CN202928225U - Plate-type integrated refrigerant thermal recovery circulation system - Google Patents
Plate-type integrated refrigerant thermal recovery circulation system Download PDFInfo
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- CN202928225U CN202928225U CN201220651762.4U CN201220651762U CN202928225U CN 202928225 U CN202928225 U CN 202928225U CN 201220651762 U CN201220651762 U CN 201220651762U CN 202928225 U CN202928225 U CN 202928225U
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Abstract
The utility model relates to a plate-type integrated refrigerant thermal recovery circulation system , which comprises a compressor (1), a condensing device and an evaporation device which are sequentially connected. The condensing device comprises a plate-type condenser (2) and a second expansion valve (7). The plate-type condenser (2) is of a structure with a condensing area (2a) and a supercooling area (2b) which are integrally molded. The condensing area (2a) and the supercooling area (2b) are isolated from each other through a first guide plate (8). The first guide plate (8) is provided with a first guide groove (9) which is used for guiding refrigerant to the supercooling area (2b). The cross section area of the first guide groove (9) is basically equal to the open area of first guide interfaces (10) at two ends. The evaporator is a plate-type evaporator (4) with an evaporation area (4a) and a superheating area (4b) which are integrally molded. Through the arrangement, the duty cycle of the entire refrigeration system is small and the heat recovery efficiency is high.
Description
Technical field
The utility model relates to field of refrigeration, specifically a kind of board-like integration system cryogen heat-recovery circulating system for handpiece Water Chilling Units.
Background technology
Refrigeration system is by cold-producing medium and four large parts, i.e. compressor, and condenser, expansion valve, evaporimeter forms.The refrigeration principle of general refrigeration machine is by compressor, the lower vapour pressure of pressure to be shortened into the higher steam of pressure, the volume of steam is reduced, pressure raises, compressor sucks the working substance steam from evaporimeter lower pressure out, make it to send into condenser after pressure raises, be condensed into the higher liquid of pressure in condenser, after the choke valve throttling, after becoming the lower liquid of pressure, send into evaporimeter, heat absorption is evaporated and is become the lower steam of pressure in evaporimeter, then sends into the entrance of compressor, thereby completes kind of refrigeration cycle.Cold-producing medium constantly circulates in refrigerant-cycle systems, state variation occurs and carry out exchange heat with the external world.In board-like integration system cryogen heat-recovery circulating system, adopt heat exchanger can improve significantly cooling system amount and Energy Efficiency Ratio, thereby be the energy-conservation parts that often adopt.what often adopt in prior art is the board-like integration system cryogen heat-recovery circulating system with heat exchanger, the circulation process that its cold-producing medium is general is: from condenser high pressure refrigerant liquid out, flow to heat exchanger entrance punishment and be two-way, one the tunnel directly enters heat exchanger, another road choke valve of flowing through enters heat exchanger after by step-down again, and absorb the heat of bypass refrigerant liquid in heat exchanger, get back to the middle air entry of compressor after being evaporated to gas, and directly enter one road refrigerant liquid of heat exchanger, siphon away heat and produced cold because being bypassed cold-producing medium, again through entering evaporimeter after the choke valve step-down, enter compressor low pressure air suction mouth after being evaporated to gas, enter condenser through after compressor compresses, emit condensation heat when being condensed into highly pressurised liquid, and continue above-mentioned circulation.
Yet, increasing the volume that heat exchanger will certainly increase whole refrigeration system in the refrigeration system of the prior art, dutycycle increases, and so not only can increase manufacturing cost, nor is beneficial to the installation and debugging of refrigeration plant.
Complicated for solving existing refrigerant system configurations, the problem that dutycycle is high, U.S. patent documents US2010/0065262Al discloses a kind of plate type heat exchanger, and it can be used as condenser and uses.Its relatively existing pipe heat exchanger is simple in structure, and floor space is little; But it does not make further cooling cooling device of condenser, and therefore, the thermal effect excessively of this evaporimeter 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 evaporimeter heat exchanging efficient in central air-conditioning.
The utility model content
For this reason, technical problem to be solved in the utility model is that the cold-producing medium heat-recovery circulating system increase heat exchanger of prior art can increase the volume of refrigeration system, increase dutycycle, complex structure, the problem that effectiveness of regenerator is low provides a kind of board-like integration system cryogen heat-recovery circulating system that dutycycle is little, effectiveness of regenerator is high that has.
for solving the problems of the technologies described above, the utility model is a kind of board-like integration system cryogen heat-recovery circulating system, comprise the compressor that is in turn connected into the loop, condensing unit, vaporising device, described condensing unit comprises plate-type condenser and the second expansion valve, described plate-type condenser comprises condensing zone, to be condensed into liquid refrigerant from the gaseous refrigerant in described compressor, the condensing heat-exchange sheet is stacked is formed by connecting by several for described condensing zone, has the first refrigerant inlet that is connected with the gas outlet end of described compressor on it, and the first refrigerant outlet of the liquid refrigerant of the described condensing zone outflow of process, cross the cold-zone, the described cold-zone of crossing is crossed by several that cold heat exchanger fin is stacked to be formed by connecting, describedly cross that the cold-zone has the second refrigerant entrance that is connected with described the first refrigerant outlet and the second refrigerant that is connected with the air entry end at described compressor middle part exports, and be connected with described the second expansion valve between described the first refrigerant outlet and described second refrigerant entrance, described cold-zone excessively is used for will be by the liquid refrigerant after the second expansion valve throttling and the described gaseous refrigerant heat exchange of crossing the cold-zone of described the first refrigerant outlet outflow, the first deflector, be arranged on described condensing zone and described the mistake between the cold-zone, be used for isolating described condensing zone and the described cold-zone of crossing, described the first deflector is provided with for the condensed cold-producing medium of described condensing zone being guided to described the first diversion groove of crossing the cold-zone, and the area of passage of the first water conservancy diversion interface at the sectional area of described the first diversion groove and two ends about equally, described vaporising device comprises plate-type evaporator and the first expansion valve, and described plate-type evaporator comprises evaporating area, is used for the cold-producing medium evaporation, and described evaporating area is by stacked being formed by connecting of a plurality of evaporation and heat-exchange sheets, the liquid refrigerant that the gaseous refrigerant that the described evaporating area that is used for the overheated zone flows out and described plate-type condenser flow out carries out heat exchange, described overheated zone is by stacked being formed by connecting of a plurality of overheated heat exchanger fins, described overheated zone has the 3rd refrigerant inlet, the 3rd refrigerant outlet, the 4th refrigerant inlet and the 4th refrigerant outlet, wherein, described the 3rd refrigerant inlet is connected with described first refrigerant outlet of described plate-type condenser, described the 3rd refrigerant outlet is connected with described the 4th refrigerant inlet by the first expansion valve, described the 4th refrigerant outlet is connected with the air entry end of described compressor.
The area difference of the area of passage of the sectional area of described the first diversion groove and described water conservancy diversion interface is no more than 10%.
Described compressor is magnetic suspension centrifuge or centrifuge.
Form the first pod apertures and a plurality of the first regularly arranged heat exchange groove for the described cold-producing medium of conducting on the plate face of described condensing heat-exchange sheet and the cold heat exchanger fin of described mistake.
Described the first heat exchange groove is herringbone, and adjacent described the first heat exchange groove is positive herringbone and the setting of falling the herringbone.
Described first pod apertures place's employing seal gasket of adjacent described condensing heat-exchange sheet and the cold heat exchanger fin of described mistake is connected and sealed.
The two ends of described plate-type condenser arrange the first heat exchange end cap.
Enter into the air entry end at described compressor middle part behind the described cold-zone excessively of described cold-producing medium process, tonifying Qi increases enthalpy to compressor.
Described evaporating area and described overheated zone are by the second deflector isolation, described the second deflector is provided with for the cold-producing medium after described evaporating area heating being guided to the second diversion groove of described overheated zone, and the area of passage of the second water conservancy diversion interface at the sectional area of described the second diversion groove and two ends about equally.
The area difference of the area of passage of the sectional area of described the second diversion groove and described the second water conservancy diversion interface is no more than 10%.
Form the second pod apertures and a plurality of the second regularly arranged heat exchange groove for the conducting cold-producing medium on the plate face of described evaporation and heat-exchange sheet and described overheated heat exchanger fin.
Described the second heat exchange groove is herringbone, and described the second heat exchange groove on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone.
The two ends of described plate-type condenser arrange the second heat exchange end cap.
The described cold-producing medium that enters the low-temp low-pressure that forms after described first expansion valve of cold-producing medium process of described overheated zone directly is circulated in described evaporating area and carries out heat exchange with freezing liquid.
Technique scheme of the present utility model has the following advantages compared to existing technology:
1, board-like integration system cryogen heat-recovery circulating system of the present utility model, it condenser that comprises is condensing zone and crosses the integrated plate-type condenser in cold-zone, the refrigerant liquid of the HTHP that compressor flows out flows into the condensing zone of flowing through after plate-type condenser and is condensed into and entered the cold-zone after liquid refrigerant and carry out heat exchange and make the liquid refrigerant temperature of high normal pressure and temperature further reduce, thereby realize entering the excessively cold of high normal pressure and temperature refrigerant liquid before expansion valve, refrigerating capacity and the Energy Efficiency Ratio of refrigeration system have been improved, the refrigerant liquid of the high pressure low temperature that flows out from condenser flows into plate-type evaporator flow through overheated zone and be evaporated to the refrigerant gas of low-pressure low-temperature in evaporating area, the refrigerant gas of this this low-temp low-pressure of low-pressure low-temperature is back to the backheat district and carries out heat exchange with the refrigerant liquid of cryogenic high pressure, make the refrigerant liquid release heat of cryogenic high pressure reduce temperature, itself absorbs heat rising temperature and flows out into compressor from evaporimeter, thereby the effective recycling of realization to the self heat of the cryogenic high pressure refrigerant liquid of condenser outflow, further improve the Energy Efficiency Ratio of cold-producing medium, simultaneously, due to the setting that all is formed in one of condenser and evaporimeter, take up room lower with respect to existing split type condenser and evaporimeter, and the diversion groove offered of deflector two end interface sectional areas corresponding with it are about equally separately for condenser of the present utility model and evaporimeter, make the flow velocity of cold-producing medium stable in air deflector, heat exchange efficiency improves greatly.
2, cold-producing medium of the present utility model carries out heat exchange from the cold-zone of crossing that enters described plate-type condenser after compressor flows out, make the gaseous refrigerant that produces in heat transfer process enter the air entry end at compressor middle part, there is tonifying Qi to increase the effect of enthalpy to compressor, improved the refrigerating capacity of whole refrigeration system when reducing the compressor power consumption.
3, a plurality of regularly arranged heat exchange groove of offering on plate-type condenser of the present utility model and plate-type evaporator, be used for flowing of heat transfer process cold-producing medium, with respect to the heat exchange plate of heat exchange groove is not set in prior art, the heat exchange efficiency between heat exchanger plates of the present utility model further improves.
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 structural principle schematic diagram of board-like integration system cryogen heat-recovery circulating system of the present utility model
Fig. 2 is the structural representation of plate-type condenser of the present utility model;
Fig. 3 is the perspective view of described the first deflector of the present utility model;
Fig. 4 is the structural representation of plate-type evaporator of the present utility model;
Fig. 5 is the perspective view of described the second deflector of the present utility model.
in figure, Reference numeral is expressed as: the 1-compressor, the 2-plate-type condenser, the 4-plate-type evaporator, 5-condensing heat-exchange sheet, 6-crosses cold heat exchanger fin, 7-the second expansion valve, 8-the first deflector, 9-the first diversion groove, 10-the first water conservancy diversion interface, 11-evaporation and heat-exchange sheet, the overheated heat exchanger fin of 12-, 13-the first expansion valve, 14-the first pod apertures, 15-the first heat exchange groove, 16-the first heat exchange end cap, 17-the second deflector, 18-the second diversion groove, 19-the second water conservancy diversion interface, 20-the second pod apertures, 21-the second heat exchange groove, 22-the second heat exchange end cap, the import of 23-freezing liquid, the outlet of 24-freezing liquid, the 2a-condensing zone, 2b-crosses the cold-zone, the 4a-evaporating area, the 4b-overheated zone, 201-the first refrigerant inlet, the outlet of 202-second refrigerant, 203-second refrigerant entrance, 204-the first refrigerant outlet, 401-the 3rd refrigerant inlet, 402-the 3rd refrigerant outlet, 403-the 4th refrigerant inlet, 404-the 4th refrigerant outlet.
The specific embodiment
Below in conjunction with accompanying drawing, the specific embodiment of the present utility model is elaborated.Should be understood that, the specific embodiment described herein only is used for description and interpretation the utility model, is not limited to the utility model.
As Fig. 1, Fig. 3 and shown in Figure 5, the board-like integration system cryogen heat-recovery circulating system that the specific embodiment of the present utility model provides comprises compressor 1, condensing unit and the vaporising device that connects successively,
Wherein:
described condensing unit comprises plate-type condenser 2 and the second expansion valve 7, described plate-type condenser 2 comprise for realize will be from the condensing zone 2a of the gaseous refrigerant of described compressor 1 and cooling fluid heat exchange and be used for realizing through the cold-producing medium after described condensing zone 2a and cold-producing medium heat exchange after the second expansion valve 7 throttlings cold-zone 2b, described condensing zone 2a and the described cold-zone 2b that crosses are by the first deflector 8 isolation, described the first deflector 8 is provided with for the first diversion groove 9 that the condensed cold-producing medium of described condensing zone 2a is guided to the described cold-zone 2b of mistake, the area of passage of the first water conservancy diversion interface 10 at the sectional area of described the first diversion groove 9 and two ends about equally, so that the flow velocity of cold-producing medium is stable in air deflector, heat exchange efficiency improves greatly.described vaporising device comprises plate-type evaporator 4 and the first expansion valve 13, described plate-type evaporator 4 comprises for the evaporating area 4a of cold-producing medium evaporation and is used for the overheated zone 4b that refrigerant gas that described evaporating area 4a flows out and the refrigerant liquid of described condenser outflow carry out backheat, described evaporating area 4a and described overheated zone 4b are by the second deflector 17 isolation, described the second deflector 17 is provided with for the cold-producing medium after described evaporating area 4a heating being guided to the second diversion groove 18 of described overheated zone 4b, the area of passage of the second water conservancy diversion interface 19 at the sectional area of described the second diversion groove 18 and two ends about equally, so that the flow velocity of cold-producing medium is more stable at described the second deflector 17 places, heat exchange efficiency further improves.
Need to prove, the area of passage of the described first water conservancy diversion interface 10 at the sectional area of described the first diversion groove 9 and two ends refers to that about equally the area of passage of the described first water conservancy diversion interface 10 at the sectional area of described diversion groove 9 and two ends can have the difference of certain limit, and the difference of this certain limit should not exert an influence or produce very slight impact the flow through stability of described the first deflector 8 flow velocitys of cold-producing medium.The area of passage of the described second water conservancy diversion interface 19 at the sectional area of described the second diversion groove 18 and two ends refers to that about equally the area of passage of the described second water conservancy diversion interface 19 at the sectional area of described the second diversion groove 18 and two ends can have the difference of certain limit, and the difference of this certain limit should not exert an influence or produce very slight impact the flow through stability of described the second deflector 17 flow velocitys of cold-producing medium.
Preferably, the area difference of the area of passage of the sectional area of the area difference of the area of passage of the sectional area of described the first diversion groove 9 and described the first water conservancy diversion interface 10 and described the second diversion groove 18 and described the second water conservancy diversion interface 19 is no more than 10%, be preferably 5%, more preferably, the sectional area of described the first diversion groove 9 is identical with the area of passage of described the first water conservancy diversion interface 10, and the sectional area of described the second diversion groove 18 is identical with the area of the area of passage of described the second water conservancy diversion interface 19.
In the present embodiment, described cold-producing medium is freon, and described freezing liquid is the associated medias such as water, salt solution, and described compressor is magnetic suspension centrifuge or centrifugal compressor, is preferably the magnetic suspension centrifuge, is not restricted at this particular type to compressor.
as Fig. 2, shown in Figure 4, described condensing zone 2a closely is formed by connecting by several condensing heat-exchange sheets 5, the described cold-zone 2b that crosses closely is formed by connecting by the cold heat exchanger fin 6 of a plurality of mistakes, form the first pod apertures 14 and a plurality of the first regularly arranged heat exchange groove 15 for the described cold-producing medium of conducting on the plate face of described condensing heat-exchange sheet 5 and the cold heat exchanger fin 6 of described mistake, described the first heat exchange groove 15 is herringbone, adjacent described the first heat exchange groove 15 is positive herringbone and the setting of falling the herringbone, described evaporating area 4a closely is formed by connecting by a plurality of evaporation and heat-exchange sheets 11, described overheated zone 4b closely is formed by connecting by several overheated heat exchanger fins 12, form the second pod apertures 20 and a plurality of the second regularly arranged heat exchange groove 21 for the conducting cold-producing medium on the plate face of described evaporation and heat-exchange sheet 11 and described overheated heat exchanger fin 12, described the second heat exchange groove 21 is herringbone, described the second heat exchange groove 21 on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone.This kind is arranged so that the heat exchange area of the heat exchanger plates in described plate-type condenser and plate-type evaporator increases, and heat exchange efficiency further improves.
In addition, described second pod apertures 20 places of described first pod apertures 14 of adjacent described condensing heat-exchange sheet 5 and the cold heat exchanger fin 6 of described mistake and adjacent described evaporation and heat-exchange sheet 11 and described overheated heat exchanger fin 12 adopt seal gasket to be connected and sealed.
In addition, the end of described plate-type condenser 2 is respectively arranged with the first heat exchange end cap 16, is welded to connect between described condensing heat-exchange sheet 5, the cold heat exchanger fin 6 of mistake and described the first deflector 8.The end of described plate-type evaporator 4 is respectively arranged with the second heat exchange end cap 22, is welded to connect between described evaporation and heat-exchange sheet 11, overheated heat exchanger fin 12 and described the second deflector 17.Form on the cold heat exchanger fin 6 of described mistake and described the first deflector 8 for described the first pod apertures 14 that cold-producing medium is guided to the described cold-zone 2b of mistake, between adjacent described the first pod apertures 14, seal washer is set, is used for described the first pod apertures 14 isolated with the described first heat exchange groove 15 of the cold heat exchanger fin 6 of described mistake.Form on described overheated heat exchanger fin 12 and described the second deflector 17 for described the second pod apertures 20 that cold-producing medium is guided to described evaporating area 4a, between adjacent described the second pod apertures 20, seal washer is set, is used for described the second pod apertures 20 isolated with the described second heat exchange groove 21 of described overheated heat exchanger fin 12.
be provided with the first refrigerant inlet 201 that flows into for cold-producing medium on described the first heat exchange end cap 16 of described condensing zone 2a and be used for freezing liquid import 23 and the freezing liquid outlet 24 that described freezing liquid flows into and flows out, be positioned at described condensing zone 2a for the pipe passage that is communicated with described freezing liquid import 23 and described freezing liquid outlet 24 inner, be provided with the described second refrigerant entrance 203 that flows into and flow out for cold-producing medium on described the first heat exchange end cap 16 of the described cold-zone 2b of mistake, described the first refrigerant outlet 202 and the outlet of described second refrigerant, 204, be positioned at the inside of the described cold-zone 2b of mistake for the pipe passage that is communicated with described second refrigerant entrance 203 and described second refrigerant outlet 204.
Be provided with the first refrigerant inlet 401 and the first refrigerant outlet 402 that flow into and flow out for cold-producing medium on described the second heat exchange end cap 22 of described overheated zone 4b, and again flow into and the second refrigerant entrance 403 that again flows out and second refrigerant outlet 404 for cold-producing medium.The pipe passage that is used for being communicated with described the first refrigerant inlet 401 and described the first refrigerant outlet 402 is positioned at the inside of described overheated zone 4b, and the pipe passage that is used for being communicated with described second refrigerant entrance 403 and described second refrigerant outlet 404 is positioned at described overheated zone 11 and described evaporating area 12 inside.
Described the first refrigerant outlet 201 is connected with described the 3rd refrigerant inlet 401.
The following circulation process that cold-producing medium in the board-like integration system cryogen heat-recovery circulating system that detailed the utility model specific embodiment provides is described according to above-mentioned structure.The flow direction of cold-producing medium is as shown in arrow in Fig. 1 or Fig. 2.
as shown in Figure 1, described compressor 1 sucks the refrigerant gas of low-pressure low-temperature, to be delivered in described condensing zone 2a by described first refrigerant inlet 201 of described plate-type condenser 2 after the refrigerant gas of its boil down to HTHP, the refrigerant gas of HTHP carries out with the cooling fluid that the outside flows into the refrigerant liquid that heat exchange is condensed into high-temperature pressure in described condensing zone 2a, be divided into afterwards two-way, one the road flows out from described the first refrigerant inlet 202 liquid refrigerant that becomes low-pressure low-temperature after described the second expansion valve 7 throttlings carries out heat exchange by the gaseous refrigerant that described second refrigerant entrance 203 enters the described cold-zone 2b of mistake and HTHP before again, the cold-producing medium of HTHP is lowered the temperature again, be that air entry end that gaseous refrigerant enters described compressor 1 middle part increases gas to it and mends enthalpy and itself also obtain heat of vaporization, described the 3rd refrigerant inlet 401 of another route enters into the overheated zone 4b of described plate-type evaporator 4, then again enter described overheated zone 4b from described the 4th refrigerant inlet 403 flow out the cold-producing medium through becoming low-pressure low-temperature after described the first expansion valve 13 throttlings from described the 3rd refrigerant outlet 402 after, then entering described evaporating area 4a and the outside cooling fluid that flows into carries out the liquid refrigerant that the heat exchange evaporation forms reflux after gaseous refrigerant described overheated zone 4b and before low-pressure low-temperature and carries out heat exchange, enter afterwards the air entry end of described compressor 1 from described the 4th refrigerant outlet 404, make the gaseous refrigerant temperature that enters described compressor 1 reduce, reduced the power consumption of compressor, refrigerating capacity and the Energy Efficiency Ratio of whole refrigeration system have been improved.
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 change still are among the protection domain of the utility model creation.
Claims (14)
1. a board-like integration system cryogen heat-recovery circulating system, comprise the compressor (1), condensing unit and the vaporising device that are in turn connected into the loop,
It is characterized in that:
Described condensing unit comprises plate-type condenser (2) and the second expansion valve (7), and described plate-type condenser (2) comprises
Condensing zone (2a), to be condensed into liquid refrigerant from the gaseous refrigerant in described compressor (1), described condensing zone (2a) is by stacked being formed by connecting of several condensing heat-exchange sheets (5), have the first refrigerant inlet (201) that is connected with the gas outlet end of described compressor (1) on it, and with flow out first refrigerant outlet (202) of liquid refrigerant through described condensing zone (2a);
cross cold-zone (2b), stacked being formed by connecting of cold heat exchanger fin (6) crossed by several in the described cold-zone (2b) of crossing, , the described cold-zone (2b) of crossing has the second refrigerant entrance (203) that is connected with described the first refrigerant outlet (202), and the second refrigerant outlet (204) that is connected with the air entry end at described compressor (1) middle part, and be connected with described the second expansion valve (7) between described the first refrigerant outlet (202) and described second refrigerant entrance (203), described cold-zone (2b) excessively is used for will be by the liquid refrigerant after the second expansion valve (7) throttling and the described gaseous refrigerant heat exchange of crossing cold-zone (2b) of described the first refrigerant outlet (202) outflow,
The first deflector (8), be arranged on described condensing zone (2a) and described the mistake between cold-zone (2b), be used for isolating described condensing zone (2a) and the described cold-zone (2b) of crossing, described the first deflector (8) is provided with for the condensed cold-producing medium of described condensing zone (2a) being guided to described the first diversion groove (9) of crossing cold-zone (2b), and the area of passage of the first water conservancy diversion interface (10) at the sectional area of described the first diversion groove (9) and two ends about equally;
Described vaporising device comprises plate-type evaporator (4) and the first expansion valve (13), and described plate-type evaporator (4) comprises
Evaporating area (4a) is used for the cold-producing medium evaporation, and described evaporating area (4a) is by stacked being formed by connecting of a plurality of evaporation and heat-exchange sheets (11);
the liquid refrigerant that the gaseous refrigerant that the described evaporating area (4a) that is used for overheated zone (4b) flows out and described plate-type condenser (2) flow out carries out heat exchange, described overheated zone (4b) is by stacked being formed by connecting of a plurality of overheated heat exchanger fins (12), described overheated zone (4b) has the 3rd refrigerant inlet (401), the 3rd refrigerant outlet (402), the 4th refrigerant inlet (403) and the 4th refrigerant outlet (404), wherein, described the 3rd refrigerant inlet (401) is connected with described first refrigerant outlet (202) of described plate-type condenser, described the 3rd refrigerant outlet (402) is connected with described the 4th refrigerant inlet (403) by described the first expansion valve (13), described the 4th refrigerant outlet (404) is connected with the air entry end of described compressor (1).
2. board-like integration system cryogen heat-recovery circulating system according to claim 1, it is characterized in that: the area difference of the area of passage of the sectional area of described the first diversion groove (9) and described water conservancy diversion interface (10) is no more than 10%.
3. board-like integration system cryogen heat-recovery circulating system according to claim 2, it is characterized in that: described compressor (1) is the magnetic suspension centrifuge.
4. board-like integration system cryogen heat-recovery circulating system according to claim 3, is characterized in that: form the first pod apertures (14) and a plurality of the first regularly arranged heat exchange groove (15) for the described cold-producing medium of conducting on the plate face of described condensing heat-exchange sheet (5) and the cold heat exchanger fin of described mistake (6).
5. board-like integration system cryogen heat-recovery circulating system according to claim 4, it is characterized in that: described the first heat exchange groove (15) is herringbone, and adjacent described the first heat exchange groove (15) is positive herringbone and the setting of falling the herringbone.
6. board-like integration system cryogen heat-recovery circulating system according to claim 5, it is characterized in that: adjacent described condensing heat-exchange sheet (5) and described first pod apertures (14) of the cold heat exchanger fin of described mistake (6) locate to adopt seal gasket to be connected and sealed.
According to claim 6 in the described board-like integration system cryogen heat-recovery circulating system of any one, it is characterized in that: the two ends of described plate-type condenser (2) arrange the first heat exchange end cap (16).
8. board-like integration system cryogen heat-recovery circulating system according to claim 1 is characterized in that: described cold-producing medium is through the described air entry end that enters into described compressor (1) middle part behind cold-zone (2b) of crossing, and tonifying Qi increases enthalpy to compressor (1).
9. the described board-like integration system cryogen heat-recovery circulating system of any one according to claim 1-8, it is characterized in that: described evaporating area (4a) is isolated by the second deflector (17) with described overheated zone (4b), described the second deflector (17) is provided with for the cold-producing medium after described evaporating area (4a) heating being guided to second diversion groove (18) of described overheated zone (4b), and the area of passage of the second water conservancy diversion interface (19) at the sectional area of described the second diversion groove (18) and two ends about equally.
10. board-like integration system cryogen heat-recovery circulating system according to claim 9, it is characterized in that: the area difference of the area of passage of the sectional area of described the second diversion groove (18) and described the second water conservancy diversion interface (19) is no more than 10%.
11. board-like integration system cryogen heat-recovery circulating system according to claim 10 is characterized in that: form the second pod apertures (20) and a plurality of the second regularly arranged heat exchange groove (21) for the conducting cold-producing medium on the plate face of described evaporation and heat-exchange sheet (11) and described overheated heat exchanger fin (12).
12. board-like integration system cryogen heat-recovery circulating system according to claim 10 is characterized in that: described the second heat exchange groove (21) is herringbone, and described the second heat exchange groove (21) on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone.
13. the described board-like integration system cryogen heat-recovery circulating system of any one according to claim 1-12, it is characterized in that: the two ends of described plate-type condenser (2) arrange the second heat exchange end cap (22).
14. board-like integration system cryogen heat-recovery circulating system according to claim 13 is characterized in that: the described cold-producing medium that enters the low-temp low-pressure that forms after cold-producing medium described first expansion valve of process (13) of described overheated zone (4b) directly is circulated in described evaporating area (4a) and carries out heat exchange with freezing liquid.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220651762.4U CN202928225U (en) | 2012-11-30 | 2012-11-30 | Plate-type integrated refrigerant thermal recovery circulation system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220651762.4U CN202928225U (en) | 2012-11-30 | 2012-11-30 | Plate-type integrated refrigerant thermal recovery circulation system |
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| CN202928225U true CN202928225U (en) | 2013-05-08 |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103303945A (en) * | 2013-06-30 | 2013-09-18 | 金川集团股份有限公司 | Vapor recovery system and method for sodium sulfite evaporation and concentration process |
| CN103851838A (en) * | 2012-11-30 | 2014-06-11 | 苏州必信空调有限公司 | Plate type integrated refrigerant heat recovery circulation system |
| CN107320988A (en) * | 2017-09-01 | 2017-11-07 | 吉林惠利现代轻工装备有限公司 | A kind of board-like feed liquid vaporising device |
-
2012
- 2012-11-30 CN CN201220651762.4U patent/CN202928225U/en not_active Withdrawn - After Issue
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103851838A (en) * | 2012-11-30 | 2014-06-11 | 苏州必信空调有限公司 | Plate type integrated refrigerant heat recovery circulation system |
| CN103851838B (en) * | 2012-11-30 | 2016-06-15 | 苏州必信空调有限公司 | Board-like integration system cryogen heat-recovery circulating system |
| CN103303945A (en) * | 2013-06-30 | 2013-09-18 | 金川集团股份有限公司 | Vapor recovery system and method for sodium sulfite evaporation and concentration process |
| CN107320988A (en) * | 2017-09-01 | 2017-11-07 | 吉林惠利现代轻工装备有限公司 | A kind of board-like feed liquid vaporising device |
| CN107320988B (en) * | 2017-09-01 | 2023-08-11 | 安徽惠利装备科技有限公司 | Plate-type feed liquid evaporation device |
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