator in refrigeration or heat pump circuits with phase-changing refrigerant.
- Mehrflutige heat exchangers consist essentially of a manifold which distributes the refrigerant to a plurality of heat exchanger tubes, a plurality of heat exchanger tubes in which the refrigerant is indirectly brought into contact with the medium to be cooled or heated and a collector in which the refrigerant after heat transfer from the different, mostly parallel heat exchanger tubes is brought together before the refrigerant then leaves the heat exchanger.
- multi-flow heat exchangers are usually formed in a vertical position of the manifolds and collectors with horizontally disposed heat transfer tubes, often the manifolds and manifolds are formed segmented, so realized in a vertical component areas for collecting and distributing refrigerant.
- a heat exchanger in a horizontal arrangement or position goes from the DE 101 11 384 B4 out. Due to the structural dimensions This heat exchanger is suitable for larger refrigeration or heat pump systems with installation on flat roofs or outdoors.
- a disadvantage of the aforementioned designs is that an effective oil separation and an effective refrigerant collector function must be taken over by additional components, which makes the use of horizontal heat exchangers more difficult and more expensive.
- the task is derived to provide a heat exchanger available at the lowest possible space and low height, the refrigerant gas or liquid distribution and oil separation before heat transfer in the heat exchanger tubes and the Kältesch remplikeits- or gas collection after heat transfer in the heat exchanger tubes with the possibility allows the phase separation of liquid and gaseous refrigerant phase.
- the object is achieved by a heat exchanger for phase-changing refrigerant with horizontal distributor tube and horizontal collector tube and intermediate refrigerant heat transfer tubes, wherein for the condenser operation of the multi-flow heat exchanger of the refrigerant gas inlet into the heat exchanger tubes in the upper region of the cross section of the manifold and the refrigerant liquid exit from the heat exchanger tubes in the upper Area of the cross section of the collector tube are arranged such that in the lower region of the cross section of the manifold Oil separation and in the lower part of the cross section of the header pipe, the refrigerant liquid separation takes place.
- the separation of the liquid from the gaseous phase in both the header and the distributor tube is realized by the arrangement of the means for taking out the phases in the respective regions of the horizontal header and distributor tubes.
- the collection or distribution of the gaseous phase takes place in each case in the upper region and the collection and distribution of the liquid phase in each case in the lower region of the collector or distributor tube cross-section.
- a horizontally arranged refrigerant gas and oil inlet nozzle are provided on the manifold and in the lower region of the cross section of the manifold a vertically arranged oil collection pipe with oil return.
- the refrigerant gas-oil mixture entering the distributor pipe is separated, whereby the gaseous phase accumulates in the horizontal distributor pipe in the upper region and the liquid oil phase in the lower region.
- the liquid oil phase is then withdrawn in the lower area via the oil collection pipe and the oil return, whereas in the upper area of the refrigerant vapor enters the heat exchanger tubes.
- the gas inlet arc enters the distributor tube horizontally in the lower part of the cross-section of the distributor tube and finally extends vertically upwards, forming a 90 ° bend.
- the gas inlet arc ends with the opening for the refrigerant gas inlet.
- the upper end of the gas inlet arc is bevelled to form a maximum baffle in the flow direction of the refrigerant vapor for the refrigerant oil droplets.
- a vertically arranged liquid outlet nozzle for the liquid refrigerant phase is provided in the lower region of the cross section of the collector tube.
- the condensed liquid phase of the refrigerant collects density-driven in the lower region of the cross section of the collector tube and then runs down through the liquid outlet nozzle.
- the refrigerant liquid outlet is formed from the heat exchanger tube in the upper region of the cross section of the collector tube via a liquid inlet arc.
- the horizontal heat exchanger tube is connected to the horizontal end of the liquid inlet arc.
- the liquid inlet arc runs, forming a 90 ° bend vertically downwards, to the collector tube and ends with the opening for the refrigerant liquid inlet in the upper region of the cross section of the collector tube.
- the invention is preferably realized in that the ratio of the tube diameter of heat exchanger tubes to distributor or collector tube is less than 0.7. This ensures that sufficient volume is made available for phase separation in the manifold and in the collector tube. According to an advantageous embodiment of the invention, a ratio of 0.2 to 0.25 is given as optimal.
- a connection for measuring devices, sensors or the like is preferably further arranged.
- the liquid outlet nozzle on the collector tube is preferably connected to a heat exchanger for subcooling the refrigerant liquid.
- the heat exchanger can be used as a flooded evaporator, wherein the horizontal distribution pipe is used in the case as a collector and the horizontal header pipe as a distributor for the refrigerant.
- FIG. 1 a heat exchanger 1 is shown in horizontal, horizontal design.
- a horizontal embodiment of the heat exchanger 1 is to be understood as meaning that the heat exchanger tubes 3 are connected to the horizontal distributor 2 horizontally in one plane in a multiple flow. This results in the flooding of the heat exchanger from the number of the Distributor tube 2 outgoing heat exchanger tubes 3.
- the heat exchanger tubes 3 pass through the heat exchanger 1 in different levels down and are introduced into the collector tube 4 in the lowest level.
- the distributor tube 2 has two gas and oil inlet connection pieces 5, via which the refrigerant vapor / oil mixture flows into the distributor tube 2 via the gas and oil inlet connection pieces 5.
- the gas and oil droplet mixture is distributed horizontally, with a separation taking place within the cross section of the distributor tube 2 in such a way that the refrigerant vapor in the upper region of the cross section and the liquid oil precipitated on the walls are deposited in the lower region of the cross section.
- the separated refrigerant oil passes via the vertically downwards from the manifold 2 outgoing oil collection pipe 7 in an oil return 8, which feeds the oil to the refrigerant circuit at a suitable location in front of the compressor, not shown again.
- the collector tube 4 forms the lowest point of the heat exchanger 1 for the accumulation of refrigerant liquid and the heat exchanger tubes 3 run in the upper region of the cross section of the collector tube 4, preferably at the highest point for the accumulation of refrigerant vapor and foreign gases.
- the condensed in the function as a condenser in the heat exchanger 1 refrigerant vapor passes as a liquid refrigerant thus in the upper region of the collector tube 4 and there is a separation possibly still existing refrigerant vapor and the refrigerant liquid over the cross section of the space of the collector tube 4 of the shape that condensed liquid refrigerant phase accumulates in the lower region and the gaseous phase of the refrigerant remains in the upper region of the collector tube 4 and there is the possibility of backward degassing in each of the collector tube 4 outgoing heat exchanger tube 3.
- the subcooling of the refrigerant remains in the heat exchanger, which has a positive effect on the efficiency of the process.
- this also leads to a lower volume for the components.
- the gas passage is effectively suppressed with pressure change due to load change, which in turn leads to an increase in the efficiency of the refrigerant circuit.
- FIG. 2 the structural configurations are shown in detail.
- the gas inlet 9 has its tapered opening for the refrigerant gas inlet in the upper region of the cross section of the manifold 2, extending vertically downwards in the arc to the side in the lower region of the manifold 2 and the distribution pipe 2 finally penetrates in the horizontal direction.
- the horizontal heat exchanger tubes 3 are connected to the horizontal ends of the gas inlet bends 9. The refrigerant gas passes via the gas inlet in the upper region of the cross section of the distributor tube 2 into the gas inlet bend 9 and through it into the heat exchanger tubes 3.
- the multiple deflection of the flow direction of the refrigerant gas ensures a separation of entrained refrigerant oil droplets, which are deposited on the walls of the manifold 2 and the gas inlet bends 9 and the contours of the manifold 2 following flow down and collect in the lower part of the manifold 2.
- the refrigerant oil is discharged via the oil collector tube 7 from the manifold 2 and passes through an oil return 8 at a suitable point back into the refrigerant circuit.
- the refrigerant gas which finally passes from the distributor tube 2 via the gas inlet bends 9 into the heat exchanger tubes 3, is now indirectly brought into thermal contact with the cooling air flow and liquefied on the way through the heat exchanger 1 down.
- the exit of the liquefied refrigerant from the heat exchanger tube 3 takes place according to FIG. 2 via a liquid inlet bend 10, which opens into the upper region of the collector tube 4.
- the end of the liquid inlet arc 10 is directly connected to the upper vertex of the collector tube 4 and soldered or welded in this, for example.
- the refrigerant liquid thus flows in the upper region in the circular cross-section space of the collector tube 4, wherein vaporous components of the refrigerant are separated from the mass flow and accumulate in the upper region of the collector tube 4.
- the refrigerant vapor in the header pipe 4 is thus able to be driven by the low density to flow back into the heat exchanger tubes 3 and then to condense further.
- the collector tube 4 has a connection as a liquid outlet nozzle 6, through which the condensate leaves the heat exchanger 1.
- a subcooler in which the condensed refrigerant is additionally subcooled to improve the efficiency of the cooling process.
- the refrigerant vapor and oil separation in the manifold 2 by the additional surfaces of the outer shell of the gas inlet arc 9 is particularly efficient and thus only very little refrigerant oil in the heat exchanger tubes 3, since the oil in a high degree in Distributed pipe 2 and discharged via the oil collector tube 7 and the oil return 8.
- the heat exchanger 1 can fulfill the function of the refrigerant collector, in particular by the volume of the collector tube 4 in a refrigerant circuit and it can be completely saved within the refrigerant circuit, the additional component of the collector.
- a particular advantage of the invention is that the refrigerant charge can be reduced by 40% to 50% by this design.
- FIG. 3 the front view of a heat exchanger 1 is shown.
- the manifold 2 and the two gas and ⁇ leinhoffsstutzen 5 form the upper horizontal position of the heat exchanger 1.
- the oil collector tube 7 and the oil return 8 are arranged approximately centrally and derive the separated refrigerant oil.
- Below the manifold 2 the levels of Heat exchanger tubes 3 visible, which are interconnected by means of sheets.
- the lowest level of the heat exchanger tubes 3 emerges horizontally from the image plane and is discharged via the gas inlet bends 9 vertically downwards.
- the gas inlet bends 9 open into the uppermost point of the collector tube 4, so that the condensed refrigerant runs down into the collector and leaves the heat exchanger 1 through the liquid outlet nozzle 6.
- the compact design of the heat exchanger 1 is very clearly visible and in particular it is shown that no additional space and in particular no additional height is required by the functional integration of oil collector and refrigerant collector in the heat exchanger.
- the heat exchanger 1 can also be used as a flooded evaporator, for example in a heat pump cycle.
- the distributor tube 2 forms the collector for the refrigerant gas from the evaporator and the collector tube 4 is the distributor for the refrigerant liquid in the heat exchanger 1, which is connected as a flooded evaporator.
- Another advantage of the realization of the invention is that an efficient backward degassing in each heat exchanger tube 3 is possible. As a result, complex measures to ensure the degassing within a refrigerant circuit are not required, which leads to further cost reductions.
- the conceptional principle of the invention is applicable to a variety of heat exchanger tasks, a particularly important application for the invention is the formation of the heat exchanger 1 as an air-cooled condenser.
- Preferred applications of the heat exchanger 1 in refrigeration circuits are in the field of stationary refrigeration, especially in the supermarket cooling.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
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Abstract
Description
Die Erfindung betrifft einen mehrflutigen Wärmeübertrager für einen Kältemittelkreislauf. Gattungsgemäße Wärmeübertrager werden beispielsweise als Kondensator oder Verdampfer in Kälte- oder Wärmepumpenkreisläufen mit phasenwechselndem Kältemittel eingesetzt.The invention relates to a multi-flow heat exchanger for a refrigerant circuit. Generic heat exchangers are used for example as a condenser or evaporator in refrigeration or heat pump circuits with phase-changing refrigerant.
Mehrflutige Wärmeübertrager bestehen im Wesentlichen aus einem Verteiler, welcher das Kältemittel auf mehrere Wärmeübertragerrohre verteilt, mehreren Wärmeübertragerrohren, in denen das Kältemittel mit dem zu kühlenden oder zu heizenden Medium indirekt in Kontakt gebracht wird und einem Sammler, in welchem das Kältemittel nach der Wärmeübertragung aus den verschiedenen, zumeist parallel geführten Wärmeübertragerrohren, zusammengeführt wird, bevor das Kältemittel dann den Wärmeübertrager verlässt.Mehrflutige heat exchangers consist essentially of a manifold which distributes the refrigerant to a plurality of heat exchanger tubes, a plurality of heat exchanger tubes in which the refrigerant is indirectly brought into contact with the medium to be cooled or heated and a collector in which the refrigerant after heat transfer from the different, mostly parallel heat exchanger tubes is brought together before the refrigerant then leaves the heat exchanger.
Im Stand der Technik sind mehrflutige Wärmeübertrager zumeist in vertikaler Aufstellung der Verteiler und Sammler mit dazwischenliegenden horizontal angeordneten Wärmeübertragerrohren ausgebildet, wobei häufig die Verteiler und Sammler segmentiert ausgebildet sind, sodass in einem vertikalen Bauteil Bereiche zum Sammeln und zum Verteilen von Kältemittel realisiert sind.In the prior art, multi-flow heat exchangers are usually formed in a vertical position of the manifolds and collectors with horizontally disposed heat transfer tubes, often the manifolds and manifolds are formed segmented, so realized in a vertical component areas for collecting and distributing refrigerant.
Für diverse Anwendungen ist eine horizontale Anordnung der Wärmeübertrager aus Platz- oder anderen Gründen jedoch wünschenswert, sodass die bekannte Kältemittelsammlung und -Verteilung in der gewohnten Weise mit vertikal angeordneten Sammler- und Verteilerbereichen innerhalb eines Bauteils aufgrund der geringen zur Verfügung stehenden Bauhöhe entfällt.For various applications, however, a horizontal arrangement of the heat exchanger for space or other reasons is desirable, so that the known refrigerant collection and distribution omitted in the usual way with vertically arranged collector and manifold areas within a component due to the low available height.
Ein Wärmeübertrager in horizontaler Anordnung oder Lage geht beispielsweise aus der
Weiterhin geht aus der
Nachteilig an vorgenannten Bauformen ist, dass eine effektive Ölabscheidung und eine effektive Kältemittelsammlerfunktion von zusätzlichen Komponenten übernommen werden müssen, was den Einsatz horizontaler Wärmeübertrager erschwert und verteuert.A disadvantage of the aforementioned designs is that an effective oil separation and an effective refrigerant collector function must be taken over by additional components, which makes the use of horizontal heat exchangers more difficult and more expensive.
Daraus leitet sich die Aufgabe ab, einen Wärmeübertrager zur Verfügung zu stellen, der bei geringstmöglichem Platzbedarf und niedriger Bauhöhe die Kältemittelgas- oder flüssigkeitsverteilung und die Ölabscheidung vor der Wärmeübertragung in den Wärmeübertragerrohren sowie die Kältemittelflüssigkeits- oder gassammlung nach der Wärmeübertragung in den Wärmeübertragerrohren mit der Möglichkeit der Phasentrennung von flüssiger und gasförmiger Kältemittelphase ermöglicht.From this, the task is derived to provide a heat exchanger available at the lowest possible space and low height, the refrigerant gas or liquid distribution and oil separation before heat transfer in the heat exchanger tubes and the Kältemittelflüssigkeits- or gas collection after heat transfer in the heat exchanger tubes with the possibility allows the phase separation of liquid and gaseous refrigerant phase.
Erfindungsgemäß wird die Aufgabe durch einen Wärmeübertrager für phasenwechselndes Kältemittel mit horizontalem Verteilerrohr und horizontalem Sammlerrohr und dazwischengeschalteten kältemittelführenden Wärmeübertragerrohren gelöst, wobei für den Verflüssigerbetrieb des mehrflutig ausgebildeten Wärmeübertragers der Kältemittelgaseintritt in die Wärmeübertragerrohre im oberen Bereich des Querschnitts des Verteilerrohres und der Kältemittelflüssigkeitsaustritt aus den Wärmeübertragerrohren im oberen Bereich des Querschnitts des Sammlerrohres derart angeordnet sind, dass im unteren Bereich des Querschnitts des Verteilerrohres die Ölabscheidung und im unteren Bereich des Querschnitts des Sammlerrohres die Kältemittelflüssigkeitsabscheidung erfolgt.According to the invention, the object is achieved by a heat exchanger for phase-changing refrigerant with horizontal distributor tube and horizontal collector tube and intermediate refrigerant heat transfer tubes, wherein for the condenser operation of the multi-flow heat exchanger of the refrigerant gas inlet into the heat exchanger tubes in the upper region of the cross section of the manifold and the refrigerant liquid exit from the heat exchanger tubes in the upper Area of the cross section of the collector tube are arranged such that in the lower region of the cross section of the manifold Oil separation and in the lower part of the cross section of the header pipe, the refrigerant liquid separation takes place.
Gemäß der Konzeption der Erfindung wird die Abscheidung der flüssigen von der gasförmigen Phase sowohl im Sammler- als auch im Verteilerrohr durch die Anordnung der Mittel zur Entnahme der Phasen in den entsprechenden Bereichen der horizontalen Sammler- und Verteilerrohre realisiert. Konzeptionsgemäß erfolgt die Sammlung oder Verteilung der gasförmigen Phase jeweils im oberen Bereich und die Sammlung und Verteilung der flüssigen Phase jeweils im unteren Bereich des Querschnitts von Sammler- oder Verteilerrohr.According to the concept of the invention, the separation of the liquid from the gaseous phase in both the header and the distributor tube is realized by the arrangement of the means for taking out the phases in the respective regions of the horizontal header and distributor tubes. According to the concept, the collection or distribution of the gaseous phase takes place in each case in the upper region and the collection and distribution of the liquid phase in each case in the lower region of the collector or distributor tube cross-section.
Durch die konzeptionsgemäße Integration dieser Funktionen in den Wärmeübertrager kann auf zusätzliche Komponenten zur Erfüllung dieser Funktionen in den jeweiligen Kältemittelkreisläufen verzichtet werden. Dies spart Platz, Bauraum und Kosten bei der Installation und im Betrieb der mit dem erfindungsgemäßen Wärmeübertrager ausgestatteten Kältemittelkreisläufen.Due to the conceptual integration of these functions in the heat exchanger can be dispensed with additional components to fulfill these functions in the respective refrigerant circuits. This saves space, space and costs in the installation and operation of the equipped with the heat exchanger refrigerant circuits according to the invention.
Nach einer vorteilhaften Ausgestaltung der Erfindung sind am Verteilerrohr ein horizontal angeordneter Kältemittelgas- und Öleintrittsstutzen und im unteren Bereich des Querschnitts des Verteilerrohres ein vertikal angeordnetes Ölsammelrohr mit Ölrückführung vorgesehen. Im Verflüssigerbetrieb wird das in das Verteilerrohr eintretende Kältemittelgas-Öl-Gemisch separiert, wobei sich in dem horizontalen Verteilerrohr im oberen Bereich die gasförmige Phase und im unteren Bereich die flüssige Öl-Phase ansammelt. Die flüssige Öl-Phase wird im unteren Bereich dann über das Ölsammelrohr und die Ölrückführung abgezogen, wohingegen im oberen Bereich der Kältemitteldampf in die Wärmeübertragerrohre eintritt.According to an advantageous embodiment of the invention, a horizontally arranged refrigerant gas and oil inlet nozzle are provided on the manifold and in the lower region of the cross section of the manifold a vertically arranged oil collection pipe with oil return. In the condenser operation, the refrigerant gas-oil mixture entering the distributor pipe is separated, whereby the gaseous phase accumulates in the horizontal distributor pipe in the upper region and the liquid oil phase in the lower region. The liquid oil phase is then withdrawn in the lower area via the oil collection pipe and the oil return, whereas in the upper area of the refrigerant vapor enters the heat exchanger tubes.
Vorteilhaft wird der Kältemittelgaseintritt in das Wärmeübertragerrohr im oberen Bereich des Querschnitts des Verteilerrohres über einen mit dem Ende des Wärmeübertragerrohres verbundenen Gaseintrittsbogen ausgebildet. Der Gaseintrittsbogen tritt im unteren Bereich des Querschnitts des Verteilerrohres horizontal in das Verteilerrohr ein und verläuft schließlich, einen 90°-Bogen bildend, vertikal nach oben. Im oberen Bereich des Querschnitts des Verteilerrohres endet der Gaseintrittsbogen mit der Öffnung für den Kältemittelgaseintritt. Zur Optimierung der Abscheidewirkung und der Strömungsmechanik ist das obere Ende des Gaseintrittsbogens angeschrägt ausgeführt, um eine maximale Prallfläche in Strömungsrichtung des Kältemitteldampfes für die Kältemittelöltröpfchen zu bilden.Advantageously, the refrigerant gas inlet into the heat exchanger tube in the upper region of the cross section of the manifold via one with the end of the Heat exchanger tube connected gas inlet arc formed. The gas inlet arc enters the distributor tube horizontally in the lower part of the cross-section of the distributor tube and finally extends vertically upwards, forming a 90 ° bend. In the upper region of the cross section of the distributor tube, the gas inlet arc ends with the opening for the refrigerant gas inlet. In order to optimize the separation effect and the fluid mechanics, the upper end of the gas inlet arc is bevelled to form a maximum baffle in the flow direction of the refrigerant vapor for the refrigerant oil droplets.
Nach einer vorteilhaften Ausgestaltung der Erfindung ist im unteren Bereich des Querschnitts des Sammlerrohres ein vertikal angeordneter Flüssigkeitsaustrittsstutzen für die flüssige Kältemittel-Phase vorgesehen. Die kondensierte flüssige Phase des Kältemittels sammelt sich dichtegetrieben im unteren Bereich des Querschnitts des Sammlerrohres und läuft dann durch den Flüssigkeitsaustrittsstutzen nach unten ab.According to an advantageous embodiment of the invention, a vertically arranged liquid outlet nozzle for the liquid refrigerant phase is provided in the lower region of the cross section of the collector tube. The condensed liquid phase of the refrigerant collects density-driven in the lower region of the cross section of the collector tube and then runs down through the liquid outlet nozzle.
Weiterhin vorteilhaft ist der Kältemittelflüssigkeitsaustritt aus dem Wärmeübertragerrohr im oberen Bereich des Querschnitts des Sammlerrohres über einen Flüssigkeitseintrittsbogen ausgebildet. Dabei ist das horizontale Wärmeübertragerrohr mit dem horizontalen Ende des Flüssigkeitseintrittsbogen verbundenen. Der Flüssigkeitseintrittsbogen verläuft schließlich, einen 90°-Bogen vertikal nach unten bildend, zum Sammlerrohr und endet mit der Öffnung für den Kältemittelflüssigkeitseintritt im oberen Bereich des Querschnitts des Sammlerrohres.Further advantageously, the refrigerant liquid outlet is formed from the heat exchanger tube in the upper region of the cross section of the collector tube via a liquid inlet arc. In this case, the horizontal heat exchanger tube is connected to the horizontal end of the liquid inlet arc. Finally, the liquid inlet arc runs, forming a 90 ° bend vertically downwards, to the collector tube and ends with the opening for the refrigerant liquid inlet in the upper region of the cross section of the collector tube.
Die Erfindung wird vorzugsweise dadurch realisiert, dass das Verhältnis der Rohrdurchmesser von Wärmeübertragerrohren zu Verteiler- oder Sammlerrohr kleiner als 0,7 ist. Damit wird realisiert, dass ausreichend Volumen für die Phasentrennung im Verteiler- und im Sammlerrohr zur Verfügung gestellt wird. Nach einer vorteilhaften Weiterbildung der Erfindung wird ein Verhältnis von 0,2 bis 0,25 als optimal angegeben.The invention is preferably realized in that the ratio of the tube diameter of heat exchanger tubes to distributor or collector tube is less than 0.7. This ensures that sufficient volume is made available for phase separation in the manifold and in the collector tube. According to an advantageous embodiment of the invention, a ratio of 0.2 to 0.25 is given as optimal.
Am Sammlerrohr ist vorzugsweise weiterhin ein Anschluss für Messgeräte, Sensoren oder Ähnliches angeordnet.At the collector pipe, a connection for measuring devices, sensors or the like is preferably further arranged.
Der Flüssigkeitsaustrittsstutzen am Sammlerrohr ist in der Ausgestaltung des Wärmeübertragers als Kondensator vorzugsweise mit einem Wärmeübertrager zur Unterkühlung der Kältemittelflüssigkeit verbunden.In the configuration of the heat exchanger as a condenser, the liquid outlet nozzle on the collector tube is preferably connected to a heat exchanger for subcooling the refrigerant liquid.
Alternativ kann der Wärmeübertrager als überfluteter Verdampfer eingesetzt werden, wobei das horizontale Verteilerrohr in dem Falle als Sammler und das horizontale Sammlerrohr als Verteiler für das Kältemittel genutzt wird.Alternatively, the heat exchanger can be used as a flooded evaporator, wherein the horizontal distribution pipe is used in the case as a collector and the horizontal header pipe as a distributor for the refrigerant.
Weitere Einzelheiten, Merkmale und Vorteile von Ausgestaltungen der Erfindung ergeben sich aus der nachfolgenden Beschreibung von Ausführungsbeispielen mit Bezugnahme auf die zugehörigen Zeichnungen. Es zeigen:
- Fig. 1:
- Perspektivische Ansicht Wärmeübertrager in liegender Ausgestaltung mit parallelen horizontalen Kältemittelverteiler- und Sammlerrohr,
- Fig. 2:
- Detail mit Querschnitt von horizontalem Verteilerrohr und horizontalem Sammlerrohr sowie Anschlüssen des Wärmeübertragers und
- Fig. 3:
- Frontansicht Wärmeübertrager.
- Fig. 1:
- Perspective view Heat exchanger in horizontal configuration with parallel horizontal refrigerant distributor and collector tube,
- Fig. 2:
- Detail with cross section of horizontal manifold and horizontal header pipe and connections of the heat exchanger and
- 3:
- Front view heat exchanger.
In
Das Sammlerrohr 4 bildet den tiefsten Punkt des Wärmübertragers 1 für die Akkumulation der Kältemittelflüssigkeit und die Wärmeübertragerrohre 3 laufen im oberen Bereich des Querschnitts des Sammlerrohres 4, vorzugsweise am höchsten Punkt zur Akkumulation des Kältemitteldampfes und von Fremdgasen, ein.The
Der in der Funktion als Verflüssiger im Wärmeübertrager 1 kondensierte Kältemitteldampf gelangt als flüssiges Kältemittel somit in den oberen Bereich des Sammlerrohres 4 und es erfolgt eine Separation eventuell noch vorhandenen Kältemitteldampfes und der Kältemittelflüssigkeit über den Querschnitt des Raumes des Sammlerrohres 4 der Gestalt, dass sich die kondensierte flüssige Kältemittel-Phase im unteren Bereich ansammelt und die gasförmige Phase des Kältemittels im oberen Bereich des Sammlerrohres 4 verbleibt und dort die Möglichkeit der Rückwärtsentgasung in jedem einzelnen vom Sammlerrohr 4 abgehenden Wärmeübertragerrohr 3 gegeben ist.The condensed in the function as a condenser in the
Als besonderen Vorteil der dargestellten Ausgestaltung der Erfindung ist herauszustellen, dass die Phasentrennung des Kältemittels nicht außerhalb des Verflüssigers erfolgt im Gegensatz zu anderen Wärmeübertragerkonzepten.As a particular advantage of the illustrated embodiment of the invention is to emphasize that the phase separation of the refrigerant does not take place outside of the condenser, in contrast to other heat transfer concepts.
Daraus resultiert, dass die Unterkühlung des Kältemittels im Wärmeübertrager verbleibt, was einen positiven Effekt für die Effizienz des Prozesses besitzt. Darüber hinaus leitet sich daraus auch ein geringeres Volumen für die Komponenten ab. Weiterhin wird der Gasdurchschuss bei Druckänderung infolge Lastwechsel wirksam unterdrückt, was wiederum zu einer Erhöhung der Effizienz des Kältemittelkreislaufes führt.As a result, the subcooling of the refrigerant remains in the heat exchanger, which has a positive effect on the efficiency of the process. In addition, this also leads to a lower volume for the components. Furthermore, the gas passage is effectively suppressed with pressure change due to load change, which in turn leads to an increase in the efficiency of the refrigerant circuit.
In
Die mehrfache Umlenkung der Strömungsrichtung des Kältemittelgases sorgt für eine Separation der mitgerissenen Kältemittelöl-Tröpfchen, welche sich an den Wandungen des Verteilerrohres 2 und der Gaseintrittsbögen 9 abscheiden und den Konturen des Verteilerrohres 2 folgend nach unten fließen und sich im unteren Bereich des Verteilerrohres 2 sammeln.The multiple deflection of the flow direction of the refrigerant gas ensures a separation of entrained refrigerant oil droplets, which are deposited on the walls of the
Besonders vorteilhaft bei dieser Ausgestaltung mit den Gaseintrittsbögen 9 ist, dass durch die mehrfache Strömungsumlenkung der dynamische Druck des Kältemittelgasstromes aus dem Gas- und Öleintrittsstutzen 5 nicht auf die Wärmeübertragerrohre 3 wirkt und somit das Mitreißen von Öltröpfchen durch den Kältemittelgasstrom weitgehend reduziert bis gänzlich ausgeschlossen ist. Ein weiterer Vorteil besteht darin, dass durch die damit konstruktiv erreichte bessere Verteilung des Gasstromes und die weitgehende Verhinderung von Kurzschlussströmen eine gleichmäßigere Flächenbelastung des Wärmeübertragers 1 erreicht wird. Darunter ist zu verstehen, dass der Kältemittelgasstrom gleichmäßiger auf die Wärmeübertragerrohre 3 verteilt wird, was die Temperaturdifferenzen im Wärmeübertrager verringert und die Effizienz desselben somit erhöht.Particularly advantageous in this embodiment with the gas inlet bends 9 is that does not act on the
Schließlich wird das Kältemittelöl über das Ölsammlerrohr 7 aus dem Verteilerrohr 2 abgeleitet und gelangt über eine Ölrückführung 8 an geeigneter Stelle zurück in den Kältemittelkreislauf.Finally, the refrigerant oil is discharged via the
Das Kältemittelgas, welches aus dem Verteilerrohr 2 über die Gaseintrittsbögen 9 schließlich in die Wärmeübertragerrohre 3 gelangt, wird nun mit dem Kühlluftstrom indirekt in thermischen Kontakt gebracht und auf dem Wege durch den Wärmeübertrager 1 nach unten verflüssigt. Der Austritt des verflüssigten Kältemittels aus dem Wärmeübertragerrohr 3 erfolgt gemäß
Das Sammlerrohr 4 weist einen Anschluss als Flüssigkeitsaustrittsstutzen 6 auf, durch welchen das Kondensat den Wärmeübertrager 1 verlässt. Nicht dargestellt ist eine vorteilhafte Weiterbildung der Erfindung, nach welcher sich an den Flüssigkeitsaustrittsstutzen 6 ein Unterkühler anschließt, in welchem das kondensierte Kältemittel zur Verbesserung der Effizienz des Kälteprozesses zusätzlich unterkühlt wird.The
Besonders vorteilhaft bei dieser Ausgestaltung der Erfindung ist, dass die Kältemitteldampf- und Ölseparation im Verteilerrohr 2 durch die zusätzlichen Flächen des Außenmantels des Gaseintrittsbogens 9 besonders effizient erfolgt und somit nur sehr wenig Kältemittelöl in die Wärmeübertragerrohre 3 hineingelangt, da das Öl in einem hohen Grade im Verteilerrohr 2 abgeschieden und über das Ölsammlerrohr 7 und die Ölrückführung 8 abgeleitet wird.It is particularly advantageous in this embodiment of the invention that the refrigerant vapor and oil separation in the
Durch die verhältnismäßig große Ausbildung des Verteilerrohres 2 und des Sammlerrohres 4 kann der Wärmeübertrager 1 die Funktion des Kältemittelsammlers, insbesondere durch das Volumen des Sammlerrohres 4 in einem Kältemittelkreislauf erfüllen und es kann das zusätzliche Bauteil des Sammlers innerhalb des Kältemittelkreislaufes gänzlich eingespart werden. Ein besonderer Vorteil der Erfindung besteht darin, dass die Kältemittelfüllmenge um 40 % bis 50 % durch diese Bauweise reduziert werden kann.Due to the relatively large design of the
In
Besonders vorteilhaft ist, dass der Wärmeübertrager 1 auch als überfluteter Verdampfer, beispielsweise in einem Wärmepumpenkreislauf, eingesetzt werden kann. Dabei bildet funktionsgemäß umgekehrt das Verteilerrohr 2 den Sammler für das Kältemittelgas aus dem Verdampfer und das Sammlerrohr 4 ist der Verteiler für die Kältemittelflüssigkeit in dem als überfluteten Verdampfer geschalteten Wärmeübertrager 1.It is particularly advantageous that the
Da derartige Kältekreisläufe mit dem Wärmeübertrager ohne Sammler betreibbar sind, ergeben sich diverse Vorteile. Beispielsweise können die Kältemittelfüllmengen in diesen Kreisläufen durch die Funktionsintegration des Sammlers in den Verflüssiger reduziert werden, was neben der aus ökologisch und wirtschaftlich günstigen Minimierung der Kältemittelfüllmengen für den Kältekreislauf zu einer Reduktion der Baugröße derartiger Kälteanlagen und somit zu sinkenden Kosten bei der Installation und der Investition derartiger Kreisläufe führt.Since such refrigeration circuits can be operated with the heat exchanger without a collector, there are various advantages. For example, the refrigerant charge in these circuits can be reduced by the functional integration of the collector in the condenser, which in addition to the ecologically and economically favorable minimization of refrigerant charge for the refrigeration cycle to reduce the size of such refrigeration systems and thus to falling costs in installation and investment leads to such circuits.
Besonders vorteilhaft ist, dass der Ölverschleppung in einem solchen Kreislauf durch die Integration der Ölabscheidung in das Verteilerrohr 2 entgegengewirkt werden kann.It is particularly advantageous that the Ölverschleppung can be counteracted in such a circuit by the integration of the oil separation in the
Ein weiterer Vorzug der erfindungsgemäßen Realisierung besteht darin, dass auch eine effiziente Rückwärtsentgasung in jedem einzelnen Wärmeübertragerrohr 3 möglich ist. Dadurch sind aufwändige Maßnahmen zur Sicherstellung der Entgasung innerhalb eines Kältemittelkreislaufes nicht erforderlich, was zu weiteren Kostenreduktionen führt.Another advantage of the realization of the invention is that an efficient backward degassing in each
Das konzeptionsgemäße Prinzip der Erfindung ist für verschiedenste Wärmeübertrager-Aufgaben anwendbar, ein besonders wichtiges Einsatzgebiet für die Erfindung besteht in der Ausbildung der Wärmeübertrager 1 als luftgekühlte Verflüssiger.The conceptional principle of the invention is applicable to a variety of heat exchanger tasks, a particularly important application for the invention is the formation of the
Weitere Einsatzgebiete bestehen wie erwähnt im Einsatz des Wärmeübertragers 1 als überflutete Verdampfer, beispielsweise bei Wärmepumpenanlagen.Other applications are as mentioned in the use of the
Besonders vorteilhaft ist weiterhin, dass die Parallelschaltung mehrerer erfindungsgemäßer Wärmeübertrager ohne die im Stand der Technik bekannten Problem der ungleichmäßigen Flächenbelastung und der Temperaturschichtung möglich ist.It is furthermore particularly advantageous that the parallel connection of a plurality of heat exchangers according to the invention is possible without the problem of the uneven surface loading and the temperature stratification which is known in the prior art.
Bevorzugte Einsatzgebiete der Wärmeübertrager 1 in Kältekreisläufen liegen auf dem Gebiet der stationären Kälteerzeugung, insbesondere bei der Supermarktkühlung.Preferred applications of the
- 11
- WärmeübertragerHeat exchanger
- 22
- Verteilerrohrmanifold
- 33
- Wärmeübertragerrohreheat exchanger tubes
- 44
- Sammlerrohrcollector pipe
- 55
- Gas- und ÖleintrittsstutzenGas and oil inlet nozzle
- 66
- FlüssigkeitsaustrittsstutzenFluid outlet port
- 77
- ÖlsammlerrohrOil collector tube
- 88th
- ÖlrückführungOil return
- 99
- GaseintrittbogenGas inlet arc
- 1010
- FlüssigkeitseintrittsbogenLiquid entrance arch
Claims (8)
- A heat exchanger (1) for phase-changing refrigerant having a horizontal distributor tube (2) and having a horizontal collector tube (4) and having refrigerant-conducting heat exchanger tubes (3) connected between these, characterized in that for the condenser operation of the multi-channel heat exchanger (1) the refrigerant gas inlet into the heat exchanger tubes (3) is arranged in the upper region of the cross-section of the distributor tube (2) and the refrigerant liquid outlet out of the heat exchanger tube (3) is arranged in the upper region of the cross-section of the collector tube (4) such that the oil separation takes place in the lower region of the cross-section of the distributor tube (2) and the refrigerant liquid separation takes place in the lower region of the cross section of the collector tube (4).
- The heat exchanger (1) according to Claim 1, characterized in that on the distributor tube (2) a horizontally arranged refrigerant gas- and oil inlet connecting piece (5) and in the lower region of the cross-section of the distributor tube (2) a vertically arranged oil collector tube (7) with oil return (8) are provided.
- The heat exchanger (1) according to Claim 1 or 2, characterized in that the refrigerant gas inlet into the heat exchanger tube (3) in the upper region of the cross-section of the distributor tube (2) is constructed by a gas inlet bend (9), connected with the end of the heat exchanger tube (3), which in the lower region of the cross-section of the distributor tube (2) enters horizontally into the distributor tube (2) and runs as a bend vertically upwards and in the upper region of the cross-section of the distributor tube (2) terminates with the opening for the refrigerant gas inlet.
- The heat exchanger (1) according to one of Claims 1 to 3, characterized in that in the lower region of the cross-section of the collector tube (4) a vertically arranged liquid outlet connecting piece (6) is provided.
- The heat exchanger (1) according to one of Claims 1 to 4, characterized in that the refrigerant liquid outlet out of the heat exchanger tube (3) in the upper region of the cross-section of the collector tube (4) is constructed by a liquid inlet bend (10), connected with the end of the heat exchanger tube (3), which terminates vertically in the upper region of the cross-section of the collector tube (4) with the opening for the refrigerant liquid inlet into the collector tube (4).
- The heat exchanger (1) according to one of Claims 1 to 5, characterized in that on the collector tube (4) a connection is provided for a measurement device or a sensor.
- The heat exchanger (1) according to one of Claims 1 to 6, characterized in that the liquid outlet connecting piece (6) is connected with a heat exchanger for the supercooling of the refrigerant liquid.
- The heat exchanger (1) according to Claim 1, characterized in that for the operation of the heat exchanger (1) as a flooded evaporator, the horizontal distributor tube (2) is constructed as a collector and the horizontal collector tube (4) is constructed as a distributor for the refrigerant.
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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EP10164993A EP2392881B1 (en) | 2010-06-04 | 2010-06-04 | Heat exchanger for phase converting coolant with horizontal distribution and collection pipe |
PCT/EP2011/058421 WO2011151218A1 (en) | 2010-06-04 | 2011-05-24 | Heat exchanger for phase-changing refrigerant, with horizontal distributing and collecting tube |
BR112012030597-2A BR112012030597B1 (en) | 2010-06-04 | 2011-05-24 | heat exchanger |
US13/687,191 US9945593B2 (en) | 2010-06-04 | 2012-11-28 | Heat exchanger for phase-changing refrigerant, with horizontal distributing and collecting tube |
CL2012003394A CL2012003394A1 (en) | 2010-06-04 | 2012-12-03 | Heat exchanger for phase change coolant, it has a horizontal distributor tube, a horizontal collector tube and heat exchange tubes with a refrigerant gas inlet arranged in the upper region of the cross section of the distributor tube, and the coolant outlet It is arranged in the upper region of the cross section of the collecting tube. |
Applications Claiming Priority (1)
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EP10164993A EP2392881B1 (en) | 2010-06-04 | 2010-06-04 | Heat exchanger for phase converting coolant with horizontal distribution and collection pipe |
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EP2392881A1 EP2392881A1 (en) | 2011-12-07 |
EP2392881B1 true EP2392881B1 (en) | 2013-01-02 |
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US (1) | US9945593B2 (en) |
EP (1) | EP2392881B1 (en) |
BR (1) | BR112012030597B1 (en) |
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EP3370020B1 (en) * | 2015-10-26 | 2020-07-01 | Mitsubishi Electric Corporation | Refrigerant distributor, and air conditioner using same |
CN209054801U (en) * | 2016-03-31 | 2019-07-02 | 三菱电机株式会社 | Heat exchanger and refrigerating circulatory device |
CN109073282B (en) * | 2016-04-18 | 2021-06-01 | 江森自控科技公司 | Condenser-evaporator system for refrigeration system |
US10274221B1 (en) * | 2017-12-22 | 2019-04-30 | Mitek Holdings, Inc. | Heat exchanger |
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US3691786A (en) * | 1971-03-31 | 1972-09-19 | Heil Quaker Corp | Air condition apparatus with refrigerant super cooler |
US3828567A (en) * | 1973-05-01 | 1974-08-13 | Carrier Corp | Level controller and liquid remover for a refrigeration system |
US4566527A (en) * | 1980-09-15 | 1986-01-28 | Pell Kynric M | Isothermal heat pipe system |
JPS58168864A (en) * | 1982-03-26 | 1983-10-05 | クラリオン株式会社 | Oil separator |
JPS61186164A (en) * | 1985-02-15 | 1986-08-19 | Sanden Corp | Production of aluminum heat exchanger |
JPH0258665U (en) * | 1988-10-18 | 1990-04-26 | ||
US4966230A (en) * | 1989-01-13 | 1990-10-30 | Modine Manufacturing Co. | Serpentine fin, round tube heat exchanger |
JP3087362B2 (en) * | 1991-08-09 | 2000-09-11 | 株式会社日立製作所 | Air conditioner |
US5551507A (en) * | 1995-03-17 | 1996-09-03 | Russell A Division Of Ardco, Inc. | Finned heat exchanger support system |
CA2160274C (en) * | 1995-10-11 | 2000-05-30 | Stanley H. Sather | Heat exchanger for a pulp dryer |
JPH10185361A (en) * | 1996-12-26 | 1998-07-14 | Calsonic Corp | Condenser |
IT1312201B1 (en) | 1999-04-21 | 2002-04-09 | Luve Spa | STRUCTURE OF HEAT EXCHANGERS WITH FINNED PACKAGE EQUIPPED WITH SIDE PROFILES OF STRENGTHENING AND REINFORCEMENT, COOPERATING WITH |
DE10111384B4 (en) | 2001-03-09 | 2004-08-05 | Löffler, Bernd | Finned tube heat exchanger |
JP4052827B2 (en) * | 2001-11-07 | 2008-02-27 | 本田技研工業株式会社 | Centrifugal gas-liquid separator |
US20060048929A1 (en) * | 2004-09-09 | 2006-03-09 | Aaron David A | Header and coil connections for a heat exchanger |
KR101175804B1 (en) * | 2005-05-18 | 2012-08-24 | 엘지전자 주식회사 | Horizontal Accumulator |
JP4904975B2 (en) * | 2006-08-08 | 2012-03-28 | 株式会社ノーリツ | Heat exchanger and water heater |
JP2010243108A (en) * | 2009-04-08 | 2010-10-28 | Sanden Corp | Oil separator |
-
2010
- 2010-06-04 EP EP10164993A patent/EP2392881B1/en active Active
-
2011
- 2011-05-24 BR BR112012030597-2A patent/BR112012030597B1/en not_active IP Right Cessation
- 2011-05-24 WO PCT/EP2011/058421 patent/WO2011151218A1/en active Application Filing
-
2012
- 2012-11-28 US US13/687,191 patent/US9945593B2/en active Active
- 2012-12-03 CL CL2012003394A patent/CL2012003394A1/en unknown
Also Published As
Publication number | Publication date |
---|---|
EP2392881A1 (en) | 2011-12-07 |
BR112012030597B1 (en) | 2020-07-28 |
WO2011151218A1 (en) | 2011-12-08 |
CL2012003394A1 (en) | 2013-07-05 |
US9945593B2 (en) | 2018-04-17 |
US20130327503A1 (en) | 2013-12-12 |
BR112012030597A2 (en) | 2017-06-20 |
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