CN103075846A - Condenser for forcibly transferring heat by reboiling - Google Patents
Condenser for forcibly transferring heat by reboiling Download PDFInfo
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- CN103075846A CN103075846A CN2013100132260A CN201310013226A CN103075846A CN 103075846 A CN103075846 A CN 103075846A CN 2013100132260 A CN2013100132260 A CN 2013100132260A CN 201310013226 A CN201310013226 A CN 201310013226A CN 103075846 A CN103075846 A CN 103075846A
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- heat exchanger
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Abstract
The invention relates to a condenser for forcibly transferring heat by reboiling. The condenser is characterized by comprising a connecting pipe, a current divider, a heat exchanger, a first current dividing pipe and a second current dividing pipe, wherein one end of the connecting pipe is communicated with the air outlet of a compressor; one end of the current divider is communicated with the other end of the connecting pipe; one end of the first current dividing pipe and one end of the second current dividing pipe are communicated with the other end of the current divider respectively; the other end of the first current dividing pipe is communicated with the inlet of the heat exchanger; the other end of the second current dividing pipe is communicated with the heat exchanger; and the distance between a position where the second current dividing pipe is communicated with the heat exchanger and the inlet of the heat exchanger is 0.3-0.62 times of the total length. According to the condenser, heat exchange of a refrigerant is mostly performed in a gas-liquid two-phase region with a large heat exchange coefficient; and meanwhile, condensation heat exchange in the gas-liquid two-phase region is reinforced in a focused way, so that the heat exchange coefficient of the condenser is increased on the whole.
Description
Technical field
The present invention relates to a kind of condenser augmentation of heat transfer technology, especially a kind of condenser of more boiling enhanced heat transfer.
Background technology
Condenser is the vitals in the refrigeration system, improves the condenser heat transfer coefficient and has important function to improving performance of refrigerant systems, reduction refrigeration plant volume and cost.In middle-size and small-size refrigeration plant, logical cold-producing medium in the general pipe of condenser, pipe is outer to be cooling medium.
At present, the method for augmentation of heat transfer mainly is to design for condensation heat transfer in the refrigerant pipe in the condenser tube, and the method for employing is mainly extended surface method and fluid rotary method.In fact cold-producing medium cools off in condenser tube through three processes in the refrigeration system, the first process is the superheated steam cooling procedure, the heat exchange mode of this process is the gas forced convertion, the second process is the gas-liquid two-phase condensation process, this process heat exchange mode is condensation heat transfer, the 3rd process is that liquid is crossed cold process, and this process heat exchange mode is the liquid forced convertion.In these three processes, the heat exchange amount of superheated steam cooling procedure accounts for 1/3 of the total heat exchange amount of condenser, and heat exchange area accounts for 1/2 of total heat exchange area, and this process intraductal heat exchange coefficient is less, only is 1/10～1/50 of condensation heat transfer coefficient; Gas-liquid two-phase condensation process heat exchange amount accounts for 2/3 of the total heat exchange amount of condenser, and heat exchange area accounts for 1/2 of total heat exchange area, and this process intraductal heat exchange coefficient is maximum; It is less that liquid is crossed cold process heat exchange amount.Obviously, improve the heat transfer coefficient of condenser, its emphasis is not only the coefficient of heat transfer that improves the gas-liquid two-phase condensation process, and the superheated steam cooling procedure is also needed to take effectively to improve measure.
Summary of the invention
The objective of the invention is to overcome the condenser that the deficiencies in the prior art provide a kind of more boiling enhanced heat transfer, the cold-producing medium heat exchange is more carried out at the larger Gas-liquid phase region of the coefficient of heat transfer, emphasis is strengthened the Gas-liquid phase region condensation heat transfer simultaneously, improves on the whole the condenser coefficient of heat transfer.
In order to achieve the above object, a kind of technology of the present invention is achieved in that it is a kind of condenser of more boiling enhanced heat transfer, is characterized in that comprising:
Tube connector, an end of described tube connector and the exhaust outlet UNICOM of compressor;
Current divider, an end of described current divider and the other end UNICOM of described tube connector;
The first isocon and the second isocon, an end of described the first isocon and the second isocon respectively with the other end UNICOM of current divider; And heat exchanger, the entrance UNICOM of the other end of described the first isocon and heat exchanger, the other end of described the second isocon and heat exchanger UNICOM, the UNICOM position of the second isocon and heat exchanger be 0.3-0.62 times of total length from the entrance of heat exchanger distance.
In order to achieve the above object, another kind of technology of the present invention is achieved in that it is a kind of condenser of more boiling enhanced heat transfer, is characterized in that comprising:
Tube connector, an end of described tube connector and the exhaust outlet UNICOM of compressor;
Current divider, an end of described current divider and the other end UNICOM of described tube connector;
The first isocon, the second isocon and the 3rd isocon, an end of described the first isocon, the second isocon and the 3rd isocon respectively with the other end UNICOM of current divider; And heat exchanger, the entrance UNICOM of the other end of described the first isocon and heat exchanger; The other end of described the second isocon and heat exchanger UNICOM, the UNICOM position of the second isocon and heat exchanger be 0.2-0.5 times of total length from the entrance of heat exchanger distance; The other end of described the 3rd isocon and heat exchanger UNICOM, the UNICOM position of the 3rd isocon and heat exchanger be 0.5-0.8 times of total length from the entrance of heat exchanger distance.
The present invention is relative, and prior art has the following advantages:
1) the superheated steam heat of cooling of desuperheating zone load reduces, and most of superheated steam heat of cooling load is transferred to the higher Gas-liquid phase region of the coefficient of heat transfer, and average heat transfer coefficient improves;
2) add refrigerant superheat steam in gas-liquid two-phase condensation heat transfer process, the operative liquid cold-producing medium is seethed with excitement again, condensation heat transfer is strengthened, and the coefficient of heat transfer further improves;
3) gas-liquid two-phase condensation heat transfer process major part is carried out in the mass dryness fraction scope of heat exchange the best, and the coefficient of heat transfer is improved.
Description of drawings
Fig. 1 is the structural representation of the embodiment of the invention one;
Fig. 2 is the structural representation of the invention process two.
The specific embodiment
The below describes embodiments of the invention in detail, and the example of described embodiment is shown in the drawings, among the figure from start to finish same or similar label represent same or similar element or the element with identical or similar functions.Be exemplary below by the embodiment that is described with reference to the drawings, only be used for explaining invention, and can not be interpreted as limitation of the present invention.
In description of the invention, term " first ", " second " reach " the 3rd " and only are used for describing purpose, and can not be interpreted as indication or hint relative importance.
Embodiment one
As shown in Figure 1, it is a kind of condenser of more boiling enhanced heat transfer, comprising:
The first isocon 3 and the second isocon 4, an end of described the first isocon 3 and the second isocon 4 respectively with the other end UNICOM of current divider 2; With heat exchanger 5, the entrance UNICOM of the other end of described the first isocon 3 and heat exchanger 5, the other end of described the second isocon 4 and heat exchanger 5 UNICOMs, the UNICOM position of the second isocon 4 and heat exchanger 5 be 0.3-0.62 times of total length from the entrance distance of heat exchanger 5.In the present embodiment, the UNICOM position of the second isocon 4 and heat exchanger 5 be 0.52 times of total length from the entrance distance of heat exchanger 5, also can determine according to the variation of heat exchanger 5 inner refrigerant mass dryness fraction calculating and delivery temperature and pressure at expulsion the UNICOM position of the second isocon 4 and heat exchanger 5.
During work, the high temperature refrigerant superheated steam that refrigeration system compressor is discharged enters current divider 2 through tube connector 1 and is divided into two-way, one the tunnel enters in the heat exchanger tube through the entrance of the first isocon 3 from heat exchanger 5, carry out forced-convection heat transfer at superheated steam zone, this part high temperature refrigerant progressively is cooled to the dry saturated steam saturation temperature and is entered the gas-liquid two-phase condensing zone in superheated steam zone, carry out condensation heat transfer, carrying out along with condensation heat transfer, gas-liquid two-phase cold-producing medium mass dryness fraction descends gradually and enters the mass dryness fraction scope of heat exchange the best from tube connector 1 beginning, further decline along with mass dryness fraction, beginning off-target heat exchange mass dryness fraction district, at this moment, another road high temperature refrigerant superheated steam is the two-phase condensing zone that enters heat exchanger 5 in 0.52 times of scope of total length through the second isocon 4 in the heat exchange tube inlet distance of distance heat exchanger 5, mix with the cold-producing medium in the two-phase section, operative liquid cold-producing medium in the two-phase section seethes with excitement again, and condensation heat transfer is further strengthened, finally by flow out behind the cold-zone.
As shown in Figure 2, it is a kind of condenser of more boiling enhanced heat transfer, comprising:
The other end of described the second isocon 4 and heat exchanger 5 UNICOMs, the UNICOM position of the second isocon 4 and heat exchanger 5 be 0.2-0.5 times of total length from the entrance distance of heat exchanger 5, in the present embodiment, the UNICOM position of the second isocon 4 and heat exchanger 5 is 0.48 of total length from the entrance distance of heat exchanger 5, also can determine according to the variation of heat exchanger 5 inner refrigerant mass dryness fraction calculating and delivery temperature and pressure at expulsion the UNICOM position of the second isocon 4 and heat exchanger 5; The other end of described the 3rd isocon 6 and heat exchanger 5 UNICOMs, the UNICOM position of the 3rd isocon 6 and heat exchanger 5 be 0.5-0.8 times of total length from the entrance distance of heat exchanger 5, in the present embodiment, the UNICOM position of the 3rd isocon 6 and heat exchanger 5 be 0.7 times of total length from the entrance distance of heat exchanger 5, also can determine according to the variation of heat exchanger 5 inner refrigerant mass dryness fraction calculating and delivery temperature and pressure at expulsion the UNICOM position of the 3rd isocon 6 and heat exchanger 5.
During work, the high temperature refrigerant superheated steam that refrigeration system compressor is discharged enters current divider 2 through tube connector 1 and is divided into two-way, one the tunnel enters in the heat exchanger tube through the entrance of the first isocon 3 from heat exchanger 5, carry out forced-convection heat transfer at superheated steam zone, this part high temperature refrigerant progressively is cooled to the dry saturated steam saturation temperature and is entered the gas-liquid two-phase condensing zone in superheated steam zone, carry out condensation heat transfer, carrying out along with condensation heat transfer, gas-liquid two-phase cold-producing medium mass dryness fraction descends gradually and enters the mass dryness fraction scope of heat exchange the best from tube connector 1 beginning, further decline along with mass dryness fraction, beginning off-target heat exchange mass dryness fraction district, at this moment, another road high temperature refrigerant superheated steam is the two-phase condensing zone that enters heat exchanger 5 in 0.48 times of scope of total length through the second isocon 4 in the heat exchange tube inlet distance of distance heat exchanger 5, mix with the cold-producing medium in the two-phase section, operative liquid cold-producing medium in the two-phase section seethes with excitement again, condensation heat transfer is further strengthened, mass dryness fraction descends again thereupon, this moment, another road high temperature refrigerant superheated steam was the two-phase condensing zone that again enters heat exchanger 5 in 0.7 times of scope of total length through the 3rd isocon 6 in the heat exchange tube inlet distance of distance heat exchanger 5, condensation heat transfer is strengthened, thereby reach best mass dryness fraction, finally by flow out behind the cold-zone.
Although illustrated and described embodiments of the invention, those having ordinary skill in the art will appreciate that: in the situation that do not break away from principle of the present invention and aim can be carried out multiple variation, modification, replacement and distortion to these embodiment, scope of the present invention is limited by claim and equivalent thereof.
Claims (2)
1. condenser of boiling enhanced heat transfer again is characterized in that comprising:
Tube connector (1), an end of described tube connector and the exhaust outlet UNICOM of compressor;
Current divider (2), the other end UNICOM of an end of described current divider (2) and described tube connector (1); The first isocon (3) and the second isocon (4), an end of described the first isocon (3) and the second isocon (4) respectively with the other end UNICOM of current divider (2); And heat exchanger (5), the entrance UNICOM of the other end of described the first isocon (3) and heat exchanger (5),
The other end of described the second isocon (4) and heat exchanger (5) UNICOM, the UNICOM position of the second isocon (4) and heat exchanger (5) be 0.3-0.62 times of total length from the entrance distance of heat exchanger (5).
2. condenser of boiling enhanced heat transfer again is characterized in that comprising:
Tube connector (1), an end of described tube connector and the exhaust outlet UNICOM of compressor;
Current divider (2), the other end UNICOM of an end of described current divider (2) and described tube connector (1); The first isocon (3), the second isocon (4) and the 3rd isocon (6), an end of described the first isocon (3), the second isocon (4) and the 3rd isocon (6) respectively with the other end UNICOM of current divider (2); And heat exchanger (5), the entrance UNICOM of the other end of described the first isocon (3) and heat exchanger (5);
The other end of described the second isocon (4) and heat exchanger (5) UNICOM, the UNICOM position of the second isocon (4) and heat exchanger (5) be 0.2-0.5 times of total length from the entrance distance of heat exchanger (5); The other end of described the 3rd isocon (6) and heat exchanger (5) UNICOM, the UNICOM position of the 3rd isocon (6) and heat exchanger (5) be 0.5-0.8 times of total length from the entrance distance of heat exchanger (5).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310013226.0A CN103075846B (en) | 2013-01-15 | 2013-01-15 | Condenser for forcibly transferring heat by reboiling |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310013226.0A CN103075846B (en) | 2013-01-15 | 2013-01-15 | Condenser for forcibly transferring heat by reboiling |
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| Publication Number | Publication Date |
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| CN103075846A true CN103075846A (en) | 2013-05-01 |
| CN103075846B CN103075846B (en) | 2015-07-01 |
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| CN201310013226.0A Active CN103075846B (en) | 2013-01-15 | 2013-01-15 | Condenser for forcibly transferring heat by reboiling |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110094902A (en) * | 2019-05-29 | 2019-08-06 | 珠海格力电器股份有限公司 | Refrigerant flow path and design method thereof |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH094941A (en) * | 1995-06-21 | 1997-01-10 | Sanyo Electric Co Ltd | Refrigerating device |
| JPH10103796A (en) * | 1996-09-30 | 1998-04-21 | Sanyo Electric Co Ltd | Steam compression type refrigerating device |
| JPH10111029A (en) * | 1996-10-04 | 1998-04-28 | Sanyo Electric Co Ltd | Vapor compression refrigerator |
| JPH10238894A (en) * | 1997-02-26 | 1998-09-08 | Sanyo Electric Co Ltd | Heat exchanger |
| JP2008256304A (en) * | 2007-04-06 | 2008-10-23 | Daikin Ind Ltd | Refrigerating device |
| JP2010261642A (en) * | 2009-05-01 | 2010-11-18 | Ｓ−Ｓｐｅｃ株式会社 | Condenser and air conditioning device having the same |
-
2013
- 2013-01-15 CN CN201310013226.0A patent/CN103075846B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH094941A (en) * | 1995-06-21 | 1997-01-10 | Sanyo Electric Co Ltd | Refrigerating device |
| JPH10103796A (en) * | 1996-09-30 | 1998-04-21 | Sanyo Electric Co Ltd | Steam compression type refrigerating device |
| JPH10111029A (en) * | 1996-10-04 | 1998-04-28 | Sanyo Electric Co Ltd | Vapor compression refrigerator |
| JPH10238894A (en) * | 1997-02-26 | 1998-09-08 | Sanyo Electric Co Ltd | Heat exchanger |
| JP2008256304A (en) * | 2007-04-06 | 2008-10-23 | Daikin Ind Ltd | Refrigerating device |
| JP2010261642A (en) * | 2009-05-01 | 2010-11-18 | Ｓ−Ｓｐｅｃ株式会社 | Condenser and air conditioning device having the same |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110094902A (en) * | 2019-05-29 | 2019-08-06 | 珠海格力电器股份有限公司 | Refrigerant flow path and design method thereof |
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| CN103075846B (en) | 2015-07-01 |
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