CN1065624C - Improvements in plate heat exchangers - Google Patents
Improvements in plate heat exchangers Download PDFInfo
- Publication number
- CN1065624C CN1065624C CN93121143A CN93121143A CN1065624C CN 1065624 C CN1065624 C CN 1065624C CN 93121143 A CN93121143 A CN 93121143A CN 93121143 A CN93121143 A CN 93121143A CN 1065624 C CN1065624 C CN 1065624C
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- Prior art keywords
- cold
- heat exchanger
- producing medium
- mentioned
- plate type
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Classifications
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
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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
- F25B39/028—Evaporators having distributing means
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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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
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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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
- F28D9/0056—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another with U-flow or serpentine-flow inside conduits; with centrally arranged openings on the plates
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
- F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
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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
- F25B39/022—Evaporators with plate-like or laminated elements
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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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0071—Evaporators
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A plate heat-exchanger (12) has an assembly of plates (16) defining and separating alternate passages (14, 16) for the flow of a refrigerant and a heat-exchange fluid. Aligned holes (15) in the plates (16) provide inlets and outlets for the refrigerant and heat-exchange fluid to the respective passages (14, 16). A refrigerant distribution tube (26, 37) is located in the refrigerant inlet defined by holes (15). The tube (26, 37) has outlet apertures (27, 38) which direct refrigerant into the refrigerant passage (14). Blanking members (29, 39) blank off part of the opening into each refrigerant passage (14) to confine the refrigerant flow from the apertures (27, 38) to a predetermined path towards the plate centreline to ensure even refrigerant distribution.
Description
The present invention relates to the improvement of plate type heat exchanger, more particularly, relate to the improvement of the heat exchanger that is used as evaporimeter in the refrigeration system.
People develop the plate type heat exchanger that is used for refrigeration system already, and it is unusual practical and effective that this heat exchanger is used for heat is passed to cold-producing medium from a kind of heat-exchange fluid (for example water).This class heat exchanger comprises one by some drawings, has the sub-assembly that the metallic plate of some protrusions and channel-shaped portion assembles.Protrusion in the sub-assembly and channel-shaped portion constitute the passage of cold-producing medium and heat-exchange fluid.Cold-producing medium flows through this heat exchanger with heat-exchange fluid in the relative both sides of every block of plate, is provided with refrigerant inlet and heat-exchange fluid outlet at an end of heat exchanger, and the other end of heat exchanger is provided with corresponding refrigerant outlet and heat-exchange fluid inlet.
When with plate type heat exchanger during as the evaporimeter in the refrigeration system, a difficult problem that often runs into is to guarantee that cold-producing medium is evenly distributed in a large amount of passages between heat exchanger and the plate.Usually, cold-producing medium expanded by an expansion valve or a cold-producing medium decompressor that was right after before heat exchanger before entering this class heat exchanger, thereby formed unsettled liquid and steam mixture in entering the cold-producing medium of this heat exchanger.That is to say, the liquid refrigerant by expansion gear or dropping equipment expand or the step-down process in can make the part of refrigerant evaporation.
The size of evaporation capacity is relevant with the degree of the temperature that enters the preceding liquid refrigerant of expansion gear and expansion or step-down.Expanding or buck stage, 50: 1 expansion ratio may cause up to 2% or more liquid evaporation.Because steam can account for liquid and gaseous state refrigerant mixture volume 50% or more, because it is liquid different with the density of gaseous refrigerant, thereby cause air flow structure to change, like this, the liquid refrigerant that some passage flow through of the plate system of plate type heat exchanger is more than other plate.This will cause by the inhomogeneous unanimity of the ratio of the liquids and gases of different coolant channels, thereby cause the steam temperature of exhaust outlet to change.The temperature that so flows through the heat-exchange fluid of heat exchanger fluid passage in some passage may be lower than the fluid temperature (F.T.) in other passages.
In the application of most of plate type heat exchangers, cause the cold-producing medium input unstable owing between the phase of expansion, partly evaporate caused unstability, thereby cause the unstable properties between the passage in the system.This means that some fractional load of heat exchanger is bigger than other parts in order to obtain predetermined efficient from heat exchanger, its peak efficiency may reduce.
Usually water is as heat-exchange fluid, if the percentage of liquid refrigerant that flows through some plate in the system is than other plate hight, passage between these plates then has icing tendency, this will cause some heat exchange flow body loop to freeze, and other loop is still unimpeded, thereby, make problem more serious, finally may cause heat exchanger failure.
In order to overcome above-mentioned shortcoming, people wish evenly to flow through in the passage of cold-producing medium between plate type heat exchanger plate and plate.
Wish that also the liquid refrigerant uniform distribution flows through the coolant channel of plate type heat exchanger.
Also be desirable to provide a kind of fairly simple and liquid refrigerant distributor that cost is cheap.
Content according to an aspect of the present invention, heat exchanger provided by the present invention comprise a sub-assembly that is assembled by some plates, and the lane device of permission cold-producing medium and flow of heat exchange fluid is separated and limited to above-mentioned plate; The cold-producing medium input unit that communicates with the coolant channel device; The heat-exchange fluid input unit that communicates with the heat-exchange fluid lane device is respectively applied for the output device of cold-producing medium and heat-exchange fluid; With the refrigerant distributing device that the cold-producing medium input unit links, this distributor comprises that regulating and guide cold-producing medium for one enters the flow control apparatus of each coolant channel device.
In a kind of structure of the present invention, refrigerant distributing device can comprise a pipe that is contained in the cold-producing medium input unit, and this pipe has some ducts to make cold-producing medium evenly flow into the aperture of corresponding coolant channel to form a row.The quantity in duct and size can be formed the quantity exchange capability of heat of the plate of heat exchanger according to the size of plate, the pressure of cold-producing medium kind, cold-producing medium and the system of use, and other running parameter is determined.Obviously, the quantity in duct needn't conform to the quantity of coolant channel, though usually like this can be better.In order to estimate the pressure loss of cold-producing medium, can change the size of each aperture along pipe.Also can change the size of aperture so that change the exchange capability of heat of heat exchanger according to designing requirement or operational factor.
In one embodiment, as expansion gear or dropping equipment, so just do not need outside expansion valve or other expansion gears or dropping equipment with the pipe of road with holes or aperture or other opening.Adopt this structure, the size of duct or aperture increases gradually from the input of this pipe, and this just can provide uniform liquid distribution for every coolant channel.
In another embodiment, as demi-inflation or dropping equipment, this device and an outside expansion valve or other expansion gear or dropping equipment link to each other with the pipe that has duct aperture or other opening.Adopt this structure, demi-inflation or step-down occur in the outside, and the last expansion or the step-down of liquid refrigerant take place in refrigerant distributing device.
In yet another embodiment, link to each other with refrigerant distributing device with an additional outside expansion valve or other expansion gears or dropping equipment.In this member, have cold-producing medium second distributor in parallel with cold-producing medium first distributor, temperature by the cold-producing medium after cold-producing medium first distributor expands will with the temperature and/or the pressure of output cold-producing medium, the temperature of heat-exchange fluid input and output and/or pressure and ambient temperature are monitored together, and outside expansion valve can be worked as requested selectively, in order to temperature and/or the pressure parameter that keeps being scheduled to.In this embodiment, the duct size in cold-producing medium second distributor is bigger, so that it is lower to be assigned to the pressure ratio of the cold-producing medium in the passage.
Another characteristics of the present invention are to have a part tripper, can partly cut off the contact between cold-producing medium input unit and the coolant channel device.Opening in the tripper or aperture direct liquid refrigerant flow by predetermined direction, preferably flow to the center of coolant channel device, for example, and the center line of course plate assembly.In a kind of structure of the present invention, above-mentioned tripper can be used to constitute refrigerant distributing device, and in another kind of structure of the present invention, above-mentioned tripper and refrigerant distributing device work together.In a preferred embodiment, tripper comprises a common C shape wire member will, this member be arranged on cold-producing medium input unit between the every pair of plate that limits the coolant channel device around.
In order more easily to understand the present invention, one embodiment of the present of invention are described below in conjunction with accompanying drawing.
Fig. 1 is a sectional schematic diagram of having indicated the standard plate type heat exchanger of flow of refrigerant approach;
Fig. 2 is similar to Fig. 1, but has indicated the flow path of heat-exchange fluid;
Fig. 3 is similar to Fig. 1, and it shows one embodiment of the present of invention;
Fig. 4 is the amplification profile diagram of the heat exchanger bottom shown in Fig. 3;
Fig. 5 is the sectional drawing of 5-5 along the line among Fig. 4;
Fig. 6 is the partial, exploded perspective view of the heat exchanger shown in Fig. 3, and it shows a kind of remodeling of the present invention;
Fig. 7 is the cross-sectional view of Fig. 6 remodeling;
Fig. 8 is similar to Fig. 4, but it shows another kind of structure of the present invention;
Fig. 9 is the sectional drawing along 9-9 line among Fig. 8;
Figure 10 is similar to Fig. 9, and it shows another embodiment of the present invention.
Referring to accompanying drawing, plate type heat exchanger 12 illustrated in figures 1 and 2 be one by some plates 30 sub-assemblies that the plate 10 that is the rib shape is assembled into for example, the flank of adjacent two boards is connected mutually, and adjacent two boards limits the passage of cold-producing medium and the passage 14 and 16 of heat-exchange fluid.Because water is as heat-exchange fluid usually, heat-exchange fluid cited below refers to water.In addition, although shown in the accompanying drawing be a kind of contra-flow heat exchanger, obviously the present invention also can be applicable to down-stream heat exchanger.
Can be clear that more that in Fig. 5 every end of every block of plate 10 has two ducts 15, the duct 15 in the sub-assembly of plate 10 forms the inlet and the outlet of cold-producing medium and water.Plate 10 is separated with coolant channel 14 and with aquaporin 16, and plate is connected mutually with plate and with soldering or similarly the solder technology sealing is together, make the fluid that flows into a following duct 15 flow through one group of cold-producing medium and aquaporin 14 and 16, flow out from the corresponding duct of going up, and the fluid that flows into another following duct 15 flows through another group passage.A cold-producing medium input house steward 17 communicates with those openings 15 that communicate with coolant channel 14, and the cold-producing medium delivery trunk 18 of heat exchanger upper end can make cold-producing medium flow out from heat exchanger.Similarly, the input house steward 19 of water and delivery trunk 21 make water circulate in aquaporin 16 respectively.
In the plate type heat exchanger 12 of standard, cold-producing medium input house steward 17 makes the expansion valve 23 of cold-producing medium step-down link to each other with a high pressure liquid refrigerant feeding mechanism 22 by one.When cold-producing medium during by above-mentioned valve 23, some cold-producing mediums flash to steam and mix with liquid refrigerant.As a result, mixture liquid and gaseous refrigerant enters heat exchanger 12.Because mixture is inhomogeneous, to account for volume much bigger because the shared volume ratio liquid refrigerant of gaseous refrigerant produces, some coolant channels 14 are accepted more liquid refrigerant than other passage, therefore, the liquid and the vapor volume that flow through every coolant channel 14 are changed, this just causes between each coolant channel 14, and the heat output between aquaporin 16 and the coolant channel 14 changes.
Among Fig. 1, line 24 has shown the variation of the local heat-exchange capacity that undergoes phase transition between liquid refrigerant and steam.Line 24 is " phase change line fully ", and this curve table illustrates the temperature of the cold-producing medium that flows out from several coolant channels 14.According to the vapor ratio that enters in every coolant channel 14, the changing value of said temperature can be from 2 ℃ to 11 ℃.
The variations in temperature of the refrigerant vapour that flows out from passage 14 causes that similar variation takes place the temperature of the water that flows out from aquaporin 16.As shown in Figure 2, the temperature of the water that flows out from aquaporin 16 can change to 10 ℃ from 2 ℃.If the temperature of water is too low and cause water freezing in any aquaporin 16, just have additional load in the other parts of heat exchanger, and heat exchanger effectiveness can descend significantly also.This freezing may cause heat exchanger failure.
Referring to Fig. 3-7, in a kind of structure of the present invention, high pressure liquid refrigerant is contained among the cold-producing medium input house steward 17 by directly flowing to and extends in the distributing pipe 26 on the plate hole road 15 that communicates with coolant channel 14.Distributing pipe 26 has some holes or aperture 27, and these holes are consistent with refrigerating channel 14 on number, and aligns with coolant channel 14 exactly.12 rear portion increases the size in above-mentioned hole 27 gradually from house steward 17 to heat exchanger, and therefore, though formation pressure drop in pipe 26, the distribution of the liquid refrigerant in every coolant channel 14 is still very even.
Because the plate hole road 15 that communicates with coolant channel 14 is in a side of every block of plate, the C-washer 29 that is contained in the coolant channel 14 is looped around around the corresponding plate hole road 15 substantially, and cuts off the inlet of direct admission passage 14.Be in opening 25 between each C-washer 29 two ends and be used for direct liquid refrigerant and flow to the center of passage 14 down, thereby liquid refrigerant is evenly distributed on the whole width of passage 14.Upborne contact-making surface 30 on the plate 16 of qualification passage 14 helps to guide the center of passage 14 into making cryogen.
Test shows, adopts the distributing pipe 26 among the present invention, and the complete phase transformation between liquid state and the vaporous cryogen is evenly distributed on all passages 14 it substantially, shown in the complete phase change line 28 among Fig. 3.The result makes the temperature of refrigerant vapour even substantially, so, also can make the water that flows out from aquaporin 16 obtain corresponding uniform temperature.
Owing to guaranteed the even distribution of liquid and steam in every coolant channel 14, thereby obviously improved the efficient of heat exchanger 12.Test also shows, compares with fluid distribution method with general expansion, in embodiment described in the invention, can make exchange capability of heat improve 10% by the identical test heat exchanger of using distributing pipe 26.So, by utilizing feature of the present invention, under the prerequisite of the mean temperature of the very approaching outflow water of minimum water temperature that in any given loop, flows out, can reduce the plate quantity in the plate type heat exchanger.Obviously, the plate quantity that reduces heat exchanger under any given situation can make cost reduce, and operational efficiency improves.
Referring to Fig. 6 and Fig. 7, the size in the hole 27 on the pipe 26 can change according to the different operating parameter in each refrigeration and the air-conditioning system, to satisfy different refrigeration demand, for this reason, aforementioned tube 26 has one with respect to pipe 26 rotating hollow shaft 26a, so that close or open hole 27 as required.Hollow shaft 26a can be by any proper device location.
Fig. 8 and Fig. 9 show a kind of remodeling of the present invention, and liquid refrigerant second distributor 31 that passes the plate hole road 15 that communicates with coolant channel 14 is arranged in this structure, and this device is parallel with liquid refrigerant first distributing pipe 26 substantially.Second pipe have on 31 with distributing pipe 26 on hole 27 quantity quite and substantially with the hole of hole 27 centerings, the size in hole 32 size than hole 27 substantially is big.
The second liquid refrigerant pipe 31 is when starting and when working under the low ambient temperature condition, provides additional cold-producing medium swell increment to satisfy the demand thereby can be heat exchanger 12 when particularly using air in the cold-producing medium circulation.On the input house steward 17 temperature sensor 36 can also be housed, also available other sensor (not shown) are measured the temperature and/or the pressure at refrigerant outlet place, and measure the entrance and exit temperature of water, so that the work of variable expansion valve 34.Second liquid refrigerant 31 can improve heat exchanger 12 in the scope of certain service condition ability to work is set, has therefore improved the efficient of the system that this class heat exchanger is housed.
As shown in Fig. 8 and 9, also utilize C type packing ring 29 among this embodiment, and two groups of holes 27 and 32 openings 25 that all face toward between the packing ring two ends.The trend in hole is a benchmark with the trend of pipe.Depart from pipe 26 to guarantee hole 32.
Referring to Figure 10, it shows another embodiment of the present invention.In this embodiment, the distribution of cold-producing medium is to be finished by a conical tube 37 that passes the plate hole road 15 that communicates with coolant channel 14.Pipe 37 is except the area of sections from the total pipe end of cold-producing medium to pipe 37 the other end reduce gradually, and others are with extremely the pipe 26 among the embodiment shown in Figure 7 is very similar at Fig. 3.Measure-alike with each hole 38 on the hole 27 corresponding conical tubes 37 of pipe on 26, and the coniform liquid refrigerant that has guaranteed to flow through in the hole 38 of pipe can evenly distribute just.
Shown in above-mentioned embodiment, though can also show another kind of tripper among Figure 10 with C shape ring or the packing ring 29 local coolant channels 14 that disconnect, this device is made up of a blanking tube that has a seam 41 along a side.Blanking tube 39 ripples insert in the plate hole road 15 (these ducts communicate with coolant channel 14), make usually to stitch 41 and down inwardly.The aperture position that is between the C-washer two ends in position and the foregoing description of seam is similar.Blanking tube can be made with the material that can weld, and can be welded on the plate 16 on every side of hole logical 15, and in this case, blanking tube 39 can be packed into before the last welding stage of assembling heat exchanger 12.In addition, blanking tube 39 reinstalls after also can in the end welding the stage, and in this case, blanking tube can be made with any suitable material (comprising plastics).If the material of blanking tube is an elastomeric material, pipe 39 external diameter can be greater than the diameter in plate hole road 15, and need only compress this pipe when packing this pipe into, makes and stitches 41 near a side, can reduce the diameter of pipe like this, be enough to make its can load plate duct 15 in.If desired, can process circular groove on blanking tube 39, like this, when being seated, the edge in plate hole road 15 just can be stuck in the circular groove.In case of necessity, desired location is installed and be sealed in to available encapsulant or adhesive with blanking tube 39.
Obviously, remodeling of the present invention can comprise that also other are used to regulate the device that flows to the liquid refrigeration stream of each passage 14 from cold-producing medium input house steward 17.Can make liquid refrigerant and every passage 14 of the balanced inflow of vaporous cryogen if change this adjusting, then be expected to obtain the effect similar to stating each specific embodiment.
Obviously, the present invention can also save common expansion valve or other expansion gear or cold-producing medium decompressor, therefore, can reduce production costs, and can also improve the performance of heat exchanger simultaneously.
Claims (25)
1. plate type heat exchanger, it comprises:
An assembly that assembles by some plates, above-mentioned plate separation also limits the lane device that supplies cold-producing medium and flow of heat exchange fluid;
The duct that has many groups to align on the plate limits the cold-producing medium input unit that communicates with the coolant channel device;
The heat-exchange fluid input unit that communicates with the heat-exchange fluid lane device;
Be respectively applied for the output device of cold-producing medium and heat-exchange fluid;
It is characterized in that, also comprise:
The refrigerant distributing device that links to each other with the cold-producing medium input unit, this distributor comprises that an adjusting and directs refrigerant go into the flow control apparatus of each coolant channel device, above-mentioned distributor comprises a pipe that is contained in the cold-producing medium input unit, this pipe has some apertures, cold-producing medium flows into every coolant channel device from above-mentioned aperture, described flow control apparatus or the size that comprises described aperture increase gradually from the end to end of pipe, comprise that perhaps pipe is tapered, its sectional area is bigger at the refrigerant inlet end, less away from an end of inlet, and the size of aperture is identical on the total length of pipe.
2. plate type heat exchanger as claimed in claim 1 is characterized in that, is provided with the adjusting device that selectively changes the aperture cross-sectional area, thereby changes the flow regime of cold-producing medium in aperture.
3. plate type heat exchanger as claimed in claim 2, it is characterized in that, the size of aforementioned tube and those apertures should be selected to and can constitute the cold-producing medium decompressor that reduces liquid refrigerant pressure, so that the liquid refrigerant of sending in the aforementioned tube reaches predetermined lower pressure.
4. plate type heat exchanger as claimed in claim 1 is characterized in that, described distributor comprises a hollow shaft with described pipe jointing, and this hollow shaft has the opening of the aperture centering of at least one and pipe.
5. plate type heat exchanger as claimed in claim 1, it is characterized in that, perhaps in every coolant channel device, be provided with local part tripper around the cold-producing medium input unit, perhaps in the cold-producing medium input unit, be provided with the part tripper, this tripper limit cold-producing medium from distributor by along the predetermined channel flow that opening limited the local tripper.
6. plate type heat exchanger as claimed in claim 5 is characterized in that the position of above-mentioned opening should be able to make the center line of each coolant channel device of refrigerant flow direction.
7. plate type heat exchanger as claimed in claim 5 is characterized in that, above-mentioned flow control apparatus with cold-producing medium from the distributor above-mentioned opening that leads.
8. plate type heat exchanger as claimed in claim 5 is characterized in that, above-mentioned part tripper comprises the C shape part of some sealing plates, and above-mentioned C shape part defines every coolant channel device and surrounded the duct that limits the cold-producing medium input unit in the plate.
9. plate type heat exchanger as claimed in claim 5 is characterized in that, above-mentioned part tripper comprises a tube-like piece, and a side of this pipe fitting has a groove, and pipe fitting is arranged in the refrigerant inlet device, and the groove on the pipe forms above-mentioned opening.
10. plate type heat exchanger as claimed in claim 1, it is characterized in that, be provided with cold-producing medium second distributor in the cold-producing medium input unit, this cold-producing medium second distributor links to each other with the high pressure liquid refrigerant feedway by a decompressor of selectively operating.
11. plate type heat exchanger as claimed in claim 10 is characterized in that, above-mentioned cold-producing medium second distributor comprises a pipe that has some bigger holes, so that with cold-producing medium each coolant channel device that leads.
12. plate type heat exchanger as claimed in claim 1, it is characterized in that, above-mentioned distributing pipe comprises a narrow meshed pipe, cold-producing medium enters this pipe by the high pressure liquid refrigerant pipeline, aforementioned tube and aperture constitute a decompressor, and pressure reduces when making cold-producing medium enter coolant channel by this decompressor.
13. plate type heat exchanger as claimed in claim 12 is characterized in that, an auxiliary refrigerating agent distributor passes above-mentioned cold-producing medium input unit, and is parallel with aforementioned tube substantially.
14. plate type heat exchanger as claimed in claim 13, it is characterized in that, above-mentioned additional distributor is a pipe, it links to each other with the high pressure liquid refrigerant pipeline by a decompressor, this decompressor reduces the refrigerant pressure in this additional allocation organ pipe, having on the additional allocation organ pipe has bigger hole, lower pressure refrigerant to flow through above-mentioned hole to be assigned in the above-mentioned coolant channel.
15. plate type heat exchanger as claimed in claim 14 is characterized in that, the size of the aperture on the above-mentioned distributing pipe strengthens to another far-end gradually from an above-mentioned end.
16. plate type heat exchanger as claimed in claim 15 is characterized in that, the cross-sectional area of above-mentioned aperture is variable.
17. plate type heat exchanger as claimed in claim 16 is characterized in that, is furnished with a hollow shaft on above-mentioned distributing pipe, this has the opening of one or more and above-mentioned aperture centering, and this axle can rotate selectively, to change the size of aperture.
18. plate type heat exchanger as claimed in claim 14 is characterized in that, is provided with tripper in cold-producing medium input unit or each bar coolant channel, so that the restriction cold-producing medium is from the pre-routing that opening limited of input unit inflow by this tripper.
19. plate type heat exchanger as claimed in claim 18 is characterized in that, above-mentioned tripper comprises the C shape wire member will that some seal above-mentioned passage and center on above-mentioned input unit.
20. plate type heat exchanger as claimed in claim 19 is characterized in that, above-mentioned tripper comprises that is arranged on a tubular body that is roughly C shape in the above-mentioned input unit.
21. plate type heat exchanger as claimed in claim 12 is characterized in that, the cross-sectional area of above-mentioned distributing pipe reduces to another far-end gradually from an end of assembly.
22. plate type heat exchanger as claimed in claim 4 is characterized in that, is provided with the part tripper in the cold-producing medium input unit, this tripper limit cold-producing medium from distributor by along the predetermined channel flow that opening limited the local tripper.
23. plate type heat exchanger as claimed in claim 22 is characterized in that, the position of above-mentioned opening should be able to make the center line of each coolant channel device of refrigerant flow direction.
24. plate type heat exchanger as claimed in claim 22 is characterized in that, above-mentioned flow control apparatus with cold-producing medium from the distributor above-mentioned opening that leads.
25. plate type heat exchanger as claimed in claim 22, it is characterized in that above-mentioned part tripper comprises a tube-like piece, a side of this pipe fitting has a groove, pipe fitting is arranged in the refrigerant inlet device that the duct that aligned by plate limits, and the groove on the pipe forms above-mentioned opening.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AUPL6223 | 1992-12-07 | ||
| AUPL622392 | 1992-12-07 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1094156A CN1094156A (en) | 1994-10-26 |
| CN1065624C true CN1065624C (en) | 2001-05-09 |
Family
ID=3776580
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN93121143A Expired - Fee Related CN1065624C (en) | 1992-12-07 | 1993-12-07 | Improvements in plate heat exchangers |
Country Status (11)
| Country | Link |
|---|---|
| EP (1) | EP0670988A4 (en) |
| JP (1) | JPH08504027A (en) |
| CN (1) | CN1065624C (en) |
| AU (1) | AU686582B2 (en) |
| CA (1) | CA2151129A1 (en) |
| IL (1) | IL107850A0 (en) |
| MX (1) | MX9307692A (en) |
| PT (1) | PT101421A (en) |
| TW (1) | TW232049B (en) |
| WO (1) | WO1994014021A1 (en) |
| ZA (1) | ZA939173B (en) |
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| CN100408953C (en) * | 2001-08-20 | 2008-08-06 | 普莱克斯技术有限公司 | Cryogenic condensation system |
| CN100434856C (en) * | 2005-06-07 | 2008-11-19 | 缪志先 | Plate type heat exchanger with heat exchange medium divider |
| CN101782298B (en) * | 2009-01-19 | 2011-12-28 | 三花丹佛斯（杭州）微通道换热器有限公司 | Heat exchanger |
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-
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- 1993-12-02 IL IL10785093A patent/IL107850A0/en unknown
- 1993-12-06 JP JP6513559A patent/JPH08504027A/en active Pending
- 1993-12-06 AU AU56195/94A patent/AU686582B2/en not_active Ceased
- 1993-12-06 TW TW082110281A patent/TW232049B/zh active
- 1993-12-06 PT PT101421A patent/PT101421A/en not_active Application Discontinuation
- 1993-12-06 WO PCT/AU1993/000627 patent/WO1994014021A1/en not_active Application Discontinuation
- 1993-12-06 EP EP94901695A patent/EP0670988A4/en not_active Withdrawn
- 1993-12-06 CA CA002151129A patent/CA2151129A1/en not_active Abandoned
- 1993-12-06 MX MX9307692A patent/MX9307692A/en not_active Application Discontinuation
- 1993-12-07 ZA ZA939173A patent/ZA939173B/en unknown
- 1993-12-07 CN CN93121143A patent/CN1065624C/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100408953C (en) * | 2001-08-20 | 2008-08-06 | 普莱克斯技术有限公司 | Cryogenic condensation system |
| CN100434856C (en) * | 2005-06-07 | 2008-11-19 | 缪志先 | Plate type heat exchanger with heat exchange medium divider |
| CN101782298B (en) * | 2009-01-19 | 2011-12-28 | 三花丹佛斯（杭州）微通道换热器有限公司 | Heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1094156A (en) | 1994-10-26 |
| PT101421A (en) | 1995-05-04 |
| TW232049B (en) | 1994-10-11 |
| EP0670988A4 (en) | 1995-11-22 |
| CA2151129A1 (en) | 1994-06-23 |
| ZA939173B (en) | 1994-08-08 |
| IL107850A0 (en) | 1994-04-12 |
| WO1994014021A1 (en) | 1994-06-23 |
| AU5619594A (en) | 1994-07-04 |
| AU686582B2 (en) | 1998-02-12 |
| EP0670988A1 (en) | 1995-09-13 |
| MX9307692A (en) | 1994-06-30 |
| JPH08504027A (en) | 1996-04-30 |
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