CN203132097U - Air conditioner and heat exchange system thereof - Google Patents
Air conditioner and heat exchange system thereof Download PDFInfo
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- CN203132097U CN203132097U CN201320100202.4U CN201320100202U CN203132097U CN 203132097 U CN203132097 U CN 203132097U CN 201320100202 U CN201320100202 U CN 201320100202U CN 203132097 U CN203132097 U CN 203132097U
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- pipeline
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Abstract
The utility model relates to the technical field of air conditioners, and provides an air conditioner and a heat exchange system thereof. The heat exchange system comprises a first pipeline, a second pipeline and a connecting heat exchanger, the heat exchanger comprises at least two flow paths which are parallelly connected with each other, a plurality of heat exchange tubes are serially connected in an end-to-end manner to form each flow path, a first one-way valve is arranged between the first pipeline and one flow path and is unidirectionally open along the first pipeline to the flow path, a second one-way valve is arranged between the other flow path and the second pipeline and is unidirectionally open along the flow path to the second pipeline, and a control valve is arranged between the first one-way valve and the second one-way valve, is closed when in the heat exchange flow direction from the first pipeline to the second pipeline, and is opened when in the heat exchange flow direction from the second pipeline to the first pipeline. More flow paths are used in refrigeration, pressure loss is reduced, heat exchange temperature difference is increased, heat exchange efficiency is improved, fewer flow paths are used in heating, the flow speed of refrigerants is increased, and cold heat exchange efficiency is improved, so that the system performance of the air conditioner is greatly improved.
Description
Technical field
The utility model relates to air-conditioning technical field, more particularly, relates to a kind of air-conditioner and heat-exchange system thereof.
Background technology
Have refrigeration and the air-conditioning system of heat-production functions at present, its structure is formed generally as shown in fig. 1, comprise compressor 100 by the pipeline connection ', cross valve 200 ', off-premises station 300 ', indoor set 400 ' and throttling arrangement 500 '.Wherein, off-premises station 300 ' in be provided with first heat-exchange system 310 ', indoor set 400 ' in be provided with second heat-exchange system 410 '.During the air-conditioning system operation, compressor 100 ' driving refrigerant circulation, refrigerant circulates in internal system, and by off-premises station 300 ' first heat-exchange system 310 ' and indoor set 400 ' in second heat-exchange system 410 ' the realize heat exchange between refrigerant and the air.
In above-mentioned air-conditioning system, freeze and when heating each interface break-make difference of cross valve.In process of refrigerastion, the break-make of cross valve as shown in fig. 1, from compressor 100 ' after coming out successively through cross valve 200 ', off-premises station 300 ', throttling arrangement 500 ' and indoor set 400 ' after get back to compressor 100 '.Through off-premises station 300 ' 310 ' time of first heat-exchange system, refrigerant is high-temperature high-pressure state, by the refrigerant condensation to the outdoor air heat release, at this moment, refrigerant by first heat-exchange system 310 ' port 310b ' flow to port 310a '; Through indoor set 400 ' in 410 ' time of second heat-exchange system, refrigerant is low-temperature condition, cools off room air by refrigerant evaporation, thereby reaches the purpose of refrigeration, at this moment, refrigerant by second heat-exchange system 410 ' port 410b ' flow to port 410a '.
In the process of heating, the break-make of cross valve as shown in Figure 2, the refrigerant of HTHP from compressor 100 ' pass through successively after coming out cross valve 200 ', indoor set 400 ', and indoor set 400 ' in second heat-exchange system 410 ' middle condensation heat release, and by indoor set 400 ' heat is spilt in the room air, thereby reach the purpose that heats, at this moment, refrigerant by second heat-exchange system 410 ' port 410a ' flow to port 410b '.Simultaneously, through the liquid refrigerants of indoor set 400 ' condensation continue by throttling arrangement 500 ' by throttling become the two-phase refrigerant of low-temp low-pressure enter off-premises station 300 ' first heat-exchange system 310 ' and evaporation heat absorption, return compressor 100 ', at this moment, refrigerant by first heat-exchange system 310 ' port 310a ' flow to port 310b '.
Off-premises station 300 ' first heat-exchange system 310 ' and indoor set 400 ' in second heat-exchange system 410 ' all include heat exchanger, when flowing in the heat exchanger tube of refrigerant at heat exchanger, increase along with flow resistance, the heat transfer temperature difference of refrigerant and air will reduce, thereby cause the heat exchange deleterious, the air conditioner performance descends.So a plurality of streams generally are set in heat exchanger, increase the flow passage sectional area with this, and shorten the length of stream, reduce flow resistance.But also can reduce the flow velocity of refrigerant in heat exchanger tube when increasing stream, thereby reduce the coefficient of heat transfer between refrigerant and the heat exchanger tube, also will cause the heat exchange deleterious of heat exchanger.Therefore, the flow path designs of heat exchanger needs the influence of equiulbrium flow dynamic resistance and coefficient of heat transfer heat exchanging effect.
By among Fig. 1 and Fig. 2 as seen, at air conditioner refrigerating and heating in the process, first heat-exchange system 310 ' with second heat-exchange system 410 ' in heat exchanger all can experience the process that the counter-rotating of refrigerant flow direction and its interior refrigerant state change between condensation or evaporating state.And refrigerant is when condensing state and evaporating state, and flow resistance and the relation between the coefficient of heat transfer of refrigerant are different in the heat exchanger.Generally speaking, for the Hoisting System performance, when refrigerant in the heat exchanger during at evaporating state, the refrigerant crushing is big and also bigger to the systematic function influence, and this moment is reduction refrigerant crushing primarily, namely adopts more stream; And in the heat exchanger refrigerant when condensing state, this moment refrigerant flow to take place send out change and the refrigerant crushing less, crushing is also smaller to the systematic function influence, this moment, the primary refrigerant flow rate that increases promoted the heat-exchange system between refrigerant and heat exchanger tube, namely adopted less stream.For the Hoisting System performance, generally when refrigerant is in evaporating state in the heat exchanger, preferably adopt more stream, and refrigerant adopts less stream when being in condensing state in the heat exchanger.That is to say that the stream distribution design of heat exchanger is contradiction, unfavorable to freezing to the favourable refrigerant flow that freezes, unfavorable to freezing to heating favourable refrigerant flow.
As shown in Figure 3, be a kind of heat exchanger with two streams in the prior art.In this heat exchanger, comprise an inlet tube 500a ', an outlet 500b ' and be connected in inlet tube 500a ' and outlet 500b ' between the first stream 600a ' and the second stream 600b '.Each stream constitutes by some end to end heat-transfer pipes (not specifically illustrating) herein.The break-make structure different with cross valve under the state of heating according to refrigeration, in Fig. 3, refrigerant is divided into two-way after being entered by inlet tube 500a ', enters the first stream 600a ' and the second stream 600b ' respectively, at last by outlet 500b ' outflow.And as shown in Figure 4, be divided into two-way after refrigerant is entered by outlet 500b ', enter the first stream 600a ' and the second stream 600b ' respectively, at last by 500a ' outflow.By Fig. 3 and Fig. 4 as can be seen, after heat exchanger structure is determined, the stream quantity of heat exchanger has just been determined, even the refrigerant flow direction changes, the stream of system can not change yet, and this does not just satisfy the requirement that refrigerant is in flow path quantity under the two kinds of situations of condensation that flow to different evaporations, can cause the cooling and warming performance unbalanced, a kind of functional, and another kind of poor-performing.
The utility model content
Technical problem to be solved in the utility model is to overcome the defective of prior art, provides a kind of fluxion quantity variable, but the heat-exchange system of balance refrigeration and heating effect and adopt the air-conditioner of this heat-exchange system.
For solving the problems of the technologies described above, the technical solution of the utility model is: a kind of heat-exchange system is provided, comprise first pipeline, second pipeline and be connected in described first pipeline and described second pipeline between heat exchanger, described heat exchanger comprises at least two streams parallel with one another, each described stream is connected in series from beginning to end by some heat exchanger tubes and forms, described first pipeline and wherein being provided with between the stream along first check valve of first pipeline to the unidirectional conducting of this stream, wherein be provided with along second check valve of the unidirectional conducting of this stream to the second pipeline between another stream and described second pipeline, be provided with control valve between described first check valve and described second check valve, when the heat exchange flow direction is first pipeline to the second pipeline, described control valve closure, when the heat exchange flow direction was second pipeline to the first pipeline, described control valve was opened.
Particularly, the heat exchanger tube quantity difference in each described stream.
Particularly, described heat exchanger has a plurality of streams, and a described wherein stream and described another stream are any two in a plurality of streams.
Preferably, described control valve is magnetic valve.
Particularly, described first check valve, described second check valve and described control valve are by pipe joint or the setting of employing welding manner.
The utility model also provides a kind of air-conditioner, comprises indoor set and off-premises station, has one of at least above-mentioned heat-exchange system in described indoor set and the described off-premises station.
In the utility model, multithread road when realizing refrigeration reduces crushing, increases heat transfer temperature difference, promotes heat exchange efficiency; And few stream when heating promotes the refrigerant flowing velocity, promotes cold heat exchange efficiency, thereby promotes the systematic function of air-conditioner significantly.
Description of drawings
Fig. 1 is the principle schematic of air-conditioner when refrigeration in the prior art;
Fig. 2 is the principle schematic of air-conditioner when heating in the prior art;
Fig. 3 is a kind of principle schematic of heat exchanger when refrigeration with two streams in the prior art;
Fig. 4 is the principle schematic of heat exchanger when heating among Fig. 3;
Fig. 5 is the stream schematic diagram of first embodiment of the heat-exchange system that provides of the utility model;
Fig. 6 is the structural representation of first embodiment of the heat-exchange system that provides of the utility model;
Fig. 7 is the principle flow chart of control valve among first embodiment of the present utility model;
Fig. 8 is the refrigerant flow schematic diagram of first embodiment of the present utility model when refrigerating state;
Fig. 9 is the refrigerant flow schematic diagram of first embodiment of the present utility model when heating state;
Figure 10 is the stream schematic diagram of second embodiment of the heat-exchange system that provides of the utility model;
Figure 11 is the stream schematic diagram of the 3rd embodiment of the heat-exchange system that provides of the utility model;
Figure 12 is the stream schematic diagram of the 4th embodiment of the heat-exchange system that provides of the utility model;
Figure 13 is the structural representation of the 5th embodiment of the heat-exchange system that provides of the utility model.
The specific embodiment
In order to make the purpose of this utility model, technical scheme and advantage clearer, below in conjunction with drawings and Examples, the utility model is further elaborated.Should be appreciated that specific embodiment described herein only in order to explaining the utility model, and be not used in restriction the utility model.
Embodiment one
With reference to Fig. 5, Fig. 6, the utility model provides a kind of heat-exchange system, comprise first pipeline 100, second pipeline 200 and be connected in first pipeline 100 and second pipeline 200 between heat exchanger 300.In the present embodiment, heat exchanger 300 comprises two streams, here for ease of explanation, with this two streams difference called after first streams 310 and second stream 320.First stream 310 and second stream 320 form by some heat exchanger tube 330 head and the tail serial connections.Certainly, heat exchanger 300 also can comprise more stream.Wherein, be provided with between first pipeline 100 and first stream 310 along first check valve 400 of first pipeline, 100 to first streams, 310 unidirectional conductings, be provided with between second stream 320 and second pipeline 200 between second check valve, 500, the first check valves 400 of second stream, 320 to second pipelines, 200 unidirectional conductings and second check valve 500 and be provided with control valve 600.
In conjunction with Fig. 7, Fig. 8 and Fig. 9.When under the sweat cooling state, heat exchange flows to when being first pipeline, 100 to second pipelines 200, control valve 600 closures, at this moment, refrigerant is the parallel flow mistake from first stream 310 and second stream 320, and namely stream is two-way, refrigerant flow rate and flow process length have been reduced, reduced flow resistance, the efficient when promoting heat exchanger 300 as evaporimeter satisfies the performance requirement under the refrigerating state; Under heating state in condensation, heat exchange flows to when being second pipeline, 200 to first pipelines 100, control valve 600 is opened, at this moment, refrigerant is earlier via second stream 320 and then through first stream 310, and namely stream is one the tunnel, has increased refrigerant flow rate like this, heat exchange effect when the lifting heat exchanger uses as condenser satisfies the performance requirement that heats under the state.As seen from the above, the heat-exchange system that the utility model provides can be good at balance and promotes air-conditioner refrigeration and heating effect, and this simple in structure, be easy to control, therefore practical.
With reference to Fig. 6, in the present embodiment, the quantity of the heat exchanger tube 300 in first stream 310 and second stream 320 is 6.Certainly, the number of the heat exchanger tube 300 that comprises in each stream there is no particular requirement, also can adjust the quantity of heat exchanger tube 300 according to actual conditions, and the heat exchanger tube 300 that comprises in each stream is freely arranged.
In the present embodiment, control valve 600 is magnetic valve.The control of magnetic valve is judged according to the connected mode of cross valve in refrigerant state and the air-conditioning system in the heat exchanger 300, therefore, need not increase new sensor, and is simple in structure, easy to use.Certainly, magnetic valve also can adopt other same devices with open and close function to replace.Same, first check valve 400 and first check valve 500 can be by direction conductings, and other non-conduction similar devices of contrary direction replace.
In the present embodiment, first check valve 400, second check valve 500 pass through pipe joint or adopt the welding manner setting with control valve 600.
Embodiment two
With reference to Figure 10, the stream schematic diagram of second embodiment of the heat-exchange system that provides for the utility model.The difference of present embodiment and embodiment one is: in the present embodiment, heat exchanger includes four streams, first stream 310, second stream 320, the 3rd stream 340 and the 4th stream 350.And the first above-mentioned check valve 400 and first check valve 500 can be arranged on any stream.Namely except shown in Figure 10, first check valve 400 also can be arranged between first pipeline 100 and the 3rd stream 340, and second check valve 400 also can be arranged between the 4th stream 350 and second pipeline 200.
Embodiment three
With reference to Figure 11, the stream schematic diagram of the 3rd embodiment of the heat-exchange system that provides for the utility model.The difference of present embodiment and embodiment one is: in the present embodiment, heat exchanger includes five streams, first stream 310, second stream 320, the 3rd stream 340, the 4th stream 350 and and the 5th stream 360.And first stream 310 and second stream 320 are made up of a part of heat exchanger tube 330 of forming heat exchanger 300.Same, namely except shown in Figure 11, first check valve 400 and first check valve 500 also can be arranged on any stream.
Embodiment four
With reference to Figure 12, the stream schematic diagram of the 4th embodiment of the heat-exchange system that provides for the utility model.Present embodiment is with the difference of embodiment one: arranging of first check valve 400, first check valve 500 and control valve 600 is different.In the present embodiment, the first above-mentioned check valve 400 is set between first pipeline 100 and second stream 320, the second above-mentioned check valve 500 is set between first stream 310 and second pipeline 200, and control valve 600 is arranged between first check valve 400 and second check valve 500.This shows each check valve and can open and close arranging of magnetic valve pipeline is not had particular requirement.
Embodiment five
With reference to Figure 13, the stream schematic diagram of the 5th embodiment of the heat-exchange system that provides for the utility model.Present embodiment is with the difference of embodiment one: the set-up mode of heat exchanger tube 330 is different.In the present embodiment, heat exchanger tube 330 is double setting, and heat exchanger tube 330 is single setting among the embodiment one.Certainly, the setting of heat exchanger tube 330 also can be many rows.
The utility model also provides a kind of air-conditioner (not shown), comprises indoor set and off-premises station, has one of at least above-mentioned heat-exchange system in indoor set and the off-premises station.Namely be, above-mentioned heat-exchange system both can apply to the off-premises station of air-conditioner, also can be used for indoor machine of air-conditioner, also can apply to simultaneously in indoor set and the off-premises station.Adopt above-mentioned heat-exchange system, multithread road when realizing refrigeration reduces crushing, increases heat transfer temperature difference, promotes heat exchange efficiency; And few stream when heating promotes the refrigerant flowing velocity, promotes cold heat exchange efficiency, thereby promotes the systematic function of air-conditioner significantly.
Below only be preferred embodiment of the present utility model, not in order to limiting the utility model, all any modifications of within spirit of the present utility model and principle, doing, be equal to and replace and improvement etc., all should be included within the protection domain of the present utility model.
Claims (6)
1. heat-exchange system, comprise first pipeline, second pipeline and be connected in described first pipeline and described second pipeline between heat exchanger, described heat exchanger comprises at least two streams parallel with one another, each described stream is connected in series from beginning to end by some heat exchanger tubes and forms, it is characterized in that: described first pipeline and wherein being provided with between the stream along first check valve of first pipeline to the unidirectional conducting of this stream, wherein be provided with along second check valve of the unidirectional conducting of this stream to the second pipeline between another stream and described second pipeline, be provided with control valve between described first check valve and described second check valve, when the heat exchange flow direction is first pipeline to the second pipeline, described control valve closure, when the heat exchange flow direction was second pipeline to the first pipeline, described control valve was opened.
2. heat-exchange system as claimed in claim 1 is characterized in that: the heat exchanger tube quantity difference in each described stream.
3. heat-exchange system as claimed in claim 1, it is characterized in that: described heat exchanger has a plurality of streams, and a described wherein stream and described another stream are any two in a plurality of streams.
4. heat-exchange system as claimed in claim 1, it is characterized in that: described control valve is magnetic valve.
5. heat-exchange system as claimed in claim 1 is characterized in that: described first check valve, described second check valve and described control valve are by pipe joint or adopt the welding manner setting.
6. an air-conditioner comprises indoor set and off-premises station, it is characterized in that: have as each described heat-exchange system in the claim 1 to 5 one of at least in described indoor set and the described off-premises station.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320100202.4U CN203132097U (en) | 2013-03-05 | 2013-03-05 | Air conditioner and heat exchange system thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320100202.4U CN203132097U (en) | 2013-03-05 | 2013-03-05 | Air conditioner and heat exchange system thereof |
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| Publication Number | Publication Date |
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| CN203132097U true CN203132097U (en) | 2013-08-14 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201320100202.4U Expired - Lifetime CN203132097U (en) | 2013-03-05 | 2013-03-05 | Air conditioner and heat exchange system thereof |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105466083A (en) * | 2015-12-24 | 2016-04-06 | 珠海格力电器股份有限公司 | Flow-way-changeable heat pump air conditioner heat exchanger and control method thereof |
| CN105865008A (en) * | 2016-04-14 | 2016-08-17 | 上海交通大学 | Heat pump type air-conditioning heat exchanger with heat exchange working medium flow direction and flow path number in synchronous change |
| CN111426103A (en) * | 2020-02-28 | 2020-07-17 | 青岛海尔空调电子有限公司 | Heat exchange device, air conditioner and control method of air conditioner |
| CN111637583A (en) * | 2020-05-25 | 2020-09-08 | 宁波奥克斯电气股份有限公司 | Condenser flow path structure, control method and air conditioner |
| CN114508797A (en) * | 2022-01-28 | 2022-05-17 | 青岛海尔空调电子有限公司 | Heat exchanger |
| WO2023188421A1 (en) * | 2022-04-01 | 2023-10-05 | 三菱電機株式会社 | Outdoor unit and air conditioner equipped with same |
-
2013
- 2013-03-05 CN CN201320100202.4U patent/CN203132097U/en not_active Expired - Lifetime
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105466083A (en) * | 2015-12-24 | 2016-04-06 | 珠海格力电器股份有限公司 | Flow-way-changeable heat pump air conditioner heat exchanger and control method thereof |
| CN105865008A (en) * | 2016-04-14 | 2016-08-17 | 上海交通大学 | Heat pump type air-conditioning heat exchanger with heat exchange working medium flow direction and flow path number in synchronous change |
| CN111426103A (en) * | 2020-02-28 | 2020-07-17 | 青岛海尔空调电子有限公司 | Heat exchange device, air conditioner and control method of air conditioner |
| WO2021169526A1 (en) * | 2020-02-28 | 2021-09-02 | 青岛海尔空调电子有限公司 | Heat exchange device, air conditioner and control method therefor |
| CN111637583A (en) * | 2020-05-25 | 2020-09-08 | 宁波奥克斯电气股份有限公司 | Condenser flow path structure, control method and air conditioner |
| CN114508797A (en) * | 2022-01-28 | 2022-05-17 | 青岛海尔空调电子有限公司 | Heat exchanger |
| CN114508797B (en) * | 2022-01-28 | 2024-05-10 | 青岛海尔空调电子有限公司 | Heat exchange device |
| WO2023188421A1 (en) * | 2022-04-01 | 2023-10-05 | 三菱電機株式会社 | Outdoor unit and air conditioner equipped with same |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| ASS | Succession or assignment of patent right |
Owner name: GUANGDONG MIDEA REFRIGERATION EQUIPMENT CO., LTD. Free format text: FORMER OWNER: MEIDI ELECTRIC APPLIANCES CO., LTD., GUANGDONG Effective date: 20131210 Owner name: MIDEA GROUP CO., LTD. Free format text: FORMER OWNER: GUANGDONG MIDEA REFRIGERATION EQUIPMENT CO., LTD. Effective date: 20131210 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20131210 Address after: 528311 Beijiao City, Guangdong Province, Shunde Town, Lin Gang Road, Foshan Patentee after: GD MIDEA AIR-CONDITIONING EQUIPMENT Co.,Ltd. Patentee after: MIDEA GROUP Co.,Ltd. Address before: 528311 Beijiao, Foshan, Shunde District, the town of Guangdong, the United States Avenue, No. 6 Patentee before: GD MIDEA HOLDING CD., Ltd. Patentee before: GD MIDEA AIR-CONDITIONING EQUIPMENT Co.,Ltd. |
|
| CX01 | Expiry of patent term |
Granted publication date: 20130814 |
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| CX01 | Expiry of patent term |