CN202928177U - Integrated type refrigerant heat-recycling and circulating system - Google Patents
Integrated type refrigerant heat-recycling and circulating system Download PDFInfo
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- CN202928177U CN202928177U CN2012206515614U CN201220651561U CN202928177U CN 202928177 U CN202928177 U CN 202928177U CN 2012206515614 U CN2012206515614 U CN 2012206515614U CN 201220651561 U CN201220651561 U CN 201220651561U CN 202928177 U CN202928177 U CN 202928177U
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Abstract
The utility model discloses an integrated type refrigerant heat-recycling and circulating system, which comprises an evaporator (1), a compressor (2), a condenser (3) and a heat exchanger (4), wherein the evaporator comprises an evaporating zone (12) and a heat returning zone (11); the evaporating zone (12) is used for evaporating refrigerant; the heat returning zone (11) is used for returning the heat for refrigerant gas which flows out from the evaporating zone as well as refrigerant liquid which flows out from the condenser; and the heat returning zone and the evaporating zone are isolated by a guide plate (13).The integrated type refrigerant heat-recycling and circulating system disclosed by the utility model is provided with the heat exchanger and the evaporator which is integrated with the heat returning function and the evaporating function, wherein the whole evaporator is compact in structure and small in floor space. Meanwhile, the cross section of a guide groove of the guide plate is almost equal to that of guide interfaces at the two ends of the guide plate, so that the flow velocity of refrigerating medium is stable at the guide plate, thereby enabling the whole refrigerant circulating system to be compact in integral structure, greatly improving the heat exchange efficiency and realizing the more effective recycling of heat of the low-temperature high-pressure refrigerant liquid which flows out from the condenser.
Description
Technical field
The utility model relates to field of refrigeration, particularly, relates to a kind of integral type cold-producing medium heat-recovery circulating system for handpiece Water Chilling Units.
Background technology
Refrigeration system generally includes the refrigerant-cycle systems that is connected to form by pipeline by compressor, evaporimeter, condenser and four basic elements of character of expansion valve, refrigerant-cycle systems coordinates with miscellaneous part installs a whole set of refrigeration system of formation, cold-producing medium constantly circulates in refrigerant-cycle systems, state variation occurs and carry out exchange heat with the external world.
the course of work and the principle of refrigerant-cycle systems are as follows: compressor sucks the refrigerant gas of low-temp low-pressure from evaporimeter by air intake duct, enter condenser by blast pipe after the refrigerant gas of compressed machine boil down to HTHP, the refrigerant gas of HTHP carries out heat exchange with cooling medium (water or air) in condenser, be condensed into cryogenic high pressure liquid, after being the refrigerant liquid of low-temp low-pressure through the expansion valve expansion throttling, again entering absorbs heat to be evaporated to low-temperature low-pressure refrigerant gas and to enter in evaporimeter carries out next circulation in compressor, thereby reach the purpose of circularly cooling.Like this, cold-producing medium is completed a kind of refrigeration cycle through pervaporation, compression, condensation and four basic processes of throttling in this circulatory system.
Refrigerant-cycle systems of the prior art, as disclosed a kind of vapour compression refrigeration unit in Chinese patent literature CN 101556090B, it comprises compressor, condenser, evaporimeter and flash drum, upper end inlet and the condenser of described flash drum join, the gas outlet, upper end joins by an input port of check valve and compressor, and the lower end liquid outlet joins by the second choke valve and evaporimeter.
But, in above-mentioned vapour compression refrigeration unit, inlet and the restricting orifice of the cryogenic high pressure refrigerant liquid of condenser output by flash drum enters flash drum and carries out gas-liquid separation, refrigerant gas enters compressor from the gas outlet of flash drum upper end, and refrigerant liquid flows into evaporimeter from the liquid outlet of flash drum lower end.carried out sufficient heat exchange with cooling medium (water or air) although enter the high-temperature high-pressure refrigerant gas of condenser in condenser, but, this exchange heat does not reach desirable state, because also there is higher heat in the cryogenic high pressure refrigerant liquid itself that condenser flows out, and in above-mentioned vapour compression refrigeration unit, flash drum is used for gas-liquid separation, this part heat is not effectively recycled, simultaneously, above-mentioned evaporimeter only is used for the refrigerant liquid of low-temp low-pressure is evaporated to the refrigerant gas of low-temp low-pressure, this part heat is not effectively recycled yet, thereby cause the great loss and waste of heat energy.
In addition, Chinese patent literature 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 comprised of pre-backing, sterilization sheet, fin, flow deflector and high-temperature heating sheet, cold liquid is through preheating and sterilization, flow out emit heat in fin after, high-temperature medium can be emitted heat with hot water or superheated vapor in heating plate, can fully exchange because they connect tight heat.But, the interior shape of the deflector in this plate type heat exchanger is parallelogram, can cause rate of flow of fluid too small during fluid process deflector, finally cause heat exchange efficiency lower, can not satisfy the requirement of the evaporimeter heat exchanging efficient in central air-conditioning or handpiece Water Chilling Units.
The utility model content
Technical problem to be solved in the utility model is the problem that the evaporimeter of existing refrigeration system takes up room greatly, effectiveness of regenerator is low, thereby a kind of integral type cold-producing medium heat-recovery circulating system with evaporimeter that dutycycle is little, effectiveness of regenerator is high is provided.
To achieve these goals, the utility model provides a kind of integral type cold-producing medium heat-recovery circulating system, comprise successively the evaporimeter, compressor and the condenser that are communicated with, described evaporimeter comprises for the evaporating area of cold-producing medium evaporation and is used for the backheat district that refrigerant gas that described evaporating area flows out and the refrigerant liquid of described condenser outflow carry out backheat; Described backheat district and described evaporating area are isolated by deflector, have on described deflector for the refrigerant gas after described evaporating area evaporation being guided to the flow-guiding channel in described backheat district, the area of passage of the water conservancy diversion interface at the sectional area of described flow-guiding channel and two ends about equally;
Described backheat district has for the first refrigerant inlet of cold-producing medium circulation, the first refrigerant outlet, second refrigerant entrance and second refrigerant outlet;
Also comprise heat exchanger, described heat transfer equipment is useful on the first inlet, the second inlet, liquid outlet and the gas outlet of cold-producing medium circulation, wherein, described the first inlet connects the refrigerant outlet end of described condenser by the second expansion valve, described the second inlet directly connects the refrigerant outlet end of described condenser; Described gas outlet connects described compressor, and described liquid outlet connects described the first refrigerant inlet; The passage that is communicated with described the first refrigerant inlet and described the first refrigerant outlet is positioned at described backheat district, be provided with the first expansion valve between described the first refrigerant outlet and second refrigerant entrance, the passage that is communicated with the outlet of described second refrigerant entrance and described second refrigerant is positioned at described backheat district and described evaporating area, and described second refrigerant outlet connects described compressor.
In above-mentioned integral type cold-producing medium heat-recovery circulating system, the sectional area of described flow-guiding channel equates with the area of passage of described water conservancy diversion interface.
In above-mentioned integral type cold-producing medium heat-recovery circulating system, described evaporating area comprises that the passage that is communicated with described entrance point and the described port of export is positioned at described evaporating area for entrance point and the port of export of heat exchange medium circulation.
In above-mentioned integral type cold-producing medium heat-recovery circulating system, described backheat district closely is formed by connecting mutually by a plurality of backheat heat exchanger fins, and described evaporating area closely is formed by connecting mutually by a plurality of evaporation and heat-exchange sheets.
In above-mentioned integral type cold-producing medium heat-recovery circulating system, form pod apertures and a plurality of regularly arranged heat exchange groove on the plate face of described evaporation and heat-exchange sheet and described backheat heat exchanger fin.
In above-mentioned integral type cold-producing medium heat-recovery circulating system, 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.
In above-mentioned integral type cold-producing medium heat-recovery circulating system, described pod apertures place's employing seal gasket of adjacent described evaporation and heat-exchange sheet and described backheat heat exchanger fin is connected and sealed.
In above-mentioned integral type cold-producing medium heat-recovery circulating system, described compressor is the magnetic suspension centrifuge.
In above-mentioned integral type cold-producing medium heat-recovery circulating system, also be provided with cooling pipe between the refrigerant outlet end of described condenser and described compressor.
Technique scheme of the present utility model has the following advantages compared to existing technology:
(1) integral type cold-producing medium heat-recovery circulating system of the present utility model, it evaporimeter that comprises has integrated backheat district and evaporating area, the refrigerant liquid of the cryogenic high pressure that condenser flows out flows into flows through the backheat district after evaporimeter and is evaporated to the refrigerant gas of low-temp low-pressure in evaporating area, the refrigerant gas of this low-temp low-pressure 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, improve the Energy Efficiency Ratio of cold-producing medium, simultaneously, due to evaporimeter with backheat district and the one-body molded setting of evaporating area, make the refrigerant-cycle systems compact overall structure, the flow resistance of cold-producing medium has been simplified and reduced to pipe arrangement.
(2) integral type cold-producing medium heat-recovery circulating system of the present utility model, the backheat district of its evaporimeter and evaporating area separate by a deflector, and the compact conformation of whole evaporimeter is lower with respect to existing split type evaporimeter floor space; Simultaneously, the sectional area of the sectional area of the diversion groove that deflector is offered and two end interfaces about equally, make the flow velocity of refrigerant stable in air deflector, thereby make the compact overall structure of whole refrigerant-cycle systems, heat exchange efficiency improves greatly, the more effective recycling of realization to the self heat of the cryogenic high pressure refrigerant liquid of condenser outflow.
(3) integral type cold-producing medium heat-recovery circulating system of the present utility model, it also comprises the heat exchanger that is connected between condenser and evaporimeter, carry out heat exchange for the first time with the refrigerant liquid of cryogenic high pressure that the refrigerant outlet end of condenser is flowed out and reclaim, improve the Energy Efficiency Ratio of cold-producing medium.
(4) integral type cold-producing medium heat-recovery circulating system of the present utility model, also be provided with cooling pipe between the refrigerant outlet end of its condenser and compressor, make the refrigerant liquid of the cryogenic high pressure that the refrigerant outlet end of condenser flows out flow into compressor, thereby compressor is played good cooling effect.
Description of drawings
Content of the present utility model is easier to be expressly understood in order to make, below in conjunction with accompanying drawing, the utility model is described in further detail, wherein,
Fig. 1 is the structural principle schematic diagram of integral type cold-producing medium heat-recovery circulating system of the present utility model.
Fig. 2 is the structural representation of evaporimeter of the present utility model;
Fig. 3 is the perspective view of deflector of the present utility model;
Description of reference numerals
the 1-evaporimeter, the 2-compressor, the 3-condenser, the 4-heat exchanger, 5-the first expansion valve, 6-the second expansion valve, the 8-gas-liquid separator, the 9-cooling pipe, 11-backheat district, the 12-evaporating area, the 13-deflector, the 14-pod apertures, 15-heat exchange groove, 16-the first end cap, 17-the second end cap, 11a-the first refrigerant inlet, 11b-the first refrigerant outlet, 11c-second refrigerant entrance, the outlet of 11d-second refrigerant, the 12a-entrance point, the 12b-port of export, the 13a-flow-guiding channel, 13b water conservancy diversion interface, the 31-water inlet, the 32-delivery port, 41-the first inlet, 42-the second inlet, the 43-liquid outlet, the 44-gas outlet, 111-backheat heat exchanger fin, 121-evaporation and heat-exchange sheet.
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 shown in Figure 1, the integral type cold-producing medium heat-recovery circulating system that the utility model specific embodiment provides comprises evaporimeter 1, compressor 2, condenser 3 and the heat exchanger 4 that is communicated with successively by refrigerant tubing, wherein:
Described evaporimeter 1 includes for the evaporating area 12 of cold-producing medium evaporation and the refrigerant liquid that is used for refrigerant gas that described evaporating area 12 flows out and 3 outflows of described condenser carries out the backheat district 11 of backheat.As shown in Figure 2, described backheat district 11 isolates by deflector 13 mutually with described evaporating area 12, have on described deflector 13 for the flow-guiding channel 13a that the refrigerant gas after 12 evaporations of described evaporating area is guided to described backheat district 11, the area of passage of the water conservancy diversion interface 13b at the sectional area of described flow-guiding channel 13a and two ends about equally, so that the flow velocity of cold-producing medium is more stable at described deflector 13 places, heat exchange efficiency improves greatly, thereby improves from the rate of recovery of the refrigerant liquid self heat of described condenser 3 outflows.
Need to prove, the area of passage meaning about equally of the water conservancy diversion interface 13b at the sectional area of described flow-guiding channel 13a and two ends refers to that the area of passage of the water conservancy diversion interface 13b at the sectional area of described flow-guiding channel 13a and two ends can have the difference of certain limit, and the difference of this certain limit should be flowed through on cold-producing medium, and stablizing of described deflector 13 flow velocitys is capable not to exert an influence or produce very slight impact.
Preferably, the area difference of the area of passage of the sectional area of described flow-guiding channel 13a and described water conservancy diversion interface 13b is no more than 10%, and more preferably, the area difference of the area of passage of the sectional area of described flow-guiding channel 13a and described water conservancy diversion interface 13b is no more than 5%.
More preferably, the sectional area of described flow-guiding channel 13a equates with the area of passage of described water conservancy diversion interface 13b, thereby makes the flow through flow velocity of described deflector 13 of cold-producing medium more stable.
As shown in Figure 2, described backheat district 11 closely is formed by connecting mutually by a plurality of backheat heat exchanger fins 111, and described evaporating area 12 closely is formed by connecting mutually by a plurality of evaporation and heat-exchange sheets 121.Form pod apertures 14 and a plurality of regularly arranged heat exchange groove 15 for cold-producing medium or heat exchange medium circulation on the plate face of described evaporation and heat-exchange sheet 121 and described backheat heat exchanger fin 111.Described heat exchange groove 15 is herringbone, and the described heat exchange groove 15 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.
In addition, the described pod apertures 14 places employing seal gasket of adjacent described evaporation and heat-exchange sheet 121 and described backheat heat exchanger fin 111 is connected and sealed.
In addition, the end of described evaporimeter is respectively arranged with the first end cap 16 and the second end cap 17, is welded to connect between described the first end cap 16, described the second end cap 17, described evaporation and heat-exchange sheet 121, described deflector 13, described backheat heat exchanger fin 111.Form on described backheat heat exchanger fin 111 and described deflector 13 for the described pod apertures 14 that cold-producing medium is guided to described evaporating area 12, between adjacent described pod apertures 14, seal washer is set, is used for described pod apertures 14 isolated with the described heat exchange groove 15 of described backheat heat exchanger fin 111.
Be provided with the first refrigerant inlet 11a and the first refrigerant outlet 11b that flow into and flow out for cold-producing medium on described first end cap 16 in described backheat district 11, and again flow into and the second refrigerant entrance 11c that again flows out and second refrigerant outlet 11d for cold-producing medium.The pipe passage that is used for being communicated with described the first refrigerant inlet 11a and described the first refrigerant outlet 11b is positioned at 11 inside, described backheat district, and the pipe passage that is used for being communicated with described second refrigerant entrance 11c and described second refrigerant outlet 11d is positioned at described backheat district 11 and described evaporating area 12 inside.
Be provided with the first expansion valve 5 between described the first refrigerant outlet 11b and described second refrigerant entrance 11c, carry out decrease temperature and pressure with the refrigerant liquid with the cryogenic high pressure by this first expansion valve 5.
Described the first refrigerant inlet 11a is connected in the refrigerant outlet end of described condenser 3 by refrigerant tubing, described second refrigerant outlet 11d is connected in the air inlet of described compressor 2 by refrigerant tubing.
The following circulation process that cold-producing medium in the integral type cold-producing medium 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 A in Fig. 1 or Fig. 2.
as shown in Figure 1, described compressor 2 sucks the refrigerant gas of low-temp low-pressure, be delivered to after refrigerant gas with its boil down to HTHP in described condenser 3, the refrigerant gas of HTHP carries out with external heat exchange medium the refrigerant liquid that heat exchange is condensed into cryogenic high pressure in described condenser 3, the cryogenic high pressure refrigerant liquid that the refrigerant outlet end of described condenser 3 flows out flows into described backheat district 11 and flows out described backheat district 11 from described the first refrigerant outlet 11b from the described first refrigerant inlet 11a of described evaporimeter 1, then the effect borehole cooling step-down at described the first expansion valve 5 is the refrigerant liquid of low-temp low-pressure and flows into by refrigerant tubing the refrigerant gas that described evaporating area 12 is evaporated to low-temp low-pressure, the refrigerant gas of this low-temp low-pressure is back to described backheat district 11 again by refrigerant tubing, due to the temperature of the refrigerant gas of the low-temp low-pressure that enters described backheat district 11 temperature lower than the refrigerant liquid of the cryogenic high pressure that flows into described backheat district 11 from described the first refrigerant inlet 11a, therefore, refrigerant liquid will carry out the recuperation of heat heat exchange with refrigerant gas, the refrigerant liquid of cryogenic high pressure is lowered the temperature release heat, the temperature of the refrigerant liquid that flows into described evaporating area 12 is further reduced, simultaneously, the refrigerant gas of low-temp low-pressure will absorb the heat that discharges and heat up, the temperature that flows out into the refrigerant gas of described compressor 2 by described second refrigerant outlet 11d is improved accordingly, at last, the refrigerant gas that obtains the low-temp low-pressure of heat again enters and carries out the circulation of recuperation of heat next time in described compressor 2.
Therefore, backheat evaporation by above-mentioned described evaporimeter 1, the temperature of the refrigerant liquid that flows into described evaporating area 12 is further reduced, make simultaneously the refrigerant gas of low-temp low-pressure absorb the heat that discharges and heat up, can effectively reduce the energy consumption of described compressor 2, can realize the effective recycling of the self heat of cryogenic high pressure refrigerant liquid that described condenser 3 is flowed out, improve the Energy Efficiency Ratio of cold-producing medium.
As shown in Figure 2, can be provided with entrance point 12a and port of export 12b for the heat exchange medium circulation on the second end cap 17 of described evaporating area 12, the pipe passage that is communicated with described entrance point 12a and described port of export 12b is positioned at described evaporating area 12.As mentioned above, because the pipe passage that is used for being communicated with described second refrigerant entrance 11c and described second refrigerant outlet 11d is positioned at described backheat district 11 and described evaporating area 12 inside equally, therefore, the heat exchange with outside medium, chilled water for example, the flow direction flows in described evaporating area 12 from described entrance point 12a as shown in arrow B in figure, flow through described evaporating area 12 and carry out heat exchange with chilled water and be evaporated to the refrigerant gas of low-temp low-pressure of the refrigerant liquid of low-temp low-pressure.
In the integral type cold-producing medium heat-recovery circulating system that the utility model provides, heat recovery rate for the refrigerant liquid that further improves the cryogenic high pressure that condenser flows out, as shown in Figure 1, this integral type cold-producing medium heat-recovery circulating system also includes heat exchanger 4, described heat exchanger 4 has the first inlet 41, the second inlet 42, liquid outlet 43 and gas outlet 44, wherein, described the first inlet 41 and the second inlet 42 are used for flowing into refrigerant liquid, described liquid outlet 43 is used for flowing out refrigerant liquid, and described gas outlet 44 is used for flowing out refrigerant gas.Described the first inlet 41 is connected in the refrigerant outlet end of described condenser 3 by the second expansion valve 6, described the second inlet 42 is directly connected in the refrigerant outlet end of described condenser 3, described gas outlet 44 is connected in described compressor 2, and described liquid outlet 43 is connected in described the first refrigerant inlet 11a.
like this, the cryogenic high pressure refrigerant liquid that the refrigerant outlet end of described condenser 3 flows out is at first by heat exchanger 4, the refrigerant liquid that is cryogenic high pressure will be divided into two-way, one the tunnel through flowing into described heat-exchanger rig 4 by described the first inlet 41 after the second expansion valve 6 decrease temperature and pressure, another road directly enters described heat-exchanger rig 4 by described the second inlet 42, effect due to described the second expansion valve 6, the two-way refrigerant liquid that flows into described heat-exchanger rig 4 has the temperature difference, therefore, this two-way refrigerant liquid carries out heat exchange for the first time in described heat-exchanger rig 4, the refrigerant liquid that temperature is lower is evaporated to gaseous refrigerant with heat absorption and enters described compressor 2 from described gas outlet 44, increase the effect of enthalpy to play tonifying Qi, the refrigerant liquid cooling that temperature is higher is rear flows out from described liquid outlet 43, and flow into the described backheat district 11 of described evaporimeter 1 to carry out follow-up flow process by described the first refrigerant inlet 11a.
Therefore, heat exchange effect by above-mentioned described heat exchanger 4, the cold-producing medium liquid state that described condenser 3 is flowed out is again cooling, and the back flow of refrigerant of the one-tenth gaseous state that evaporates when improving the degree of supercooling of system has to described compressor 2 effect that tonifying Qi increases enthalpy.
In addition, in order to improve heat exchange efficiency, reduce the floor space of heat exchanger, preferably, described heat exchanger 4 is plate type heat exchanger.Certainly, described heat exchanger 4 can adopt the heat exchanger of other types, is not restricted at this.
In addition, due to described condenser 3 outflows are refrigerant liquids of high pressure, therefore, for causing described evaporimeter 1, the high pressure that prevents refrigerant liquid damages or causes the unstable of system's operation, preferably, can be connected with expansion valve between the described first refrigerant inlet 11a of the described liquid outlet 43 of described heat exchanger 4 and described evaporimeter 1, enter the pressure of the refrigerant liquid of described evaporimeter 1 with reduction.
In addition, as shown in Figure 1, also can be connected with gas-liquid separator 8 between the described second refrigerant outlet 11d of described evaporimeter 1 and the air inlet of described compressor 2.Due to the effect in the described backheat district 11 of described evaporimeter 1, the temperature of the refrigerant gas of the low-temp low-pressure of described evaporimeter 1 output can be improved accordingly, thereby reduces moisture in refrigerant gas.On this basis; in order further to reduce in refrigerant gas moisture and to protect described compressor 2 to avoid suffering liquid hit phenomenon; be connected with described gas-liquid separator 8 between the air inlet of described second refrigerant outlet 11d and described compressor 2, thereby provide further protection more reliably to described compressor 2.
Also can be provided with cooling pipe 9 between the refrigerant outlet end of described condenser 3 and described compressor 2, make the refrigerant liquid of the cryogenic high pressure that the refrigerant outlet end of described condenser 3 flows out be back to described compressor 2, thereby described compressor 2 is played good cooling effect.
Described condenser 3 can have water inlet 31 and delivery port 32, make as the chilled water of heat exchange medium and can flow in described condensers 3 and carry out heat exchange with the refrigerant gas of the HTHP that flows into described condenser 3 from described water inlet 31, chilled water flows out from described delivery port 32 after absorbing heat, simultaneously, the refrigerant gas release heat of HTHP is condensed into the refrigerant liquid of cryogenic high pressure and flows out from the refrigerant outlet end of described condenser 3.
In addition, compressor 2 can adopt centrifugal compressor, and more preferably, described compressor 2 can adopt the magnetic suspension centrifuge.Certainly, the compressor that described compressor 2 also can adopt any existing driver element and compression unit to be integrated does not limit at this particular type to compressor 2.
In order to guarantee that the refrigerant liquid that enters described evaporimeter 1 does not contain impurity, preferably, can be provided with filter between the described first refrigerant inlet 11a of the described liquid outlet 43 of described heat exchanger 4 and described evaporimeter 1, thereby guarantee to enter refrigerant liquid pure of described evaporimeter 1.
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 (10)
1. an integral type cold-producing medium heat-recovery circulating system, comprise the evaporimeter (1), compressor (2) and the condenser (3) that are communicated with successively, it is characterized in that:
Described evaporimeter (1) comprises for the evaporating area (12) of cold-producing medium evaporation and is used for the backheat district (11) that refrigerant gas that described evaporating area (12) flows out and the refrigerant liquid of described condenser (3) outflow carry out backheat; Described backheat district (11) isolates by deflector (13) with described evaporating area (12), have on described deflector (13) for the refrigerant gas after described evaporating area (12) evaporation being guided to the flow-guiding channel (13a) in described backheat district (11), the area of passage of the water conservancy diversion interface (13b) at the sectional area of described flow-guiding channel (13a) and two ends about equally;
Described backheat district (11) has that the first refrigerant inlet (11a), the first cold-producing medium for cold-producing medium circulation goes out (11b), second refrigerant enters (11c) and second refrigerant outlet (11d);
Also comprise heat exchanger (4), described heat exchanger (4) has the first inlet (41) for cold-producing medium circulation, the second inlet (42), liquid outlet (43) and gas outlet (44), wherein,
Described the first inlet (41) connects the refrigerant outlet end of described condenser (3) by the second expansion valve (6), described the second inlet (42) connects the refrigerant outlet end of described condenser (3); Described gas outlet (44) connects described compressor (2), and described liquid outlet (43) connects described the first refrigerant inlet (11a); Be communicated with the passage that described the first cold-producing medium enters (11a) and described the first refrigerant outlet (11b) and be positioned at described backheat district (11), described the first cold-producing medium goes out (11b) and second refrigerant enters to be provided with the first expansion valve (5) between (11c), be communicated with the passage that described second refrigerant entrance (11c) and described second refrigerant go out (11d) and be positioned at described backheat district (11) and described evaporating area (12), described second refrigerant goes out (11d) and connects described compressor (2).
2. integral type cold-producing medium heat-recovery circulating system according to claim 1, is characterized in that, the sectional area of described flow-guiding channel (13a) equates with the area of passage of described water conservancy diversion interface (13b).
3. integral type cold-producing medium heat-recovery circulating system according to claim 1 and 2, it is characterized in that, described evaporating area (12) comprises entrance point (12a) and the port of export (12b) for the heat exchange medium circulation, and the passage that is communicated with described entrance point (12a) and the described port of export (12b) is positioned at described evaporating area (12).
4. integral type cold-producing medium heat-recovery circulating system according to claim 3, it is characterized in that, described backheat district (11) closely is formed by connecting mutually by a plurality of backheat heat exchanger fins (111), and described evaporating area (12) closely is formed by connecting mutually by a plurality of evaporation and heat-exchange sheets (121).
5. integral type cold-producing medium heat-recovery circulating system according to claim 4, it is characterized in that, form pod apertures (14) and a plurality of regularly arranged heat exchange groove (15) on the plate face of described evaporation and heat-exchange sheet (121) and described backheat heat exchanger fin (111).
6. integral type cold-producing medium heat-recovery circulating system according to claim 5, is characterized in that, described heat exchange groove (15) is herringbone, and the described heat exchange groove (15) on adjacent heat exchanger fin is positive herringbone and the setting of falling the herringbone.
7. according to claim 5 or 6 described plate-type evaporators, is characterized in that, adjacent described evaporation and heat-exchange sheet (121) and the described pod apertures (14) of described backheat heat exchanger fin (111) locate to adopt seal gasket to be connected and sealed.
8. integral type cold-producing medium heat-recovery circulating system according to claim 1, is characterized in that, described heat exchanger (4) is plate type heat exchanger.
9. integral type cold-producing medium heat-recovery circulating system according to claim 1, is characterized in that, described compressor (2) is the magnetic suspension centrifuge.
10. integral type cold-producing medium heat-recovery circulating system according to claim 9, is characterized in that, also is provided with cooling pipe (9) between the refrigerant outlet end of described condenser (3) and described compressor (2).
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| Application Number | Priority Date | Filing Date | Title |
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| CN2012206515614U CN202928177U (en) | 2012-11-30 | 2012-11-30 | Integrated type refrigerant heat-recycling and circulating system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2012206515614U CN202928177U (en) | 2012-11-30 | 2012-11-30 | Integrated type refrigerant heat-recycling and circulating system |
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| CN2012206515614U Withdrawn - After Issue CN202928177U (en) | 2012-11-30 | 2012-11-30 | Integrated type refrigerant heat-recycling and circulating system |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103851813A (en) * | 2012-11-30 | 2014-06-11 | 苏州必信空调有限公司 | Integrated type refrigerant heat-recycling and circulating system |
| CN104019585A (en) * | 2014-06-24 | 2014-09-03 | 山东雅士股份有限公司 | Flooded evaporator and flooded air conditioning unit |
| CN104420902A (en) * | 2013-08-19 | 2015-03-18 | 财团法人工业技术研究院 | Heat exchanger with reheating and condensing functions, heat cycle system and method thereof |
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2012
- 2012-11-30 CN CN2012206515614U patent/CN202928177U/en not_active Withdrawn - After Issue
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103851813A (en) * | 2012-11-30 | 2014-06-11 | 苏州必信空调有限公司 | Integrated type refrigerant heat-recycling and circulating system |
| CN103851813B (en) * | 2012-11-30 | 2016-08-03 | 苏州必信空调有限公司 | Integral type cold-producing medium heat-recovery circulating system |
| CN104420902A (en) * | 2013-08-19 | 2015-03-18 | 财团法人工业技术研究院 | Heat exchanger with reheating and condensing functions, heat cycle system and method thereof |
| CN104420902B (en) * | 2013-08-19 | 2017-01-18 | 财团法人工业技术研究院 | Heat exchanger with reheating and condensing functions, heat cycle system and method thereof |
| CN104019585A (en) * | 2014-06-24 | 2014-09-03 | 山东雅士股份有限公司 | Flooded evaporator and flooded air conditioning unit |
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