CN101688731A - The micro-channel evaporator of band frosting Detection ﹠ Controling - Google Patents
The micro-channel evaporator of band frosting Detection ﹠ Controling Download PDFInfo
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- CN101688731A CN101688731A CN200780052876A CN200780052876A CN101688731A CN 101688731 A CN101688731 A CN 101688731A CN 200780052876 A CN200780052876 A CN 200780052876A CN 200780052876 A CN200780052876 A CN 200780052876A CN 101688731 A CN101688731 A CN 101688731A
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- vapor compression
- refrigerant vapor
- compression system
- heat exchanger
- evaporimeter
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/002—Defroster control
- F25D21/006—Defroster control with electronic control circuits
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/06—Removing frost
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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
- F25B39/02—Evaporators
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/02—Detecting the presence of frost or condensate
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A kind of refrigerant vapor compression system comprises evaporimeter, and this evaporimeter has the flat heat exchange tube of a plurality of longitudinal extensions of arranging with parallel spaced-apart relation.Each heat exchanger tube all has flat cross section, and defines refrigerant flow channels a plurality of separation, longitudinal extension.One or more frosting detecting sensors are mounted to related with evaporator operation, are used to detect the frosting/icing existence at least one flat heat exchange tube and the relevant thermofin.Defrost system is provided, and this defrost system and this evaporating heat exchanger operative association.Controller function connects this defrost system and this one or more frosting detecting sensors, has the signal of frosting on this controller response expression flat heat exchange tube and the thermofin, optionally activates this defrost system to start the evaporator defrost circulation.
Description
Technical field
[0001] the present invention relates generally to evaporating heat exchanger, particularly the long-pending frost on the outer surface of evaporating heat exchanger with a plurality of parallel, flat heat exchange tube is provided the control of improvement.
Background technology
[0002] adopt the air-conditioning of refrigerant vapor compression cycle and heat pump to be generally used for cooling off or cooling is supplied to the air of the zone of comfort of the climate controlled in shelter, office building, hospital, school, restaurant or other facilities.Refrigerant vapor compression system also is generally used for cooling off air, or other secondary media, as water or ethylene glycol solution, think that the Food ﹠ Drink in showcase, bottle cooler or other similar devices in supermarket, convenience store, grocery store, cafeteria, restaurant and other catering service places provide refrigerating environment.
[0003] traditionally, these refrigerant vapor compression systems comprise compressor, condenser, expansion gear and the evaporimeter of connecting in the mode of cold-producing medium stream connection.Above-mentioned basic refrigerant vapor compression system assembly is interconnected by the refrigerant lines in the closed refrigerant circuit, and according to the vapor-compression cycle setting of adopting.Expansion gear is generally the metering device of expansion valve or constant aperture, and as throttle orifice or capillary, it is arranged in the refrigerant lines, and the position in refrigerant loop is positioned at vaporizer upstream and is positioned at the condenser downstream with respect to cold-producing medium stream.The liquid refrigerant that expansion gear is operated the refrigerant lines of will flow through connection condenser and evaporimeter is expanded to lower pressure and temperature.Any comprises for example R-12, R-22, R-134a, R-404A, R-410A, R-407C, R717, R744 or other compressible fluids in the multiple cold-producing medium of refrigerant vapor compression system inflatable.
[0004] in some refrigerant vapor compression system, evaporimeter is parallel pipe heat exchanger, it has between the collector of the first basic vertical collector that extends or manifold and the second basic vertical extension or manifold a plurality of flat multichannel heat exchanger tube that concerns longitudinal extension with parallel interval, the cross section of the multichannel heat exchanger tube that this is flat is generally rectangle or ellipse, and one in first collector or manifold and second collector or the manifold is used as inlet header/manifold.Inlet header receives cold-producing medium stream from refrigerant loop, and is flowing by this cold-producing medium of distribution in a plurality of parallel stream of heat exchanger.Another collector is used to collect the cold-producing medium stream when leaving stream separately, and collected conductance is returned refrigerant lines, so that return compressor in single-pass exchanger, or returns parallel heat exchanger tube downstream group in multipass exchanger.Under latter event, this collector is intermediate manifold or manifold cavity, and serves as to the inlet header of the next downstream group of parallel heat exchanger tube.
[0005] each heat exchanger tube has a plurality of flow channels that extend along whole pipe range parallel longitudinal usually, and each passage provides the refrigerant flow path with relative small cross sectional.Therefore, the heat exchanger of band multi-channel tube has refrigerant flow path a large amount of relatively little cross-sectional areas, that extend between inlet header and outlet header, and wherein this multi-channel tube extends in parallel between the inlet header of this heat exchanger and outlet header.Sometimes, this multi-channel heat exchanger structure also is known as micro-channel heat exchanger or minichannel heat exchanger.Usually for evaporator application, heat exchanger generally comprises the thermofin between heat-transfer pipe, to strengthen heat transfer, structural rigidity and design of heat exchanger compactedness.Heat-transfer pipe and fin for good and all be attached to each other (and being attached to manifold) in slice weldering operation.That fin can have is flat, wave, ripple or venetian blind type design, forms triangle, rectangle, side set shape (offset) or trapezoidal gas channel usually.
[0006], flows through this evaporimeter and from this air, condense and accumulate on the outer surface of above-mentioned heat exchanger tube and thermofin from the airborne moisture that the outer surface of the heat exchanger tube of the refrigerant conveying of this evaporimeter and related thermofin flows through when heat exchanger during as the evaporimeter in the refrigerant vapor compression system.According to operating conditions, the moisture that condensation goes out from air can gather at the heat exchanger tube of evaporimeter and the outer surface of thermofin, and forms frost or ice.Because the gas channel between fin and the pipe is closed in the increase of gathering of frost or ice and increase on heat exchanger tube and the thermofin, particularly in fin and the zone that contacts of pipe, therefore the heat transfer between cold-producing medium in the pipe and the process air of this pipe can descend, and this is because frost layer or ice sheet have caused the increase of hot conduction resistance.In addition, if the frost between the fin increases too much, the pressure drop meeting of then passing through the air side of evaporimeter increases, and the air-flow of being carried by air moving device is reduced, thereby has further worsened the overall performance of evaporating heat exchanger.
[0007] in addition, be different from the larger-diameter circular heat exchanger tube that is generally used for the relatively large pipe interbody spacer of having of conventional refrigerants evaporimeter, the flat multi-channel tube that defines the flow channel of a plurality of little cross-sectional areas stands the damage that is caused by long-pending frost on heat exchanger tube and the relevant thermofin outer surface or accumulated ice and is easy to suffer this to damage.For traditional pipe and plate-fin heat exchanger structure, condensed water often tends to drain along thermofin from heat exchanger tube.Yet on flat tube, condensate water is often tended to gather, rather than drains from pipe.Therefore, unless with ponding from managing removal, otherwise ponding will alternately be frozen into frost or ice and all or part of thawing in defrost cycle subsequently under some operating conditions.Because water can expand when freezing, so freezing repeatedly and thaw of the condensed water that gathers, particularly the condensed water in the restricted clearance between thermofin and flat heat exchange tube freezes repeatedly and (for example thaws, in the zone of fin contact flat tube) thus can damage this heat exchanger by making pipe distortion or cracking, and cause that fin separates from pipe.In addition, in follow-up defrost cycle, more ice may be assembled on the outer surface of the heat exchanger tube of evaporating heat exchanger and thermofin, even may stop up gas channel fully, force evaporimeter to operate in outside the specific operation scope (with regard to pressure of inspiration(Pi)), and jeopardize the reliability of refrigerant system or cause disadvantageous stopping production, the two obviously all is the incident of highly not expecting.
[0008] in the refrigerant vapor compression system of the evaporimeter with traditional fin pipe and plate wing, the common way of evaporator defrost is the defrosting that continues definite time interval periodically, or carries out according to instruction when detecting the needs defrosting.For example, United States Patent (USP) 6205800 discloses a kind of instruction Defrost method that is used for the refrigerated display cabinet evaporator defrost, when the difference between detection air themperature in the cabinet and the detection refrigerant temperature equals or exceeds the defrosting threshold value, starts defrost cycle.Refrigerant temperature sensors is external to be installed on the refrigerant inlet pipe of evaporimeter, or is installed in the evaporator coil on other positions, or built-in being installed in the refrigerant inlet pipe.Be used for connecting with evaporimeter instruction defrost control system the frost sensor of use, disclosed in the art example comprises: thermistor, as disclosed in United States Patent (USP) 4305259; Capacitive sensor plate is as disclosed in United States Patent (USP) 4347709; The air velocity sensor is as disclosed in United States Patent (USP) 4831833; Fibre Optical Sensor is as disclosed in United States Patent (USP) 4860551; And heat flow transducer, as disclosed in United States Patent (USP) 6467282.
Summary of the invention
[0009] a kind of cold-producing medium that comprises flows back to the refrigerant vapor compression system on road, and this loop has coolant compressor, condenser, expansion gear and the evaporimeter that is connected in series with cold-producing medium stream mode of communicating.Evaporimeter has a plurality of parallel interval flat heat exchange tube that be provided with, longitudinal extension.Each heat exchanger tube has flat cross section, and can limit refrigerant flow channel a plurality of separation, longitudinal extension.At least one frosting detecting sensor is mounted to related with evaporator operation, is used to detect frosting or icing existence at least one flat heat exchange tube or the thermofin, and the generation indication exists frosting or icing signal on this flat heat exchange tube and thermofin.Defrost system is related with evaporator operation.Controller function connects frost/ice detecting sensor and defrost system, and there is frosting/icing signal in its response indication at least one flat heat exchange tube and thermofin, optionally activates defrost system to start the defrost cycle of evaporimeter.Frost/ice detecting sensor can be the single-sensor that is installed in single position on the heat exchanger, perhaps can be mounted in a plurality of frosting detecting sensors at diverse location place on the heat exchanger.
[0010] in one embodiment, the frosting detecting sensor can be the sensor on the outer surface that is installed in one of one of flat heat exchange tube or thermofin.In one embodiment, a plurality of frosting detecting sensors can be installed on the outer surface of many different flat heat exchange tube, thermofin or their combinations.In one embodiment, defrost system can be electric Defrost heater system.In one embodiment, defrost system can be the hot gas defrosting system, is used for optionally making flowing through the evaporimeter heat exchanger tube from compressor to the small part refrigerant vapour.
[0011] heat exchanger can have flat heat exchange tube, and this heat exchanger tube has basic flattened rectangular or plurality of stepped serrations, and each heat exchanger tube of this heat exchanger all can limit a plurality of internal fluid flow channel with circular cross-section or noncircular cross section flow region.Heat exchanger also can be included in a plurality of fins that extend between the adjacent flat heat exchanger tube.These fins can be a plurality of vertical substantially fins that extend between adjacent heat exchange tubes, perhaps a plurality of fins can be included in the wave-fin that extends between adjacent heat exchange tubes, and can be shutter, wave, side set or flat configuration.
Description of drawings
[0012] in the present invention's detailed description subsequently, understand with reference to the accompanying drawings, in the accompanying drawing:
[0013] Fig. 1 is the schematic diagram that is combined with as the refrigerant vapor compression system of the multi-channel heat exchanger of evaporimeter;
[0014] Fig. 2 is the perspective view of the embodiment of the evaporating heat exchanger of outfit defrosting sensor;
[0015] Fig. 3 is the schematic diagram of refrigerant vapor compression system that is combined with the multichannel heat exchange evaporimeter of band defrosting sensor and related electric Defrost heater; And
[0016] Fig. 4 is the schematic diagram of refrigerant vapor compression system that is combined with the multichannel heat exchange evaporimeter of band defrosting sensor and related hot gas defrosting device.
The specific embodiment
[0017] described heat exchanger of the present invention at this, it is as the evaporimeter that is connected with the air-conditioning circulating refrigerant vapor compression system 100 of as shown in Figure 1 simplification.Although exemplary refrigerant vapor compression shown in Figure 1 circulation is the air-conditioning circulation of simplifying, but it should be understood that, heat exchanger of the present invention can be used for the refrigerant vapor compression system of various designs, include but not limited to heat pump cycle, economizer cycle, the circulation that has the string shaft assembly as compressor and heat exchanger, cooler circulation, the circulation that has heating again and other circulations that comprise various options and feature.
[0018] refrigerant vapor compression system 100 comprises compressor 105, condenser 110, expansion gear 120 and the heat exchanger 10 that moves as evaporimeter, and they are connected in the closed-loop refrigerant circuits by refrigerant lines 102,104 and 106.Compressor 105 makes the thermal high refrigerant vapour cycle through the inlet header that exhaust refrigerant lines 102 enters condenser 110, and the heat exchanger tube by condenser 110 thus, when hot refrigerant vapor refrigerant flows through these heat exchanger tubes with the relation with heat exchange, this refrigerant vapour is lowered the temperature, be condensed into liquid and usually by cold excessively, this cooling fluid is for example air, and it is driven by condenser fan 115 and flows through from heat exchanger tube.Although heat exchanger 110 refers to condenser in the text, as is known to the person skilled in the art, the subcritical condensing heat exchanger of main two-phase can become the single phase gas cooler in striding critical applications.Heat exchanger 110 subcritical and stride critical applications and all can benefit from invention as herein described equally.
[0019] high pressure liquid refrigerant leaves condenser 110, and flow through liquid refrigerant pipeline 104 thus and arrive evaporating heat exchangers 10, this cold-producing medium passes expansion gear 120, and cold-producing medium is expanded to lower pressure and temperature to form refrigerant liquid/vapor mixture passes in expansion gear 120.The heat exchanger tube 40 of evaporating heat exchanger 10 is flow through in swell refrigeration agent under this lower pressure and the lower temperature thus, when cold-producing medium flows through with the relation with the air heat exchange in these heat exchanger tubes, this cold-producing medium is evaporated and usually by overheated, this air is cooled and is dehumidified in many cases, and this air is driven from heat exchanger tube 40 and related thermofin 50 by evaporator fan 15 and flows through.Cold-producing medium mainly is to leave evaporating heat exchanger with the heat of steam mechanical state, and flows through air-breathing refrigerant lines 106 so that return compressor 105 by suction port.
[0020] when the air-flow that passes evaporating heat exchanger 10 with the relation of the cold-producing medium heat exchange of flowing through heat exchanger tube 40 on heat exchanger tube 40 and the thermofin 50 through out-of-date, this air is cooled, and flow through evaporating heat exchanger 10 and from this air, condense, and be collected on the outer surface of heat exchanger tube 40 and thermofin 50 from this airborne moisture that the outer surface of the conveying pipe of refrigerant 40 of evaporating heat exchanger 10 and thermofin 50 flows through.Drain pan 45 is provided at the below of evaporating heat exchanger 10, is used to collect the condensed water from heat exchanger tube 40 and the discharge of thermofin 50 outer surfaces.
[0021] parallel-flow heat exchanger 10 comprises the heat exchanger tube 40 of a plurality of basic flat cross section, and these a plurality of heat exchanger tubes 40 are configured to basic vertical row with parallel relation.As shown in Figure 2 in the illustrative embodiments of heat exchanger 10, each heat exchanger tube 40 extends along the direction of basic horizontal between basic vertical first collector 20 that extends and basic vertical second collector 30 that extends along its longitudinal axis, thereby a plurality of parallel refrigerant flow paths are provided between two collectors.Although refrigernant collector 20 and 30 is illustrated as cylindrical configuration, arrange that according to refrigerant path it also can be rectangle, semicylinder or any other shape, also can have the design of single chamber or multi-cavity.Each heat exchanger tube 40 has first end that is mounted to first collector 20, be mounted to second end of second collector 30, and at least one flow channel 42 of longitudinal extension (promptly, the longitudinal axis that on whole pipe range, all is parallel to this pipe), thus the cold-producing medium stream that stream is communicated with is provided between first collector 20 and second collector 30.The heat exchanger refrigerant pass arrangement can be the multipass configuration, as shown in Figure 2, or single pass configuration, it depends on specific application requirements.
[0022] each heat exchanger tube 40 comprises the elongated tubular member of extending and have basic flat cross section along its longitudinal axis, for example square-section or elliptic cross-section.Flat tubular element has upper wall 46 and lower wall 48, and limits the internal fluid flow channel 42 of at least one longitudinal extension.This at least one internal fluid flow channel 42 can be further divided into a plurality of parallel, internal fluid flow channel 42 independently, and this internal fluid flow channel 42 is parallel to the longitudinal axis longitudinal extension of the heat exchanger tube 40 that is arranged side by side, thereby the multichannel heat exchanger tube is provided.Each flat heat exchanger tube 40 has with respect to the leading edge 41 of facing the upstream by the air-flow of heat exchanger 10, and with respect to the trailing edge 43 of facing the downstream by the air-flow of heat exchanger 10.
[0023] has the circular heat exchanger tube that diameter is 1/2 inch, 3/8 inch or 7 millimeters in the conventional art, each flat multi-channel tube 40 for example can have width and about 2 millimeters or the littler height of 50 millimeters or littler (being generally 10 millimeters to 30 millimeters), and this width is to measure along the transversal line that extends to trailing edge 43 from leading edge 41.In order to be easy to explanation and detailed description, heat exchanger tube 40 is shown to have ten inner passages 42 that are defined as the square-section stream in the accompanying drawings.But it should be understood that each multichannel heat exchanger tube 40 can have about ten usually to about 20 inner flow passage 42 in application.In general, each inner flow passage 42 has hydraulic diameter, and its four times of being defined as the cross section flow area are divided by wetted perimeter, and the scope of this hydraulic diameter is usually from about 200 microns to about 3 millimeters.Although have the square-section as shown in the figure, inner flow passage 42 can have circle, triangle, ellipse or trapezoid cross section, or the on-circular cross-section of any other expectation.In addition, heat-transfer pipe 40 can have other internal heat transfer and strengthen element, as blender and boundary layer destructor.
[0024] in traditional method, for improve from flat heat-transfer pipe 40 outer surfaces flow through the air of heat exchanger 10 with the cold-producing medium of the inside parallel flow channels 42 that flows through heat-transfer pipe 40 between heat transfer, heat exchanger 10 is included in a plurality of external heat transfer fins 50 of extension between every group of pipe that is arranged in parallel 40.Thermofin is by soldering or otherwise be attached to securely on the outer surface of lower wall on the corresponding tubular member of adjacent heat exchange tubes 40, to set up heat transfer contact by the heat conduction between the outer surface of thermofin 50 and flat heat exchange tube 40.Therefore, the outer surface of heat exchanger tube 40 forms external heat transfer surfaces with the surface of thermofin 50, and this external heat transfer surfaces participates in the air that flows through heat exchanger 10 and the heat transfer flow through between the cold-producing medium of inner passage 42 interacts.External heat transfer fins 50 also provides structural rigidity for heat exchanger 10, and often assists air-flow to be redirected, to improve heat-transfer character.
[0025] in the illustrative embodiments of heat exchanger 10 shown in Figure 2, thermofin 50 constitutes a plurality of sections of wing plate, these a plurality of sections snakelike series that form basic V-arrangement or basic U-shaped section, and both be arranged to following outer surface heat transfer contact with the lower wall 48 of a heat exchanger tube 40, again with outer surface heat transfer contact on the upper wall 46 of the adjacent heat exchange tubes 40 below this heat exchanger tube.Alternatively, fin can constitute a plurality of plates parallel, that arrange and substantially vertically extend at interval between heat exchanger tube 40.It should be understood that the configuration of other fins, for example form the basic corrugated of triangle, rectangle or trapezoidal gas channel, wavy, shutter or offset strip fin and also can be used in the heat exchanger of the present invention.
[0026] as mentioned above, as refrigerant vapor compression system (such as but not limited to, air-conditioning or refrigeration system) the heat exchanger of the evaporimeter water that gone out by from the air stream that flows through evaporimeter condensation and collect at the heat exchange pipe external surface and the thermofin outer surface of this heat exchanger.Under some operating conditions that in course of normal operation, experiences usually, condensed water will freeze and form frost or ice on the outer surface up and down 46,48 of flat heat exchange tube 40 and thermofin 50, particularly in the zone of thermofin 50 contact heat-exchanging pipes outer surface about in the of 40.
[0027] in order to detect the frosting on the heat exchanger 10 or to freeze, at least one frosting detecting sensor 60 is mounted to and heat exchanger 10 operative association.In the embodiment of heat exchanger 10, frosting detecting sensor 60 is installed on the outer surface of one of heat exchanger tube 40 as shown in Figure 2.But it should be understood that frosting detecting sensor 60 alternately is installed on the surface of one of thermofin 50.In addition, it should be understood that a plurality of frosting detecting sensors 60 can be installed on a plurality of positions that are positioned at comprising on the heat exchanger 10 on heat exchanger tube and/or the thermofin, wherein each defrosting detecting sensor 60 is installed in the diverse location place in the heat exchanger 10.For example, the frosting detecting sensor can be installed in the zone that frost/ice in the heat exchanger 10 at first is easy to gather and gathers at most, and perhaps frosting detecting sensor 60 can be installed on each of the diverse location that a plurality of frosts/ice is easy to gather that spreads all over heat exchanger 10.The one or more definite installation site of frosting detecting sensor is those skilled in the art's a selection item in the particular heat exchanger.In the general knowledge that is chosen in those skilled in the art of frosting detecting sensor 60 types of usefulness, not restriction of the present invention.Frosting detecting sensor 60 can be heat flux sensor, strain-ga(u)ge pickup, maybe can detect any other type sensors of heat exchanger tube 40 outer surface frostings.
[0028] frosting detecting sensor 60 operation is attached to controller 80, and the signal of the frosting of indication on the outer surface of the heat exchanger tube 40 related with sensor 60 is provided to controller 80.In one embodiment, frosting detecting sensor 60 provides the signal of the frosting practical extent of indication on the outer surface of the heat exchanger tube 40 related with sensor 60 to controller 80.Controller 80 is handled the signal of receiving from one or more frosting detecting sensors 60, and determines whether the indicated frosting degree of these signals is too much.If controller 80 starts defrost cycle subsequently to melt the frosting on the evaporating heat exchanger 10.
[0029] with reference now to accompanying drawing 3, in the refrigerant vapor compression system of being described in the figure 100, electric defrost system and evaporating heat exchanger 10 operative association.The electricity defrost system comprises electric Defrost heater, and it comprises spreading with respect to air puts at the air intake place that is positioned at evaporating heat exchanger 10 or at least one electrical heating elements 65 of upstream slightly.In illustrative embodiments shown in Figure 3, provide 65, one electrical heating elements 65 of a plurality of electrical heating elements related with each heat exchanger 40.When controller 80 decisions started defrost cycle, controller 80 gave electrical heating elements 65 energisings.Electrical heating elements 65 is operated in a conventional manner, fully is heated above 0 ℃ with the air that will enter evaporating heat exchanger 10, thus the feasible frost melts that when heated air flow is crossed heat exchanger, causes being formed in the heat exchanger.In addition, the outer surface of electrical heating elements 65 meeting heating heat exchangers 10, this also will help ice-melt.Alternatively, in place if safety and spacer assembly are mounted, at least some heat exchanger tubes 40 or thermofin 50 can be used as electrical heating elements 65.After the preselected time interval, controller 80 can give electrical heating elements 65 outages, thereby finishes defrost cycle.
[0030] in the illustrative embodiments of refrigerant vapor compression system 100 shown in Figure 4, hot gas defrosting system and evaporating heat exchanger 10 operative association.The hot gas defrosting system comprises hot gas defrosting pipeline 70 and the arrangements of operations flow control valve 90 in hot gas defrosting pipeline 70.Hot gas defrosting pipeline 70 has the inlet opening that becomes cold-producing medium stream to be communicated with the intermediate pressure stage of compressor 105, and the exit opening that is communicated with 104 one-tenth cold-producing mediums of refrigerant lines stream, the position of this exit opening is positioned at the upstream of evaporating heat exchanger 10 with respect to cold-producing medium stream and is positioned at the downstream of expansion gear 120.Therefore, hot gas defrosting pipeline 70 provides the refrigerant flow path from the intermediate pressure stage of compressor 105 to the refrigerant inlet pipeline of evaporating heat exchanger 10.Flow control valve 90 alternatives are between closed position and open position, flow control valve 90 cuts out the hot gas defrosting pipeline 70 that cold-producing medium stream therefrom passes when the closed position, and flow control valve 90 is opened the hot gas defrosting pipeline 70 that cold-producing medium stream passes from mouth when open position.In one embodiment, flow control valve 90 can be the electrically operated flow control valve of electromagnetism.In addition, flow control valve 90 can be modulation type or pulse pattern, close and open position between correspondingly the modulation or the circulation.In addition, if compressor 105 is not equipped with intermediate pressure port, the exhaust refrigerant vapour can be used to the purpose that defrosts replacedly, and this method obviously within the scope of the present invention.
[0031] flow control valve 90 operations connect controller 80.As previously mentioned, controller 80 is handled the signal of receiving from one or more frosting detecting sensors 60, and determines whether the indicated frosting/ice amount of these signals is too much.If then controller 80 starts defrost cycle subsequently, with by sending command signals, cause that flow control valve 90 partly or entirely opens, thereby melt the frost/ice that is formed on evaporating heat exchanger 10 outer surfaces to flow control valve 90.Along with flow control valve 90 is opened, refrigerant vapour to the refrigerant vapour of small part intermediate pressure or pressure at expulsion enters refrigerant lines 104 from compressor 105 through hot gas defrosting pipelines 70, and mix, thereby improve temperature through the refrigerant vapour of the heat exchanger tube 40 of evaporating heat exchanger 10 with refrigerant vapour from the expansion of expansion gear 120.When the refrigerant vapour of this higher temperature passes the flow channel 42 that passes through from heat exchanger tube 40, the temperature that the refrigerant vapour of this higher temperature has improved the cast element that limits heat exchanger tube 40 reaches and enough is higher than 0 ℃ temperature, thereby cause the thawing of the frosting/ice in the heat exchanger 10, as heated air flows through this evaporating heat exchanger.After the preselected time section, controller 80 command stream control valves 90 are closed, thereby prevent that refrigerant vapour from flowing to refrigerant line 104 from compressor 105 through flow control valve 90, and have stopped defrost cycle.In addition, if desired, when defrost cycle starts, can be blocked fully by the cold-producing medium stream of main refrigerant circuit.In the case, the additional flow control valve will be installed on the exhaust line 102, and be closed by controller 80 during defrost cycle.
[0032] as previously mentioned, if intermediate-pressure vapor can not just can be used the pressure at expulsion steam as the defrosting medium.In this case, the inlet of hot gas defrosting pipeline 70 will become cold-producing medium stream to be communicated with the discharge pressure side of compressor 105.The outlet of hot gas defrosting pipeline 70 becomes cold-producing medium stream to be communicated with being positioned at evaporimeter 10 upstreams with respect to cold-producing medium stream and being positioned at expansion gear 120 location downstream again with refrigerant loop.In addition, if refrigerant system 100 is heat pumps, the switching between the heating and cooling operator scheme can be used as the defrosting means.
[0033] it should be understood that equally, although disclose embodiments of the present invention, and these embodiments help being applied on the evaporating heat exchanger of the straight heat exchanger tube row with horizontal alignment most, but invention disclosed herein also helps being applied on the evaporating heat exchanger with other heat exchanger tube orientations and configuration, heat exchanger tube that for example is vertically oriented or the heat exchanger tube that is orientated to angle of inclination between 90 degree with 0 degree with respect to horizontal axis.
[0034] although as shown in drawings, the present invention is shown and described with reference to preference pattern, one skilled in the art will realize that: but do not deviating from the multiple variation on the implementation detail in the spirit and scope of the invention that limits as claims.
Claims (30)
1. one kind comprises that cold-producing medium flows back to the refrigerant vapor compression system on road, and described system comprises:
Flow back to coolant compressor, heat rejection heat exchanger, expansion gear and the evaporimeter that is connected in series with cold-producing medium stream mode of communicating in the road at cold-producing medium, described evaporimeter has a plurality of with parallel spaced-apart relation flat heat exchange tube that arrange, longitudinal extension, and each described heat exchanger tube all has flat cross section;
At least one frosting detecting sensor, it is mounted to related with described evaporator operation, is used to detect frosting or icing existence on the described evaporator external, and generation indication at least one position in evaporimeter exists frosting or icing signal;
The defrost system related with described evaporator operation; And
Operation is attached to the controller of described defrost system and described at least one frosting detecting sensor, at least one position in the described evaporimeter of described controller response indication exists frosting or icing described signal, optionally activates described defrost system to start the defrost cycle of described evaporimeter.
2. refrigerant vapor compression system as claimed in claim 1, wherein, the described flat heat exchange tube of each of described evaporimeter defines the refrigerant flow channel of a plurality of inner separation, longitudinal extension.
3. refrigerant vapor compression system as claimed in claim 1, wherein, described defrost system comprises the electric heating system related with described evaporator operation.
4. refrigerant vapor compression system as claimed in claim 1, wherein, described defrost system comprises the hot gas defrosting system, and described hot gas defrosting system is used to make and optionally flows through the described heat exchanger tube of described evaporimeter from described compressor to the small part refrigerant vapour.
5. refrigerant vapor compression system as claimed in claim 4, wherein, described hot gas defrosting system comprises:
The hot gas defrosting pipeline, it has inlet opening and exit opening, described inlet opening becomes cold-producing medium stream to be communicated with the intermediate pressure stage of described compressor, described exit opening becomes cold-producing medium stream to be communicated with in a position with described refrigeration cycle, and described position is positioned at the upstream of described evaporimeter with respect to cold-producing medium stream and is positioned at the downstream of described expansion gear; And
The refrigerant flow control device, it is arranged in the described hot gas defrosting pipeline and operation connects described controller, and described refrigerant flow control device can selectivity be located between closed position and open position.
6. refrigerant vapor compression system as claimed in claim 5, wherein, described refrigerant flow control device is modulation type or pulse pattern.
7. refrigerant vapor compression system as claimed in claim 4, wherein, described hot gas defrosting system comprises:
The hot gas defrosting pipeline, it has inlet opening and exit opening, described inlet opening becomes cold-producing medium stream to be communicated with the discharge pressure side of described compressor, described exit opening becomes cold-producing medium stream to be communicated with in a position with described refrigeration cycle, and described position is positioned at the upstream of described evaporimeter with respect to cold-producing medium stream and is positioned at the downstream of described expansion gear; And
The refrigerant flow control device, it is arranged in the described hot gas defrosting pipeline and operation connects described controller, and described refrigerant flow control device can optionally be positioned between closed position and the open position.
8. refrigerant vapor compression system as claimed in claim 7, wherein, described refrigerant flow control device is modulation type or pulse pattern.
9. refrigerant vapor compression system as claimed in claim 1, wherein, described refrigerant system is a heat pump, and described defrost system is included in the switching between heating operation pattern and the cooling down operation pattern.
10. refrigerant vapor compression system as claimed in claim 1, wherein, described at least one frosting detecting sensor comprises the frosting detecting sensor on the outer surface that is installed in one of described flat heat exchange tube.
11. refrigerant vapor compression system as claimed in claim 1, wherein, described at least one frosting detecting sensor comprises the lip-deep frosting detecting sensor that is installed between described heat exchanger tube and forever is attached to one of the thermofin of these heat exchanger tubes.
12. refrigerant vapor compression system as claimed in claim 1, wherein, described at least one frosting detecting sensor comprises a plurality of frosting detecting sensors, and each described frosting detecting sensor is installed in the diverse location place in the described evaporimeter.
13. refrigerant vapor compression system as claimed in claim 1, wherein, described at least one frosting detecting sensor comprises a plurality of frosting detecting sensors, and each described frosting detecting sensor is installed on the outer surface of a different pipe in the described flat heat exchange tube.
14. refrigerant vapor compression system as claimed in claim 1, wherein, described at least one frosting detecting sensor comprises a plurality of frosting detecting sensors, and each described frosting detecting sensor is installed between described heat exchanger tube and forever is attached on the surface of a different thermofin in a plurality of thermofins of these heat exchanger tubes.
15. refrigerant vapor compression system as claimed in claim 1, wherein, described flat heat exchange tube has flattened rectangular cross section or flattened oval tee section.
16. refrigerant vapor compression system as claimed in claim 2, wherein, the fluid flowing passage of described a plurality of inner separation, longitudinal extension has the flow area of circular cross-section.
17. refrigerant vapor compression system as claimed in claim 2, wherein, the fluid flowing passage of described a plurality of inner separation, longitudinal extension has the flow area of noncircular cross section.
18. refrigerant vapor compression system as claimed in claim 1 further is included in a plurality of thermofins that extend between the adjacent flat heat exchanger tube of described evaporimeter.
19. refrigerant vapor compression system as claimed in claim 18, wherein, described a plurality of thermofins are included in a plurality of vertical substantially fins that extend between the adjacent heat exchange tubes.
20. refrigerant vapor compression system as claimed in claim 18, wherein, described a plurality of thermofins are included in the wave-fin that extends between the adjacent heat exchange tubes.
21. refrigerant vapor compression system as claimed in claim 20, wherein, the described snakelike thermofin that extends between adjacent heat exchange tubes forms a kind of in fundamental triangle, rectangle or the trapezoidal gas channel.
22. refrigerant vapor compression system as claimed in claim 18, wherein, described a plurality of thermofins are at least a in venetian blind type, wave, bayonet-type or the flat configuration.
23. refrigerant vapor compression system as claimed in claim 1, wherein, described evaporimeter has first manifold and second manifold, and at the longitudinal extension between first manifold and second manifold of flat heat exchange tube described in the single pass configuration.
24. refrigerant vapor compression system as claimed in claim 1, wherein, described evaporimeter has first manifold and second manifold, and at flat heat exchange tube longitudinal extension between first manifold and second manifold described in the multipass configuration.
25. refrigerant vapor compression system as claimed in claim 1, wherein, the described flat heat exchange tube of described evaporimeter has the orientation of basic horizontal.
26. refrigerant vapor compression system as claimed in claim 1, wherein, the described flat heat exchange tube of described evaporimeter has vertical substantially orientation.
27. refrigerant vapor compression system as claimed in claim 1, wherein, the described flat heat exchange tube of described evaporimeter has at 0 degree to the angle of inclination between 90 degree with respect to horizontal axis.
28. refrigerant vapor compression system as claimed in claim 1, wherein, described evaporimeter has vertical substantially orientation.
29. refrigerant vapor compression system as claimed in claim 1, wherein, described evaporimeter has at 0 degree to the angle of inclination between 90 degree with respect to horizontal axis.
30. refrigerant vapor compression system as claimed in claim 1, wherein, the described flat heat exchange tube of described evaporimeter has straight substantially configuration.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US2007/005724 WO2008108757A1 (en) | 2007-03-06 | 2007-03-06 | Micro-channel evaporator with frost detection and control |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101688731A true CN101688731A (en) | 2010-03-31 |
Family
ID=39738524
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200780052876A Pending CN101688731A (en) | 2007-03-06 | 2007-03-06 | The micro-channel evaporator of band frosting Detection ﹠ Controling |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20100024452A1 (en) |
| EP (1) | EP2135020A1 (en) |
| CN (1) | CN101688731A (en) |
| WO (1) | WO2008108757A1 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102141334A (en) * | 2011-04-22 | 2011-08-03 | 朱云良 | Fin frosting detection device of refrigeration plant and automatic defroster applied by same |
| CN103512103A (en) * | 2012-06-29 | 2014-01-15 | 太仓南极风能源设备有限公司 | Frost sensing device of outdoor unit of air-conditioner |
| CN106766328A (en) * | 2016-11-30 | 2017-05-31 | 广东美的制冷设备有限公司 | Heat pump and its defrosting control method |
| CN106989494A (en) * | 2017-05-10 | 2017-07-28 | 广东美的制冷设备有限公司 | Air conditioner and its frosting detection device and method |
| CN107782029A (en) * | 2016-08-31 | 2018-03-09 | 青岛海尔智能技术研发有限公司 | The frosting degree detecting method and apparatus of outdoor machine of air-conditioner evaporator |
| CN109668363A (en) * | 2018-12-24 | 2019-04-23 | 北京机科国创轻量化科学研究院有限公司 | Defrost ancillary equipment, method and control device |
| CN111669944A (en) * | 2020-06-22 | 2020-09-15 | 深圳市鸿富诚屏蔽材料有限公司 | 3D phase change superconducting radiator |
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| JP4736872B2 (en) * | 2006-03-10 | 2011-07-27 | 株式会社デンソー | Air conditioner |
| DE102011077838A1 (en) * | 2011-06-20 | 2012-12-20 | Behr Gmbh & Co. Kg | Heat exchanger and method for producing a heat exchanger |
| US9970696B2 (en) | 2011-07-20 | 2018-05-15 | Thermo King Corporation | Defrost for transcritical vapor compression system |
| JP5772748B2 (en) * | 2012-07-23 | 2015-09-02 | 株式会社デンソー | Evaporator |
| SE538309C2 (en) * | 2013-11-26 | 2016-05-10 | Fläkt Woods AB | Apparatus and method for heating air in an air treatment device |
| US9581371B2 (en) * | 2014-03-21 | 2017-02-28 | Lennox Industries Inc. | System for operating an HVAC system having tandem compressors |
| US20160025403A1 (en) * | 2014-07-28 | 2016-01-28 | Infineon Technologies Austria Ag | Temperature regulating system and method of deicing the temperature regulating system |
| JP7106814B2 (en) * | 2017-02-23 | 2022-07-27 | 株式会社富士通ゼネラル | Heat exchanger |
| US11022382B2 (en) | 2018-03-08 | 2021-06-01 | Johnson Controls Technology Company | System and method for heat exchanger of an HVAC and R system |
| WO2020018543A2 (en) | 2018-07-17 | 2020-01-23 | Carrier Corporation | Refrigerated cargo container cargo sensor |
| WO2020083591A1 (en) * | 2018-10-22 | 2020-04-30 | Arcelik Anonim Sirketi | A heat pump dishwasher comprising a defrost receptacle |
| EP3870017A1 (en) * | 2018-10-24 | 2021-09-01 | Arçelik Anonim Sirketi | A heat pump dishwasher with improved evaporator performance |
| EP3760953B1 (en) * | 2019-07-05 | 2022-10-26 | Vestel Elektronik Sanayi ve Ticaret A.S. | Apparatus and method for detecting a formation of ice in a household appliance |
| US11542147B2 (en) * | 2019-09-30 | 2023-01-03 | Marmon Foodservice Technologies, Inc. | Beverage dispensers with heat exchangers |
| CN114857806B (en) * | 2022-05-05 | 2023-07-14 | 山东和同信息科技股份有限公司 | Multifunctional complementary air source heat pump system with defrosting function |
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- 2007-03-06 CN CN200780052876A patent/CN101688731A/en active Pending
- 2007-03-06 WO PCT/US2007/005724 patent/WO2008108757A1/en active Search and Examination
- 2007-03-06 EP EP07752425A patent/EP2135020A1/en not_active Withdrawn
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102141334A (en) * | 2011-04-22 | 2011-08-03 | 朱云良 | Fin frosting detection device of refrigeration plant and automatic defroster applied by same |
| CN103512103A (en) * | 2012-06-29 | 2014-01-15 | 太仓南极风能源设备有限公司 | Frost sensing device of outdoor unit of air-conditioner |
| CN107782029A (en) * | 2016-08-31 | 2018-03-09 | 青岛海尔智能技术研发有限公司 | The frosting degree detecting method and apparatus of outdoor machine of air-conditioner evaporator |
| CN106766328A (en) * | 2016-11-30 | 2017-05-31 | 广东美的制冷设备有限公司 | Heat pump and its defrosting control method |
| CN106989494A (en) * | 2017-05-10 | 2017-07-28 | 广东美的制冷设备有限公司 | Air conditioner and its frosting detection device and method |
| CN109668363A (en) * | 2018-12-24 | 2019-04-23 | 北京机科国创轻量化科学研究院有限公司 | Defrost ancillary equipment, method and control device |
| CN111669944A (en) * | 2020-06-22 | 2020-09-15 | 深圳市鸿富诚屏蔽材料有限公司 | 3D phase change superconducting radiator |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2008108757A1 (en) | 2008-09-12 |
| EP2135020A1 (en) | 2009-12-23 |
| US20100024452A1 (en) | 2010-02-04 |
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