CN210861761U - Double-process microchannel evaporator refrigerating system with liquid level control and bypass air guide tube - Google Patents
Double-process microchannel evaporator refrigerating system with liquid level control and bypass air guide tube Download PDFInfo
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- CN210861761U CN210861761U CN201921796105.7U CN201921796105U CN210861761U CN 210861761 U CN210861761 U CN 210861761U CN 201921796105 U CN201921796105 U CN 201921796105U CN 210861761 U CN210861761 U CN 210861761U
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Abstract
The utility model discloses a double-flow micro-channel evaporator refrigerating system with liquid level control and bypass air guide tubes, which comprises a compressor, a non-straight-through floating ball throttle valve and a double-flow micro-channel evaporator, wherein the air outlet of a confluence collecting tube of the evaporator is connected with the air outlet of an outlet collecting tube through the air guide tubes; the exhaust port of the compressor is connected with the refrigerant inlet of the oil separator; the refrigerant outlet of the oil separator is connected with the refrigerant inlet of the condenser; the refrigerant outlet of the condenser is connected with the first refrigerant inlet of the heat regenerator; a first refrigerant outlet of the heat regenerator is communicated with a refrigerant inlet of the floating ball throttle valve; the second refrigerant inlet of the heat regenerator is communicated with the air outlet of the outlet header; a second refrigerant outlet of the heat regenerator is connected with an air suction port of the compressor; the floating ball throttle valve refrigerant outlet is connected with the liquid inlet of the inlet header. The utility model discloses can effectively solve the gas-liquid two-phase flow mutual interference that current microchannel evaporator exists and influence the technical problem of heat transfer performance.
Description
Technical Field
The utility model relates to the field of refrigeration technology, especially, relate to take two process microchannel evaporator refrigerating system of liquid level control and bypass air duct.
Background
At present, the development of a microchannel heat exchanger is very rapid in recent years due to the advantages of compact structure, small refrigerant charge, high efficiency, energy saving and the like, and the microchannel heat exchanger is widely used as a condenser, but the technology applied as an evaporator is not mature, and particularly the microchannel evaporator has the problems of uneven flow distribution from a collecting pipe to a flat pipe, reduced heat exchange performance and the like. In addition, the problem of vapor-liquid two-phase flow in the microchannel is an extremely complex problem, and the fluid action mechanism, distribution mechanism and heat transfer characteristics of the microchannel are not completely mastered so far. The gas phase fluid is a main factor influencing the uniform distribution of the liquid supply of the microchannel evaporator. The gasified refrigerant easily blocks the flow of the liquid refrigerant, thereby easily influencing the heat exchange effect of the microchannel evaporator, causing the instability of the heat exchange performance of the microchannel evaporator and further influencing the refrigeration performance and the stability of the whole refrigeration system.
Therefore, it is very important to further research the heat transfer performance of the microchannel evaporator and improve the structure of the microchannel evaporator.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a take two-flow microchannel evaporator refrigerating system of liquid level control and bypass air duct to the technical problem that the gas-liquid two-phase flow mutual interference that current microchannel evaporator exists influences heat transfer performance.
For this reason, the utility model provides a take two flow microchannel evaporator refrigerating system of liquid level control and bypass air duct, including compressor, oil separator, condenser, regenerator, first solenoid valve, non-through formula floater choke valve and two flow path microchannel evaporators, wherein:
the double-flow-path micro-channel evaporator comprises a hollow collecting pipe and a main collecting pipe which are arranged at left and right intervals;
the opposite sides of the confluence collecting pipe and the main collecting pipe are communicated through a plurality of flat pipes which are distributed transversely;
the main collecting pipe is internally provided with a split-range baffle which is transversely distributed;
the range dividing baffle plate divides the main collecting pipe into an inlet collecting pipe and an outlet collecting pipe;
the inlet header is located below the outlet header;
the air outlet at the top of the confluence collecting pipe is communicated with the air outlet in the middle of the right side of the outlet collecting pipe through an air duct;
wherein, the exhaust port on the top of the compressor is communicated with the refrigerant inlet of the oil separator;
the refrigerant outlet of the oil separator is communicated with the refrigerant inlet of the condenser;
the refrigerant outlet of the condenser is communicated with the first refrigerant inlet of the heat regenerator;
a first refrigerant outlet of the heat regenerator is communicated with a refrigerant inlet of the non-straight-through floating ball throttle valve through a first electromagnetic valve;
the second refrigerant inlet of the heat regenerator is communicated with the air outlet of the outlet header in the double-process microchannel evaporator;
the second refrigerant outlet of the heat regenerator is communicated with the air suction port of the compressor;
the refrigerant outlet of the non-straight-through type floating ball throttle valve is communicated with a liquid inlet at the bottom of an inlet collecting pipe in the double-flow-path micro-channel evaporator.
The oil inlet of the compressor is communicated with one end of the second electromagnetic valve through a hollow connecting pipeline;
the other end of the second electromagnetic valve is communicated with an oil return port at the bottom of the oil separator through a hollow connecting pipeline.
Wherein, the non-straight-through type floating ball throttle valve comprises a main valve;
the main valve is arranged on a refrigerant inlet of the non-straight-through floating ball throttle valve;
a hollow floating ball chamber is arranged in the non-straight-through type floating ball throttle valve;
the floating ball chamber is provided with a floating ball which floats on the liquid level of the refrigerant liquid in the floating ball chamber;
the first interface of the non-straight-through type floating ball throttle valve is communicated with the lower part of the right side of the inlet collecting pipe through a liquid balance pipe;
and the second interface of the non-straight-through type floating ball throttle valve is communicated with the air outlet of the outlet collecting pipe through an air balance pipe.
As can be seen from the above technical scheme provided by the utility model, compared with the prior art, the utility model provides a two-flow microchannel evaporator refrigerating system with liquid level control and bypass air duct, it can realize the control to refrigerant liquid level in the inlet header of microchannel evaporator, guarantee that each flat tube pipeline in the first flow of microchannel evaporator (the inlet header and the flat tube that the inlet header corresponds are evaporator first flow; the outlet header and the flat tube that the outlet header corresponds are evaporator second flow) evenly supplies liquid refrigerant; meanwhile, the bypass air duct can separate the gas and the liquid of the refrigerant evaporated in the first flow, so that the liquid of the refrigerant efficiently enters the flat tubes of the second flow to be evaporated, the interference of the gas-phase refrigerant on the distribution of the liquid-phase refrigerant in each flat tube is avoided, the heat exchange area of the evaporator is fully utilized, the overall heat exchange performance of the microchannel evaporator is improved, and the microchannel evaporator has great production practice significance.
Furthermore, it is right the utility model provides a take two flow microchannel evaporator refrigerating system of liquid level control and bypass air duct, the regenerator that it has still can avoid the refrigerant gas after the evaporation to wrap up in the liquid drop of holding by the side with most gaseous phase refrigerant and directly gets into the compressor induction port, prevents that the compressor from producing the liquid and hits, also can utilize the backheat circulation, improves refrigerating system's performance.
Drawings
Fig. 1 is a schematic structural view of a dual-flow microchannel evaporator refrigeration system with liquid level control and a bypass air duct provided by the present invention.
Detailed Description
In order to make the technical field of the present invention better understand, the present invention is further described in detail with reference to the accompanying drawings and embodiments.
Referring to fig. 1, the utility model provides a take two processes microchannel evaporator refrigerating system of liquid level control and bypass air duct, including compressor 1, oil separator 2, condenser 3, regenerator 4, first solenoid valve 5, non-through formula floater choke valve 6 and two processes microchannel evaporator 7, wherein:
the dual-pass microchannel evaporator 7 includes a hollow collecting header 73 and a main header 70 which are provided at a left-right interval;
the opposite sides of the confluence collecting pipe 73 and the main collecting pipe 70 are communicated through a plurality of flat pipes 72 which are distributed transversely;
a laterally distributed split-range baffle 75 is arranged in the main header 70;
the split baffle 75 divides the main header 70 into two cavities, an inlet header 71 and an outlet header 74;
the inlet header 71 is located below the outlet header 74;
the gas outlet m (i.e., the gaseous refrigerant outlet) at the top of the collecting header 73 communicates with the gas outlet n at the right middle portion of the outlet header 74 via a gas guide tube 76;
wherein, the exhaust port on the top of the compressor 1 is communicated with the refrigerant inlet a of the oil separator 2;
a refrigerant outlet b of the oil separator 2 communicating with a refrigerant inlet d of the condenser 3;
a refrigerant outlet e of the condenser 3 is communicated with a first refrigerant inlet f of the heat regenerator 4;
a first refrigerant outlet g of the heat regenerator 4 is communicated with a refrigerant inlet j of the non-straight-through type floating ball throttle valve 6 through a first electromagnetic valve 5;
a second refrigerant inlet h of the regenerator 4 communicating with the gas outlet n of the outlet header 74 of the dual-pass microchannel evaporator 7 (the outlet header 74 is a gas header);
a second refrigerant outlet i of the heat regenerator 4 is communicated with the air suction port of the compressor 1;
the refrigerant outlet k of the non-through type ball throttle 6 communicates with a liquid inlet at the bottom of the inlet header 71 in the two-pass microchannel evaporator 7 (the inlet header 71 is a liquid header).
In the utility model, in the concrete implementation, the oil inlet of the compressor 1 is communicated with one end of the second electromagnetic valve 8 through a hollow connecting pipeline;
the other end of the second electromagnetic valve 8 is communicated with an oil return port c at the bottom of the oil separator 2 through a hollow connecting pipeline.
In the present invention, it is noted that the inlet header 71 and the outlet header 74 are completely spaced apart from each other by the split baffles 75. The flat tube 72 is a flat tube, and the flat tube 72 has a plurality of microchannels (for example, tens of fine flow channels) therein. Similar to the prior art, the description is not provided herein.
In the present invention, in particular, the non-straight-through type floating ball throttle valve 6 includes a main valve 61;
the main valve 61 is arranged on the refrigerant inlet j of the non-straight-through floating ball throttle valve 6;
the non-through type floating ball throttle valve 6 is internally provided with a hollow floating ball chamber 62;
a float 63 in the float chamber 62, which floats on the surface of the refrigerant liquid in the float chamber 62;
a first port (communicating with the float chamber 62) of the non-through type float ball throttle valve 6 communicating with the lower right side portion of the inlet header 71 through the liquid balance pipe 64;
the second port of the non-straight-through ball throttle 6, which communicates with the ball chamber 62, communicates with the outlet port of the outlet header 74 through the gas balance pipe 65.
It should be noted that, for the present invention, the non-straight-through type floating ball throttle valve main valve 61 is mainly used for throttling and depressurizing the high-temperature and high-pressure refrigerant into a low-temperature and low-pressure two-phase fluid;
the floating ball chamber 62 is mainly used for storing gas-liquid two-phase refrigerant; the floating ball 63 is used for liquid level control, and the opening degree of the main valve 61 is adjusted according to the liquid level height of the refrigerant in the inlet header 71, so that the purpose of liquid level control is achieved; the liquid balance pipe 64 and the gas balance pipe 65 are used for respectively connecting the liquid part and the gas part of the float chamber with the inlet header (i.e. as a liquid header) 71 and the outlet header (i.e. as a gas header) 74 of the dual-flow microchannel evaporator 7, ensuring the pressure balance of the dual-flow microchannel evaporator 7 and the float chamber 62, so that the liquid level of the float chamber 62 is consistent with the liquid level of the inlet header (i.e. as a liquid header) 71, and achieving the purpose of controlling the liquid level of the inlet header (i.e. as a liquid header) 71.
Note that, in the present invention, the main functions of the inlet header 71 are: the refrigerant liquid supplied from the direction of the non-straight-through type floating ball throttle valve 6 is filled in the collecting pipe, which is beneficial to uniformly supplying liquid to each branch of the flat pipe 72. The refrigerant exchanges heat with air in each branch of the micro-channel flat tube 72, absorbs heat in the air, evaporates into low-temperature steam, reduces the temperature of the air and achieves the aim of refrigeration. The evaporated refrigerant is collected from the tops of the respective branches of the flat tubes 72 toward the outlet header 74, and is collected and flows to the regenerator 4.
It should be noted that, in the present invention, the oil separator 2 is used for separating the refrigerant oil (i.e., the lubricating oil) from the high-pressure refrigerant vapor discharged from the compressor, so as to ensure the safe and efficient operation of the device.
It should be noted that, in the present invention, the heat regenerator 4 not only can supercool the condensed liquid refrigerant, but also can prevent the liquid drops wrapped by the evaporated refrigerant gas from directly entering the air suction port of the compressor 1;
the utility model discloses in, non-through floating ball expansion valve 6 for the liquid level of entry header 71 among the control regulation two-flow process microchannel evaporator 7 to guarantee that liquid refrigerant is full of whole entry header 71, guarantee promptly that refrigerant liquid evenly distributes in first flow (entry header and the flat pipe that the entry header corresponds are the first flow of evaporator).
The utility model discloses in, gas-liquid separation can be carried out with the refrigerant after the evaporation in first flow to air duct 76, guarantees that the effectual entering second flow of refrigerant liquid (the flat pipe that export collector and export collector correspond is the evaporimeter second flow) in the evaporation heat absorption.
It should be noted that, for the present invention, any two mutually communicated components are communicated with each other through a section of pipeline, as shown in fig. 1.
In the present invention, in the specific implementation, the regenerator 4 may specifically adopt an existing conventional regenerator, for example, a regenerator with a model number B3-27-42 manufactured by new heat exchanger limited in guangzhou city.
In particular, the non-straight-through type floating ball throttle valve 6 can be a FPF-T non-straight-through type floating ball throttle valve produced by Sanhua group in Zhejiang.
In particular, the dual-flow micro-channel evaporator 7 may be an existing dual-flow micro-channel evaporator, for example, a micro-channel evaporator manufactured by danfoss corporation and having a model number D1400-E.
In the present invention, it should be noted that the compressor 1 is used for compressing the low-temperature and low-pressure refrigerant gas into the high-temperature and high-pressure refrigerant gas, then, the lubricating oil in the high-pressure steam is separated by the oil separator 2 and enters the condenser 3 for condensation, the condenser 3 condenses the high-temperature high-pressure gas into low-temperature high-pressure liquid, the condensed refrigerant liquid enters the heat regenerator 4 for further supercooling, the supercooled refrigerant liquid enters the main valve 61 in the non-straight-through type floating ball throttle valve 6 for throttling, since the float chamber 62 is connected to the inlet header 71 of the dual-flow microchannel evaporator 7 by the liquid balance tube 64, the heights of the two are maintained in agreement (i.e., the liquid level in the float chamber 62 is maintained in agreement with the liquid level in the inlet header 71), and therefore, the level of liquid in the inlet header 71 of the dual-pass microchannel evaporator 7 can be adjusted by changing (i.e., raising and lowering) the position of the float 63.
When the liquid level is lower than a set value (the set value is the height value of the range-dividing baffle 75 of the double-flow-range microchannel evaporator 7), the floating ball 63 descends, the opening degree of the main valve 61 is increased, the liquid supply amount is also increased, and vice versa, the set value is the height value of the range-dividing baffle 75 of the double-flow-range microchannel evaporator 7, so that the inlet collecting pipe 71 can be filled with liquid-phase refrigerant, and the liquid refrigerant can be uniformly supplied to each flat pipe 72 in the first flow of the microchannel evaporator; in addition, the bypass air duct 76 separates the refrigerant evaporated in the first flow into gas and liquid, and after the refrigerant is evaporated in the flat tube in the first flow, the pressure in the confluence header 73 is increased, so that gas enters the bypass air duct 76, and meanwhile, under the action of gravity, the refrigerant liquid fully enters the flat tube in the second flow, so that the distribution uniformity of the refrigerant in the flat tube 72 in the second flow is greatly improved, the interference of the gas-phase refrigerant in the confluence header on the distribution characteristic of the liquid-phase refrigerant is avoided, the whole heat exchange area of the microchannel evaporator can be effectively utilized, and the heat exchange performance of the microchannel evaporator is improved.
In addition, the evaporated refrigerant gas enters the air suction port of the compressor 1 through the heat regenerator 4, so that liquid drops wrapped by the refrigerant gas can be prevented from directly entering the air suction port of the compressor 1, the compressor is prevented from generating liquid impact, and the performance of a refrigeration system can be improved by utilizing heat regeneration circulation.
In summary, compared with the prior art, the utility model provides a take two-flow microchannel evaporator refrigeration system of liquid level control and bypass air duct, it can realize the control to refrigerant liquid level height in the entry header of microchannel evaporator, guarantees that each flat tube line evenly supplies liquid refrigerant in the first flow of microchannel evaporator (the flat pipe that entry header and entry header correspond is the first flow of evaporator; the flat pipe that exit header and exit header correspond is the second flow of evaporator); meanwhile, the bypass air duct can separate the gas and the liquid of the refrigerant evaporated in the first flow, so that the liquid of the refrigerant efficiently enters the flat tubes of the second flow to be evaporated, the interference of the gas-phase refrigerant on the distribution of the liquid-phase refrigerant in each flat tube is avoided, the heat exchange area of the evaporator is fully utilized, the overall heat exchange performance of the microchannel evaporator is improved, and the microchannel evaporator has great production practice significance.
Furthermore, it is right the utility model provides a take two flow microchannel evaporator refrigerating system of liquid level control and bypass air duct, the regenerator that it has still can avoid the refrigerant gas after the evaporation to wrap up in the liquid drop of holding by the side with most gaseous phase refrigerant and directly gets into the compressor induction port, prevents that the compressor from producing the liquid and hits, also can utilize the backheat circulation, improves refrigerating system's performance.
The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, a plurality of modifications and decorations can be made without departing from the principle of the present invention, and these modifications and decorations should also be regarded as the protection scope of the present invention.
Claims (3)
1. Take liquid level control and bypass air duct's two-flow microchannel evaporator refrigerating system, its characterized in that, including compressor (1), oil separator (2), condenser (3), regenerator (4), first solenoid valve (5), non-through formula floater choke valve (6) and two-flow-path microchannel evaporator (7), wherein:
the double-flow micro-channel evaporator (7) comprises a hollow confluence header (73) and a main header (70) which are arranged at left and right intervals;
the opposite sides of the confluence collecting pipe (73) and the main collecting pipe (70) are communicated through a plurality of flat pipes (72) which are distributed transversely;
a branch baffle (75) which is transversely distributed is arranged in the main collecting pipe (70);
the range dividing baffle (75) divides the main header (70) into two cavities, namely an inlet header (71) and an outlet header (74);
the inlet header (71) is located below the outlet header (74);
the air outlet at the top of the confluence collecting pipe (73) is communicated with the air outlet in the middle of the right side of the outlet collecting pipe (74) through an air duct (76);
wherein, the exhaust port at the top of the compressor (1) is communicated with the refrigerant inlet of the oil separator (2);
the refrigerant outlet of the oil separator (2) is communicated with the refrigerant inlet of the condenser (3);
the refrigerant outlet of the condenser (3) is communicated with the first refrigerant inlet of the heat regenerator (4);
a first refrigerant outlet of the heat regenerator (4) is communicated with a refrigerant inlet of the non-straight-through floating ball throttle valve (6) through a first electromagnetic valve (5);
a second refrigerant inlet of the heat regenerator (4) is communicated with an air outlet of an outlet header (74) in the double-flow-path micro-channel evaporator (7);
a second refrigerant outlet of the heat regenerator (4) is communicated with an air suction port of the compressor (1);
the refrigerant outlet of the non-straight-through type floating ball throttle valve (6) is communicated with a liquid inlet at the bottom of an inlet header (71) in the double-flow-path micro-channel evaporator (7).
2. The dual-flow microchannel evaporator refrigeration system as set forth in claim 1, wherein the oil inlet of the compressor (1) communicates with one end of the second solenoid valve (8) through a hollow connecting pipe;
the other end of the second electromagnetic valve (8) is communicated with an oil return port at the bottom of the oil separator (2) through a hollow connecting pipeline.
3. The dual flow microchannel evaporator refrigeration system as set forth in claim 1 wherein the non-straight-through floating ball throttle valve (6) comprises a main valve (61);
the main valve (61) is arranged on a refrigerant inlet of the non-straight-through floating ball throttle valve (6);
a hollow floating ball chamber (62) is arranged in the non-through type floating ball throttle valve (6);
a float ball (63) is arranged in the float chamber (62) and floats on the liquid level of the refrigerant liquid in the float chamber (62);
a first port of the non-straight-through type floating ball throttle valve (6) is communicated with the lower part of the right side of the inlet header pipe (71) through a liquid balance pipe (64);
and a second port of the non-straight-through type floating ball throttle valve (6) is communicated with an air outlet of the outlet header pipe (74) through an air balance pipe (65).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921796105.7U CN210861761U (en) | 2019-10-24 | 2019-10-24 | Double-process microchannel evaporator refrigerating system with liquid level control and bypass air guide tube |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921796105.7U CN210861761U (en) | 2019-10-24 | 2019-10-24 | Double-process microchannel evaporator refrigerating system with liquid level control and bypass air guide tube |
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| Publication Number | Publication Date |
|---|---|
| CN210861761U true CN210861761U (en) | 2020-06-26 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201921796105.7U Expired - Fee Related CN210861761U (en) | 2019-10-24 | 2019-10-24 | Double-process microchannel evaporator refrigerating system with liquid level control and bypass air guide tube |
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| CN (1) | CN210861761U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114396373A (en) * | 2022-01-28 | 2022-04-26 | 烟台珈群高效节能设备有限公司 | Oil cooling subsystem of evaporative condenser |
-
2019
- 2019-10-24 CN CN201921796105.7U patent/CN210861761U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114396373A (en) * | 2022-01-28 | 2022-04-26 | 烟台珈群高效节能设备有限公司 | Oil cooling subsystem of evaporative condenser |
| CN114396373B (en) * | 2022-01-28 | 2024-01-16 | 烟台珈群高效节能设备有限公司 | Oil cooling subsystem for evaporative condenser |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20200626 Termination date: 20201024 |
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| CF01 | Termination of patent right due to non-payment of annual fee |