CN101311647B - Composite type full-liquid type heat converter for refrigerant circulation system - Google Patents
Composite type full-liquid type heat converter for refrigerant circulation system Download PDFInfo
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- CN101311647B CN101311647B CN 200710104278 CN200710104278A CN101311647B CN 101311647 B CN101311647 B CN 101311647B CN 200710104278 CN200710104278 CN 200710104278 CN 200710104278 A CN200710104278 A CN 200710104278A CN 101311647 B CN101311647 B CN 101311647B
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Abstract
The invention discloses a compound and flooded heat exchanger used in a refrigerant circulatory system; wherein, the refrigerant flows through the outside of a tube bundle to conveniently carry out heat exchanging with the heat transfer medium flowing in the tube bundle; the bundle comprises at least two varieties of tubes suitable for different heat exchanging types, that is, at least comprises a heat exchange tube suitable for the evaporation of the refrigerant and a heat exchange tube suitable for the condensation of the refrigerant. Compared with the dry evaporator adopted by a traditional heat pump, the compound and flooded heat exchanger of the invention increasing the heat exchanging efficiency remarkably; compared with the flooded evaporator, the compound and flooded heat exchanger of the invention increases the heat exchange efficiency as a condenser. The compound and flooded heat exchanger of the invention can be used as a flooded evaporator and also be used as a condenser, thereby especially being suitable for being used in a heat pump device.
Description
Technical field
Present invention relates in general to the heat exchanger for refrigerant-cycle systems, relate in particular to a kind of composite type full-liquid type heat converter for the heat pump type refrigerating agent circulatory system.The invention still further relates to a kind of heat exchanging process that uses this composite type full-liquid type heat converter.
Background technology
The conventional heat pump type refrigerating agent circulatory system (for example heat pump handpiece Water Chilling Units) has been widely used in the various air-conditioning occasions.The source pump of this routine generally includes the compressor of reciprocating type or screw, (in kind of refrigeration cycle to extraneous heat rejection and removal, in heating circulation from extraneous absorbing heat) the first heat exchanger, expansion gear and (kind of refrigeration cycle from extraneous absorbing heat, to extraneous heat rejection and removal in heating circulation) second heat exchanger.
This second heat exchanger is used as evaporimeter so that so that cold-producing medium evaporation in kind of refrigeration cycle, and is used as condenser so that so that condensation of refrigerant in heating circulation.In this second heat exchanger, cold-producing medium carries out heat exchange with the heat transfer medium of for example water or ethylene glycol solution, cold-producing medium evaporates in this heat exchanger in kind of refrigeration cycle, in order to cool off this heat transfer medium, this heat transfer medium can be used for again cooling off the environment of pending air conditioning; Cold-producing medium condensation in this heat exchanger in heating circulation, in order to heat this heat transfer medium, this heat transfer medium can be used for again heating the environment of pending air conditioning.
In the source pump of routine, this second heat exchanger is configured to dry evaporator usually.Carry out heat exchange at the heat transfer medium in the heat-transfer pipe outside and the cold-producing medium in heat-transfer pipe, liquid cold-producing medium absorbs from the heat of heat transfer medium and is evaporated to gaseous refrigerant, thus so that the temperature of heat transfer medium reduction.On a part of heat exchange area in this dry evaporator, the cold-producing medium (rather than liquid refrigerant) that is evaporated to gaseous state carries out heat exchange with heat transfer medium, therefore this part heat exchange area can not be effectively utilized, even 20% can not being effectively utilized of total heat exchange area.
Propose in the art, use flooded evaporator as the second heat exchanger.On the whole heat exchange area of flooded evaporator, heat transfer medium carries out heat exchange with the cold-producing medium of liquid state all the time, has increased thus the efficient of evaporimeter.Yet this flooded evaporator only is only applicable to the heat exchange of cold-producing medium evaporation type, and is unsuitable for the heat exchange of condensation of refrigerant type.If adopt this evaporimeter in source pump, then this evaporimeter is used as condenser inadequately and adversely in heating cyclic process, and this will reduce the efficient of condensation effect and whole circulation significantly.Certainly can increase the size of this evaporimeter and heat exchange area obtaining desirable condensation effect, but this can increase manufacturing cost and difficulty.
Therefore still exist in the art a kind of needs that can overcome or alleviate at least the full-liquid type heat exchanger of the related problem of prior art and shortcoming are provided.
Summary of the invention
Therefore, a purpose of the present invention is to provide a kind of improved full-liquid type heat exchanger that is applicable to the heat pump type refrigerating agent circulatory system.
Another object of the present invention is to provide a kind of full-liquid type heat exchanger that refrigerant evaporator also is suitable for use as refrigerant condenser that is suitable for use as.
A further object of the present invention be to provide a kind of simple in structure, be convenient to make, multiduty heat exchanger that cost reasonably is used for refrigerant circulation.
Of the present invention one preferred aspect in, a kind of composite type full-liquid type heat converter for refrigerant-cycle systems is provided, described heat exchanger comprises a cylindrical shell, wherein is provided with a plurality of pipes of flowing through for heat transfer mediums; Be arranged on the end plate at each end place of cylindrical shell, be provided with a plurality of through holes in order to described tube bank is installed at end plate; Be arranged on the end cap on the end plate; Be arranged on refrigerant inlet port and outlet port on the cylindrical shell; And be arranged on the heat transfer medium inlet port on the end cap and export port.The cold-producing medium described tube bank of flowing through in the outside of described tube bank, in order to carry out heat exchange with the described heat transfer medium that in described tube bank, flows, described tube bank comprises at least two kinds of pipes that are suitable for different heat exchange types, namely comprises at least the pipe of the heat exchange that is suitable for the cold-producing medium evaporation and the pipe that is suitable for the heat exchange of condensation of refrigerant.
By full-liquid type heat exchanger of the present invention, improved significantly heat exchanger effectiveness, so that namely can be used as flooded evaporator, this heat exchanger can be used as again condenser.Compare with the dry evaporator that traditional heat pump adopts, improved heat exchange efficiency; Compare with traditional flooded evaporator, improved the heat exchange efficiency as condenser.Reduce cost of investment, also improved the reliability of whole system.
Description of drawings
By the reference accompanying drawing and in conjunction with the detailed description of specific embodiments of the invention, can understand better the present invention other and other purpose, feature and advantage, in the accompanying drawings:
Fig. 1 is the schematic diagram that adopts the refrigerant circulation of heat exchanger of the present invention;
Fig. 2 is the structural representation according to an embodiment of heat exchanger of the present invention;
Fig. 3 is the sectional view according to another embodiment of heat exchanger of the present invention;
Fig. 4 is the again sectional view of an embodiment according to heat exchanger of the present invention;
Fig. 5 is a kind of schematic diagram of the pipe for heat exchanger of the present invention; With
Fig. 6 is the another kind of schematic diagram that is used for the pipe of heat exchanger of the present invention.
In the accompanying drawings, identical Reference numeral represents parts identical or equivalence.
The specific embodiment
Describe heat exchanger of the present invention in detail referring to accompanying drawing.Although in a preferred embodiment of the invention, be described with reference to horizontal shell and tube heat exchanger, but those of ordinary skill in the art is to be understood that, heat exchanger of the present invention is not limited to this, heat exchange principle of the present invention can be applicable to other any suitable heat exchanger, for example shell-tube coil type heat exchanger of vertical shell and tube heat exchanger and water-cooled etc.In addition, although the present invention circulates to be described with reference to the hot pump type means for refrigeration agent of steam compression type, those of ordinary skill in the art should be appreciated that heat exchanger of the present invention also can be used for the refrigerant circulation of other type.
Fig. 1 shows the refrigerant circulation of exemplary heat pump type air conditioner system, and it is generally by Reference numeral 101 expressions.The refrigerant circulation of this vapor-compression formula consists essentially of: the compressor 111 that is used for compressed refrigerant; In kind of refrigeration cycle to the first heat exchanger 109 of extraneous heat rejection and removal; So that the liquid refrigerant of high pressure is expanded to the expansion gear 107 of low pressure refrigerant; The second heat exchanger 105 of absorbing heat in kind of refrigeration cycle; And so that the cross valve 140 that this refrigerant circulation switches between refrigeration mode (kind of refrigeration cycle) and heating mode (heating circulation).
Those of ordinary skill in the art is to be understood that the refrigerant circulation shown in Fig. 1 is schematic or illustrative, and non-limiting.For example, although the compressor shown in Fig. 1 is screw compressor, also can adopt reciprocating type or centrifugal compressor.Equally, although the expansion gear shown in Fig. 1 is electric expansion valve (EXV), can according to application scenario and other Consideration of this system, use the expansion valve of other type, for example heating power expansion valve (TXV).If necessary, other favourable device also can be set in order to improve cycle efficieny, for example economizer cycle 144.In addition, also can be provided with other accessory, for example liquid trap 110, be used for to reclaim the separator of lubricating oil and control module 113 and the sensor 147,149 that is used for this circulation of control.These are not major parts of the present invention.
Shown in Fig. 1 and arrow wherein, refrigerant circulation 101 is with refrigeration mode work.High pressure after the compressed machine compression and the gaseous refrigerant of high temperature flow to the first heat exchanger 109 via pipeline 139 and cross valve 140.In this first heat exchanger 109, this gaseous refrigerant is condensed into liquid refrigerant and to extraneous heat rejection and removal.Condensed cold-producing medium flows to expansion valve 107 via pipeline 143 and economizer 144 successively.The liquid refrigerant of this high pressure is expanded to the cold-producing medium of low pressure in expansion valve 107, and flows to the second heat exchanger 105 via pipeline 145.In this second heat exchanger 105, cold-producing medium for example hydrogen fluorohydrocarbon (HFC) and/or HCFC (HCFC) and heat transfer medium for example water carry out heat exchange, specifically, liquid cold-producing medium flashes to gaseous refrigerant and absorbs heat from heat transfer medium, thereby cools off this heat transfer medium.Cold-producing medium includes but not limited to R-22, R-134a, R-407c and R-410a.The space that heat transfer medium flows to fan coil and need cool off by this fan coil cooling.This gaseous refrigerant turns back to compressor 111 via pipeline 133, liquid trap 110 and pipeline 157, in order to finish this refrigerant circulation.
The cold-producing medium that has been shown in dotted line in the cross valve 140 shown in Figure 1 heats circulation, that is, and and with heat pump or heating mode work.For the sake of simplicity, the flow direction of cold-producing medium in heating mode is not shown among Fig. 1, yet this flow direction that heats circulation also should be known to persons of ordinary skill in the art.After cross valve 140 switches to the flow path shown in the dotted line, compressed cold-producing medium at first flows to the second heat exchanger 105, this gaseous refrigerant is condensed into the liquid refrigerant co-current flow through the heat transfer medium heat rejection and removal of this second heat exchanger 105, namely heats this heat transfer medium.Heated heat transfer medium can be used for heating the space that needs heat supply.This liquid refrigerant successively via expansion valve, economizer, the first heat exchanger, turns back to compressor again, in order to finish this heat pump cycle.
Shown in Fig. 2,3 and 4, the second heat exchanger 105 is configured to shell and tube heat exchanger.Be provided with the tube bank 203 that is formed by a plurality of heat-transfer pipes in tubular barrel 201, heat transfer medium flows in pipe, and cold-producing medium carries out heat exchange in the pipe outside with heat transfer medium.This heat exchanger also comprises the end plate 205 at each the end place that is arranged on cylindrical shell.Described heat-transfer pipe extends between end plate and is supported by end plate.In shell and tube heat exchanger shown in Figure 2, the tube bank 203 of heat-transfer pipe is configured to two Process flows, but is to be understood that the tube bank that also can adopt other form, for example single process or multipaths.A plurality of baffle plates 215 also can be set in heat exchanger, so that maintenance is restrained and directs refrigerant is moving, thereby avoid occurring the zone of mobile short circuit and heat exchanger effectiveness decline.
As Fig. 3 and 4 clear shown in, tube bank 203 is included in the heat- transfer pipe 301 and 303 that the aspects such as structure, function and application scenario differ from one another.Pipe 301 is heat-transfer pipes that the heat exchange when evaporating for cold-producing medium is optimized, and hereinafter referred to as " evaporation tube ", is heat-transfer pipes that the heat exchange during for condensation of refrigerant is optimized and manage 303, hereinafter referred to as " condenser pipe ".In other words, evaporation tube 301 is suitable for the heat exchange of cold-producing medium evaporation, and condenser pipe 303 is suitable for the heat exchange of condensation of refrigerant.Employed in this manual term " for ... heat exchange is optimized " or " being suitable for ... heat exchange " refer to the technological means of heat-transfer effect between the heat transfer medium that comprises any cold-producing medium that is suitable for improving the pipe outside and pipe inboard, for example tiny fin and the inboard jog of pipe in the pipe outside grades, in order to increase heat transfer area or strengthen Fluid Flow in A, even comprise that the material that for example increases with thermal conductivity makes heat-transfer pipe.The technological means of these augmentation of heat transfer effects can be based on changing such as the characteristic of tube bank and the factor such as the characteristic of cold-producing medium and heat transfer medium, and these factors include but not limited to fluid temperature (F.T.), flow rate, phase transformation, liquid form and flow direction each other.The technological means of these augmentation of heat transfer effects can be known for the ordinary skill in the art.
In kind of refrigeration cycle, the second heat exchanger 105 is as evaporimeter, introduces these cylindrical shells from the liquid refrigerant of the low temperature of expansion valve 107 from the lower port 305 of cylindrical shell 201.The liquid level of liquid refrigerant is controlled so as to and is in such position in cylindrical shell 201, namely, so that the evaporation tube 301 of the overwhelming majority is submerged under the liquid refrigerant liquid level, being preferably whole evaporation tube 301 is submerged under the liquid level, more preferably all tube banks are submerged, like this, so that this evaporimeter is configured to flooded evaporator.Liquid refrigerant absorbs subsequently from the heat of the inboard heat transfer medium of pipe and flashes to refrigerant vapour in the pipe outside, cool off thus the heat transfer medium of flowing pipe.The refrigerant vapour that produces leaves this heat exchanger and returns compressor from the upper port 307 that is positioned at cylindrical shell top.This cylindrical shell also can arrange a phase separator, carries liquid refrigerant secretly and causes the compressor liquid hammer in order to prevent the refrigerant vapour that leaves.
Heat transfer medium for example water is introduced tube bank 203 from (unshowned) bottom entrance.In a preferred embodiment, the tube bank that is formed by evaporation tube 301 be positioned the tube bank that formed by condenser pipe 303 below.Particularly, evaporation tube 301 is arranged in bottom and/or the middle part of cylindrical shell 201, and condenser pipe 303 is arranged in the top of cylindrical shell 201, referring to Fig. 4.In other embodiments, condenser pipe 303 can be arranged to the middle part near cylindrical shell 201, in order to flooded by liquid refrigerant as described below whole or in part, as shown in Figure 3.In order conveniently to install and/or take into account the Consideration of heat exchange, evaporation tube 301 and condenser pipe 303 distance that can be spaced apart from each other.In another embodiment, they also can arrange with abutting one another.
The heat transfer medium evaporation tube 301 of can at first flowing through.This moment, different from dry evaporator, heat transfer medium carries out heat exchange with pipe liquid refrigerant outward all the time, all evaporation tubes 301 are utilized fully in order to conduct heat, increase heat transfer area and efficient, and compared with dry evaporator, also reduced the degree of superheat of the refrigerant vapour that leaves.The heat transfer medium that is cooled is flowed through subsequently and is arranged on condenser pipe 303 on the evaporation tube 301, in order to be cooled further.Thereafter, heat transfer medium leaves condenser pipe 303 via the top outlet.
On the other hand, heating in the circulation of for example defrost operation or operation of heat pump, the second heat exchanger 105 is as condenser, introduces these cylindrical shells from the gaseous refrigerant of the high temperature of compressor 111 from the upper port 307 of cylindrical shell 201.This gaseous refrigerant at first with the heat transfer medium of the condenser pipe 303 of flowing through for example cooling water carry out heat exchange, that is to say that the heat dissipation of gaseous refrigerant is condensed into refrigerant liquid as the heat transfer medium of cooling agent and in the outside of condenser pipe 303.As mentioned above, condenser pipe 303 is to optimize the heat exchange that is used for condensation of refrigerant, and therefore it shows splendid heat transfer coefficient in condensation process, has significantly improved thus the heat that passes to heat transfer medium, and has improved the temperature of the heat transfer medium that obtains.Condensed refrigerant liquid drops onto the bottom of cylindrical shell from the pipe outer wall, and gathers to form the liquid level of certain altitude in cylindrical shell, in order to preferably flood basically all evaporation tubes 301.The refrigerant liquid that obtains leaves this heat exchanger from the lower port 305 of cylindrical shell, in order to flow to expansion valve.
Because evaporation tube 301 is submerged under the liquid level, therefore so that the heat transfer medium of the evaporation tube 301 of flowing through can provide the further cooling to cold-producing medium.By the condenser of above-mentioned structure, can reduce on the whole the condensation temperature of condensation of refrigerant process, so that condensation of refrigerant pressure obviously descends, for example condensing pressure can reduce about 5kgf for the cold-producing medium of R-134a thus.
Should be noted that in heating circulation, cold-producing medium enters this heat exchanger and leaves from lower port from upper port, the flow direction of its flow direction generally during with kind of refrigeration cycle is opposite.Corresponding control device, valve and pipeline can be set realize this mobile switching.Perhaps, except port 305,307, other port can be set to be used as the entrance and exit that heats the cold-producing medium in the cyclic process.
Similar to kind of refrigeration cycle, heat transfer medium can be introduced tube bank 203 from the bottom entrance, flows to the outlet of (unshowned) top.Those of ordinary skill in the art is to be understood that, heat transfer medium also can at first be directed to the condenser pipe 303 from upper entrance, in this case, can obtain the larger heat transfer temperature difference between heat transfer medium and the cold-producing medium, this is conducive to the condensation on condenser pipe 303 of cold-producing medium.As mentioned above, this need to arrange corresponding control device, valve and pipeline and realize this mobile switching.These are well known for those of ordinary skill in the art, and for the sake of simplicity, have saved description to it at this.
Fig. 5 and 6 shows respectively the outside fin of exemplary evaporation tube 301 and condenser pipe 303.The outside fin of this exemplary evaporation tube 301 is formed with the nucleation hole that helps the cold-producing medium boiling, in order to strengthen heat exchange.Evaporation tube can be any suitable from the market obtainable heat-transfer pipe, and for example the model of Gao Kelian company (Wolverine Tube Inc.) manufacturing is the pipe of EDE3.Certainly, the pipe that those of ordinary skill in the art can select other after understanding principle of the present invention is as evaporation tube.
The outside fin of this exemplary condenser pipe 303 helps the cold-producing medium of condensation to drip, and outside fin also increased heat transfer area, thereby improves heat exchange effect.Condenser pipe can be any suitable from the market obtainable heat-transfer pipe, and for example the model of Gao Kelian company manufacturing is the pipe of SPIKE FIN2.Those of ordinary skill in the art should be appreciated that the condenser pipe that also can adopt other type.
In an alternate embodiment, condenser pipe and evaporation tube also can be the heat-transfer pipes of same type to a certain extent, as long as this pipe is applicable to the heat exchange of condensation of refrigerant and evaporation simultaneously.Although in some cases, the outside fin of pipe can not both be optimized for for condensation and also be optimized for for evaporation, and pipe can be constructed with a plurality of sections, comprised at least the section's section and the section's section that is optimized to for evaporation that are optimized to for condensation.And, the invention is not restricted to this, in the situation that increases within bounds flow resistance, the inside pipe wall of condenser pipe and evaporation tube also can arrange same or different fins, in order to strengthen the turbulent flow of heat transfer medium.
In addition, in this heat exchanger, the spacing of condenser pipe and evaporation tube, diameter, position etc. can be selected based on concrete condition, and this is known for a person skilled in the art.
Although only have two rows at the condenser pipe 303 shown in Fig. 3 and 4, can be according to needing the different condenser pipe of magnitude setting.For example, if wish to adopt the air-conditioning system of heat exchanger of the present invention mainly to move, less condenser pipe can be set under refrigeration mode, slot milling arranges more evaporation tube, is convenient to like this this heat exchanger mainly as flooded evaporator.On the contrary, if air-conditioning system is intended to then more condenser pipe should be set as heat pump, in order to as condenser the time, obtain higher heat exchange efficiency.In addition, the quantity of condenser pipe also depends on other the factor such as selected evaporation tube and condenser pipe.For example, if selected evaporation tube is only applicable to the heat of evaporation exchange and is unsuitable for condensation heat exchange, then can increase the quantity of condenser pipe.Generally speaking, condenser pipe lacks than evaporation tube.
The present inventor has carried out a large amount of experiments for different operating modes.When the EDE3 pipe that uses Gao Kelian company to make as evaporation tube and when using SPIKE FIN2 pipe that Gao Kelian company makes as condenser pipe, preferably condenser pipe accounts for 10% in the tube bank, in order to take into account kind of refrigeration cycle and heat circulation, obtain simultaneously desirable running parameter.Generally speaking, the ratio of condenser pipe is 5-80%.
The present invention also can be applicable to the transformation of flooded evaporator, that is to say, increases condenser pipe in existing flooded evaporator, in order to be used as condenser pipe in heating circulation.Perhaps, those of ordinary skill in the art also can contemplate with condenser pipe and replace the part evaporation tube.
As mentioned above, those of ordinary skill in the art should be appreciated that the invention provides a kind of have several functions heat exchanger, other refrigerant circulation that it can be used for except heat pump for example only uses under defrosting mode.
Although described in conjunction with the preferred embodiments the present invention, those of ordinary skills can carry out modification and replacement without departing from the scope of the invention.For example when as the modification of existing system or transform when implementing, the details of existing system can affect the details of enforcement significantly.Although the present invention is described with reference to the state of fundamental system and simplification, principle of the present invention can be applicable to many more complicated parts or system form, and no matter these parts or system are existing or also do not develop.Therefore, the present invention comprise subsequently claim and whole modification and the replacement in the protection domain of its equivalents.
Claims (13)
1. full-liquid type heat exchanger that is used for refrigerant-cycle systems, described heat exchanger comprises a cylindrical shell, wherein is provided with the tube bank of flowing through for heat transfer medium; Be arranged on the end plate at each end place of described cylindrical shell, be provided with a plurality of through holes in order to described tube bank is installed at described end plate; That form with this cylindrical shell or cover hermetically the end cap of described end plate; The ingress port and the outlet port that are used for this cold-producing medium; And the ingress port and the outlet port that are used for this heat transfer medium,
It is characterized in that, the described tube bank of flowing through in the outside of described tube bank of described cold-producing medium, in order to carry out heat exchange with the described heat transfer medium that flows in described tube bank, described tube bank comprises at least two kinds of pipes that are suitable for different heat exchange types,
Wherein, described tube bank comprises the pipe of the heat exchange that is suitable for the cold-producing medium evaporation and the pipe that is suitable for the heat exchange of condensation of refrigerant.
2. full-liquid type heat exchanger as claimed in claim 1, it is characterized in that, this heat exchanger causes the horizontal shell and tube type heat exchanger, wherein said tube bank horizontal-extending, and the described pipe that is suitable for the heat exchange of cold-producing medium evaporation be arranged on the described heat exchange that is suitable for condensation of refrigerant pipe below.
3. full-liquid type heat exchanger as claimed in claim 2, it is characterized in that, this heat exchanger can be used as refrigerant evaporator and refrigerant condenser, when this heat exchanger is used as evaporimeter, thereby liquid refrigerant is evaporated to gaseous refrigerant from the heat that lower port enters this heat exchanger and absorbs the heat transfer medium of the described tube bank of flowing through, the gaseous refrigerant that obtains leaves from upper port, and, when this heat exchanger is used as condenser, thereby gaseous refrigerant enters this heat exchanger and is condensed into liquid refrigerant for the heat transfer medium of the described tube bank of flowing through heat dissipation from upper port, and the liquid refrigerant that obtains leaves from lower port.
4. full-liquid type heat exchanger as claimed in claim 2 or claim 3 is characterized in that, this heat transfer medium at first flows into the described pipe that is suitable for the heat exchange of cold-producing medium evaporation, flows into subsequently the described pipe that is suitable for the heat exchange of condensation of refrigerant.
5. full-liquid type heat exchanger as claimed in claim 2 or claim 3 is characterized in that this heat transfer medium at first flows into the described pipe that is suitable for the heat exchange of condensation of refrigerant, flows into subsequently the described pipe that is suitable for the heat exchange of cold-producing medium evaporation.
6. full-liquid type heat exchanger as claimed in claim 1 is characterized in that, the described pipe that is suitable for the heat exchange of condensation of refrigerant accounts for the 5-80% of tube bank.
7. full-liquid type heat exchanger as claimed in claim 6 is characterized in that, the quantity of the pipe of the described heat exchange that is suitable for condensation of refrigerant is less than the quantity of the pipe of the heat exchange that is suitable for the cold-producing medium evaporation.
8. full-liquid type heat exchanger as claimed in claim 7 is characterized in that, the described pipe that is suitable for the heat exchange of condensation of refrigerant accounts for greatly 10% of tube bank.
9. such as each described full-liquid type heat exchanger among the claim 1-3, it is characterized in that, gathered liquid refrigerant in this heat exchanger, its liquid level is in such position, that is, liquid refrigerant floods the described pipe that is suitable for the heat exchange of cold-producing medium evaporation at least.
10. full-liquid type heat exchanger as claimed in claim 9 is characterized in that, described liquid refrigerant floods all tube banks.
11. one kind comprises that this refrigerant-cycle systems moves such as the refrigerant-cycle systems of each described full-liquid type heat exchanger among the claim 1-10 under heat pump and/or defrosting mode.
12. one kind comprises the steam compression type air-conditioning system such as each described full-liquid type heat exchanger among the claim 1-10.
13. a method of transforming existing flooded evaporator arranges the pipe of the heat exchange that is suitable for condensation of refrigerant in this evaporimeter, or replaces at least a portion in original tube bank with the pipe of the heat exchange that is suitable for condensation of refrigerant.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200710104278 CN101311647B (en) | 2007-05-25 | 2007-05-25 | Composite type full-liquid type heat converter for refrigerant circulation system |
| HK09104512.2A HK1126270A1 (en) | 2007-05-25 | 2009-05-18 | Hybrid flooded heat exchanger for refrigerant cycle system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200710104278 CN101311647B (en) | 2007-05-25 | 2007-05-25 | Composite type full-liquid type heat converter for refrigerant circulation system |
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| Publication Number | Publication Date |
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| CN101311647A CN101311647A (en) | 2008-11-26 |
| CN101311647B true CN101311647B (en) | 2013-02-27 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 200710104278 Active CN101311647B (en) | 2007-05-25 | 2007-05-25 | Composite type full-liquid type heat converter for refrigerant circulation system |
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| CN (1) | CN101311647B (en) |
| HK (1) | HK1126270A1 (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101701757B (en) * | 2009-10-31 | 2011-06-01 | 苏州吉来冷冻空调设备配件有限公司 | Shell-tube evaporator |
| CN101936618A (en) * | 2010-08-27 | 2011-01-05 | 殷尧其 | Internal switching water source heat pump unit with heat recovery |
| CN101949618A (en) * | 2010-10-08 | 2011-01-19 | 浙江盾安人工环境股份有限公司 | Refrigerant switching sewage-source heat pump system |
| CN102954629A (en) * | 2012-11-13 | 2013-03-06 | 顺德职业技术学院 | Controlled-dryness reinforced heat transfer evaporator |
| US9677795B2 (en) * | 2012-12-21 | 2017-06-13 | Trane International Inc. | Refrigerant management in a HVAC system |
| CN105588374B (en) * | 2016-03-03 | 2017-10-24 | 苏州市农业机械有限公司 | New Evaporator |
| US10077682B2 (en) | 2016-12-21 | 2018-09-18 | General Electric Company | System and method for managing heat duty for a heat recovery system |
| CN106969549B (en) * | 2017-05-10 | 2023-10-13 | 英得艾斯（上海）冷冻空调有限公司 | Marine flowing type evaporator and application method thereof |
| CN107606974B (en) * | 2017-09-14 | 2019-05-10 | 上海铠韧气体工程股份有限公司 | Integrated combination heat exchanger |
| CN109341120B (en) * | 2018-11-15 | 2024-03-01 | 苏州利玛特能源装备有限公司 | Flooded refrigerating system |
| CN109682121A (en) * | 2019-02-26 | 2019-04-26 | 江苏世林博尔制冷设备有限公司 | A kind of flooded type condenser evaporator combinations system |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000230760A (en) * | 1999-02-08 | 2000-08-22 | Mitsubishi Heavy Ind Ltd | Refrigerating machine |
| JP2003083638A (en) * | 2001-07-05 | 2003-03-19 | Sekisui Chem Co Ltd | Heat pump, and heat pump system for supplying hot water |
-
2007
- 2007-05-25 CN CN 200710104278 patent/CN101311647B/en active Active
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2009
- 2009-05-18 HK HK09104512.2A patent/HK1126270A1/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| HK1126270A1 (en) | 2009-08-28 |
| CN101311647A (en) | 2008-11-26 |
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