CN203629388U - Spiral-plate heat exchanger - Google Patents
Spiral-plate heat exchanger Download PDFInfo
- Publication number
- CN203629388U CN203629388U CN201320655890.0U CN201320655890U CN203629388U CN 203629388 U CN203629388 U CN 203629388U CN 201320655890 U CN201320655890 U CN 201320655890U CN 203629388 U CN203629388 U CN 203629388U
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- plate
- thread plate
- heat exchanger
- threaded plate
- spiral
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Abstract
The utility model discloses a spiral-plate heat exchanger. The heat exchanger comprises a heat exchange body. The heat exchange body comprises a center partition plate, a first threaded plate and a second threaded plate. One end of the first threaded plate is fixedly connected with one side of the center partition plate in a sealing mode, one end of the second threaded plate is fixedly connected with the other side of the center partition plate in a sealing mode, and the first threaded plate and the second threaded plate are concentrically wound into a cylinder in the same direction. The first threaded plate and the second threaded plate are both provided with ripples with the same shape and the same size. In the winding process, the wave crests of the inner ring threaded plate are attached to the wave troughs of the outer ring threaded plate adjacent to the inner ring threaded plate, and a fluid channel is formed between the wave troughs of the inner ring threaded plate and the wave crests of outer ring threaded plate adjacent to the inner ring threaded plate. The spiral-plate heat exchanger is good in heat transfer performance and high in pressure bearing capacity, saves materials and reduces the welding processes.
Description
Technical field
The utility model relates to heat-exchange apparatus field, relates in particular to a kind of spiral heat exchanger.
Background technology
Spiral heat exchanger is a kind of high-performance heat exchanger, be widely used in the industries such as chemical industry, light industry, food, having the following advantages: (1) overall heat-transfer coefficient is high-because fluid is subject to the effect of centrifugal inertial force and the interference of spacing column in spirality channel, low reynolds number (Re=1400～1800) is lower can reach turbulent flow, permissible velocity of flow is large, and (liquid is 2m/s, gas is 20m/s), therefore heat transfer coefficient is large.If water is to water heat transfer process K=2000～3000W/m
2k.(2) less scaling and stop up-because flow velocity is higher and flow through, have souring voluntarily in spirality channel, therefore the suspension in fluid is difficult for depositing.(3) can utilize low-temperature heat source because runner is long and two fluids can reach complete adverse current, thereby heat transfer temperature difference is large, can make full use of the thermal source that temperature is lower.(4) compact conformation is due to the thin 2～4mm of plate, and the heat transfer area of unit volume can reach 150～500m
2/ m
3.
Spiral heat exchanger is placed on together to roll by two longer sheet packs and forms, and is welded with in uniform way spacing column on every plate, and it makes to produce certain distance between two plates, forms two spirality channels, between cold fluid and hot fluid, carry out heat exchange by spiral wooden partition.The spiral-plate heat exchanger of prior art is constructed as shown in Figure 1, and 210 is fluid passage, and 220 is steel plate, and 230 is spacing column, and 240 is round steel, and 250 is sealing welding rod; Then and between heat exchanger plates, carry out two seals welding helical duct edge tamps with round steel.The spacing column of spiral plate has the effect of three aspects: (1) controls the spacing of helical duct; (2) increase spirochetal strength and stiffness; (3) make flow media turbulization, augmentation of heat transfer.
But the spiral heat exchanger bearing capacity of existing employing spacing column is limited, and need to weld spacing column, also need to adopt round steel and two seal weldings, increased material cost, and heat exchange area is little, cause the temperature difference of heat exchanger plates both sides large, heat exchange efficiency is low.
Summary of the invention
For this reason, the purpose of this utility model is to provide a kind of heat exchange property height to save again the rotation plate type heat exchanger of material.
For achieving the above object, the utility model provides a kind of spiral heat exchanger, comprise heat exchange body, described heat exchange body comprises central partition plate, the first thread plate and the second thread plate, end of described the first thread plate and a limit fixed seal connection of central partition plate, end of the second thread plate and another limit fixed seal connection of central partition plate, the first thread plate and the second thread plate roll into cylindrical with the same center of circle of same direction; Wherein, described the first thread plate and the second thread plate all have all identical ripples of shape size, roll in process, the trough of the crest of inner ring thread plate and adjacent outer ring thread plate fits, and between the crest of the trough of inner ring thread plate and adjacent outer ring thread plate, forms fluid passage.
Alternatively, according to spiral heat exchanger of the present utility model, the top of described heat exchange body and sidewall are respectively equipped with the first medium entrance and the first medium outlet that flow into and flow out for first medium, and, be respectively equipped with at bottom and the sidewall of described heat exchange body the second medium entrance and the second medium outlet that flow into and flow out for second medium.
Alternatively, according to spiral heat exchanger of the present utility model, described ripple is herringbone ripple.
Alternatively, according to spiral heat exchanger of the present utility model, the corrugation pitch of described ripple equates with trough spacing.
Alternatively, according to spiral heat exchanger of the present utility model, the edge of described the first thread plate and Second Wave card is all higher than the height of ripple.
Alternatively, according to spiral heat exchanger described in the utility model, the thickness of described the first thread plate and the second thread plate is 2mm.
The helical duct of spiral heat exchanger described in the utility model easily forms turbulent flow, has effectively increased heat exchange area, good heat-transfer; Because ripple is evenly arranged, its strong point density that is evenly distributed is large, in the situation that plate thickness is identical, adopts ripple stronger than adopting spacing column bearing capacity, and replaces spacing column with ripple, saves material, has reduced welding sequence.
Accompanying drawing explanation
By reading below detailed description of the preferred embodiment, various other advantage and benefits will become cheer and bright for those of ordinary skills.Accompanying drawing is only for the object of preferred embodiment is shown, and do not think restriction of the present utility model.In the accompanying drawings:
Fig. 1 is the structural representation of spiral heat exchanger in prior art;
Fig. 2 is the structural representation of spiral heat exchanger described in the utility model;
Fig. 3 is the sectional view of heat exchange body in spiral heat exchanger described in the utility model; And
Fig. 4 is the structural representation of thread plate in spiral heat exchanger described in the utility model.
The specific embodiment
Below in conjunction with accompanying drawing and concrete embodiment, the utility model will be further described.
Fig. 2 shows the structural representation of spiral heat exchanger described in the utility model.As shown in Figure 2, described spiral heat exchanger comprises heat exchange body 100, top and sidewall at described heat exchange body 100 are respectively equipped with the first medium entrance 140 and the first medium outlet 150 that flow into and flow out for first medium, and, be respectively equipped with at bottom and the sidewall of described heat exchange body 100 the second medium entrance 160 and the first medium outlet 170 that flow into and flow out for second medium.First medium and the second medium for the treatment of heat exchange enter heat exchange body from described first medium entrance 140 and second medium entrance 160 respectively, after heat exchange, then flow out from described first medium outlet 150 and second medium outlet 170 respectively, complete heat transfer process.
Fig. 3 shows the sectional view of heat exchange body in spiral heat exchanger described in the utility model.As shown in Figure 3, described heat exchange body 100 comprises central partition plate 110, the first thread plate 120 and the second thread plate 130, and described the first thread plate 120 and the second thread plate 130 are rectangle.End of described the first thread plate 120 and a limit fixed seal connection of central partition plate 110, end of the second thread plate 130 and another limit (corresponding with the limit that the first thread plate is connected) fixed seal connection of central partition plate 110, the first thread plate 120 and the second thread plate 130 roll into cylindrical with the same center of circle of same direction; Wherein, described the first thread plate 120 and the second thread plate 130 all have all identical ripples of shape size, roll in process, the first thread plate 120 and the second thread plate 130 multi-turn that rolls bonded to each other, for example roll 3-15 circle, the trough of the crest of inner ring thread plate and adjacent outer ring thread plate fits, and between the crest of the trough of inner ring thread plate and adjacent outer ring thread plate, forms fluid passage 180,190, and what wherein flowed in fluid passage 180 and fluid passage 190 is first medium and second medium.Consider the requirement of processing technology, the thickness of described the first thread plate and the second thread plate is advisable with 2mm.
In spiral heat exchanger described in the utility model, described ripple is herringbone ripple.So-called herringbone, all become exactly the angle of 15-75 degree with this center line, and the crest 1201 of both sides is symmetrical with center line along the crest 1201 of the center line both sides of thread plate length direction and trough 1202, and the trough 1202 of both sides is also symmetrical with center line.Preferably, the spacing of the crest 1201 of described ripple equates with the spacing of trough 1202.Runner between the plate of the spiral heat exchanger that employing herringbone corrugated plating is made, it is a runner that cross section is changeable, tortuous, in addition helical duct, make it easily form turbulent flow, end user's font line replaces spacing column, has effectively increased heat exchange area, uses chevron than using spacing column by theoretical with experimental results show that, in the situation that other condition is identical, the critical Reynolds number of fluid is much lower, and when the heat exchange of water-water, the heat transfer coefficient maximum of chevron spiral heat exchanger can reach 5000W/(m
2, and the heat transfer coefficient maximum of common spiral heat exchanger is generally no more than 3000W/(m K)
2k).
In spiral heat exchanger described in the utility model, the edge of described the first thread plate 120 and the second thread plate 130 is all higher than the height of ripple.The edge of thread plate is higher than the height of curl, the edge of thread plate can be carried out to flanging by mould rolling in process, make the edge laminating of edge portion after folding and adjacent thread plate, weld strip of paper used for sealing with one, saved welding material and operation.
Except good heat-transfer, load performance is good, save material, outside reducing costs, spiral heat exchanger described in the utility model also has the following advantages: radiation loss is little: hot fluid can be taken over the inside that directly enters herringbone line spiral heat exchanger by center, helical structure also makes heat exchanger less to the area of function of environment heat emission, and both sides helical duct end face easily adopts Insulation, makes herringbone line spiral heat exchanger distribute in the heat loss of environment little; Heat transfer temperature difference is little: in herringbone line spiral heat exchanger, cold and hot liquids is generally pressed counter-current operation, for same heat exchange area, the length of spiral plate can change by wide being adjusted in larger scope of plate, accurately manual control of the outlet temperature of cold fluid and hot fluid, the minimum of a value of the cold fluid and hot fluid temperature difference is only 1 ℃ of left and right, therefore can make full use of low-temperature heat source; Thermal (temperature difference) stress is little: because helical duct is an entirety, and the inner saltation zone that does not have temperature, the amount of expanding with heat and contract with cold of spiral plate is just evenly absorbed by spirochetal path clearance, and herringbone line also has certain absorption to the amount of expanding with heat and contract with cold; Compact conformation: the heat-transfer area of spiral heat exchanger unit volume is more much bigger than shell-and-tube heat exchanger, and herringbone line spiral heat exchanger is larger than the heat transfer area of common spiral heat exchanger unit volume.
It should be noted, above-described embodiment describes the utility model rather than the utility model is limited, and those skilled in the art can design alternative embodiment in the case of not departing from the scope of claims.In the claims, any reference symbol between bracket should be configured to limitations on claims.Word " comprises " not to be got rid of existence and is not listed as element or step in the claims.The use of word first, second and C grade does not represent any order, can be title by these word explanations.
Claims (6)
1. a spiral heat exchanger, comprise heat exchange body (100), it is characterized in that described heat exchange body (100) comprises central partition plate (110), the first thread plate (120) and the second thread plate (130), end of described the first thread plate (120) and a limit fixed seal connection of central partition plate (110), end of the second thread plate (130) and another limit fixed seal connection of central partition plate (110), the first thread plate (120) and the second thread plate (130) roll into cylindrical with the same center of circle of same direction; Wherein, described the first thread plate (120) and the second thread plate (130) all have all identical ripples of shape size, roll in process, the trough of the crest of inner ring thread plate and adjacent outer ring thread plate fits, and between the crest of the trough of inner ring thread plate and adjacent outer ring thread plate, forms fluid passage.
2. spiral heat exchanger according to claim 1, it is characterized in that: the top of described heat exchange body (100) and sidewall are respectively equipped with the first medium entrance (140) and the first medium outlet (150) that flow into and flow out for first medium, and, be respectively equipped with at bottom and the sidewall of described heat exchange body (100) the second medium entrance (160) and the second medium outlet (170) that flow into and flow out for second medium.
3. spiral heat exchanger according to claim 1, is characterized in that: described ripple is herringbone ripple.
4. spiral heat exchanger according to claim 3, is characterized in that: the corrugation pitch of described ripple equates with trough spacing.
5. spiral heat exchanger according to claim 1, is characterized in that: the edge of described the first thread plate (120) and Second Wave card (130) is all higher than the height of ripple.
6. according to the spiral heat exchanger described in any one in claim 1-5, it is characterized in that: the thickness of described the first thread plate (120) and the second thread plate (130) is 2mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320655890.0U CN203629388U (en) | 2013-10-23 | 2013-10-23 | Spiral-plate heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320655890.0U CN203629388U (en) | 2013-10-23 | 2013-10-23 | Spiral-plate heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203629388U true CN203629388U (en) | 2014-06-04 |
Family
ID=50815854
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320655890.0U Expired - Fee Related CN203629388U (en) | 2013-10-23 | 2013-10-23 | Spiral-plate heat exchanger |
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| Country | Link |
|---|---|
| CN (1) | CN203629388U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111076576A (en) * | 2019-12-27 | 2020-04-28 | 中国航空工业集团公司沈阳飞机设计研究所 | Spiral plate type heat exchanger |
-
2013
- 2013-10-23 CN CN201320655890.0U patent/CN203629388U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111076576A (en) * | 2019-12-27 | 2020-04-28 | 中国航空工业集团公司沈阳飞机设计研究所 | Spiral plate type heat exchanger |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140604 Termination date: 20151023 |
|
| EXPY | Termination of patent right or utility model |