CN1228591C - Heat exchanger for cooling air - Google Patents
Heat exchanger for cooling air Download PDFInfo
- Publication number
- CN1228591C CN1228591C CN03146293.6A CN03146293A CN1228591C CN 1228591 C CN1228591 C CN 1228591C CN 03146293 A CN03146293 A CN 03146293A CN 1228591 C CN1228591 C CN 1228591C
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- Prior art keywords
- pipe fitting
- refrigerant
- air
- evaporimeter
- cycle systems
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- 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
- F28D1/0535—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 the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
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- 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
- F28D1/0478—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 the conduits having a non-circular cross-section
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- 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
- F28D1/0535—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 the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—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
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- 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
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
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- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
- F28F19/006—Preventing deposits of ice
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/02—Streamline-shaped elements
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Defrosting Systems (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
In a heat exchanger for cooling air, a tube has a streamlined-shaped cross-section so that air flows along an outer surface of the tube without stagnating. Therefore, it is less likely that moisture contained in the air will adhere on the outer surface of the tube. Accordingly, the formation of frost is restricted.
Description
Technical field
The present invention relates to be used to cool off the refrigerant-cycle systems of air.Particularly, the present invention relates to be used for the evaporimeter of refrigerator and freezer unit.
Background technology
According to the disclosed evaporimeter that is used for refrigerator of JP-A-2002-115934, have the longitudinal axis that the pipe fitting of oval-shaped cross section substantially is arranged as described cross section and be parallel to air-flow direction.Outside heat sink is not set between pipe fitting, and the outer surface of pipe fitting generally is exposed in the air.Adopt this structure, the air downstream part that can be suppressed at pipe fitting produces frost thick and fast and form frost between pipe fitting, and described frost will cause the obstruction of air duct.Therefore, air flow resistance has reduced, and the cooling capacity of evaporimeter has been improved.
Summary of the invention
The purpose of this invention is to provide a kind of refrigerant-cycle systems that is used to cool off air, described refrigerant-cycle systems can improve the efficient of heat exchange.
Another object of the present invention provides a kind of refrigerant-cycle systems that is used to cool off air, and described refrigerant-cycle systems can suppress to form frost thereon.
According to an aspect of the present invention, the refrigerant-cycle systems that is used to cool off air comprises a kind of refrigerant-cycle systems that is used to cool off air, comprising: compressor, its compressed refrigerant;
Condenser, its cooling is from the high-temperature high-pressure refrigerant of compressor discharge; Decompressor, it reduces from the pressure of the cold-producing medium of condenser discharging; Evaporimeter, the cold-producing medium that its evaporation is depressurized; Bypass channel, it walks around decompressor will introduce evaporimeter from the high temperature refrigerant of compressor; Defrost valve, it allows high temperature refrigerant to flow through bypass channel; And control module, its control defrost valve is so that high temperature refrigerant passes through the bypass channel inflow evaporator, wherein evaporimeter comprises pipe fitting, cold-producing medium flows by this pipe fitting, the outer surface that described pipe fitting is set to them generally is exposed in the air, described pipe fitting has fusiform cross section so that air is mobile along the outer surface of described pipe fitting, be formed with a plurality of coolant channels with each pipe fitting, wherein, with respect to the flow area of the downstream passage of air-flow direction flow area greater than upstream passageway.
Because air flows around the pipe fitting smoothly and do not block, it is very little to cause producing the possibility that the moisture of frost sticks on the outer surface of pipe fittings.Therefore, suppress white grain and adhered to and on pipe fitting, generating frost on the pipe fitting.Therefore, reduced air flow resistance and improved heat exchanger effectiveness.
According to a further aspect in the invention, refrigerant-cycle systems comprises: compressor, its compressed refrigerant; Condenser, its cooling is from the high-temperature high-pressure refrigerant of compressor discharge; Decompressor, it reduces from the pressure of the cold-producing medium of condenser discharging; Evaporimeter, the cold-producing medium that its evaporation is depressurized; Bypass channel, it walks around decompressor will introduce evaporimeter from the high temperature refrigerant of compressor; Defrost valve, it allows high temperature refrigerant to flow through bypass channel; And control module, its control defrost valve is so that high temperature refrigerant passes through the bypass channel inflow evaporator, wherein evaporimeter comprises flat pipe fitting, cold-producing medium flows by described flat pipe fitting, described flat pipe fitting has and generally is exposed to airborne outer surface, the longitudinal centre line that described flat pipe fitting is arranged as the cross section of pipe is parallel to air-flow direction and forms fold along the direction perpendicular to air-flow direction, be formed with a plurality of coolant channels with each flat pipe fitting, wherein, with respect to the flow area of the downstream passage of air-flow direction flow area greater than upstream passageway.
Described refrigerant-cycle systems is not established outside heat sink.Therefore, if humid air flows around the pipe fitting, moisture is in the condensation and generate frost thick and fast of the air downstream position of described pipe fitting.Because frost is grown being parallel on the direction of air-flow direction, can not block air and flow.Therefore, reduced resistance, thereby improved the efficient of refrigerant-cycle systems through flow air around the pipe fitting.
Description of drawings
With reference to the accompanying drawing detailed description of the present invention, other purpose of the present invention, feature and advantage will become clearer by following, and wherein identical parts are marked by identical numeral, and, wherein:
Fig. 1 is the perspective illustration according to the refrigerator car of first embodiment of the invention;
Fig. 2 is the schematic diagram according to the steam compression refrigerant circulating system of the refrigerator car of first embodiment of the invention;
Fig. 3 be according to the refrigerator car of first embodiment of the invention the perspective view of rearward end;
Fig. 4 is the perspective view according to the evaporimeter of the steam compression refrigerant circulating system of first embodiment of the invention;
Fig. 5 is the fragmentary, perspective view of the core of evaporimeter, is used to explain according to the air of first embodiment of the invention and flowing of cold-producing medium;
Fig. 6 A is the profile according to the pipe fitting of the evaporimeter of first embodiment of the invention;
Fig. 6 B is the key-drawing according to the pipe fitting of first embodiment of the invention;
Fig. 6 C is the partial enlarged drawing of the air downstream part of the pipe fitting shown in Fig. 6 B, is used to explain at the air downstream part ambient air stream according to the pipe fitting of first embodiment of the invention;
Fig. 7 is the profile of evaporimeter, is used to show the fitting structure according to first embodiment of the invention;
Fig. 8 is a time diagram, and the operating time that shows engine, door and defrost valve according to first embodiment of the invention arranges;
Fig. 9 A and 9B are the profiles according to the evaporimeter pipe fitting of second embodiment of the invention;
Figure 10 is the profile according to the evaporimeter pipe fitting of third embodiment of the invention;
Figure 11 is the profile according to the evaporimeter pipe fitting of fourth embodiment of the invention;
Figure 12 is the hygrogram according to fifth embodiment of the invention;
Figure 13 is the fragmentary, perspective view according to the evaporimeter pipe fitting of sixth embodiment of the invention;
Figure 14 is the part sectioned view according to the pipe fitting of sixth embodiment of the invention;
Figure 15 A is the part sectioned view according to the evaporimeter pipe fitting of seventh embodiment of the invention;
Figure 15 B is the key-drawing according to the pipe fitting of seventh embodiment of the invention;
Figure 15 C is the partial enlarged drawing of the air downstream part of the pipe fitting shown in Figure 15 B, is used to explain at the air downstream part ambient air stream according to the pipe fitting of seventh embodiment of the invention.
The specific embodiment
Embodiments of the invention hereinafter will be described with reference to the drawings.
As an example, being used to of first embodiment heat exchanger that cools off air be used for the evaporimeter 13 of refrigerator car 1, the storage of described refrigerator car transportation goods is as frozen food and keep goods to be in low-temperature condition, as shown in Figure 1.
Refrigerator car 1 has the household freezer 2 that is used to store goods.The rear end of household freezer 2 has opening 18, door 3 and 4.Goods loads and output by opening 18.
The steam compression refrigerant circulating system 5 that is used for cooling off the air of household freezer 2 is installed in the front portion of refrigerator car 1.As shown in Figure 2, system 5 comprises compressor 6, condenser 9, electric fan 10, receiver 11, decompressor 12 and evaporimeter 13.
In addition, between the refrigerant inlet of the refrigerant outlet of evaporimeter 13 and compressor 6, gatherer (accumulator) 14 is set.Gatherer 14 is separated into gas refrigerant and liquid refrigerant with the cold-producing medium of flash-pot 13 dischargings.Gas refrigerant is drawn in the compressor 6, and liquid refrigerant is stored in the gatherer 14.
Then 4 to 6C describe evaporimeter 13 in detail with reference to the accompanying drawings.As shown in Figure 4, evaporimeter 13 comprises: a plurality of pipe fittings 131, and cold-producing medium flows by described pipe fitting; Storage tank 133, its longitudinal end that is connected to pipe fitting is to be communicated with pipe fitting 131.Pipe fitting 131 constitutes core, is used for carrying out between cold-producing medium and air heat exchange.
Notice outside heat sink is not set between pipe fitting 131, this fin is typically connected on the outer surface of pipe fitting, thereby the outer surface of pipe fitting 131 generally is exposed in the air.As shown in Figure 6A, pipe fitting 131 has fairshaped cross section and disperses (see example Fluids Engineering, Universityof Tokyo Press) in the air downstream part of pipe fitting (rear side) from pipe fitting 131 to prevent pipe fitting 131 ambient airs.Streamlined is with respect to the longitudinal centre line CL symmetry of cross section.The air upstream portion (front side) of pipe fitting 131 is crooked gradually.Hereinafter, term " downstream " and " upstream " are for the direction A1 of the air of the evaporimeter 13 of flowing through.
In the present embodiment, adopt teardrop shape (wing) as streamline shape.Be increased to maximum perpendicular to the size (thickness) of the pipe fitting 131 of centre line C L direction at cardinal principle medium position place, and reducing towards the air downstream position with respect to the pipe fitting of air-flow direction A1.
Each pipe fitting 131 is formed with a plurality of refrigerant tubings 132.Pipeline 132 is parallel to each other and be in line to downstream position from the upstream portion of pipe fitting.In the present embodiment, for example, pipe fitting 131 by aluminium through extruding and drawing and be shaped.Therefore, refrigerant tubing 132 is shaped in molded pipe fitting 131.
As shown in Figure 5, pipe fitting 131 defines rows on the direction perpendicular to air-flow direction A1.And as shown in Figure 7, pipe fitting 131 is arranged with cross structure.The first array pitch Tp1 of pipe fitting 131 that is positioned at upstream row is greater than the second array pitch Tp2 of the pipe fitting 131 that is positioned at downstream row.Here, pitch Tp1 and Tp2 are that the edge is perpendicular to the distance between the centre line C L of the pipe fitting on the direction of air-flow direction A1 131.
Pipe fitting 131 among the same row is communicated with same storage tank 133.Face perspective view leniently, shown in arrow R1, cold-producing medium flows to the air downstream from the air upstream side in evaporimeter 13.
Then electronic control unit will be described.Control module 22 comprises computer, as microcomputer.Control module 22 is programmed so that based on the operation of controlling the steam compression refrigerant circulation from the signal of following sensor and switch.
Cold-producing medium switch 26 is by manual operation.Cold-producing medium switch 26 produces the switching signal of steam compression refrigerant circulating system 5.Power operation switch 27 produces signal according to the on off state of engine 8.Door switch 28 is arranged on opening 18 peripheries.Door switch 28 opens and closes according to the opening and closing door of door 3 and 4.
In addition, control module 22 control electromagnetic clutch 7, electric fan 10 and 17, defrost valve 16, pressure fan unit 19 or the like.
Then 8 refrigerating operations of describing refrigerator car 1 with reference to the accompanying drawings.When refrigerator car was walked, compressor 6 passed through electromagnetic clutch 7 by the power drive from engine 8. Electric fan 10,17 operations.Simultaneously, steam compression refrigerant circulating system 5 is opened.Meanwhile, the air that is cooled off by evaporimeter 13 is blown in the household freezer 2 by electric fan 17, thus the goods in the cooling household freezer 2.At this moment, can be mobile thereby close cold-producing medium by bypass 15 except that case valve 16.
When engine 8 stops so that loading and when exporting goods, the electric fan 17 of cooling unit 130 (Fig. 1) is closed.Then, when door 3 and 4 is opened, thereby door switch 28 open cross flow fan 21 and 22 begin the operation.Bottom at opening 18 flows into the restriction extraneous air to forming gas curtain between the top.
At this moment, defrost valve 16 is opened.Under the action of pressure between the upstream portion of the outlet of compressor 6 and evaporimeter 13, hot gas flows to evaporimeter 13 by bypass 15.Therefore, the frost in the evaporimeter 13 is fused into water and is discharged to the outside.When door 3 and 4 is closed, thereby door switch 28 is closed defrost valve 16 and is closed.
The advantage of present embodiment then will be described.
Because pipe fitting 131 has the streamlined cross section, air flows along the outer surface smoother ground of pipe fitting 131 and can not stagnate, shown in Fig. 6 C.So just suppressed moisture (described moisture can cause form frost) condensation or be bonded on the outer surface of pipe fitting 131.Like this, suppressed on pipe fitting 131 to form frost and suppressed further on pipe fitting, to adhere to the frost grain.In the evaporimeter 13 of present embodiment, to compare with existing evaporimeter, frosting degree is reduced to about 1/5th.
And shown in Fig. 6 C, the formation of frost is limited in the downstream part of pipe fitting 131.Because moisture is not bonded on the side surface of pipe fitting 131, the air duct between pipe fitting 131 is less by white possibility of jamming.Therefore, air flow resistance can not increased by frost.Therefore, the cooling capacity of evaporimeter 13 has improved.
Because pipe fitting 131 is staggered, the pipe fitting 131 of downstream row is not in the hot boundary layer that the pipe fitting row 131 by the air upstream produces.Therefore, the heat exchanger effectiveness of evaporimeter 13 has improved.
In a second embodiment, shown in Fig. 9 A, the cold-producing medium flow area of the coolant channel 132 in downstream is greater than the cold-producing medium flow area of the coolant channel 132 of upstream.
Because pipe fitting 131 has the streamlined cross section, has reduced the adhesion of moisture on pipe fitting 131.Yet, be difficult to prevent fully the formation of frost.Although amount seldom, also have frost to form in the downstream part of pipe fitting 131.
Because downstream coolant channel 132 has the flow area greater than the coolant channel 132 of upstream, the flow of hot gas increases in the downstream part of pipe fitting 131.Therefore, even in the frosting of the downstream part of pipe fitting 131, during defrosting mode, also be easy to defrosting.Shown in Fig. 9 B, coolant channel 132 can have the cross section that is roughly rectangle.
In the 3rd embodiment, as shown in figure 10, the cold-producing medium flow area changes along with the external dimensions (thickness W) of pipe fitting 131.Equally in this embodiment, evaporimeter 13 has the advantage that is similar to first embodiment.
In the 4th embodiment, as shown in figure 11, pipe fitting 131 has fusiform cross sectional shape, and described cross section is asymmetric with respect to centre line C L.Equally, in this embodiment, evaporimeter 13 has the advantage that is similar to first embodiment.
In the 5th embodiment, pipe fitting 131 is coated with defrosting compound, is used to suppress the outer surface that moisture and fog particle stick to pipe fitting 131.For example, defrosting compound comprises coating with super repellency and the material that has a water resisting property, as special teflon.
With reference to Figure 12, for example, the temperature of household freezer 2 is-20 degrees centigrade (T1).When door 3 and 4 was opened, extraneous air (for example 35 degrees centigrade, 60% relative humidity) entered household freezer 2.Air is cooled to below the freezing point rapidly, and the inner air satiety is closed.For example, the temperature T that is lower than freezing point 2 times, the form that a spot of steam (M1) can moisture (water vapour) is discharged in the inner air.
Therefore, be included in the extraneous air moisture (M2) for satiety close steam and the distillation for the distillation particle do not liquefy.The particle of literization adheres on the outer surface of pipe fitting 131 and becomes frost.In the present embodiment, pipe fitting 131 is coated with defrosting compound.Therefore, the possibility that sticks on the pipe fitting 131 of the particle of distillation (frost grain) is very little.Correspondingly, suppressed on pipe fitting 131, to form frost.
In the 6th embodiment, as shown in figure 13, evaporimeter 13 comprises flat pipe fitting 231 and storage tank 233.Storage tank 233 is connected the end of pipe fitting 231.Be similar to first embodiment, pipe fitting 231 is formed by a plurality of coolant channels, and makes by extruding and drawing.
The centre line C L that pipe fitting 231 is set to the cross section is parallel to air-flow direction A1.And shown in Figure 13 and 14, pipe fitting 231 forms fold in the direction perpendicular to air-flow direction A1.
The straight portion 231b of pipe fitting 231 connects by sweep 231a.As shown in figure 14, pipe fitting 231 is arranged as straight portion 231b and intermeshes.As an example, the display pitch Tp4 of the straight portion 231b of downstream pipe fitting 231 is less than the array pitch Tp3 of the straight portion 231b of upstream pipe fitting 231.Perhaps, pitch Tp3 and Tp4 can equate.
Equally, in this embodiment, pipe fitting 231 has the fusiform cross section that is similar to first embodiment.Therefore, pipe fitting 231 has those advantages that are similar to first to fourth embodiment.
In the 7th embodiment, pipe fitting 231 has the plurality of stepped serrations of being roughly shape.Shown in Figure 15 A and 15B, the straight portion 231b of pipe fitting 231 comprises flat substantially face, and these faces are parallel to air-flow direction A1.The upstream side of straight portion 231b and downstream are crooked gradually, and described straight portion 231b connects the plane.
Shown in Figure 15 C, the air bound district is formed at the air downstream part of pipe fitting 231.Shown in arrow A 2, pipe fitting 231 ambient airs stream is from pipe fitting 231 dispersions and in the rotation of the downstream part of pipe fitting 231.
If humid air is through around the pipe fitting 231, moisture sticks to the downstream part of pipe fitting 231 and become frost on pipe fitting.Because pipe fitting 231 is not provided with outside heat sink, frost only forms in the downstream part of the pipe fitting 231 that is parallel to air-flow direction.The possibility that produces frost and obstruction air flow passage therebetween on straight portion 231b is very little.Therefore, air flow resistance has reduced, thereby has improved the cooling capacity of evaporimeter.
As distortion, refrigerant flow channel can have except that circular and square Any shape.Array pitch Tp1, Tp2, Tp3, the Tp4 of pipe fitting 131 and straight portion 231b can be changed.And, do not limit row's number of pipe fitting 131.
The present invention can be used for refrigeration machine to be used for other purpose.For example, the present invention can be used to refrigeration.And the present invention can be used to heat exchanger that the air with sensible heat is cooled off.And,, have fusiform pipe shape and can be used to other the heat exchanger that between fluid and air, carries out heat exchange except being used to cool off the heat exchanger of air.
The present invention is not limited to the disclosed embodiments, under the situation that does not depart from essence of the present invention, can also otherwise implement.
Claims (12)
1. refrigerant-cycle systems that is used to cool off air comprises:
Compressor, its compressed refrigerant;
Condenser, its cooling is from the high-temperature high-pressure refrigerant of compressor discharge;
Decompressor, it reduces from the pressure of the cold-producing medium of condenser discharging;
Evaporimeter, the cold-producing medium that its evaporation is depressurized;
Bypass channel, it walks around decompressor will introduce evaporimeter from the high temperature refrigerant of compressor;
Defrost valve, it allows high temperature refrigerant to flow through bypass channel; With
Control module, its control defrost valve is so that high temperature refrigerant passes through the bypass channel inflow evaporator, wherein
Evaporimeter comprises pipe fitting, and cold-producing medium flows by this pipe fitting,
The outer surface that described pipe fitting is set to them is exposed in the air,
Described pipe fitting have fusiform cross section in case air along the outer surface of described pipe fitting flow and
Each pipe fitting is formed with a plurality of coolant channels, wherein, and with respect to the flow area of the downstream passage of air-flow direction flow area greater than upstream passageway.
2. refrigerant-cycle systems according to claim 1 is characterized in that: described pipe fitting sets in a row with cross structure.
3. refrigerant-cycle systems according to claim 1 and 2 is characterized in that: the streamlined cross section is with respect to its longitudinal centre line symmetry.
4. refrigerant-cycle systems according to claim 1 and 2 is characterized in that: described pipe fitting forms fold along the direction perpendicular to air-flow direction.
5. refrigerant-cycle systems that is used to cool off air comprises:
Compressor, its compressed refrigerant;
Condenser, its cooling is from the high-temperature high-pressure refrigerant of compressor discharge;
Decompressor, it reduces from the pressure of the cold-producing medium of condenser discharging;
Evaporimeter, the cold-producing medium that its evaporation is depressurized;
Bypass channel, it walks around decompressor will introduce evaporimeter from the high temperature refrigerant of compressor;
Defrost valve, it allows high temperature refrigerant to flow through bypass channel; With
Control module, its control defrost valve is so that high temperature refrigerant passes through the bypass channel inflow evaporator, wherein
Evaporimeter comprises flat pipe fitting, and cold-producing medium flows by described flat pipe fitting,
Described flat pipe fitting has and is exposed to airborne outer surface,
The longitudinal centre line that described flat pipe fitting is arranged as the cross section of pipe be parallel to air-flow direction and along form perpendicular to the direction of air-flow direction fold and
Each flat pipe fitting is formed with a plurality of coolant channels, wherein, and with respect to the flow area of the downstream passage of air-flow direction flow area greater than upstream passageway.
6. refrigerant-cycle systems according to claim 5 is characterized in that: described pipe fitting has and is roughly oval-shaped cross section.
7. refrigerant-cycle systems according to claim 5 is characterized in that: described pipe fitting has fusiform cross section so that air flows along outer surface.
8. refrigerant-cycle systems according to claim 7 is characterized in that: the streamlined cross section is with respect to the longitudinal centre line symmetry of cross section.
9. according to claim 5 or 7 described refrigerant-cycle systems, it is characterized in that: maximum and reduce in position, air middle reaches substantially towards the air downstream position of described pipe fitting perpendicular to the cross sectional dimensions of the above pipe fitting of direction of air-flow direction.
10. according to any described refrigerant-cycle systems of claim 5 to 7, it is characterized in that: also comprise the storage tank that is connected to pipe fitting end.
11. refrigerant-cycle systems according to claim 1 or 5 is characterized in that: described pipe fitting is coated with and suppresses the defrosting compound that the frost grain adheres to.
12. refrigerant-cycle systems according to claim 1 or 5, it is characterized in that: described pipe fitting is coated with water repellent agent.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002204335 | 2002-07-12 | ||
| JP2002204335 | 2002-07-12 | ||
| JP2002204334 | 2002-07-12 | ||
| JP2002204334A JP2004044940A (en) | 2002-07-12 | 2002-07-12 | Cooler |
| JP2003082577A JP2004093103A (en) | 2002-07-12 | 2003-03-25 | Cooler |
| JP200382577 | 2003-03-25 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1475713A CN1475713A (en) | 2004-02-18 |
| CN1228591C true CN1228591C (en) | 2005-11-23 |
Family
ID=29783089
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN03146293.6A Expired - Fee Related CN1228591C (en) | 2002-07-12 | 2003-07-07 | Heat exchanger for cooling air |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20040035562A1 (en) |
| CN (1) | CN1228591C (en) |
| DE (1) | DE10331518A1 (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20050081549A1 (en) * | 2003-10-16 | 2005-04-21 | Wu Ho H. | Evaporation type condensation radiator piping for refrigeration and air-conditioning facilities |
| DE102010046471A1 (en) * | 2010-09-24 | 2012-03-29 | Gm Global Technology Operations Llc (N.D.Ges.D. Staates Delaware) | Heat exchanger for radiator arrangement of motor car to remove waste heat produced during operation of drive aggregate to environment, has tubes arranged so that flow cross section is larger at discharge surface than at inlet surface |
| WO2012168598A1 (en) * | 2011-04-21 | 2012-12-13 | Peugeot Citroen Automobiles Sa | Evaporator for a heat pump |
| FR2974407B1 (en) * | 2011-04-21 | 2013-10-18 | Peugeot Citroen Automobiles Sa | HEAT PUMP EVAPORATOR |
| US20120291993A1 (en) * | 2011-05-18 | 2012-11-22 | K&N Engineering, Inc. | Intercooler system |
| US20180334952A1 (en) * | 2011-05-18 | 2018-11-22 | K&N Engineering, Inc. | Intercooler system |
| US10697707B2 (en) | 2013-12-21 | 2020-06-30 | Kyocera Corporation | Heat exchange member and heat exchanger |
| ES2674241T3 (en) | 2014-03-13 | 2018-06-28 | Bae Systems Plc | Heat exchanger |
| JP2016102600A (en) * | 2014-11-27 | 2016-06-02 | 株式会社デンソー | On-vehicle heat exchanger |
| US10378359B2 (en) * | 2016-05-17 | 2019-08-13 | United Technologies Corporation | Heat exchanger with precision manufactured flow passages |
| DE102017105265A1 (en) | 2017-03-13 | 2018-09-13 | Stiebel Eltron Gmbh & Co. Kg | Heat exchanger tube and heat exchanger assembly |
| US10962306B2 (en) | 2018-03-23 | 2021-03-30 | Raytheon Technologies Corporation | Shaped leading edge of cast plate fin heat exchanger |
| BR112021013690A2 (en) * | 2019-02-07 | 2021-09-21 | Hydac Cooling Gmbh | HEAT EXCHANGER |
| US11098962B2 (en) * | 2019-02-22 | 2021-08-24 | Forum Us, Inc. | Finless heat exchanger apparatus and methods |
| US11525618B2 (en) * | 2019-10-04 | 2022-12-13 | Hamilton Sundstrand Corporation | Enhanced heat exchanger performance under frosting conditions |
| GB2599691A (en) * | 2020-10-09 | 2022-04-13 | Rolls Royce Plc | A heat exchanger |
| GB2599693B (en) * | 2020-10-09 | 2022-12-14 | Rolls Royce Plc | A heat exchanger |
| WO2023163680A1 (en) * | 2022-02-24 | 2023-08-31 | Renta Elektrikli Ev Aletleri Sanayi Ve Dis Ticaret Limited Sirketi | Innovation in condenser units of dryers |
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|---|---|---|---|---|
| US1929365A (en) * | 1930-07-30 | 1933-10-03 | Mautsch Robert | Heat exchange apparatus |
| US2431228A (en) * | 1945-06-04 | 1947-11-18 | Burgess Russell Harvey | Heat exchange unit |
| US2759248A (en) * | 1950-06-22 | 1956-08-21 | Russell H Burgess | Method of making heat transfer units |
| US3241608A (en) * | 1955-12-29 | 1966-03-22 | Olin Mathieson | Heat exchanger element |
| US3885936A (en) * | 1972-03-01 | 1975-05-27 | Lund Basil Gilbert Alfred | Heat exchangers |
| CS165037B1 (en) * | 1972-03-30 | 1975-11-28 | ||
| US3976126A (en) * | 1973-12-26 | 1976-08-24 | Gea Luftkuhlergesellschaft Happel Gmbh & Co. Kg | Air cooled surface condenser |
| US4487139A (en) * | 1979-10-04 | 1984-12-11 | Heat Exchanger Industries, Inc. | Exhaust gas treatment method and apparatus |
| CH666538A5 (en) * | 1985-05-15 | 1988-07-29 | Sulzer Ag | HEAT EXCHANGER WITH SEVERAL PARALLEL TUBES AND FINS ATTACHED ON THESE. |
| FI86475C (en) * | 1985-11-27 | 1992-08-25 | Mitsubishi Materials Corp | Heat transfer material and its manufacturing process |
| DE3610618A1 (en) * | 1986-03-29 | 1987-10-01 | Mtu Muenchen Gmbh | PROFILE TUBE WITH ELLIPTICAL OR LANZETT-SHAPED SECTION FOR TUBE HEAT EXCHANGER AND METHOD FOR THE PRODUCTION THEREOF |
| DE3636762C1 (en) * | 1986-10-29 | 1988-03-03 | Mtu Muenchen Gmbh | Heat exchanger |
| DE3735846A1 (en) * | 1987-10-23 | 1989-05-03 | Mtu Muenchen Gmbh | METHOD FOR PRODUCING A TUBE BOTTOM STRUCTURE OF A HEAT EXCHANGER |
| US5181558A (en) * | 1990-11-13 | 1993-01-26 | Matsushita Refrigeration Company | Heat exchanger |
| DE4201791A1 (en) * | 1991-06-20 | 1993-07-29 | Thermal Waerme Kaelte Klima | FLAT TUBES FOR INSTALLATION IN A FLAT TUBE HEAT EXCHANGER AND METHOD FOR SEPARATING THE FLAT TUBES |
| DE4234006C2 (en) * | 1992-10-09 | 1995-05-04 | Mtu Muenchen Gmbh | Profile tube for heat exchangers |
| DE19845336A1 (en) * | 1998-10-01 | 2000-04-06 | Behr Gmbh & Co | Multi-channel flat tube |
| JP2001165532A (en) * | 1999-12-09 | 2001-06-22 | Denso Corp | Refrigerant condenser |
| US6536255B2 (en) * | 2000-12-07 | 2003-03-25 | Brazeway, Inc. | Multivoid heat exchanger tubing with ultra small voids and method for making the tubing |
-
2003
- 2003-07-07 CN CN03146293.6A patent/CN1228591C/en not_active Expired - Fee Related
- 2003-07-11 US US10/618,196 patent/US20040035562A1/en not_active Abandoned
- 2003-07-11 DE DE10331518A patent/DE10331518A1/en not_active Withdrawn
Also Published As
| Publication number | Publication date |
|---|---|
| US20040035562A1 (en) | 2004-02-26 |
| DE10331518A1 (en) | 2004-01-22 |
| CN1475713A (en) | 2004-02-18 |
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