CN203881187U - Thin type non-equivalence flow air-to-air heat exchanger - Google Patents
Thin type non-equivalence flow air-to-air heat exchanger Download PDFInfo
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- CN203881187U CN203881187U CN201420277924.1U CN201420277924U CN203881187U CN 203881187 U CN203881187 U CN 203881187U CN 201420277924 U CN201420277924 U CN 201420277924U CN 203881187 U CN203881187 U CN 203881187U
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Abstract
The utility model discloses a thin type non-equivalence flow air-to-air heat exchanger. The thickness of a heat exchange core in the Z direction is set to be 0.5 to 1 time that of the heat exchanger core in the Y direction, the thickness of the heat exchange core in the Z direction is 80-200 mm, and the height of the heat exchange core in the Y direction is 400-800 mm. The distance of plate sheets of a primary air channel is set to be 0.5-2 times that of plate sheets of a secondary air channel. The distance of the plate sheets of the primary air channel is 2-4 mm, and the distance of the plate sheets of the secondary air channel is 6-10 mm. According to the thin type non-equivalence flow air-to-air heat exchanger, the thickness of the heat exchange core is reduced, the high heat exchange efficiency can be ensured, the shape and size design of the heat exchange core can be more flexible, the size of the heat exchange core is smaller, the thin type non-equivalence flow air-to-air heat exchanger can be placed in narrow space more conveniently, the application range is wider, the heat exchange efficiency is slightly reduced, the unexpected heat exchange effect is achieved, and the thin type non-equivalence flow air-to-air heat exchanger can conform to the development trend of the thin appearance design of current products.
Description
Technical field
The utility model belongs to heat exchange field, relates in particular to the board-like gas-gas heat exchange core of a kind of cross-current, and especially a kind of thickness height is little a lot, is applicable to the slim not reciprocity flow air-air heat exchanger of narrow space.
Background technology
Gas-gas heat exchange core is the core component for thermal energy exchange in ventilating system, the board-like gas-gas heat exchange core of a kind of cross-current, stacked a series of plate is set, between plate, form runner, adjacent channels is right-angled intersection turnover and forms an orthogonal air channel and secondary air duct, and cold airflow, thermal current carry out heat exchange by plate respectively in the time that two runners flow through.
In decades, the board-like gas-gas heat exchange core of existing cross-current is generally that thickness is the cube structure of 1:1:1 with height, width substantially, and the flow process in an air channel and the flow process of secondary air duct equate.The board-like gas-gas heat exchange core of cross-current of the flowage structure such as this, simple in structure, therefore air channel and secondary air duct adopt the spacing of identical plate conventionally, can ensure the heat exchange efficiency up to 50% left and right than being easier to, for a long time, it is believed that this kind of structure is the most rational, it is right and proper optimum structure, due to this cube structure, relevant machinery equipment structural design is subject to this limitation and easily makes volume become large, and never someone attempts breaking this traditional structure.
To cube structure there is the shortcoming that volume is large, take up space in it, especially exists the shortcoming people that cannot be placed in narrow space to hold the attitude of tolerance.
There is a saying to set up: if the thickness of the board-like gas-gas heat exchange core of cross-current is reduced, though can reduce the volume of heat exchange core, but because the flow process of two runners of slim heat exchange core after reduction thickness there are differences, the heat exchange efficiency of slim heat exchange core can decline to a great extent with the reduction of thickness, cause heat transfer effect extreme difference, cannot market application.
But, slim appearance design, except being the use in order to adapt to usage space, also the same with current many products, the trend that product design is pursued just, such as slim TV, thin type cell phone, slim notebook computer etc., be all seek assiduously of excellent design teachers, be also consumers in general's the expectation of raising one's head and looking.Certainly one centimetre, one millimeter of the every attenuation of the said goods, has designer to pay how many outstanding work, supports with the birth of how many new material new constructions simultaneously.
Today, in the actual use so for many years of the board-like gas-gas heat exchange core product of existing cross-current, the figure of rarely seen slim product, let alone extensive use.Trace it to its cause, exactly because after thickness direction is significantly reduced, can not meet the requirement that heat exchange efficiency only slightly declines, especially be thinned to after the degree of height 1/3rd at thickness direction, it is all quite difficult continuing one centimetre of every minimizing again, needs people to pay great effort.
A kind of board-like gas-gas heat exchange core of slim cross-current that still can ensure higher heat exchange efficiency thus, will be because of its spatial adaptation power and product appearance development pursuit flexibly, become the board-like gas-gas heat exchange core of the cross-current trend in future, this also just people want for a long time to reach and fail realize target.
Conventional a kind of length as shown in Figure 1 of prior art, highly, thickness is the board-like gas-gas heat exchange core of square cross-current of 560 millimeters, the spacing of the spacing of the plate in its air channel and the plate of secondary air duct is 5 millimeters, when the volume flow of air channel and secondary air duct is 500 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, one time ducting outlet temperature is down to 31.2 DEG C, utilize experimental data, heat exchange efficiency by calculating air-flow in a known air channel is up to 56.3%, when the volume flow of air channel and secondary air duct is 625 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, one time ducting outlet temperature is down to 31.2 DEG C, utilize experimental data, the heat exchange efficiency by calculating air-flow in a known air channel is up to 56.4%, when the volume flow in an air channel be 625 cubic metres per hour, the volume flow of secondary air duct is 500 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, one time ducting outlet temperature is down to 32 DEG C, utilizes experimental data, and the heat exchange efficiency by calculating air-flow in a known air channel is up to 50%.
Utility model content
The technical problems to be solved in the utility model is to overcome the mistaken ideas of people's traditional concept and a kind of slim not reciprocity flow air-air heat exchanger is provided, the utility model is in 0.5 to 0.1 scope of height by the reduced down in thickness of original cube structure, its heat exchange efficiency still can remain on 45% to 50%, has only declined several percentage points.
The utility model is by adopting following technical scheme to realize:
Manufacture and design a kind of slim not reciprocity flow air-air heat exchanger, comprise some plates of stacked setting, between described plate, form some air channels, adjacent channels is right-angled intersection turnover and forms an orthogonal air channel and secondary air duct, a described air channel carries over heat exchange core thickness Z direction, described secondary air duct carries over heat exchange core height Y-direction, especially:
The Z direction thickness of heat exchange core is in the scope of 0.5 to 0.1 times of Y-direction height; The spacing of the plate in an air channel is 0.5 to 0.2 times of spacing of the plate of secondary air duct.
The spacing of the plate in a described air channel is 2～4mm;
The spacing of the plate of described secondary air duct is 6～10mm;
The Z direction thickness of described heat exchange core is 80～200mm;
The Y-direction height of described heat exchange core is 400～800mm.
On an air channel face in an air channel, along Y direction and Z-direction, small embossment is set, Z-direction, for row, Y direction is row, arranges a large projection to secondary air duct face direction projection between two small embossments of every row and every row.
Secondary air duct face surface is reductus shape, along Y direction, ripple is set, described waviness width 1.2～3.2mm, height 0.4～0.8mm.
Small embossment is row in Z-direction, is row in Y direction; Be listed as and the 40～60mm that is spaced apart being listed as row and the 40～60mm that is spaced apart going.
1/2 of the spacing of the plate that the height of large projection is secondary air duct; The height of small embossment be the plate in an air channel spacing 1/2.
These reductus shapes can, in the time that air-flow passes through runner, play the effect of rough air, make cold air, hot gas in hot and cold air-flow all can arrive plate surface and carry out sufficient heat exchange by plate, further ensure higher heat exchange efficiency.
The utility model can ensure higher heat exchange efficiency in reduction heat exchange core thickness, can make the geomery design of heat exchange core more flexible, the volume of heat exchange core is less, be more convenient for being placed in narrow space, the scope of application is more extensive, and only slightly decline of heat exchange efficiency, obtain beyond thought heat transfer effect, make the utility model meet the development trend of the slim appearance design of current product.
Brief description of the drawings
Fig. 1 is the schematic diagram of prior art cube structure heat exchange core 100;
Fig. 2 is air channel 1 of air-air heat exchanger and the schematic diagram of secondary air duct 2;
Fig. 3 is the schematic diagram of the heat exchange core 200 of the slim not reciprocity flow air-air heat exchanger of the utility model;
Fig. 4 is the schematic diagram of an air channel plate surface structure of the slim not reciprocity flow air-air heat exchanger of the utility model;
Fig. 5 is the schematic diagram of the secondary air duct plate surface structure of the slim not reciprocity flow air-air heat exchanger of the utility model;
Fig. 6 is the schematic diagram that the surperficial large projection 121 of the plate 10 in the slim not reciprocity flow air-air heat exchanger of the utility model and small embossment 111 arrange;
Fig. 7 is that large projection in the slim not reciprocity flow air-air heat exchanger of the utility model and ripple struction launch 15 schematic diagram;
Fig. 8 is that the small embossment structure in the slim not reciprocity flow air-air heat exchanger of the utility model is launched 16 schematic diagram.
Detailed description of the invention
Below in conjunction with accompanying drawing, the utility model is described in further detail:
With reference to Fig. 1～Fig. 8, the schematic diagram of the cube heat exchange core 100 that Fig. 1 is prior art, as seen from the figure, the size of X, Y, tri-directions of Z is substantially equal, is a having the shape of a real square device, can take unavoidably the volumetric spaces in equipment.
Manufacture and design slim not reciprocity flow air-air heat exchanger, comprise some plates of stacked setting, between described plate, form some air channels, adjacent channels is right-angled intersection turnover and forms an orthogonal air channel 1 and secondary air duct 2, a described air channel 1 carries over heat exchange core thickness Z direction, described secondary air duct 2 carries over heat exchange core height Y-direction, especially:
The Z direction thickness of heat exchange core 200 is in the scope of 0.5 to 0.1 times of Y-direction height; The spacing of the plate in an air channel 1 is 0.5 to 0.2 times of spacing of the plate of secondary air duct 2.The spacing of the plate in a described air channel 1 is 2～4mm;
The spacing of the plate of described secondary air duct 2 is 6～10mm;
The Z direction thickness of described heat exchange core 200 is 80～200mm;
The Y-direction height of described heat exchange core 200 is 400～800mm.
On an air channel face 11 in an air channel 1, along Y direction and Z-direction, small embossment 111 is set, Z-direction, for row, Y direction is row, arranges one to large protruding 121 of secondary air duct face 12 direction projections between two small embossments 111 of every row and every row.
Plate surface is reductus shape, along Y direction, ripple 123 is set, described ripple 123 width 1.2～3.2mm, height 0.4～0.8mm.
Small embossment 111 is row in Z-direction, is row in Y direction; Be listed as and the 40～60mm that is spaced apart being listed as row and the 40～60mm that is spaced apart going.
1/2 of the spacing that large protruding 121 height is the plate of secondary air duct 2; The height of small embossment 111 be the plate in an air channel 1 spacing 1/2.
In Fig. 7,1/2 of the spacing that large protruding 121 large height of projection 122 is the plate of secondary air duct 2.
In Fig. 8, the small embossment height 112 of small embossment 111 be the plate in an air channel 1 spacing 1/2.
Several specific embodiments are provided below
Embodiment 1:
Referring to Fig. 3～Fig. 8, slim not reciprocity flow air-air heat exchanger, comprise some plates of stacked setting, between plate, form some air channels, adjacent air channel is right-angled intersection turnover and forms an orthogonal air channel and secondary air duct, one time air channel carries over heat exchange core thickness direction, and secondary air duct carries over heat exchange core short transverse.
This slim not reciprocity flow air-air heat exchanger, length is 560 millimeters, is highly 500 millimeters, and thickness is 200 millimeters, and thickness is 0.4 of height; The spacing of the plate in an air channel is 2 millimeters, and the spacing of the plate of secondary air duct is 8 millimeters, 0.25 of the spacing of the plate that spacing of the plate in an air channel is secondary air duct.
According to the General Requirements of ventilation under normal service condition, when the volume flow of air channel and secondary air duct is 500 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, one time ducting outlet temperature is down to 31.7 DEG C, heat exchange efficiency concept according to air-flow actual heat variation in an air channel in the unit interval with maximum possible thermal change ratio, utilize experimental data, the heat exchange efficiency by calculating air-flow in a known air channel is up to 52.9%.
When the volume flow of air channel and secondary air duct is 625 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, one time ducting outlet temperature is down to 31.8 DEG C, utilize experimental data, the heat exchange efficiency by calculating air-flow in a known air channel is up to 52.1%.
When the volume flow in an air channel is 625 cubic metres time per hour, the volume flow of secondary air duct is 500 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, one time ducting outlet temperature is down to 32.4 DEG C, utilizes experimental data, and the heat exchange efficiency by calculating air-flow in a known air channel is up to 46.6%.
Embodiment 2:
With the difference of embodiment 1 be: this slim not reciprocity flow air-air heat exchanger, length is 560 millimeters, is highly 500 millimeters, and thickness is 150 millimeters, and thickness is 0.3 of height; The spacing of the plate in an air channel is 2 millimeters, and the spacing of the plate of secondary air duct is 5 millimeters, 0.4 of the spacing of the plate that spacing of the plate in an air channel is secondary air duct.
According to the General Requirements of ventilation under normal service condition, when the volume flow of air channel and secondary air duct is 500 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, first flow outlet temperature is down to 31.6 DEG C, utilizes experimental data, and the heat exchange efficiency by calculating air-flow in a known air channel is up to 53.6%.
When the volume flow of air channel and secondary air duct is 625 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, one time ducting outlet temperature is down to 31.7 DEG C, utilize experimental data, the heat exchange efficiency by calculating air-flow in a known air channel is up to 52.8%.
When the volume flow in an air channel be 625 cubic metres per hour, the volume flow of secondary air duct is 500 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, one time ducting outlet temperature is down to 32.3 DEG C, utilizes experimental data, and the heat exchange efficiency by calculating air-flow in a known air channel is up to 47.4%.
Embodiment 3:
With the difference of embodiment 1,2 be: this slim not reciprocity flow air-air heat exchanger, length is 560 millimeters, is highly 500 millimeters, and thickness is 100 millimeters, and thickness is 0.2 of height; The spacing of the plate in an air channel is 2 millimeters, and the spacing of the plate of secondary air duct is 4 millimeters, 0.5 of the spacing of the plate that spacing of the plate in an air channel is secondary air duct.
According to the General Requirements of ventilation under normal service condition, when the volume flow of first flow and the second runner is 500 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, one time ducting outlet temperature is down to 31.9 DEG C, utilizes experimental data, and the heat exchange efficiency by calculating air-flow in a known air channel is up to 51.1%.
When the volume flow of air channel and secondary air duct is 625 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, one time ducting outlet temperature is down to 32 DEG C, utilize experimental data, the heat exchange efficiency by calculating air-flow in a known air channel is up to 50.1%.
When the volume flow in an air channel be 625 cubic metres per hour, the volume flow of secondary air duct is 500 cubic metres time per hour, if initial airflow temperature is 38 DEG C in an air channel, in secondary air duct, initial airflow temperature is 26 DEG C, when diabatic process arrives after stable state, one time ducting outlet temperature is down to 32.6 DEG C, utilizes experimental data, and the heat exchange efficiency by calculating air-flow in a known air channel is up to 45.3%.
Slim not reciprocity flow air-air heat exchanger in embodiment 1,2,3, thickness significantly reduces, volume obviously reduces, heat exchange efficiency in the environment for use of three kinds of different volumes flows still can remain on 45%～53%, compare respectively knownly with the heat exchange efficiency of the board-like gas-gas heat exchange core 50%～56% of existing conventional cube cross-current, the heat exchange efficiency fall of the device of slim not reciprocity flow air-air of the present utility model heat exchange only has several percentage points.
Concrete data are relatively referring to following table:
As can be seen here, the utility model adopts the method for not reciprocity flow air-air heat exchange, obtain beyond thought heat transfer effect, made the utility model meet the development trend of the slim appearance design of current product, made heat exchange core device become slim imagination and be able to successfully.
Claims (6)
1. slim not reciprocity flow air-air heat exchanger, comprise some plates of stacked setting, between described plate, form some air channels, adjacent channels is right-angled intersection turnover and forms an orthogonal air channel (1) and secondary air duct (2), a described air channel (1) carries over heat exchange core thickness Z direction, described secondary air duct (2) carries over heat exchange core height Y-direction, it is characterized in that:
The Z direction thickness of heat exchange core (200) is in the scope of 0.5 to 0.1 times of Y-direction height; The spacing of the plate in an air channel (1) is 0.5 to 0.2 times of spacing of the plate of secondary air duct (2).
2. slim not reciprocity flow air-air heat exchanger according to claim 1, is characterized in that:
The spacing of the plate in a described air channel (1) is 2～4mm;
The spacing of the plate of described secondary air duct (2) is 6～10mm;
The Z direction thickness of described heat exchange core (200) is 80～200mm;
The Y-direction height of described heat exchange core (200) is 400～800mm.
3. slim not reciprocity flow air-air heat exchanger according to claim 1, is characterized in that:
On an air channel face (11) in an air channel (1), along Y direction and Z-direction, small embossment (111) is set, Z-direction is row, Y direction, for row, arranges a large projection (121) to secondary air duct face (12) direction projection between two small embossments (111) of every row and every row.
4. slim not reciprocity flow air-air heat exchanger according to claim 1, is characterized in that:
Plate surface is reductus shape, along Y direction, ripple (123) is set, described ripple (123) width 1.2～3.2mm, height 0.4～0.8mm.
5. slim not reciprocity flow air-air heat exchanger according to claim 3, is characterized in that:
Small embossment (111) is row in Z-direction, is row in Y direction; Be listed as and the 40～60mm that is spaced apart being listed as row and the 40～60mm that is spaced apart going.
6. slim not reciprocity flow air-air heat exchanger according to claim 3, is characterized in that: the height of large projection (121) be the plate of secondary air duct (2) spacing 1/2; The height of small embossment (111) be the plate in an air channel (1) spacing 1/2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420277924.1U CN203881187U (en) | 2014-05-28 | 2014-05-28 | Thin type non-equivalence flow air-to-air heat exchanger |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201420277924.1U CN203881187U (en) | 2014-05-28 | 2014-05-28 | Thin type non-equivalence flow air-to-air heat exchanger |
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| Publication Number | Publication Date |
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| CN203881187U true CN203881187U (en) | 2014-10-15 |
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| CN201420277924.1U Expired - Lifetime CN203881187U (en) | 2014-05-28 | 2014-05-28 | Thin type non-equivalence flow air-to-air heat exchanger |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104019683A (en) * | 2014-05-28 | 2014-09-03 | 广东蒙特科瑞莱空气处理设备有限公司 | Thin type unequal flow air-to-air heat exchange method and device |
-
2014
- 2014-05-28 CN CN201420277924.1U patent/CN203881187U/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104019683A (en) * | 2014-05-28 | 2014-09-03 | 广东蒙特科瑞莱空气处理设备有限公司 | Thin type unequal flow air-to-air heat exchange method and device |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
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| CP01 | Change in the name or title of a patent holder |
Address after: Wanjiang 523000 Guangdong city in Dongguan Province on the way to a community of Fen River No. 81 Patentee after: GUANGDONG SYMPHONY KERUILAI AIR COOLERS Co.,Ltd. Address before: Wanjiang 523000 Guangdong city in Dongguan Province on the way to a community of Fen River No. 81 Patentee before: Munters Keruilai Air Treatment Equipment (Guangdong) Co.,Ltd. |
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| CX01 | Expiry of patent term |
Granted publication date: 20141015 |
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| CX01 | Expiry of patent term |