CN102213507A - Plate type heat exchanger and air conditioner equipped therewith - Google Patents
Plate type heat exchanger and air conditioner equipped therewith Download PDFInfo
- Publication number
- CN102213507A CN102213507A CN2011100839855A CN201110083985A CN102213507A CN 102213507 A CN102213507 A CN 102213507A CN 2011100839855 A CN2011100839855 A CN 2011100839855A CN 201110083985 A CN201110083985 A CN 201110083985A CN 102213507 A CN102213507 A CN 102213507A
- Authority
- CN
- China
- Prior art keywords
- heat
- plate type
- working fluid
- exchangers
- inflow pipe
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims abstract description 27
- 239000003507 refrigerant Substances 0.000 claims description 8
- 230000004941 influx Effects 0.000 abstract 2
- 238000007599 discharging Methods 0.000 abstract 1
- 238000005057 refrigeration Methods 0.000 description 6
- 239000007788 liquid Substances 0.000 description 5
- 238000002474 experimental method Methods 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 239000012467 final product Substances 0.000 description 2
- 239000013529 heat transfer fluid Substances 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000010606 normalization Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 239000012047 saturated solution Substances 0.000 description 1
- 239000011550 stock solution Substances 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
-
- 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
- F28D21/0001—Recuperative heat exchangers
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention relates to a plate type heat exchanger of an air conditioner, which comprises a plurality of heat transfer plates, an influx pipe for the flowing of the working fluid and a discharge pipe for discharging the working fluid. The depth of the plate type heat exchanger is set to be H (mm) and the inner diameter of the influx pipe for the flowing of the working fluid is set to be D (mm). The density of the working fluid is set to be rho (kg / m3). An effective allocation exponent (K) is defined to be K=rho / 1n (D*H). The effective allocation exponent (K) is greater than 0.1 and less than 1.2.
Description
Technical field
The present invention relates to air regulator, in more detail, relate to the heat-exchangers of the plate type that to finish the heat transfer of cold-producing medium by overlapping a plurality of heat transfer plates.
Background technology
Recently, can realize kind of refrigeration cycle and heat pump cycle, and optionally finish indoor refrigeration and the changes in temperature that heat increase with the popularity of air regulator (so-called heat pump) with a device.Usually, heat pump comprises indoor set, the compressor with heat exchanger, the off-premises station with heat exchanger and expander.
Changes in temperature with air regulator as follows with refrigeration mode using time reason: as evaporimeter, make the cold-producing medium of the liquid condition of the low temperature that passed through, low pressure evaporate heat in the absorption chamber indoor heat converter, freeze to indoor thus.Refrigerant gas by the middle temperature behind the evaporimeter, low pressure passes through compressor once more, becomes the refrigerant gas of high temperature, high pressure thus.With respect to this, changes in temperature are as follows with air regulator mechanism under heating mode: indoor heat converter is used as condenser, the cold-producing medium of the gaseous state of high temperature, high pressure is on one side by above-mentioned condenser, heat be released to indoor on one side, heat indoor thus.That is, off-premises station used as condenser in summer, and used as evaporimeter in the winter time.
Changes in temperature with said structure are with the heat exchanger that uses as evaporimeter when the refrigeration in the air regulator, use shell (shell and tube) formula heat exchanger and heat-exchangers of the plate type, wherein recently superior and shared little small-sized heat-exchangerss of the plate type in space that are provided with of heat-transfer character that use more.Heat-exchangers of the plate type forms by overlapping a plurality of heat transfer plates, and cold-producing medium flows in the one side of heat transfer plate, and heat-transfer fluid flows at another side, conducts heat each other thus.
Yet there are the following problems for heat-exchangers of the plate type in the past,, the cold-producing medium that is flowed into can not be assigned to each heat transfer plate equably that is, produces the deviation of cold-producing medium, causes losing the available heat exchange area thus.
Summary of the invention
The present invention makes in order to address the above problem, and its purpose is, provide a kind of by distributing the working fluid that is flowed into equably the air regulator that can make the heat-exchangers of the plate type of maximizes heat exchange efficiency and comprise this heat-exchangers of the plate type.
In order to reach above-mentioned purpose, the invention provides a kind of heat-exchangers of the plate type, this heat-exchangers of the plate type has a plurality of heat transfer plates, and comprise and be used for inflow pipe that working fluid flows into and the discharge pipe that is used to discharge working fluid, be made as H (mm), the internal diameter of the inflow pipe of described working fluid is made as D (mm), the density of described working fluid is made as ρ (kg/m in the degree of depth described heat-exchangers of the plate type
3), and during the following formula 1 effective distribution index of definition (K),
[formula 1]
K＝ρ/ln(D·H)
The value of described effective distribution index (K) is greater than 0.1 and less than 1.2.
In addition, above-mentioned inflow pipe can have and directly is connected the straight sections on the above-mentioned heat-exchangers of the plate type and is connected bend on the above-mentioned straight sections.
In addition, the angle of above-mentioned bend (θ) is that 20 °＜θ＜90 ° get final product.Here, be made as V (m/s), the length of the straight sections of above-mentioned inflow pipe is made as L (m), the internal diameter of the inflow pipe of above-mentioned working fluid is made as D (m), the kinematic coefficient of viscosity of above-mentioned working fluid is made as λ (m in speed the working fluid in the above-mentioned inflow pipe
2/ s), and during following formula 2 definition dimensionless numbers (T),
[formula 2]
T＝4.5·e
-9·sinθ·V·D
2/(L·λ)
The value of above-mentioned dimensionless number can be less than 0.15.
In addition, the angle of above-mentioned bend (θ) is that 90 °＜θ＜150 ° get final product.Here, be made as V (m/s), the length of the straight sections of above-mentioned inflow pipe is made as L (m), the internal diameter of the inflow pipe of above-mentioned working fluid is made as D (m), the kinematic coefficient of viscosity of above-mentioned working fluid is made as λ (m in speed the working fluid in the above-mentioned inflow pipe
2/ s), and following formula 3 definition dimensionless numbers (dimensionless number) are (T) time,
[formula 3]
T＝4.5e
-9(1+1/sinθ)·V·D
2/(L·λ)
The value of above-mentioned dimensionless number can be less than 0.15.
In addition, the invention provides a kind of air regulator, this air regulator comprises the heat-exchangers of the plate type of each record in the technical scheme 1 to 3, and above-mentioned working fluid is a cold-producing medium, liquid refrigerant flows into after the above-mentioned inflow pipe, discharges gas refrigerant from above-mentioned discharge pipe.
In the heat-exchangers of the plate type of embodiments of the present invention with said structure, can improve the efficient of heat exchanger by the flow distribution of appropriate cold-producing medium, and along with the raising of the efficient of heat exchanger, what reduce that the high-pressure section of the circulatory system and low voltage section divide is poor, can save operating cost thus.
In addition, in the heat-exchangers of the plate type of embodiments of the present invention, utilize the uniform flow distribution of cold-producing medium to be reduced in the pressure loss in the heat-exchangers of the plate type, and alleviate the load of compressor, can save operating cost thus.
In addition, in the heat-exchangers of the plate type of embodiments of the present invention, reduce the low pressure loss that causes by the normalization that flows, can prevent the icing phenomenon of the entrance side of heat-exchangers of the plate type thus.
Description of drawings
Fig. 1 is the figure that is shown schematically in the air regulator of embodiments of the present invention.
Fig. 2 is the figure that is shown schematically at the heat-exchangers of the plate type shown in Fig. 1.
Fig. 3 shows the average figure based on the temperature deviation of effective distribution index of the heat-exchangers of the plate type of embodiments of the present invention.
Fig. 4 is the figure that is shown schematically in the heat-exchangers of the plate type of other embodiments of the present invention.
Fig. 5 shows the average figure based on the temperature deviation of the dimensionless number of the heat-exchangers of the plate type of other embodiments of the present invention.
The specific embodiment
Below, the air regulator that comprises compressor of present invention will be described in detail with reference to the accompanying embodiment.
Fig. 1 is the figure that is shown schematically in the air regulator of embodiments of the present invention, Fig. 2 is shown schematically in the figure at the heat-exchangers of the plate type shown in Fig. 1, and Fig. 3 shows the average figure based on the temperature deviation of effective distribution index of the heat-exchangers of the plate type of embodiments of the present invention.
With reference to figure 1, the air regulator of an embodiment of the invention (heat pump) 300 comprises off-premises station 100 and indoor set 200; Off-premises station 100 comprises heat exchanger 10, is used to promote the compressor 30 of the heat exchange fan 20 of heat exchange between cold-producing medium and the extraneous air, compressed refrigerant, expander 40.Connect heat exchanger 10, compressor 30 and expander 40 by the conduit 50 that is used for flow of refrigerant.Arrow among Fig. 1 is represented the direct of travel of cold-producing medium, and the direct of travel of cold-producing medium when heating is shown in the present embodiment.
Front end at compressor 30 is provided with gas-liquid separator 60, and in the rear end of compressor 30 oil eliminator 70 is set.Gas-liquid separator 60 prevents liquid refrigerant to compressor 30 intrusions, and oil eliminator 70 is separating oil from the cold-producing medium that compressor 30 is sprayed.Oil eliminator 70 is provided with oily recovery tube 52, and the oil that can flow into compressor 30 is delivered to the front end of compressor 30.
Can be when in addition, indoor set 200 comprises refrigeration as the heat-exchangers of the plate type 90 of evaporimeter use.
With reference to figure 2, heat-exchangers of the plate type 90 forms by overlapping a plurality of heat transfer plates 91, is connected with the inflow pipe 92 of cold-producing medium in the bottom, is connected with the discharge pipe 93 of cold-producing medium on top.On the one side of such heat transfer plate 91, be formed with concavo-convex (the herringbone pattern: herringbone pattern) of predetermined pattern.Cold-producing medium flows in the one side of heat transfer plate 91, can flow at another side with the heat-transfer fluid that cold-producing medium conducts heat.
In the heat-exchangers of the plate type 90 of said structure, it is particularly important to flow into each heat transfer plate that the cold-producing medium of heat-exchangers of the plate type 90 is assigned in a plurality of heat transfer plates 91 equably by inflow pipe 92.The applicant finds that the index of the redetermination that the distribution of the cold-producing medium of such heat-exchangers of the plate type 90 and effective distribution index (K) are such is relevant.
Be made as H (mm), the internal diameter of the inflow pipe 92 of above-mentioned cold-producing medium is made as D (m), the density of above-mentioned cold-producing medium is made as ρ (kg/m in the degree of depth above-mentioned heat-exchangers of the plate type 90
3) time, effectively distribution index (K) is defined as following formula 1.
[formula 1]
K＝ρ/ln(D·H)
Here, as an example, the density of cold-producing medium is meant the density of 5 ℃ of saturated solutions.
The applicant tests in order to confirm the relevance that above-mentioned effective distribution index (K) and cold-producing medium distribute.As shown in Figure 2, the applicant on 93 direction from inflow pipe 92 to discharge pipe 3D and the each point (stain Fig. 2) of the position of 5D be provided with the thermocouple (thermocouple) that can measure temperature respectively, and the kind, the degree of depth (H) of heat-exchangers of the plate type 90 and the internal diameter (D) of inflow pipe 92 that change cold-producing medium have carried out the parameter experiment.That is, measured the mean value of the temperature standard deviation of effective distribution index (K) and 2 row thermocouples.Here, the mean value of temperature standard deviation is after the standard deviation of obtaining the thermocouple (for example 6) that is arranged on each row respectively, and the mean value of obtaining the standard deviation of each row (being 2 row in the present embodiment) draws.
Here, set the reasons are as follows of position of thermocouple as described above, promptly, if thermocouple too is configured in downside, the temperature difference can not appear because of the inlet near cold-producing medium then, on the contrary, if thermocouple too is configured in upside, then because of excessively carrying out the temperature difference can not occurring equally with the heat exchange of secondary side thermal medium.
According to above-mentioned result of experiment, can draw the curve map of illustrating as shown in Figure 3 based on the mean value of the temperature deviation of effective distribution index (K).As shown in Figure 3, can confirm: the value of effective distribution index (K) greater than 0.1 and less than 1.2 situation under, the mean value minimum of temperature deviation, and in scope in addition, the mean value of temperature deviation increases sharply.The mean value of temperature deviation means that for a short time the loss of available heat exchange area is little, carries out the distribution of cold-producing medium equably.
Fig. 4 is the figure that is shown schematically in the heat-exchangers of the plate type of other embodiments of the present invention, and Fig. 5 shows the average figure based on the temperature deviation of the dimensionless number of the heat-exchangers of the plate type of other embodiments of the present invention.
As shown in Figure 4, the inflow pipe 97 of cold-producing medium can have: straight sections 95, and it directly is connected on the heat-exchangers of the plate type 90; Bend 96, it is connected the front end of this straight sections 95, and forms with respect to angle (θ) bending of straight sections 95 with defined.
The applicant finds, utilizes the next distribution that influences cold-producing medium as the dimensionless number of giving a definition (T) of angle (θ) of above-mentioned bend.
The speed of the cold-producing medium in will exporting the required above-mentioned inflow pipe 97 of rated power is made as V (m/s), the length of the straight sections 95 of above-mentioned inflow pipe 97 is made as L (m), the internal diameter of the inflow pipe 97 of above-mentioned cold-producing medium is made as D (m), the kinematic coefficient of viscosity of above-mentioned cold-producing medium is made as λ (m
2/ s) time, dimensionless number (T) is defined as following formula 2 and formula 3.
[formula 2]
T＝4.5·e
-9·sinθ·V·D
2/(L·λ)
(20°＜θ＜90°)
[formula 3]
T＝4.5e
-9(1+1/sinθ)·V·D
2/(L·λ)
(90°＜θ＜150°)
Here, to be 5 ℃ with the cold-producing medium evaporating temperature be benchmark to the kinematic coefficient of viscosity (λ) of setting the speed (V) of cold-producing medium and cold-producing medium.
The applicant utilizes and the above-mentioned same method of experimental technique, determines mean value based on the temperature deviation of the thermocouple of dimensionless number (T) while change each parameter.Its result can draw the curve map based on the mean value of the temperature deviation of dimensionless number (T) of illustrating as shown in Figure 5.As shown in Figure 5, can confirm: the value of dimensionless number (T) less than 0.15 situation under, the mean value minimum of temperature deviation, and the mean value of temperature deviation increases sharply in scope in addition.The mean value of temperature deviation means that for a short time the loss of available heat exchange area is little, carries out the distribution of cold-producing medium equably.
More than illustrated the embodiment of plate heat exchanger applications, but the present invention is not limited to this, can be applied to use all industry devices of heat-exchangers of the plate type in air regulator.
So far illustrated preferred embodiment of the present inventionly, but the present invention is not limited to this, can implement various distortion in the scope of claim, specification and accompanying drawing, and this also belongs to scope of the present invention certainly.
Claims (4)
1. a heat-exchangers of the plate type has a plurality of heat transfer plates, and comprises inflow pipe that is used for the working fluid inflow and the discharge pipe that is used to discharge working fluid, it is characterized in that,
Be made as H (mm), the internal diameter of the inflow pipe of described working fluid is made as D (mm), the density of described working fluid is made as ρ (kg/m in the degree of depth described heat-exchangers of the plate type
3) time, as the effective distribution index (K) of giving a definition, promptly
K＝ρ/ln(D·H)
The value of described effective distribution index (K) is greater than 0.1 and less than 1.2.
2. heat-exchangers of the plate type as claimed in claim 1 is characterized in that:
Described inflow pipe has and directly is connected the straight sections on the described heat-exchangers of the plate type and is connected bend on the described straight sections,
The angle of described bend (θ) is 20 °＜θ＜90 °,
Be made as V (m/s), the length of the straight sections of described inflow pipe is made as L (m), the internal diameter of the inflow pipe of described working fluid is made as D (m), the kinematic coefficient of viscosity of described working fluid is made as λ (m in speed the working fluid in the described inflow pipe
2/ s) time, as the dimensionless number of giving a definition (T), promptly
T＝4.5·e
-9·sinθ·V·D
2/(L·λ)
The value of described dimensionless number is less than 0.15.
3. heat-exchangers of the plate type as claimed in claim 1 is characterized in that:
Described inflow pipe has and directly is connected the straight sections on the described heat-exchangers of the plate type and is connected bend on the described straight sections,
The angle of described bend (θ) is 90 °＜θ＜150 °,
Be made as V (m/s), the length of the straight sections of described inflow pipe is made as L (m), the internal diameter of the inflow pipe of described working fluid is made as D (m), the kinematic coefficient of viscosity of described working fluid is made as λ (m in speed the working fluid in the described inflow pipe
2/ s) time, as the dimensionless number of giving a definition (T), promptly
T＝4.5·e
-9(1+1/sinθ)·V·D
2/(L·λ)
The value of described dimensionless number is less than 0.15.
4. an air regulator is characterized in that,
Described air regulator comprises the heat-exchangers of the plate type of each record in the claim 1 to 3;
Described working fluid is a cold-producing medium, after described inflow pipe influent cold-producing medium, discharges gas refrigerant from described discharge pipe.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020100030750A KR101155811B1 (en) | 2010-04-05 | 2010-04-05 | Plate heat exchanger and air conditioner including the same |
| KR10-2010-0030750 | 2010-04-05 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102213507A true CN102213507A (en) | 2011-10-12 |
| CN102213507B CN102213507B (en) | 2013-11-20 |
Family
ID=44744917
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011100839855A Expired - Fee Related CN102213507B (en) | 2010-04-05 | 2011-03-30 | Plate type heat exchanger and air conditioner equipped therewith |
Country Status (2)
| Country | Link |
|---|---|
| KR (1) | KR101155811B1 (en) |
| CN (1) | CN102213507B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102775311B1 (en) * | 2022-12-26 | 2025-02-28 | 조선대학교산학협력단 | Performance prediction method of plate heat exchanger |
| KR102722107B1 (en) * | 2023-08-14 | 2024-10-28 | 부산대학교 산학협력단 | Methdod, apparatus and computer program for analyzing convective heat transfer in heat exchangers |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0415492A (en) * | 1990-05-10 | 1992-01-20 | Mitsubishi Electric Corp | Air conditioning heat exchanger |
| CN1297524A (en) * | 1998-03-11 | 2001-05-30 | Swep国际股份公司 | Three circuit plate head exchanger |
| CN101069058A (en) * | 2004-08-28 | 2007-11-07 | Swep国际股份公司 | A plate heat exchanger |
| JP2009174833A (en) * | 2008-01-28 | 2009-08-06 | Hitachi Cable Ltd | Heat exchanger tube for heat exchanger and heat exchanger using the same |
| CN201413074Y (en) * | 2009-06-25 | 2010-02-24 | 大连九圆热交换设备制造有限公司 | Plate type heat exchanger plate with novel seal groove structure |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR0128678B1 (en) * | 1994-07-21 | 1998-04-04 | 김광호 | Air-condition machinery of heat exchanger |
-
2010
- 2010-04-05 KR KR1020100030750A patent/KR101155811B1/en not_active Expired - Fee Related
-
2011
- 2011-03-30 CN CN2011100839855A patent/CN102213507B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0415492A (en) * | 1990-05-10 | 1992-01-20 | Mitsubishi Electric Corp | Air conditioning heat exchanger |
| CN1297524A (en) * | 1998-03-11 | 2001-05-30 | Swep国际股份公司 | Three circuit plate head exchanger |
| CN101069058A (en) * | 2004-08-28 | 2007-11-07 | Swep国际股份公司 | A plate heat exchanger |
| JP2009174833A (en) * | 2008-01-28 | 2009-08-06 | Hitachi Cable Ltd | Heat exchanger tube for heat exchanger and heat exchanger using the same |
| CN201413074Y (en) * | 2009-06-25 | 2010-02-24 | 大连九圆热交换设备制造有限公司 | Plate type heat exchanger plate with novel seal groove structure |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20110111601A (en) | 2011-10-12 |
| KR101155811B1 (en) | 2012-06-12 |
| CN102213507B (en) | 2013-11-20 |
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