EP0330198B1 - Wärmeaustauscher als Einspritzverdampfer für eine Kältemaschine - Google Patents

Wärmeaustauscher als Einspritzverdampfer für eine Kältemaschine Download PDF

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Publication number
EP0330198B1
EP0330198B1 EP89103178A EP89103178A EP0330198B1 EP 0330198 B1 EP0330198 B1 EP 0330198B1 EP 89103178 A EP89103178 A EP 89103178A EP 89103178 A EP89103178 A EP 89103178A EP 0330198 B1 EP0330198 B1 EP 0330198B1
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EP
European Patent Office
Prior art keywords
section
evaporator
heat exchanger
refrigerant
exchanger according
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 - Lifetime
Application number
EP89103178A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0330198A3 (en
EP0330198A2 (de
Inventor
Ulrich Dipl.- Ing. Klüe
Wilhelm Dipl.- Ing. Hartmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kluee Ulrich Dipl-Ing
Original Assignee
Kluee Ulrich Dipl-Ing
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Publication date
Application filed by Kluee Ulrich Dipl-Ing filed Critical Kluee Ulrich Dipl-Ing
Priority to AT89103178T priority Critical patent/ATE71709T1/de
Publication of EP0330198A2 publication Critical patent/EP0330198A2/de
Publication of EP0330198A3 publication Critical patent/EP0330198A3/de
Application granted granted Critical
Publication of EP0330198B1 publication Critical patent/EP0330198B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • 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
    • F25B39/022—Evaporators with plate-like or laminated elements
    • F25B39/024—Evaporators with plate-like or laminated elements with elements constructed in the shape of a hollow panel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels

Definitions

  • evaporators for refrigeration machines which also include heat pumps in the present context
  • the refrigerant is supplied in the liquid phase and discharged with mixed phases, a separator being required for phase separation. Since the pressure loss and the static pressure difference within the evaporator are small, the evaporation temperature, which is determined by the pressure of the refrigerant, is essentially constant over the height of the evaporator. This is favorable for the energy balance and for those applications in which the controllability of the temperature profile in the medium to be cooled is important, for example in the ice-free cooling of water near freezing point with a high heat flux density.
  • the plate heat exchanger for flooded evaporators (DE-A 3147378, US-A 2028213) are characterized by a refrigerant space in which the evaporating refrigerant mixture rises against gravity and which have such a large flow cross section that the mixture spreads across the width of the heat exchanger can distribute sufficiently evenly due to the effects of gravity.
  • the refrigerant is supplied to the evaporator without prior separation as a mixture of the liquid and the gaseous phase and completely evaporated, whereby to reliably avoid liquid hammer in the compressor and to control the injection valve designed as a thermostatic expansion valve a certain amount of overheating has to be accepted.
  • the expenditure on equipment for a refrigeration machine in injection mode is lower, which is why this design is often preferred for smaller systems (for example below 200 KW).
  • the forced flow is intended, on the one hand, to ensure that the compressor lubricating oil, which remains after evaporation of the refrigerant as the only liquid component in the evaporator, is discharged through a sufficient gas velocity.
  • it is intended to ensure that the heat exchanger surfaces are wetted evenly despite the small amount of liquid (only a few% by volume at the evaporator inlet) are.
  • injection evaporators It is known in the case of injection evaporators to provide a plurality of separate sections with different flow cross sections within a plate evaporator; However, these only form a structural unit, but not a functional unit, because they are each separately provided with an injection valve, which requires a high level of control engineering and construction. The basic disadvantage that a high pressure drop and thus a large temperature difference occurs in injection evaporators cannot be avoided by these means.
  • the invention aims to achieve a low pressure drop, comparable to that of a flooded evaporator.
  • the solution according to the invention consists in a method for operating a refrigeration machine, which is characterized in that the refrigerant passes from a first section of the heat exchanger with a second flow cross section and gravity distribution of the rising refrigerant into a second section with a narrower flow cross section in the not yet fully evaporated state, wherein the refrigerant in the second section has a speed sufficient to convey failed oil.
  • the invention is based on the knowledge that, in the case of an injection evaporator, a significantly increased speed of the refrigerant is only required in the area in which the complete evaporation of the liquid phase of the refrigerant takes place, so that there is uniform overheating without entrained residues of the liquid phase and because also it is only here that the concentration of the oil in the liquid refrigerant component becomes so great as a result of refrigerant evaporation that there is a risk of oil failure. Furthermore, the invention is based on the knowledge that even in the injection mode, the liquid portion in the evaporator is still large enough to ensure adequate liquid wetting of the evaporator inner surfaces even at a relatively low medium speed.
  • An evaporator for a household refrigerator is known (US Pat. No. 2,414,952) which, as the refrigerant flow increases, comprises a first section with a number of channels connected in parallel and a second, higher section which is formed by only one channel.
  • the only information about the flow cross-sections is that they should be so large in the second section that liquid refrigerant can flow back to the first section against the gas flow. The gas velocity is therefore not high enough to carry away any oil that falls out. This then accumulates in the evaporator.
  • the size of the first section in relation to the second depends on the type of refrigerant and the type and amount of compressor lubricant to be expected. The more miscible the lubricant is even with small amounts of the liquid refrigerant, the safer it can be that the lubricant is diluted so much by the liquid refrigerant in the end region of the first evaporator section and the viscosity is therefore reduced so much that it is transported with sufficient security.
  • the temperature also plays a role. A calculation has shown that when using the refrigerant Frigen R 22 using oil as a lubricant for a piston compressor, the oil is transported in the evaporator's liquid phase with sufficient certainty as long as the liquid component is not less than about 20 Weight percent of the refrigerant.
  • the first section can be designed in the manner of a flooded evaporator, namely as an essentially uniform space of comparatively large horizontal cross-section, in which the mixture can flow essentially vertically upwards.
  • Constrictions can be limited to the purpose of equalizing the flow movement over the entire cross-section and improving the heat transfer, namely preferably in the form of welded connections between the plates delimiting the flow space, which are alternately offset with respect to the vertical direction and as short welding distances, welding spots or the like can be trained.
  • Each welding point forms an evaporation core.
  • the evaporator can be used in immersed mode, i.e. in the container filled with the liquid to be cooled.
  • a collector forming the upper end of the plate can be thickened horizontally transversely to the plane of the plate in order to give the falling lines of the water flowing down from the outside a stronger horizontal component, which causes the water to spread out as a uniform film.
  • the second evaporator section is designed in the form of horizontal channels which are alternately connected at both ends, it can be provided that the uppermost of these channels is horizontally thicker than the following channels in order to perform this function.
  • an increased threshold is provided on the inlet side at the lower channel boundary.
  • devices can be provided which facilitate the entrainment of the oil to the next upper channel, for example a narrowing of the flow cross section to increase the gas velocity and to intensify the delivery effect.
  • the connecting piece discharging the refrigerant gas from the evaporator is expediently connected near the lower limit of the associated channel of the second section, so that the oil does not have to be raised again.
  • the injector supplying the evaporator is expediently a thermostatic control valve which is designed with a connection to an overheated refrigerant gas leading from the evaporator so that the refrigerant supply to the evaporator is regulated as a function of the superheating temperature. This ensures that the thermally undesired overheating area of the evaporator remains as small as possible.
  • the refrigeration machine is set so that the refrigerant essentially has a sufficient liquid portion to prevent lubricant failure when the boundary between the first and the second evaporator section is reached. Non-compliance with this condition is permitted for a short time, namely for such short periods of time that the lubricant cannot accumulate excessively in the first evaporator section and thus endanger the lubrication of the compressor.
  • the goal is achieved in this way, the total pressure loss and the Reduce evaporation temperature change to about a third.
  • the change in the evaporation temperature in a typical application is no longer acceptable at approx. 9 ° C, thanks to the invention it drops to approx. 3 ° C, whereby the greatest drop in temperature is reduced to a small, upper section of the evaporator, in which the water temperature is still comparatively high and the risk of ice formation is therefore low.
  • This makes it possible for the first time to use an injection evaporator to cool water near freezing.
  • the offset weld seam arrangement achieves a better distribution of the water film, an increased heat transfer due to a higher degree of turbulence and thereby a higher wall temperature, which likewise improves the possibilities of cooling closer to the freezing point without ice build-up.
  • the controlled and more uniform temperature curve in the evaporator plate guarantees a more uniform growth of the ice than is possible with injection evaporators of conventional design. Ice blasting from the plates by means of hot gas injection can also be used.
  • the refrigerator consists of evaporator 1, compressor 2, condenser 3 and thermostatic expansion valve 4, the pulse line 5 of which connects to a temperature sensor 6, which is arranged on line 7, which supplies the superheated gas from evaporator 1 to compressor 2.
  • the evaporator 1 is a vertical plate evaporator, through which the refrigerant flows from bottom to top. It consists of a first section 11 and a second section 12. The first section of the refrigerant flows substantially uniformly over its entire width from bottom to top similar to a flooded evaporator, with horizontal welding sections 13 arranged offset to the vertical direction ensuring a uniform flow and good heat transfer . Since the available flow cross-section is large, the pressure loss is low.
  • the flow path is formed by a meandering channel 14, which is composed of a plurality of horizontal channel sections which are alternately connected at the ends and which are formed by horizontal weld seams 15 connecting the sheets forming the plate evaporator.
  • the cross section of the channel 14 is significantly smaller than that of the first evaporator section.
  • the flow cross section in the first section is preferably at least three times, better at least five times and usually at least ten times larger than in the second section, which results in a correspondingly higher gas velocity for the second section.
  • the evaporator is operated so that the refrigerant with a bottom Weight fraction of the liquid phase of, for example, 70% is supplied.
  • the quantity supplied is determined as a function of the temperature of the superheated gas in line 7 by the injection valve. This ensures that the refrigerant always reaches the beginning of the second section 12 with such a large liquid fraction that the transport of the oil into the second section is ensured, where the refrigerant evaporates completely and the gas velocity is so high that the oil is entrained becomes.
  • a threshold 16 can expediently be provided at the beginning of the channel. Instead, it would also be conceivable to arrange the horizontal channels to fall slightly. Furthermore, baffles (not shown) can be provided in the vertical channel connections in order to intensify the gas flow there and to improve the oil transport.
  • the discharge pipe 18 is arranged near the lower boundary of the channel 17 in order to be able to discharge the oil there more easily. Furthermore, the uppermost channel 17 can be bulged more than the ones below it, in order to improve the liquid film formation on the outside of the evaporator when it is sprinkled, as is indicated by dashed lines in FIG. 2.
  • the ascending movement of the refrigerant ensures that the inner surfaces are evenly wetted despite the relatively slow flow without separation phenomena.
  • the predominantly horizontal flow is considered to be advantageous, so that in those areas in which oil must be expected to separate depending on the gas velocity, this can collect in the lower area of the horizontal channels, to a lesser extent by wetting the other inner surfaces deteriorate the heat transfer.
  • a falling connection of the horizontal channels can also be provided, the uppermost channel 17 being connected directly to the first section 11 by a vertical channel 20, as shown in FIG. 3.
  • the two evaporator sections are parts of a uniform, one-piece plate evaporator.
  • the evaporator plate (s) forming the first section being arranged in a group in a different way and at a different location than that forming the second sections. It is important that the evaporator sections form a uniform flow path connected to a single injection valve.
  • FIG. 4 illustrates the temperature profile of the refrigerant and in relation to the temperature profile 19 of the sprinkler water in ° C. over the height H of a plate heat exchanger according to FIG. 1 in solid lines.
  • the refrigerant-side temperature profiles of a flooded evaporator are shown in broken lines and a conventional injection evaporator is shown in dash-dotted lines.
  • the refrigerant and the sprinkling water move in counterflow.
  • the flooded evaporator achieves the most uniform temperature profile, in which, in a typical application example, the low pressure drop causes a temperature difference of only around 0.5 ° C across the height of the evaporator.
  • the conventional desuperheater shows a sharp drop in temperature of, for example, 9 ° C with a risk of icing up in the middle.
  • the temperature profile of the evaporator according to the invention comprises a lower section 11 ', which corresponds to the lower evaporator section 11 and in which the temperature reduction corresponds approximately to that of the flooded evaporator.
  • the second curve section 12 ' follows, which corresponds to that part of the second evaporator section 12 in which the liquid phase is still present and in which the temperature accordingly drops in accordance with the reduction in the evaporation temperature caused by the pressure drop.
  • the flow path length in the narrow flow cross section is much less than in conventional injection evaporators, only a correspondingly lower pressure loss will take place overall.
  • the lowest temperature point is close to the uppermost point of the evaporator, where the temperature of the sprinkling water is relatively high and the risk of icing is therefore low.
  • a curve section 12 ' which corresponds to that part of the second evaporator section 12 in which the overheating of the dry, gaseous refrigerant takes place.
  • the temperature profile of the injection evaporator according to the invention is very similar to that of a flooded evaporator and that it is therefore also suitable for applications in which the temperature profile of the medium to be cooled has to be controlled, for example closely its freezing point, like this is required for the water side with temperature curve 19 in diagram 4 with cooling down to 0.5 ° C.
  • the temperature in the first section remains 11 ′.
  • the dotted temperature curve 12 erargues results, the lowering of the temperature of which in relation to the water curve 19 is somewhat less favorable because the temperature minimum is reached at a lower water temperature; however, this minimum is at a higher temperature than in the case of curve 12 'because the falling arrangement of the second evaporator section enables lower gas velocities and thus less pressure loss.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP89103178A 1988-02-23 1989-02-23 Wärmeaustauscher als Einspritzverdampfer für eine Kältemaschine Expired - Lifetime EP0330198B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89103178T ATE71709T1 (de) 1988-02-23 1989-02-23 Waermeaustauscher als einspritzverdampfer fuer eine kaeltemaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8802339U 1988-02-23
DE8802339U DE8802339U1 (de) 1988-02-23 1988-02-23 Wärmeaustauscher mit geringem Druckverlust

Publications (3)

Publication Number Publication Date
EP0330198A2 EP0330198A2 (de) 1989-08-30
EP0330198A3 EP0330198A3 (en) 1990-09-19
EP0330198B1 true EP0330198B1 (de) 1992-01-15

Family

ID=6820997

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89103178A Expired - Lifetime EP0330198B1 (de) 1988-02-23 1989-02-23 Wärmeaustauscher als Einspritzverdampfer für eine Kältemaschine

Country Status (5)

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EP (1) EP0330198B1 (es)
AT (1) ATE71709T1 (es)
CH (1) CH676036A5 (es)
DE (2) DE8802339U1 (es)
ES (1) ES2029732T3 (es)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6557371B1 (en) 2001-02-08 2003-05-06 York International Corporation Apparatus and method for discharging fluid
ES2884624T3 (es) * 2019-02-04 2021-12-10 Carrier Corp Intercambiador de calor
EP4324666A1 (en) * 2021-04-13 2024-02-21 Zhejiang Sanhua Automotive Components Co., Ltd. Fluid management apparatus

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE161027C (es) *
US1622376A (en) * 1925-09-08 1927-03-29 Chicago Pneumatic Tool Co Apparatus for refrigerating systems
DE570166C (de) * 1932-04-26 1933-02-11 Linde Eismasch Ag Verfahren zum Ausgleich der Fluessigkeitsspiegel in aus mehreren Elementen bestehenden Verdampfern von Kaeltemaschinen
US2028213A (en) * 1933-04-21 1936-01-21 Arthur R Hemphill Heat exchanger or cooler
DE690583C (de) * 1936-08-28 1940-04-30 Pfaudler Co Roehrenverdampfer fuer Kaeltemaschinen
US2414952A (en) * 1944-09-08 1947-01-28 Houdaille Hershey Corp Evaporator unit
GB1286446A (en) * 1970-01-30 1972-08-23 Johannes Burmester & Co Plate heat exchanger
NL7905978A (nl) * 1979-08-03 1981-02-05 Brink Luchtverwarming Bv Warmtewisselaar, in het bijzonder voor een met gas gestookte verwarmingsinrichting.
DE3147378C2 (de) * 1981-11-30 1985-05-23 Johs. Burmester & Co GmbH, 2054 Geesthacht Rieselfilm-Verdampferplatte für eine Kälteanlage
DE3309979A1 (de) * 1983-03-19 1984-09-20 Hans 2000 Hamburg Sladky Verdampfer
FR2549585A1 (en) * 1983-07-21 1985-01-25 Axergie Sa Evaporator for an installation with a closed thermodynamic loop for the flow of a working fluid, and installation incorporating this evaporator
JPS60200089A (ja) * 1984-03-23 1985-10-09 Hitachi Ltd 直膨式蓄熱用熱交換器
US4712612A (en) * 1984-10-12 1987-12-15 Showa Aluminum Kabushiki Kaisha Horizontal stack type evaporator

Also Published As

Publication number Publication date
EP0330198A3 (en) 1990-09-19
DE8802339U1 (de) 1988-04-14
ATE71709T1 (de) 1992-02-15
ES2029732T3 (es) 1992-09-01
DE58900709D1 (de) 1992-02-27
EP0330198A2 (de) 1989-08-30
CH676036A5 (es) 1990-11-30

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