CN202928178U - Heat exchanging system for air conditioner - Google Patents
Heat exchanging system for air conditioner Download PDFInfo
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- CN202928178U CN202928178U CN201220651840.0U CN201220651840U CN202928178U CN 202928178 U CN202928178 U CN 202928178U CN 201220651840 U CN201220651840 U CN 201220651840U CN 202928178 U CN202928178 U CN 202928178U
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Abstract
The utility model provides a heat exchanging system for an air conditioner. The system uses an efficient evaporator, an efficient condenser and a cylindrical heat exchanger. The efficient condenser integrates condensation and supercooling, the efficient evaporator integrates evaporation and overheating, and the cylindrical heat exchanger exchanges heat for a gas from the evaporator to a liquid from the condenser, so that heat of a refrigerating medium from the condenser and heat of a refrigerating medium from the evaporator are effectively utilized, and the efficiency of the system is improved. Meanwhile, an overheating area and an evaporating area of the evaporator are communicated through an overheating guide plate, so that the system is compact in structure, and the sectional area of an overheating guide groove is substantially equal to the open areas of overheating guide connectors at both ends, so that the flow rate of the refrigerating medium is stable at the guide plate, and therefore, the heat exchange efficiency is greatly improved.
Description
Technical field
The utility model relates to a kind of heat-exchange system, and particularly a kind of high efficient heat exchanging system for field of air conditioning belongs to air-conditioning heat exchange field.
Background technology
Common central air conditioner system for from condenser out the liquid coolant heat and all effectively do not recycle from evaporator outlet gas coolant heat out.
Chinese patent literature CN102095268A discloses a kind of aircondition of the propane refrigerant with regenerator, this device is done change in original air-conditioning system, added regenerator, described regenerator has the inner tube import that is communicated with the outlet of condenser and the inner tube that is communicated with electric expansion valve outlet, the outlet of described expansion valve is communicated with the import of evaporimeter, the outer tube import of the outlet of evaporimeter and regenerator is communicated with, the outer tube outlet of regenerator is communicated with compressor inlet, and compressor outlet is communicated with condenser.This kind aircondition is by increasing regenerator, making can be to lowering the temperature from condenser liquid refrigerant out from evaporimeter gas coolant out, thereby make the temperature of the refrigerator that enters evaporimeter further reduce, thereby improved the volatility of evaporimeter, and then improved the refrigeration performance of whole aircondition.But this aircondition does not relate to the improvement of condenser and evaporimeter internal structure, and adopts existing conventional condenser and the structure of evaporimeter.
What the condenser of existing conventional central air-conditioning adopted basically is pipe heat exchanger, and cold-producing medium carries out heat exchange by the heat exchanger tube that is arranged in outer cover of heat exchanger with extraneous water, realizes refrigeration.For the condensation efficiency that makes condenser is further improved, liquid outlet end at trumpet cooler, generally also be provided with supercooling tube, guarantee further cooling from the condenser fluid, but in this kind method, the low-temperature receiver of supercooling tube is the cooling water that enters from the external world, is subjected to the restriction (30 ℃ of left and right of coolant water temperature) of low-temperature receiver, the degree of supercooling of this condenser is relatively low, and heat exchange efficiency is also relatively low.Because can only being communicated with the cooling water of GB requirement, this supercooling tube can not be communicated with other coolant medias; Therefore, as new technological trend, in the middle of the application of trumpet cooler, set up at the fluid pipeline section of condenser and be equipped with board-like subcooler, utilize board-like subcooler to realize the heat exchange between the cryogenic refrigeration medium after refrigerant and throttling, further improve the degree of supercooling of condenser, so just can improve simultaneously whole unit refrigerating capacity.But the structure of this split type condenser is very complicated, and parts are various, and trouble is installed, and overall volume is larger, takes up room also larger, makes the floor space of whole central air-conditioning larger.
Complicated for solving condenser structure, the problem that dutycycle is higher, U.S. patent documents US2010/0065262Al discloses a kind of plate type heat exchanger, and it can be used as condenser and uses.The heat exchanger structure of its relative tubular type is simple, and floor space is little; But it does not make further cooling supercooling apparatus of condenser, and therefore, the condensation efficiency of this condenser can not meet the demands.And in prior art, it is also the split-type structural that connects by pipeline that this board-like condenser installs subcooler additional.Its floor space still can not satisfy the requirement of compact central air conditioner system.
Chinese patent file CN2604667Y discloses a kind of preheating, sterilization, cooling plate type heat exchanger of integrating.For solve sterilization and quick cooling employing two cover autonomous devices in prior art move simultaneously the using energy source of existence insufficient, waste water and problem that equipment investment is large.This heat exchanger is that the multi-disc plate type heat exchanger is closely connected, set up flow deflector in the centre and formed waste heat exchange area and high-temperature sterilization district, it is by pre-backing 1, sterilization sheet 4, fin 2, flow deflector 3 and high-temperature heating sheet 5 form, cold liquid is through preheating and sterilization, flows out emit heat in fin after, and high-temperature medium can be with hot water or superheated vapor, emit heat in heating plate, can fully exchange because they connect tight heat.But the interior shape of the deflector 3 in this plate type heat exchanger is parallelogram, can cause rate of flow of fluid too small during fluid process deflector 3, finally causes heat exchange efficiency lower, can not satisfy the requirement of the condenser heat exchanging efficient in central air-conditioning.
Therefore, the heat-exchange system for field of air conditioning of the prior art can't satisfy compact conformation and the high advantage of heat exchange efficiency simultaneously.
The utility model content
Therefore, the technical problems to be solved in the utility model is to provide a kind of compact conformation and the higher air-conditioning heat-exchange system of heat exchange efficiency.
For this reason, the utility model provides a kind of air-conditioning heat-exchange system, comprises compressor, and described compressor is used for providing refrigerant; Condenser, the cold-zone excessively that described condenser has condensing zone and is communicated with described condensing zone, described condensing zone is communicated with the refrigerant outlet of described compressor, be used for realizing the heat exchange of described refrigerant and cooling fluid, the described cold-zone of crossing is used for realizing to through described condensing zone condensation and through the refrigerant of electric expansion valve throttling with through described condensing zone condensation and do not pass through heat exchange between the refrigerant of electric expansion valve throttling, and will again imports in described compressor through the refrigerant entrance of the refrigerant after the electric expansion valve throttling by compressor; Barrel type heat exchanger, have inner and outer tubes, the import of described inner tube is communicated with described condensing zone, the outlet of described inner tube is communicated with the import of evaporimeter, the inflow entrance of described outer tube is communicated with evaporimeter, the flow export of described outer tube is communicated with described compressor, and described barrel type heat exchanger be used for to be realized from the liquid refrigeration medium of condenser and heat exchange from evaporimeter gaseous state refrigerant out; Evaporimeter, the evaporating area that has the overheated zone and be communicated with described overheated zone, the entrance of described overheated zone is communicated with the outlet of described inner tube, the outlet of described overheated zone is communicated with the import of described outer tube, described evaporating area be used for to realize from condensing zone and through described overheated zone and by the heat exchange of the refrigerant of the second electric expansion valve throttling and cooling fluid, and will re-enter through the refrigerant after heat exchange described overheated zone, with realize to through the cooling medium of described overheated zone with from condenser and the heat exchange that do not enter the refrigerant before the overheated zone; Described evaporating area and described overheated zone are by an overheated deflector isolation, described overheated deflector is provided with for the described refrigerant after described evaporating area heat exchange being guided to the overheated diversion groove of described overheated zone, and the area of passage of crossing the thermally induced flow interface at the sectional area of described overheated diversion groove and two ends about equally.
The sectional area of described overheated diversion groove equates with the area of passage of crossing the thermally induced flow interface at two ends.
Described condensing zone and the described cold-zone of crossing are by a cold deflector isolation of mistake, the cold deflector of described mistake is provided with for the condensed described refrigerant of described condensing zone being guided to the described cold diversion groove of mistake of crossing the cold-zone, and the area of passage of the cold water conservancy diversion interface of mistake at the sectional area of the cold diversion groove of described mistake and two ends about equally.
The sectional area of the cold diversion groove of described mistake equates with the area of passage of the cold water conservancy diversion interface of the mistake at two ends.
Described condensing zone closely is formed by connecting by a plurality of condensing heat-exchange sheets, the described cold-zone of crossing closely is formed by connecting by the cold heat exchanger fin of a plurality of mistakes, forms pod apertures and a plurality of regularly arranged heat exchange groove for the conducting heat transferring medium on the plate face of described condensing heat-exchange sheet and the cold heat exchanger fin of described mistake.
Described heat exchange groove is herringbone, and the described heat exchange groove on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone.
Described overheated zone closely is formed by connecting by a plurality of overheated heat exchanger fins, described evaporating area closely is formed by connecting by a plurality of evaporation and heat-exchange sheets, forms the first pod apertures and a plurality of the first regularly arranged heat exchange groove for the conducting heat transferring medium on the plate face of described overheated heat exchanger fin and described evaporation and heat-exchange sheet.
Described heat exchange groove is herringbone, and the described heat exchange groove on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone.
Described inner tube has at least two straight lengths and the bend loss that is connected the adjacent straight pipeline section, and described straight length is along vertical setting of described outer tube.
Described compressor is the magnetic suspension centrifuge.
Need to prove, the implication of " about equally " described in the utility model is: the sectional area of diversion groove is set to equate fully or compares to differ up and down be no more than 10% with the area of passage of the water conservancy diversion interface at two ends, and scope preferably differs up and down and is no more than 5%.
The air-conditioning heat-exchange system that the utility model provides has the following advantages:
1. the air-conditioning heat-exchange system that provides of the utility model, its condenser adopts condensation and crosses cold integrated plank frame, its condensing zone makes cold-producing medium liquefaction by realizing the heat exchange between cold-producing medium and cooling fluid, and carry out heat exchange between the liquid refrigerant after crossing cold-zone realization liquefaction and gas refrigerant, thereby make the degree of supercooling of the liquid refrigerant that flows out condenser improve; Its evaporimeter adopts the plate-type evaporator of overheated and evaporation integral, realizes heat exchange between gaseous refrigerant and sub-cooled liquid refrigerant making the cold-producing medium cooling that enters evaporating area by the overheated zone, has improved the degree of superheat of system; Barrel type heat exchanger makes the high-temperature liquid state cold-producing medium that comes from condenser and from the heat exchange of evaporimeter cryogenic gaseous cold-producing medium out, make the liquid refrigerant cooling that enters the first electric expansion valve, improved the excessively cold of system, also make the gaseous refrigerant that enters compressor heat up, thereby improved the overheated of system, and then made the refrigerating capacity of system and Energy Efficiency Ratio that improvement significantly be arranged.In addition, evaporimeter of the present utility model adopts the plate-type heat-exchange sheet to realize heat exchange, and it has increased an overheated zone, and overheated zone and evaporating area separate by a deflector, the compact conformation of whole evaporimeter is less with respect to existing split type evaporimeter floor space; Simultaneously, the sectional area of the sectional area of the diversion groove that deflector of the present utility model is offered and two end interfaces makes the flow velocity of refrigerant stable in air deflector about equally, and heat exchange efficiency improves greatly.
2. air-conditioning heat-exchange system of the present utility model, its condenser adopts plate-type heat-exchange sheet to realize heat exchange, and it has increased by one and cross the cold-zone, crosses cold-zone and condensing zone and separates by a deflector, the compact conformation of whole condenser is lower with respect to existing split type condenser floor space; Simultaneously, the sectional area of the diversion groove that deflector of the present utility model is offered equates with the sectional area of two end interfaces, makes the flow velocity of refrigerant stable in air deflector, and heat exchange efficiency is further enhanced.
3. air-conditioning heat-exchange system of the present utility model, offer a plurality of regularly arranged heat exchange grooves on heat exchanger plates and be used for flowing of heat transferring medium, this heat exchange groove is herringbone, with respect to the existing heat exchange plate that the heat exchange groove is not set, the heat exchange efficiency between heat exchanger plates of the present utility model further improves.
4. air-conditioning heat-exchange system of the present utility model, the described inner tube of described barrel type heat exchanger has at least two straight lengths and the bend loss that is connected the adjacent straight pipeline section, and described straight length is along vertical setting of described outer tube.Described inner tube has at least two straight lengths and the bend loss that is connected the adjacent straight pipeline section, described straight length is along vertical setting of described outer tube, increased the currency of fluid in inner tube, there is the outer fluid of sufficient time and inner tube to carry out heat exchange thereby make in described inner tube near tube wall with near the fluid of die section, thereby solved the inhomogeneous problem of inner tube inside heat exchange in the prior art.
Description of drawings
For content of the present utility model is more likely to be clearly understood, the below is described in further detail the utility model, wherein according to specific embodiment of the utility model also by reference to the accompanying drawings
Fig. 1 is the systematic schematic diagram of air-conditioning heat-exchange system of the present utility model;
Fig. 2 is the structural representation of the evaporimeter of air-conditioning heat-exchange system of the present utility model;
Fig. 3 is the structural representation of the condenser of air-conditioning heat-exchange system of the present utility model;
Fig. 4 is the structural representation of the barrel type heat exchanger of air-conditioning heat-exchange system of the present utility model;
Fig. 5 is the structural representation of the overheated deflector that adopts in evaporimeter of the present utility model;
Fig. 6 is the structural representation of the cold deflector of mistake that adopts in condenser of the present utility model.
In figure, Reference numeral is expressed as:
The 1-compressor; The 2-condenser; The 21-condensing zone; 22-crosses the cold-zone; 211-condensing heat-exchange sheet; 221-crosses cold heat exchanger fin; 23-crosses cold deflector; 231-crosses cold diversion groove; 232-crosses cold water conservancy diversion interface; The 2111-pod apertures; 2112-heat exchange groove; The 3-electric expansion valve; The 4-barrel type heat exchanger; The 41-inner tube; The 42-outer tube; The 411-import; The 412-outlet; The 421-inflow entrance; The 422-flow export; The 401-straight length; The 402-bend loss; The 6-evaporimeter; The 61-overheated zone; The 62-evaporating area; The overheated deflector of 63-; The overheated diversion groove of 631-; 632-crosses the thermally induced flow interface; The overheated heat exchanger fin of 611-; 621-evaporation and heat-exchange sheet; 6111-the first pod apertures; 6112-the first heat exchange groove; The A-refrigerant; The B-cooling fluid; 2a-condensing zone entrance; 2b-crosses the cold-zone outlet; 2c-crosses the cold-zone entrance; 2d-crosses cold-zone the second outlet; 6a-overheated zone entrance; The outlet of 6b-overheated zone; 6c-overheated zone the second entrance; The second outlet of 6d-overheated zone; 7-the second electric expansion valve.
The specific embodiment
The utility model provides a kind of air-conditioning heat-exchange system, and this air-conditioning heat-exchange system integrates efficient condenser 2, high-efficiency evaporator 6 and barrel type heat exchanger 4, has realized heat-exchange system compact structure and higher heat exchange efficiency.
Introduce clearly for the operation principle of air-conditioning heat-exchange system that the utility model is provided, introduce at first respectively structure and the operation principle of efficient condenser 2, high-efficiency evaporator 6 and barrel type heat exchanger 4 that the utility model provides.
Embodiment 1
as shown in Figure 3, the present embodiment provides a kind of efficient condenser 2 for the air-conditioning heat-exchange system, described condenser 2 is plate-type condenser, comprise condensing zone 21, described condensing zone 21 closely is formed by connecting by a plurality of condensing heat-exchange sheets 211, is used for realization from the heat exchange of refrigerant A and the cooling fluid B of compressor 1, cross cold-zone 22, the described cold-zone 22 of crossing closely is formed by connecting by the cold heat exchanger fin 221 of a plurality of mistakes, the described cold-zone 22 of crossing is used for realization through the A heat exchange of the refrigerant A after described condensing zone 21 and the refrigerant after electric expansion valve 3 throttlings, described condensing zone 21 is isolated by a cold deflector 23 of mistake with the described cold-zone 22 of crossing, the cold deflector 23 of described mistake is provided with for the condensed described refrigerant A of described condensing zone 21 being guided to the described cold diversion groove 231 of mistake of crossing cold-zone 22, the area of passage of the cold water conservancy diversion interface 32 of mistake at the sectional area of the cold diversion groove 231 of described mistake and two ends about equally, the flow velocity that makes refrigerant A is to cross cold deflector 23 places stable, heat exchange efficiency improves greatly.
Form the first pod apertures 2111 and a plurality of the first regularly arranged heat exchange groove 2112 for the conducting heat transferring medium on the plate face of described condensing heat-exchange sheet 211 and the cold heat exchanger fin 221 of described mistake, described the first heat exchange groove 2112 is herringbone, described the first heat exchange groove 2112 on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone, the heat exchange area of this heat exchanger plates is large, and heat exchange efficiency further improves.
Pod apertures place's employing seal gasket of adjacent described condensing heat-exchange sheet 211 and the cold heat exchanger fin 221 of described mistake is connected and sealed.
The course of work of condenser shown in Figure 3 is as follows:
cooling fluid B enters in the described condensing heat-exchange sheet 211 of described condensing zone 21 interior interval setting by end cap 8, enter in the described condensing heat-exchange sheet 211 adjacent with described cooling fluid B of described condensing zone 21 by condensing zone entrance 2a from the gaseous state refrigerant A of compressor 1 HTHP out, realize heat exchange, after heat exchange, the gaseous state refrigerant A of HTHP becomes the liquid refrigeration medium A, described liquid refrigeration medium A enters to the described cold-zone 22 of crossing through the cold water conservancy diversion interface 232 of described mistake of the cold deflector 23 of described mistake, after cross cold-zone outlet 2b and discharge through the refrigerant A of the low-temp low-pressure after electric expansion valve 3 throttlings, the refrigerant A of described low-temp low-pressure entered cold-zone 22 from crossing cold-zone entrance 2c, with come from condensing zone 21 do not carried out heat exchange by the refrigerant A of throttling, after obtaining raising, the refrigerant A self-temperature of low-temp low-pressure discharges from the second outlet 2d that crosses cold-zone 22.
As shown in Figure 2, the present embodiment provides a kind of high-efficiency evaporator for the air-conditioning heat-exchange system, described evaporimeter 6 is plate-type evaporator, described evaporimeter 6 comprises overheated zone 61 and evaporating area 62, described evaporating area 62 closely is formed by connecting by a plurality of evaporation and heat-exchange sheets 621, is used for realizing the heat exchange of refrigerant A and freezing liquid B; Described overheated zone 61 closely is formed by connecting by a plurality of overheated heat exchanger fins 611, the gaseous state refrigerant A after being used for realizing evaporating through described evaporating area 61 and the heat exchange through the liquid refrigeration medium A after condenser; Described evaporating area 62 is isolated by an overheated deflector 63 with described overheated zone 61, described overheated deflector 63 is provided with for the described gaseous state refrigerant A after described evaporating area 62 heating being guided to the overheated diversion groove 631 of described overheated zone 61, the area of passage of crossing thermally induced flow interface 632 at the sectional area of described overheated diversion groove 631 and two ends about equally, make the flow velocity of refrigerant stable in air deflector, heat exchange efficiency improves greatly.
As a kind of preferably embodiment, the sectional area of the described overheated diversion groove 631 in the present embodiment equates with the area of passage of crossing thermally induced flow interface 632 at two ends.
Form pod apertures 6111 and a plurality of regularly arranged heat exchange groove 6112 for the conducting heat transferring medium on the plate face of described evaporation and heat-exchange sheet 621 and described overheated heat exchanger fin 611, described heat exchange groove 6112 is herringbone, described heat exchange groove 6112 on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone, the heat exchange area of this heat exchanger plates is large, and heat exchange efficiency further improves.
Pod apertures place's employing seal gasket of adjacent described evaporation and heat-exchange sheet 621 and described overheated heat exchanger fin 611 is connected and sealed.
The course of work of evaporimeter shown in Figure 2 is as follows:
freezing liquid B enters on the described evaporation and heat-exchange sheet 621 of interval setting, flow in the heat exchanger channels of described the first heat exchange groove 6111 formation, after entering overheated zone 61 from the refrigerant A of condenser by overheated zone entrance 6a, flow out from overheated zone outlet 6b and enter the second electric expansion valve 7, formed the refrigerant A of low-temp low-pressure after the second electric expansion valve 7 throttlings, described refrigerant A reenters overheated zone 61 by overheated zone the second entrance 6c, and directly enter on the evaporation and heat-exchange sheet 621 adjacent with described freezing liquid B in described evaporating area 62 by overheated pod apertures 6111, carry out heat exchange with described freezing liquid B, become gaseous state refrigerant A after heat exchange, described gaseous state refrigerant A enters to described overheated zone 61 through overheated diversion groove 631 and the described thermally induced flow interface 632 of crossing of process of described overheated deflector 63 again, carry out heat exchange with the overheated zone 61 described refrigerant A before that enters from condenser, discharge finally by evaporator outlet (being overheated zone the second outlet 6d).
as shown in Figure 4, the present embodiment provides a kind of barrel type heat exchanger 4 for the air-conditioning heat-exchange system, described barrel type heat exchanger 4 has inner tube 41 and outer tube 42, the import 411 of described inner tube 41 is communicated with described condensing zone 21, the outlet 412 of described inner tube 41 is communicated with the first electric expansion valve 5, the inflow entrance 421 of described outer tube 42 is communicated with the overheated zone of evaporimeter 6 the second outlet 6d, the flow export 422 of described outer tube 42 is communicated with described compressor 1, described barrel type heat exchanger be used for to be realized from the liquid refrigeration medium A of condenser 21 and heat exchange from evaporimeter 6 gaseous state refrigerant A out.
In order to improve the uniformity of barrel type heat exchanger heat exchange, in the present embodiment, described inner tube 41 has at least two straight lengths 401 and the bend loss 402 that is connected adjacent straight pipeline section 401, and described straight length 401 is along vertical setting of described outer tube 42.
Need to prove, for realizing core purpose of the present invention, the quantity of the inner tube 41 of described barrel type heat exchanger 4 is unrestricted, can be set to one, also can be set to many.
The present embodiment provides a kind of air-conditioning heat-exchange system, and described air-conditioning heat-exchange system has adopted disclosed condenser, evaporimeter and barrel type heat exchanger in embodiment 1-3.
as shown in Figure 1, the concrete structure of this air-conditioning system is: comprise compressor 1, described compressor 1 is used for providing refrigerant A, condenser 2(sees Fig. 3), the cold-zone 22 excessively that described condenser 2 has condensing zone 21 and is communicated with described condensing zone 21, described condensing zone 21 is communicated with the refrigerant outlet of described compressor 1, be used for realizing the heat exchange of described refrigerant A and cooling fluid B, the described cold-zone 22 of crossing is used for realizing to through described condensing zone 21 condensations and through the refrigerant A of electric expansion valve 3 throttlings with through described condensing zone 21 condensations and do not pass through heat exchange between the refrigerant A of electric expansion valve 3 throttlings, and will again import in described compressor 1 by the refrigerant entrance of compressor 1 through the refrigerant A after electric expansion valve 3 throttlings, barrel type heat exchanger 4(sees Fig. 4), have inner tube 41 and outer tube 42, the import 411 of described inner tube 41 is communicated with described condensing zone 21, the outlet 412 of described inner tube 41 is communicated with the first electric expansion valve 5, the inflow entrance 421 of described outer tube 42 is communicated with evaporimeter 6, and the flow export 422 of described outer tube 42 is communicated with described compressor 1, evaporimeter 6 (seeing Fig. 2), the evaporating area 62 that has overheated zone 61 and be communicated with described overheated zone 61, the entrance of described overheated zone 61 is communicated with described the first electric expansion valve 5, the outlet of described overheated zone 61 is communicated with the import of described outer tube, described evaporating area 62 is used for realizing to from condensing zone 21 and through described overheated zone 61 and by the heat exchange of the refrigerant A of the second electric expansion valve 7 throttlings and cooling fluid B, and will re-enter through the refrigerant A after heat exchange described overheated zone 61, with realize to through the cooling medium A of described overheated zone 61 with from condenser 2 and the heat exchange that do not enter the refrigerant A before overheated zone 61, wherein, described evaporating area 61 is isolated (seeing Fig. 5) with described overheated zone 62 by an overheated deflector 63, described overheated deflector 63 is provided with for the described refrigerant A after described evaporating area 61 heat exchange being guided to the overheated diversion groove 631 of described overheated zone 62, and the area of passage of crossing thermally induced flow interface 632 at the sectional area of described overheated diversion groove 631 and two ends about equally, described condensing zone 21 is isolated (see figure 6)s with the described cold-zone 22 of crossing by a cold deflector 23 of mistake, the cold deflector 23 of described mistake is provided with for the condensed described refrigerant A of described condensing zone 21 being guided to the described cold diversion groove 231 of mistake of crossing cold-zone 22, and the area of passage of the cold water conservancy diversion interface 232 of mistake at the sectional area of the cold diversion groove 231 of described mistake and two ends about equally.
As a kind of preferably embodiment, the sectional area of the cold diversion groove 231 of described mistake equates with the area of passage of the cold water conservancy diversion interface 232 of the mistake at two ends.
Further, described condensing zone 21 closely is formed by connecting by a plurality of condensing heat-exchange sheets 211, the described cold-zone 22 of crossing closely is formed by connecting by the cold heat exchanger fin 221 of a plurality of mistakes, forms pod apertures 2111 and a plurality of regularly arranged heat exchange groove 2112 for the conducting heat transferring medium on the plate face of described condensing heat-exchange sheet 211 and the cold heat exchanger fin 221 of described mistake; Described heat exchange groove 2112 is herringbone, and the described heat exchange groove 2112 on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone.
Again further, described overheated zone 61 closely is formed by connecting by a plurality of overheated heat exchanger fins 611, described evaporating area 62 closely is formed by connecting by a plurality of evaporation and heat-exchange sheets 621, forms the first pod apertures 6111 and a plurality of the first regularly arranged heat exchange groove 6112 for the conducting heat transferring medium on the plate face of described overheated heat exchanger fin 611 and described evaporation and heat-exchange sheet 621; Described heat exchange groove 6112 is herringbone, and the described heat exchange groove 6112 on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone.
In order further to utilize from the heat of described condenser 2 outlets refrigerant out, high efficient heat exchanging system in the present embodiment also comprises reflux line, described reflux line connects the 2b outlet and described compressor 1 of described condenser 2, is used for realizing cooling to compressor 1 of condensate liquid.
In the present embodiment, described compressor is the magnetic suspension centrifuge.
Need to prove, the implication of " about equally " described in the present embodiment is: the sectional area of diversion groove is set to equate fully or compares to differ up and down be no more than 5% with the area of passage of the water conservancy diversion interface at two ends.
The course of work of the air-conditioning heat-exchange system that the present embodiment provides is as follows:
compressor 1 is discharged the gaseous state refrigerant A that the gaseous state refrigerant A of low-temp low-pressure is collapsed into HTHP from compressor outlet, the gaseous state refrigerant of HTHP enters by condensing zone entrance 2a in the condensing heat-exchange sheet 211 that the interval of the condensing zone 211 of condenser 2 arranges, meanwhile, cooling fluid B enters in described condensing heat-exchange sheet 211 adjacent with described refrigerant A in described condensing zone 21, realizes heat exchange, after heat exchange, the gaseous state refrigerant A of HTHP becomes the liquid refrigeration medium A, after becoming the liquid refrigeration medium A, it is divided into two-way, one tunnel described liquid refrigeration medium A enters to the described cold-zone 22 of crossing through the cold water conservancy diversion interface 232 of described mistake of the cold deflector 23 of described mistake, after discharging, cold-zone outlet 2b enters electric expansion valve 3 from crossing, become the liquid refrigerant A of low-temp low-pressure after electric expansion valve 3 throttlings, the liquid refrigerant A of low-temp low-pressure reentered in cold-zone 22 from crossing cold-zone entrance 2c, do not carry out heat exchange with the refrigerant A after process electric expansion valve 3 throttlings that come from condensing zone 21, after heat exchange, after being raise, itself temperature becomes gaseous state refrigerant A, after gaseous state refrigerant A discharges from the second outlet 2d that crosses cold-zone 22, again clamp-on the interior confession of compressor 1 recycles from the suction port of compressor, the described liquid refrigeration medium A in another road from cross cold-zone 22 cross cold-zone outlet 2b out afterwards the import 411 of the inner tube 41 by barrel type heat exchanger 4 enter in inner tube 41, and after thereby the outlet 412 by inner tube 41 enters overheated zone entrance 6a and enters overheated zone 61, flow out from overheated zone outlet 6b and enter the second electric expansion valve 7, become again the refrigerant A of low-temp low-pressure through the second electric expansion valve 7 throttlings, described refrigerant A directly enters on the evaporation and heat-exchange sheet 621 that in described evaporating area 62, the interval arranges by the overheated pod apertures 6111 of described refrigerant, meanwhile, freezing liquid B enters on the interior heat exchanger fin adjacent with evaporation and heat-exchange sheet 621 of described evaporating area 62, and flow in the heat exchanger channels of described the first heat exchange groove 6111 formation, carry out heat exchange with the refrigerant A of low-temp low-pressure, after heat exchange, the liquid refrigeration medium A of low-temp low-pressure becomes the gaseous state refrigerant, described gaseous state refrigerant A enters to described overheated zone 61 through the described thermally induced flow interface 632 of crossing of described overheated deflector 63 again, carry out heat exchange with the overheated zone 61 liquid refrigeration medium A before that enters from condenser, make the temperature of the liquid refrigeration medium that is about to enter evaporating area 62 reduce, improved the evaporability of evaporating area 62, the second outlet 6d discharges described gaseous state refrigerant A through the overheated zone, the gaseous state refrigerant A that the second outlet 6d discharges from the overheated zone enters described barrel type heat exchanger 4 from described outer tube inflow entrance 421, carry out heat exchange with the liquid refrigerant of the HTHP that comes from condenser 2 that is positioned at inner tube 41, thereby make the refrigerant A temperature before the second electric expansion valve throttling be further reduced, the temperature of himself is enhanced, and is again clamp-oned at last the interior confession of compressor 1 and recycles.
Obviously, above-described embodiment is only for example clearly is described, and is not the restriction to embodiment.For those of ordinary skill in the field, can also make other changes in different forms on the basis of the above description.Here need not also can't give all embodiments exhaustive.And the apparent variation of being extended out thus or the change still be in protection domain of the present utility model within.
Claims (10)
1. an air-conditioning heat-exchange system, comprise
Compressor (1), described compressor (1) is used for providing refrigerant (A);
condenser (2), the cold-zone (22) excessively that described condenser (2) has condensing zone (21) and is communicated with described condensing zone (21), described condensing zone (21) is communicated with the refrigerant outlet of described compressor (1), be used for realizing the heat exchange of described refrigerant (A) and cooling fluid (B), the described cold-zone (22) of crossing is used for realizing to through (21) condensation of described condensing zone and through the refrigerant (A) of electric expansion valve (3) throttling with through (21) condensation of described condensing zone and do not pass through heat exchange between the refrigerant (A) of electric expansion valve (3) throttling, and will again import in described compressor (1) through the refrigerant entrance of the refrigerant (A) after electric expansion valve (3) throttling by compressor (1),
barrel type heat exchanger (4), have inner tube (41) and outer tube (42), the import (411) of described inner tube (41) is communicated with the outlet of described condensing zone (21), the outlet (412) of described inner tube (41) is communicated with the import of evaporimeter (6), the inflow entrance (421) of described outer tube (42) is communicated with the outlet of evaporimeter (6), the flow export (422) of described outer tube (42) is communicated with described compressor (1), described barrel type heat exchanger be used for to be realized from the liquid refrigeration medium (A) of condenser (21) and heat exchange from evaporimeter (6) gaseous state refrigerant (A) out,
evaporimeter (6), the evaporating area (62) that has overheated zone (61) and be communicated with described overheated zone (61), the entrance of described overheated zone (61) is communicated with the outlet (412) of described inner tube (41), the outlet of described overheated zone (61) is communicated with the import of described outer tube, described evaporating area (62) be used for to realize from condensing zone (21) and through described overheated zone (61) and by the heat exchange of the refrigerant (A) of the second electric expansion valve (7) throttling with cooling fluid (B), and will re-enter described overheated zone (61) through the refrigerant after heat exchange (A), with realize to through the cooling medium (A) of described overheated zone (61) with from condenser (2) and the heat exchange that do not enter overheated zone (61) refrigerant (A) before,
It is characterized in that: described evaporating area (61) is isolated by an overheated deflector (63) with described overheated zone (62), described overheated deflector (63) is provided with for the described refrigerant (A) after described evaporating area (61) heat exchange being guided to the overheated diversion groove (631) of described overheated zone (62), and the area of passage of crossing thermally induced flow interface (632) at the sectional area of described overheated diversion groove (631) and two ends about equally.
2. air-conditioning heat-exchange system according to claim 1 is characterized in that: the sectional area of described overheated diversion groove (631) equates with the area of passage of crossing thermally induced flow interface (632) at two ends.
3. air-conditioning heat-exchange system according to claim 2, it is characterized in that: described condensing zone (21) is isolated by a cold deflector of mistake (23) with the described cold-zone (22) of crossing, the cold deflector of described mistake (23) is provided with for the condensed described refrigerant of described condensing zone (21) (A) being guided to the described cold diversion groove of mistake (231) of crossing cold-zone (22), and the area of passage of the sectional area of the cold diversion groove of described mistake (231) and the cold water conservancy diversion interface of the mistake at two ends (232) about equally.
4. the described air-conditioning heat-exchange system of any one according to claim 1-3, it is characterized in that: the sectional area of the cold diversion groove of described mistake (231) equates with the area of passage of the cold water conservancy diversion interface of the mistake at two ends (232).
5. air-conditioning heat-exchange system according to claim 4, it is characterized in that: described condensing zone (21) closely is formed by connecting by a plurality of condensing heat-exchange sheets (211), the described cold-zone (22) of crossing closely is formed by connecting by the cold heat exchanger fin of a plurality of mistakes (221), forms pod apertures (2111) and a plurality of regularly arranged heat exchange groove (2112) for the conducting heat transferring medium on the plate face of described condensing heat-exchange sheet (211) and the cold heat exchanger fin of described mistake (221).
6. air-conditioning heat-exchange system according to claim 5, it is characterized in that: described heat exchange groove (2112) is herringbone, and the described heat exchange groove (2112) on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone.
7. air-conditioning heat-exchange system according to claim 6, it is characterized in that: described overheated zone (61) closely are formed by connecting by a plurality of overheated heat exchanger fins (611), described evaporating area (62) closely is formed by connecting by a plurality of evaporation and heat-exchange sheets (621), forms the first pod apertures (6111) and a plurality of the first regularly arranged heat exchange groove (6112) for the conducting heat transferring medium on the plate face of described overheated heat exchanger fin (611) and described evaporation and heat-exchange sheet (621).
8. air-conditioning heat-exchange system according to claim 7, it is characterized in that: described heat exchange groove (6112) is herringbone, and the described heat exchange groove (6112) on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone.
9. air-conditioning heat-exchange system according to claim 8, it is characterized in that: described inner tube (41) has at least two straight lengths (401) and the bend loss that is connected adjacent straight pipeline section (401) (402), and described straight length (401) is along vertical setting of described outer tube (42).
10. air-conditioning heat-exchange system according to claim 9, it is characterized in that: described compressor (1) is the magnetic suspension centrifuge.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220651840.0U CN202928178U (en) | 2012-11-30 | 2012-11-30 | Heat exchanging system for air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220651840.0U CN202928178U (en) | 2012-11-30 | 2012-11-30 | Heat exchanging system for air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202928178U true CN202928178U (en) | 2013-05-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201220651840.0U Expired - Fee Related CN202928178U (en) | 2012-11-30 | 2012-11-30 | Heat exchanging system for air conditioner |
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| Country | Link |
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| CN (1) | CN202928178U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103851812A (en) * | 2012-11-30 | 2014-06-11 | 苏州必信空调有限公司 | Air-conditioning heat exchange system |
| CN109140831A (en) * | 2018-07-17 | 2019-01-04 | 江苏中关村科技产业园节能环保研究有限公司 | A kind of integrated plate heat exchanger of air conditioning for automobiles |
-
2012
- 2012-11-30 CN CN201220651840.0U patent/CN202928178U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103851812A (en) * | 2012-11-30 | 2014-06-11 | 苏州必信空调有限公司 | Air-conditioning heat exchange system |
| CN103851812B (en) * | 2012-11-30 | 2016-08-03 | 苏州必信空调有限公司 | A kind of air conditioner heat exchange system |
| CN109140831A (en) * | 2018-07-17 | 2019-01-04 | 江苏中关村科技产业园节能环保研究有限公司 | A kind of integrated plate heat exchanger of air conditioning for automobiles |
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Granted publication date: 20130508 Termination date: 20171130 |