CN211781669U - Air-cooled partial heat recovery unit system - Google Patents
Air-cooled partial heat recovery unit system Download PDFInfo
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- CN211781669U CN211781669U CN201922445322.8U CN201922445322U CN211781669U CN 211781669 U CN211781669 U CN 211781669U CN 201922445322 U CN201922445322 U CN 201922445322U CN 211781669 U CN211781669 U CN 211781669U
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Abstract
The utility model provides an air-cooled partial heat recovery unit system, belonging to the field of air conditioning systems, comprising a compressor, a hot water side heat exchanger, a high pressure side gas-liquid separator, an air side heat exchanger and an air conditioner water side heat exchanger; the medium sequentially passes through the hot water side heat exchanger, the high-pressure side gas-liquid separator and the electronic expansion valve from the compressor to the air conditioner water side heat exchanger, and a first electromagnetic valve is arranged on the first branch; a medium sequentially passes through the hot water side heat exchanger, the high-pressure side gas-liquid separator, the air side heat exchanger and the electronic expansion valve from the compressor to the air conditioner water side heat exchanger, a throttling capillary tube is arranged in parallel with the electronic expansion valve, and a second electromagnetic valve is arranged on a branch where the throttling capillary tube is located; and in the fifth branch, the medium flows back to the compressor from the air-conditioning water side heat exchanger. The utility model discloses the compressor is stable, is difficult to appear jumping the problem of low pressure.
Description
Technical Field
The utility model belongs to the air conditioning system field relates to forced air cooling part heat recovery unit system.
Background
Various problems can occur in the actual operation of the heat recovery unit of the current air cooling module machine part, and the problems mainly comprise the following conditions: (1) when in refrigeration operation, 1, when the environment temperature is higher and the heat recovery water temperature is lower, the heat exchange capacity of the fin tube type heat exchanger (condenser) is weakened and the heat exchange capacity of the heat recovery heat exchanger is improved, at the moment, high-temperature and high-pressure gaseous refrigerants in the system enter the heat recovery heat exchanger to perform convective heat exchange, and the refrigerants are excessively cooled to a wet saturation area, so that the refrigerants coming out of the heat recovery heat exchanger are in a gas-liquid mixing state, for a heat pump type unit, when the refrigerants coming out of the heat recovery heat exchanger pass through a four-way reversing valve, a large amount of liquid refrigerants easily hit the four-way reversing valve due to the fact that the refrigerants are in the gas-liquid mixing state, on the other hand, when the gas-liquid mixing refrigerants coming out of the four-way reversing valve enter the fin tube type heat exchanger, liquid separation of each branch, the supercooling degree of the system is reduced, a large amount of gaseous refrigerant appears in front of the expansion valve, so that choked flow appears in the throttling process, the pipeline behind the expansion valve is seriously frosted, and the compressor frequently jumps to low pressure; 2. when the ring temperature is low and the water temperature is low, at the moment, because a condensation fan of the unit is influenced by the ring temperature or the fin temperature or the high pressure of the system, the air volume is reduced (if the air volume is not reduced, the high pressure and the low pressure of the compressor are reduced when part of the heat recovery water pump stops non-heat recovery, and the pressure of the compressor is jumped to be low), the capacity of the fin tube type heat exchanger is also reduced, but the heat exchange capacity in the heat recovery heat exchanger is improved, the supercooling degree of the system is low under the condition, a large amount of gaseous refrigerant is generated in front of the expansion valve, and the pressure of the; 3. when the heat recovery water pump is started from a stop state under any working condition, the high-pressure side pressure of the system is suddenly reduced to drive the low pressure to be also suddenly reduced due to the heat recovery heat exchanger for heat exchange and cooling of high-temperature and high-pressure refrigerants, and the running compressor is easy to jump to the low pressure at the moment; 4. for achieving the purpose of controlling the heat exchange capacity of hot water on the heat recovery side by controlling the air volume of the condensing fan, when the condensing air volume is suddenly reduced, part of the heat recovery heat exchange capacity is improved at the moment, the high pressure of the system is improved, but the low pressure is reduced, because on one hand, the heat exchange capacity of the fin tube type heat exchanger is reduced, and on the other hand, the part of the heat recovery heat exchange capacity is improved, the refrigerant at an outlet is in a gas-liquid mixed state, the refrigerant distribution uniformity is influenced when the refrigerant enters the fin tube type heat exchanger, so that the low pressure is lower, a pipeline behind an expansion valve frosts.
(2) During heating operation, 1, when the temperature of water at the air conditioner side is higher and the temperature of hot water at the hot water side is lower, the heat exchange capacity at the side of a partial heat recovery heat exchanger is improved, and the heat exchange capacity of a shell-and-tube heat exchanger or a plate heat exchanger is reduced, so that a refrigerant coming out of the partial heat recovery heat exchanger is in a wet saturation state and contains a large amount of liquid refrigerant, the four-way valve is easily subjected to liquid impact when passing through the four-way valve, in addition, the refrigerant is unevenly distributed when entering the shell-and-tube heat exchanger or the plate heat exchanger, in conclusion, the supercooling degree of a system is reduced, a large amount of gaseous refrigerant is contained in front of an expansion valve, choked flow occurs; 2. under the conditions that the water temperature of an air conditioner side is low and the hot water temperature of a hot water side is low, the refrigerant on the high pressure side of the system is fully subjected to heat exchange, the high pressure of the system is low, the quantity of the refrigerant participating in circulation is relatively insufficient, the supercooling degree is low, the gaseous refrigerant is contained in front of an expansion valve, the low pressure of the system is reduced along with the high pressure, if the refrigerant is replenished according to the condition, the high pressure is high after the hot water pump is stopped, the refrigerant of the system is excessive under other operation working conditions, and if the refrigerant is not replenished, the finned tube heat exchanger (which is used as an evaporator at the moment) is frequently frosted; 3. when the heat recovery water pump is started from a stop state under any working condition, the heat recovery heat exchanger participates in heat exchange and cooling of high-temperature and high-pressure refrigerants, so that the high-pressure side pressure of the system is suddenly reduced, the low pressure is also suddenly reduced, and the running compressor is easy to jump to the low pressure at the moment.
SUMMERY OF THE UTILITY MODEL
The to-be-solved problem of the utility model is to provide an air-cooled partial heat recovery unit system, the compressor is stable, is difficult to appear jumping the problem of low pressure.
In order to solve the technical problem, the utility model discloses a technical scheme is: the air cooling part heat recovery unit system comprises a compressor, a hot water side heat exchanger, a high-pressure side gas-liquid separator, an air side heat exchanger and an air conditioner water side heat exchanger;
the medium sequentially passes through the hot water side heat exchanger, the high-pressure side gas-liquid separator and the electronic expansion valve from the compressor to the air-conditioning water side heat exchanger, a first electromagnetic valve is arranged on the first branch, the first electromagnetic valve is arranged between the high-pressure side gas-liquid separator and the electronic expansion valve, a throttling capillary tube is arranged in parallel with the electronic expansion valve, and a second electromagnetic valve is arranged on a branch where the throttling capillary tube is arranged;
a medium sequentially passes through the hot water side heat exchanger, the high-pressure side gas-liquid separator, the air side heat exchanger and the electronic expansion valve from the compressor to the air conditioner water side heat exchanger, a throttling capillary tube is arranged in parallel with the electronic expansion valve, and a second electromagnetic valve is arranged on a branch where the throttling capillary tube is located;
and in the fifth branch, the medium flows back to the compressor from the air-conditioning water side heat exchanger.
Furthermore, a check valve is arranged between the electronic expansion valve and the air-conditioning water side heat exchanger on the first branch, and a check valve is arranged between the air side heat exchanger and the electronic expansion valve on the second branch.
Furthermore, the outlet of the check valve on the first branch is communicated with the outlet of the check valve on the second branch through a third branch, the third branch is provided with the check valve and flows to the second branch from the first branch, the inlet of the check valve on the first branch is communicated with the one-way inlet on the second branch through a fourth branch, and the third branch is provided with the check valve and flows to the second branch from the first branch.
Furthermore, the first branch and the second branch are converged and then communicated with the electronic expansion valve after passing through the drying filter, and the fifth branch is provided with a second filter.
Furthermore, the first branch and the second branch are converged to a high-pressure side liquid storage device, and an outlet end of the high-pressure side liquid storage device is communicated with the electronic expansion valve after passing through a drying filter.
Furthermore, on the second branch, the high-pressure side gas-liquid separator is connected with the air side heat exchanger through a four-way reversing valve, and on the fifth branch, the air-conditioning water side heat exchanger is communicated with the compressor after passing through the four-way reversing valve and then passing through the low-pressure side gas-liquid separator and the second filter.
Furthermore, the first branch and the second branch are converged to a high-pressure side liquid storage device, and an outlet end of the high-pressure side liquid storage device is communicated with the electronic expansion valve after passing through a drying filter.
Furthermore, the outlet of the check valve on the first branch is communicated with the outlet of the check valve on the second branch through a third branch, the third branch is provided with the check valve and flows to the second branch from the first branch, one side of the third branch close to the air-conditioning water side heat exchanger is provided with a high-pressure side liquid reservoir, the inlet of the check valve on the first branch is communicated with the one-way inlet on the second branch through a fourth branch, and the fourth branch is provided with the check valve and flows to the second branch from the first branch.
Compared with the prior art, the utility model has the advantages and positive effect as follows.
1. The utility model discloses set up the throttle capillary parallelly connected with electronic expansion valve, be equipped with the second solenoid valve on the branch road that throttle capillary is located, and the second solenoid valve is strictly opened and is closed according to the condition of setting for, avoid the plug flow, the heat transfer ability of air side heat exchanger has been guaranteed, guarantee refrigerant distribution uniformity, the compressor steady operation, whole unit operation is stable, the high low pressure is steady in the operation process, be difficult for appearing undulant, can guarantee that any condition primary circuit electronic expansion valve front refrigerant has sufficient super-cooled rate, start and stop the process and under the different hot water temperature at the hot-water pump, can not appear low pressure trouble under the different ring temperature;
2. the first branch is provided with the first electromagnetic valve, and the opening and closing of the first electromagnetic valve are also strictly opened and closed according to set conditions, so that when defrosting is carried out, the first electromagnetic valve can be closed in a delayed mode, shunting and current limiting are effectively realized, frosting of a pipeline is avoided, the stability of the operation of a structure is improved, and the stable operation of the compressor is ensured;
3. set up third branch road and fourth branch road, realized thermal recovery and recycled, the structure of this application has fine the problem of having solved existence among the background art, has realized the even running of compressor, long service life.
Drawings
The accompanying drawings, which form a part hereof, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention without undue limitation. In the drawings:
FIG. 1 is a flow chart of an embodiment 1 of the air-cooled partial heat recovery unit system of the present invention;
FIG. 2 is a flow chart of embodiment 2 of the air-cooled partial heat recovery unit system of the present invention;
FIG. 3 is a flow chart of embodiment 3 of the air-cooled partial heat recovery unit system of the present invention;
fig. 4 is a flow chart of embodiment 4 of the air-cooled partial heat recovery unit system of the present invention.
Reference numerals:
1. a hot water side heat exchanger; 2. a compressor; 3. a first filter; 4. a low-pressure side gas-liquid separator; 5. an air-side heat exchanger; 6. a four-way reversing valve; 7. a high pressure side gas-liquid separator; 8. a first solenoid valve; 9. an electronic expansion valve; 10. a one-way valve; 11. a high-pressure side reservoir; 12. throttling the capillary tube; 13. a second solenoid valve; 14. drying the filter; 15. an air-conditioning water side heat exchanger; 20. a first branch; 30. a second branch circuit; 40. a fourth branch; 50. a third branch; 60. and a fifth branch.
Detailed Description
It should be noted that, in the present invention, the embodiments and features of the embodiments may be combined with each other without conflict.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are used merely for convenience of description and for simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present invention. Furthermore, the terms "first", "second", etc. are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first," "second," etc. may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art through specific situations.
The following detailed description of the embodiments of the present invention will be made with reference to the accompanying drawings.
As shown in fig. 1, example 1: the utility model relates to an air-cooled partial heat recovery unit system, which comprises a compressor 2, a hot water side heat exchanger 1, a high pressure side gas-liquid separator 7, an air side heat exchanger 5 and an air conditioner water side heat exchanger 15;
a first branch 20, from the compressor 2, the medium sequentially passes through the hot water side heat exchanger 1, the high pressure side gas-liquid separator 7 and the electronic expansion valve 9 to the air-conditioning water side heat exchanger 15, a first electromagnetic valve 8 is arranged on the first branch, the first electromagnetic valve 8 is arranged between the high pressure side gas-liquid separator 7 and the electronic expansion valve 9, a throttling capillary tube 12 is arranged in parallel with the electronic expansion valve 9, and a second electromagnetic valve 13 is arranged on the branch where the throttling capillary tube 12 is located;
a second branch 30, in which a medium sequentially passes through the hot water side heat exchanger 1, the high pressure side gas-liquid separator 7, the air side heat exchanger 5, the electronic expansion valve 9 and the air-conditioning water side heat exchanger 15 from the compressor 2, a throttle capillary tube 12 is arranged in parallel with the electronic expansion valve 9, a second electromagnetic valve 13 is arranged on a branch where the throttle capillary tube 12 is located, the first branch 20 and the second branch 30 are converged and then pass through the electronic expansion valve 9, namely, a flow path behind the electronic expansion valve 9, and the first branch 20 and the second branch 30 are the same;
and a fifth branch 60, through which the medium flows from the air-conditioning water-side heat exchanger 15 back to the compressor 2.
Preferably, a check valve 10 is arranged between the electronic expansion valve 9 and the air-conditioning water side heat exchanger 15 on the first branch, and the check valve 10 is arranged between the air side heat exchanger 5 and the electronic expansion valve 9 on the second branch.
Preferably, the outlet of the check valve 10 on the first branch is communicated with the outlet of the check valve on the second branch through a third branch, the third branch 50 is provided with the check valve 10 and flows from the first branch to the second branch, the inlet of the check valve 10 on the first branch is communicated with the one-way inlet on the second branch through a fourth branch 40, and the third branch is provided with the check valve 10 and flows from the first branch to the second branch.
Preferably, the first branch and the second branch are merged and then communicated with the electronic expansion valve 9 after passing through the dry filter 14, and the fifth branch is provided with a second filter.
The above structure is a single-cooling type structure, and a plurality of embodiments can be further extended for the above structure, and the analysis is as follows.
As shown in fig. 2, example 2: different from the above structure, the first branch and the second branch are collected in the high-pressure side reservoir 11, and the outlet end of the high-pressure side reservoir 11 is communicated with the electronic expansion valve 9 after passing through the dry filter 14.
As shown in fig. 3, example 3: the difference from the embodiment 2 is that, on the second branch, the high-pressure side gas-liquid separator 7 is connected with the air side heat exchanger 5 through the four-way reversing valve 6, and on the fifth branch, the air-conditioning water side heat exchanger 15 is communicated with the compressor 2 after passing through the four-way reversing valve 6, then passing through the low-pressure side gas-liquid separator 4 and the second filter.
As shown in fig. 4, example 4: the difference from the embodiment 1 is that, on the second branch, the high-pressure side gas-liquid separator 7 is connected with the air side heat exchanger 5 through the four-way reversing valve 6, on the fifth branch, the air-conditioning water side heat exchanger 15 passes through the four-way reversing valve 6, then passes through the low-pressure side gas-liquid separator 4 and the second filter, and then is communicated with the compressor 2, and on one side of the third branch, which is close to the air-conditioning water side heat exchanger 15, the high-pressure side liquid accumulator 11 is arranged.
The working processes of the embodiments 1 and 2 are the same as those of the embodiment 4, or the working processes of the other embodiments are the same as those of the embodiment 4, or are part of the embodiment 4.
In the practical application process, during refrigeration, high-temperature high-pressure superheated gaseous refrigerant discharged by a compressor 2 firstly passes through a hot water side heat exchanger 1 for sensible heat exchange, the refrigerant discharged from the hot water side heat exchanger 1 passes through a high-pressure side gas-liquid separator 7, then the gaseous refrigerant is discharged from the upper side to a four-way reversing valve 6, liquid refrigerant is discharged from the lower side and enters a high-pressure side reservoir 11 through a first electromagnetic valve 8, the gaseous refrigerant discharged from the four-way reversing valve enters an air side heat exchanger 5, the air side heat exchanger 5 is a fin-tube heat exchanger system (condenser), the gaseous refrigerant is cooled again for heat exchange, then is changed into high-pressure medium-temperature liquid refrigerant and enters a high-pressure side reservoir 11, and then enters an air-conditioning water side heat exchanger 15 after passing through an electronic expansion valve 9, a second electromagnetic valve 13 and a throttling capillary tube 12, and, the chilled water absorbs heat from the air conditioner side, enters the four-way reversing valve 6 and the low-pressure gas-liquid separator, and returns to the compressor 2 to complete a heat recovery cycle of a refrigeration part.
During heating, high-temperature high-pressure superheated gaseous refrigerant discharged from the compressor 2 firstly passes through the hot water side heat exchanger 1 for sensible heat exchange, the gaseous refrigerant discharged from the hot water side heat exchanger 1 passes through the high-pressure side gas-liquid separator 7 and then is discharged into the four-way reversing valve 6 from the upper side, liquid refrigerant is discharged from the lower side and enters the high-pressure side liquid reservoir 11 through the first electromagnetic valve 8, the gaseous refrigerant discharged from the four-way reversing valve 6 enters the air-conditioning water side heat exchanger 15, the air-conditioning water side heat exchanger 15 is a shell-and-tube heat exchanger or a plate heat exchanger (evaporator), is subjected to heat exchange and cooling again to form high-pressure medium-temperature liquid refrigerant, enters the high-pressure side liquid reservoir 11, passes through the expansion valve, the second electromagnetic valve 13 and the throttling capillary tube 12 and then enters the air side heat exchanger 5, the air side heat exchanger 5 is a fin-tube heat exchanger system (condenser), absorbs heat from ambient air And (6) recycling.
The system control is as follows:
opening condition of the first electromagnetic valve 8:
(1) starting a heat recovery water pump;
(2) the hot water temperature of the heat recovery device is less than or equal to a set value T1;
(3) when in refrigerating operation, the condensing fan in the air side heat exchanger 5 is low-speed air;
(4) when in heating operation, the water temperature of the air-conditioning water side heat exchanger 15 is higher than a set value T2;
(5) when in refrigeration operation, the system low pressure is lower than a set value LPC 1;
(6) during heating operation, the system low pressure is below the set point LPh 1.
The condition (1) is a precondition, the conditions (2), (3), and (5) during cooling are determined on the basis of the condition (1), the first solenoid valve 8 is opened as long as one of the conditions (2), (3), and (5) is satisfied and the condition (1) is satisfied, and the conditions (2), (4), and (6) during heating are determined on the basis of the condition 1, and the first solenoid valve 8 is opened as long as one of the conditions (2), (4), and (6) is satisfied and the condition (1) is satisfied.
First solenoid valve 8 closed condition:
(1) the heat recovery water pump is closed;
(2) the hot water temperature of the heat recovery device is higher than a set value T1;
(3) during the refrigeration operation, a condensing fan in the air side heat exchanger 5 is high-speed air;
(4) when in heating operation, the water temperature of the air-conditioning water side heat exchanger 15 is less than or equal to a set value T2;
(5) when in refrigerating operation, the system low pressure is more than or equal to a set value LPc1+ Δ Pc 1; LP low pressure, C1-refrigeration low pressure, H1: heating low pressure, Δ Pc1 — refrigeration low pressure recovery value;
(6) when the heating operation is performed, the low pressure of the system is greater than or equal to a set value LPh1+ delta Ph 1;
after the condition (1) is met, whether other conditions are met or not, the first electromagnetic valve 8 is closed within a delay time t (the delay time can be set) after the heat recovery water pump is closed; if the condition (1) is not met, the first electromagnetic valve 8 is allowed to be closed only if the conditions (2), (3) and (5) are met simultaneously during the refrigerating operation; during heating operation, the conditions (2), (4), and (6) must be satisfied at the same time, and the first electromagnetic valve 8 is allowed to be closed.
If partial heat recovery water pump is opened when the unit meets defrosting, the unit enters defrosting and the partial heat recovery water pump is closed at the same time, the condition (1) is met, and the first electromagnetic valve 8 is closed after the heat recovery water pump is closed for delay time t.
Opening condition of the second electromagnetic valve 13:
(1) opening a heat recovery water pump;
(2) when in refrigeration operation, the system low pressure is lower than a set value LPC 2;
(3) during heating operation, the low pressure of the system is lower than a set value LPh 2;
the conditions (2) and (3) are judged on the basis of the condition (1), and when the conditions (1) and (2) are met during the refrigerating operation, the second electromagnetic valve 13 is allowed to be opened; in the heating operation, the second electromagnetic valve 13 is allowed to be opened only when the conditions (1) and (3) are satisfied.
(1) the heat recovery water pump is closed;
(2) when in refrigerating operation, the system low pressure is more than or equal to a set value LPc2+ Δ Pc 2;
(3) when the heating operation is performed, the low pressure of the system is greater than or equal to a set value LPh2+ delta Ph 2;
if the unit meets the condition (1), the conditions (2) and (3) are not needed to be judged, and the second electromagnetic valve 13 is directly closed; if the condition (1) is not met, the condition (2) is met during the refrigerating operation, the second electromagnetic valve 13 is directly closed, the condition (3) is met during the heating operation, and the second electromagnetic valve 13 is directly closed; in addition, during defrosting, the heat recovery water pump is forcibly closed, and at the moment, the second electromagnetic valve 13 is directly closed when meeting the condition (1).
Wherein:
the set value of the refrigeration low pressure LPc2 is less than or equal to LPc1, and the set return difference value delta Pc2 is less than or equal to delta Pc 1;
the heating low pressure set value LPh2 is not more than LPh1, and the heating low pressure is set back to the difference value delta Ph2 is not more than delta Ph 1;
and the above set values may be set in a program by a low pressure sensor or satisfy the control process by selecting a low pressure switch of a corresponding value.
While one embodiment of the present invention has been described in detail, the description is only a preferred embodiment of the present invention, and should not be considered as limiting the scope of the present invention. All the equivalent changes and improvements made according to the application scope of the present invention should still fall within the patent coverage of the present invention.
Claims (8)
1. Air-cooled partial heat recovery unit system, its characterized in that: the system comprises a compressor, a hot water side heat exchanger, a high-pressure side gas-liquid separator, an air side heat exchanger and an air conditioner water side heat exchanger;
the medium sequentially passes through the hot water side heat exchanger, the high-pressure side gas-liquid separator and the electronic expansion valve from the compressor to the air-conditioning water side heat exchanger, a first electromagnetic valve is arranged on the first branch, the first electromagnetic valve is arranged between the high-pressure side gas-liquid separator and the electronic expansion valve, a throttling capillary tube is arranged in parallel with the electronic expansion valve, and a second electromagnetic valve is arranged on a branch where the throttling capillary tube is arranged;
a medium sequentially passes through the hot water side heat exchanger, the high-pressure side gas-liquid separator, the air side heat exchanger and the electronic expansion valve from the compressor to the air conditioner water side heat exchanger, a throttling capillary tube is arranged in parallel with the electronic expansion valve, and a second electromagnetic valve is arranged on a branch where the throttling capillary tube is located;
and in the fifth branch, the medium flows back to the compressor from the air-conditioning water side heat exchanger.
2. The air-cooled partial heat recovery unit system of claim 1, wherein: and a check valve is arranged between the electronic expansion valve and the air-conditioning water side heat exchanger on the first branch, and a check valve is arranged between the air side heat exchanger and the electronic expansion valve on the second branch.
3. The air-cooled partial heat recovery unit system of claim 2, wherein: the one-way valve outlet on the first branch is communicated with the one-way valve outlet on the second branch through a third branch, the third branch is provided with a one-way valve and flows to the second branch from the first branch, the inlet of the one-way valve on the first branch is communicated with the one-way inlet on the second branch through a fourth branch, and the third branch is provided with a one-way valve and flows to the second branch from the first branch.
4. The air-cooled partial heat recovery unit system of claim 1, wherein: the first branch and the second branch are converged, then are communicated with the electronic expansion valve after passing through the drying filter, and the fifth branch is provided with a second filter.
5. The air-cooled partial heat recovery unit system of claim 1, wherein: the first branch and the second branch are converged to the high-pressure side liquid storage device, and the outlet end of the high-pressure side liquid storage device is communicated with the electronic expansion valve after passing through the drying filter.
6. The air-cooled partial heat recovery unit system of claim 1, wherein: on the second branch, the high-pressure side gas-liquid separator is connected with the air side heat exchanger through a four-way reversing valve, and on the fifth branch, the air-conditioning water side heat exchanger is communicated with the compressor after passing through the four-way reversing valve and then passing through the low-pressure side gas-liquid separator and the second filter.
7. The air-cooled partial heat recovery unit system of claim 6, wherein: the first branch and the second branch are converged to the high-pressure side liquid storage device, and the outlet end of the high-pressure side liquid storage device is communicated with the electronic expansion valve after passing through the drying filter.
8. The air-cooled partial heat recovery unit system of claim 6, wherein: the one-way valve outlet on the first branch is communicated with the one-way valve outlet on the second branch through a third branch, the third branch is provided with a one-way valve and flows to the second branch from the first branch, one side of the third branch, which is close to the air-conditioning water side heat exchanger, is provided with a high-pressure side liquid reservoir, the inlet of the one-way valve on the first branch is communicated with the one-way inlet on the second branch through a fourth branch, and the fourth branch is provided with a one-way valve and flows to the second branch from the first branch.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922445322.8U CN211781669U (en) | 2019-12-28 | 2019-12-28 | Air-cooled partial heat recovery unit system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201922445322.8U CN211781669U (en) | 2019-12-28 | 2019-12-28 | Air-cooled partial heat recovery unit system |
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| CN211781669U true CN211781669U (en) | 2020-10-27 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111059665A (en) * | 2019-12-28 | 2020-04-24 | 维克（天津）有限公司 | Air-cooled partial heat recovery unit system and control mode |
| CN112696840A (en) * | 2020-12-18 | 2021-04-23 | 无锡同方人工环境有限公司 | All-weather wide-range bidirectional flow regulating device and regulating process thereof |
-
2019
- 2019-12-28 CN CN201922445322.8U patent/CN211781669U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111059665A (en) * | 2019-12-28 | 2020-04-24 | 维克（天津）有限公司 | Air-cooled partial heat recovery unit system and control mode |
| CN111059665B (en) * | 2019-12-28 | 2024-03-29 | 维克（天津）有限公司 | Air-cooled part heat recovery unit system and control mode |
| CN112696840A (en) * | 2020-12-18 | 2021-04-23 | 无锡同方人工环境有限公司 | All-weather wide-range bidirectional flow regulating device and regulating process thereof |
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