CN109882939B - Dual-evaporation fresh air handling unit - Google Patents
Dual-evaporation fresh air handling unit Download PDFInfo
- Publication number
- CN109882939B CN109882939B CN201910104679.1A CN201910104679A CN109882939B CN 109882939 B CN109882939 B CN 109882939B CN 201910104679 A CN201910104679 A CN 201910104679A CN 109882939 B CN109882939 B CN 109882939B
- Authority
- CN
- China
- Prior art keywords
- heat exchanger
- valve
- fresh air
- compressor
- branch
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Abstract
The invention discloses a double-evaporation fresh air unit, which belongs to the field of air conditioning and refrigeration and comprises a compressor, an outdoor heat exchanger, a liquid storage device and an indoor unit, the indoor unit comprises a first heat exchanger, a second heat exchanger and a blower, fresh air is enabled to sequentially pass through the first heat exchanger and the second heat exchanger, the air outlet of the compressor is connected with the outdoor heat exchanger, the outdoor heat exchanger is connected with the liquid storage device, the outlet of the liquid storage device is provided with a first electromagnetic valve, the outlet of the liquid storage device is respectively connected with a first branch provided with a first throttling device and a first heat exchanger in sequence, and a second branch which is sequentially connected with a second throttling device and the second heat exchanger, wherein the first branch and the second branch are connected with an air suction port of the compressor to form a loop. Due to the use of the double-evaporation-temperature compressor, the efficiency of the compressor in a refrigeration mode is obviously higher than that of a common fresh air handling unit.
Description
Technical Field
The invention relates to the field of air conditioner refrigeration, in particular to a double-evaporation fresh air handling unit.
Background
The new air system has become popular in foreign office spaces and homes, but has just emerged in china. In the coming years, with the development of Chinese economy, the requirements of people on living environment are higher and higher, and the industry of the fresh air system enters a rapid development period. The use of a dual evaporating temperature compressor now makes it possible to have two different evaporating temperatures in one refrigeration system, and also provides a new method for warm-humid treatment of outdoor air. The double-evaporation temperature compressor has the characteristics of double cylinders and double suction, and two cylinders share one crankshaft. The refrigerants from the two evaporators enter the corresponding cylinders respectively to be compressed, and the compressed refrigerants are mixed in a discharge cavity of the compressor and then are sent into the condenser. Because the exhaust gas shares one exhaust cavity, the double evaporation temperature compressor only has one exhaust gas pressure.
In view of the above advantages, those skilled in the art have made an effort to develop a dual-evaporation fresh air handling unit, which combines refrigeration with a fresh air system using a dual-evaporation temperature compressor to improve energy efficiency ratio (COP) and refrigeration efficiency, and has various operation modes.
Disclosure of Invention
In view of the above-mentioned drawbacks of the prior art, the technical problem to be solved by the present invention is to simplify the unit architecture, integrate multiple operation modes, and improve the energy efficiency ratio and the refrigeration efficiency.
In order to achieve the above object, the present invention provides a dual-evaporation fresh air unit, comprising a compressor, an outdoor heat exchanger, a reservoir, and an indoor unit, wherein the indoor unit comprises a first heat exchanger and a second heat exchanger, and further comprises a blower for passing fresh air through the first heat exchanger and the second heat exchanger in sequence, an exhaust port of the compressor is connected to the outdoor heat exchanger, the outdoor heat exchanger is further connected to the reservoir, an outlet of the reservoir is provided with a first electromagnetic valve, an outlet of the reservoir is respectively provided with a first branch provided with a first throttling device and the first heat exchanger in sequence, and a second branch provided with a second throttling device and the second heat exchanger in sequence, the first branch and the second branch are connected to an air suction port of the compressor, a loop is formed.
Further, the exhaust port of the compressor is connected with the outdoor heat exchanger by using a four-way reversing valve, and the compressor uses a double-evaporation-temperature compressor.
Furthermore, the indoor unit set further comprises a third heat exchanger, the liquid storage device is further provided with a third branch, the third branch is provided with a second electromagnetic valve connected with an inlet of the third heat exchanger, and an outlet of the third heat exchanger is connected with the first branch and the second branch.
Furthermore, a fourth branch is arranged between the compressor and the outdoor heat exchanger, the fourth branch is provided with a first electronic expansion valve which is connected with an inlet of the third heat exchanger, and a second electronic expansion valve is arranged between the outdoor heat exchanger and the liquid storage device.
Further, the first electronic expansion valve and the second electronic expansion valve have a first drift diameter and a second drift diameter, and the flow resistance of the first drift diameter is larger than that of the second drift diameter.
Furthermore, the device also comprises a first one-way valve and a second one-way valve, wherein the first one-way valve is connected with the first throttling device in parallel, the second one-way valve is connected with the second throttling device in parallel, and the flow directions of the first one-way valve and the second one-way valve are opposite to the flow directions of the first throttling device and the second throttling device.
Further, the first throttling device and the second throttling device use electronic expansion valves, and the electronic expansion valves only have one-section drift diameter.
Furthermore, the indoor unit set is also provided with a bypass air valve.
Further, a humidity sensor is arranged at an outlet of the indoor unit, and the operating frequency of the compressor is reduced after a preset humidity is reached.
The fresh air handling unit has three different working modes (including a refrigeration mode, an enhanced dehumidification refrigeration mode and an isothermal dehumidification mode) according to three typical conditions (including high temperature, high temperature and high humidity and humidity) of outdoor air in summer, and can carry out different treatments on fresh air in winter in addition to the heating mode. And the use of three indoor heat exchangers and a bypass air valve enables the temperature and humidity of fresh air sent into the room to be controlled better.
Because the high evaporation temperature is adopted in the circulation, and the use of the indoor third heat exchanger plays a role in recovering partial condensation heat or supercooling, the energy efficiency ratio (COP) of the unit is improved, and the energy consumption of the system is reduced.
The conception, the specific structure and the technical effects of the present invention will be further described with reference to the accompanying drawings to fully understand the objects, the features and the effects of the present invention.
Drawings
Fig. 1 is a schematic diagram of an assembly according to a preferred embodiment of the present invention.
Wherein 1-double evaporation temperature compressor; 2-a first heat exchanger; 3-a second heat exchanger; 4-a third heat exchanger; 5-a blower; 6-outdoor heat exchanger; 7-a reservoir; 8-a first four-way reversing valve; 9-a second four-way reversing valve; 10-a first solenoid valve; 11-a second solenoid valve; 12-a first electronic expansion valve; 13-a second electronic expansion valve; 14-a third electronic expansion valve; 15-a fourth electronic expansion valve; 16-a first one-way valve; 17-a second one-way valve; 18-a bypass air valve; a-a high pressure suction cavity; b-a low pressure suction chamber.
Detailed Description
The technical contents of the preferred embodiments of the present invention will be more clearly and easily understood by referring to the drawings attached to the specification. The present invention may be embodied in many different forms of embodiments and the scope of the invention is not limited to the embodiments set forth herein.
In the drawings, structurally identical elements are represented by like reference numerals, and structurally or functionally similar elements are represented by like reference numerals throughout the several views. The size and thickness of each component shown in the drawings are arbitrarily illustrated, and the present invention is not limited to the size and thickness of each component. The thickness of the components may be exaggerated where appropriate in the figures to improve clarity.
As shown in the figures, the dual-evaporation fresh air handling unit disclosed by the invention comprises a dual-evaporation temperature compressor 1, a first heat exchanger 2, a second heat exchanger 3, a third heat exchanger 4, a blower 5, an outdoor heat exchanger 6, a liquid storage device 7, a first four-way reversing valve 8, a second four-way reversing valve 9, a first electromagnetic valve 10, a second electromagnetic valve 11, a first electronic expansion valve 12, a second electronic expansion valve 13, a third electronic expansion valve 14, a fourth electronic expansion valve 15, a first one-way valve 16, a second one-way valve 17 and a bypass air valve 18. Wherein the first heat exchanger 2, the second heat exchanger 3, and the third heat exchanger 4 are disposed indoors. An exhaust cavity of the double-evaporation-temperature compressor 1 is respectively connected with a first four-way reversing valve 8 and a second four-way reversing valve 9, output ends of the first four-way reversing valve 8 and the second four-way reversing valve 9 are combined and divided into two paths, one path is connected with a third heat exchanger 4 and is controlled by a fourth electronic expansion valve 15 in flow rate, the other path is connected with an outdoor heat exchanger 6 and is then connected with a liquid storage device 7, and a pipeline between the outdoor heat exchanger 6 and the liquid storage device 7 is controlled by a first electronic expansion valve 12. The liquid storage device 7 is divided into two paths for output, one path is controlled by a first electromagnetic valve 10 and is sequentially connected with one end of the first heat exchanger 2, one end of the second heat exchanger 3 and one end of the third heat exchanger 4, the flow of the first heat exchanger 2 is controlled by a second electronic expansion valve 13, and the flow of the second heat exchanger is controlled by a third electronic expansion valve 14. Further, the second electronic expansion valve 13 and the third electronic expansion valve 14 are connected in parallel with a first check valve 16 and a second check valve 17, respectively, and the flow direction is set to be opposite to the flow direction of the second electronic expansion valve 13 and the third electronic expansion valve 14. The other branch of the liquid storage device 7 is controlled by a second electromagnetic valve 11, and is combined with a branch led out by a fourth electronic expansion valve 15 and then directly connected with the third heat exchanger 4. The other end of the first heat exchanger 2 is connected with a second four-way reversing valve 9 and then connected into a high-pressure air suction cavity of the double-evaporation-temperature compressor 1, and the second heat exchanger 3 is connected with a first four-way reversing valve 8 and then connected into a low-pressure air suction cavity of the double-evaporation-temperature compressor 1. A bypass damper 18 is provided above the second heat exchanger 3, and the opening degree can be adjusted as needed in accordance with the humidity of the outdoor air, thereby increasing or decreasing the amount of air to be dehumidified entering the second heat exchanger 3.
It should be noted that the bypass damper above the second heat exchanger 3 may not be provided, and the dehumidification capability adjustment range of the unit is slightly smaller.
The first electronic expansion valve 12 is the same as the fourth electronic expansion valve 15, and has two sections of drift diameters, wherein one section of drift diameter is small, the flow is small, and the drift diameter is small, and the other section of drift diameter is large, the flow resistance is small, and the throttling function is absent. The second electronic expansion valve 13 is the same as the third electronic expansion valve 14, and has only one path, and is used as a throttle valve.
Due to the use of the dual evaporating temperature compressor 1, the system may contain two different evaporating temperatures, the first heat exchanger 2 being set to have a higher evaporating temperature, pre-cooling the fresh air. The second heat exchanger 3 is arranged to have a lower evaporation temperature and dehumidify the fresh air. Taking the refrigeration mode as an example, the refrigeration cycle flow can be divided into: 1-9-6-12-7-10-13-2-9-a-1 is a high evaporation temperature refrigeration cycle, and 1-8-6-12-7-10-14-3-8-b-1 is a low evaporation temperature refrigeration cycle.
Example 1
This embodiment describes the operation of the dual-evaporation fresh air handling unit in the cooling mode. In the cooling mode, the first electronic expansion valve 12 and the first solenoid valve 10 are opened, wherein the first electronic expansion valve 12 is opened at the second path, and the second solenoid valve 11 and the fourth electronic expansion valve 15 are closed. The first four-way reversing valve 8 and the second four-way reversing valve 9 are switched to the cooling mode.
After the refrigerant passes through the double-evaporation-temperature compressor 1, high-temperature and high-pressure refrigerant steam is discharged from the exhaust cavity, passes through the first four-way reversing valve 8 and the second four-way reversing valve 9, exchanges heat with outdoor air through the outdoor heat exchanger 6, and is changed into low-temperature and high-pressure liquid refrigerant, the refrigerant passes through the first electronic expansion valve 12, the liquid reservoir 7 and the first electromagnetic valve 10 and is divided into two paths, one path of the refrigerant enters the first heat exchanger 2 to perform high-evaporation-temperature refrigeration cycle, and the other path of the refrigerant enters the second heat exchanger 3 to perform low-evaporation-temperature refrigeration cycle. The low-temperature high-pressure liquid refrigerant entering the first heat exchanger 2 is throttled by the second electronic expansion valve 13 to become low-temperature low-pressure liquid refrigerant, and is evaporated and precooled in the first heat exchanger 2 to become low-temperature low-pressure refrigerant vapor, and the refrigerant vapor returns to the high-pressure suction cavity a of the double-evaporation-temperature compressor 1 through the second four-way reversing valve 9. The low-temperature high-pressure liquid refrigerant entering the second heat exchanger 3 is throttled by the third electronic expansion valve 14 to become low-temperature low-pressure liquid refrigerant, and is evaporated in the second heat exchanger 3 and dehumidifies fresh air to become low-temperature low-pressure refrigerant vapor, and the refrigerant vapor returns to the low-pressure suction cavity b of the double-evaporation-temperature compressor 1 through the first four-way reversing valve 8. The low-temperature and low-pressure refrigerant vapor passing through the double-evaporation-temperature compressor 1 is recompressed into high-temperature and high-pressure refrigerant vapor, and the refrigeration cycle is performed in such a way that the cycle is repeated.
For the indoor fresh air, the fresh air is firstly precooled through the first heat exchanger 2, then one part of the fresh air is dehumidified through the second heat exchanger 3, the other part of the fresh air directly passes through the bypass air valve 18, the two parts of the fresh air and the bypass air valve are mixed, and the fresh air is sent into the room after the temperature and humidity requirements of the air supply are met.
Example 2
This embodiment describes the operation of the dual-evaporation fresh air handling unit in the enhanced dehumidification cooling mode. In the enhanced dehumidification cooling mode, the first solenoid valve 10 and the fourth electronic expansion valve 15 are closed, and the first electronic expansion valve 12 and the second solenoid valve 11 are opened, wherein the first electronic expansion valve 12 is opened by the second path. The first four-way selector valve 8 and the second four-way selector valve 9 remain in the cooling mode, as in embodiment 1. Since the first solenoid valve 10 is closed, the low-temperature and high-pressure liquid refrigerant output from the accumulator 7 first enters the third heat exchanger 4 through the second solenoid valve 11, and the refrigerant is subcooled, so that the temperature of the refrigerant is further reduced, and at the same time, the fresh air from the second heat exchanger 3 is reheated. The refrigerant then flows into the first heat exchanger 2 and the second heat exchanger 3 again, and the rest of the flow process is the same as in embodiment 1.
For the indoor fresh air, the fresh air is firstly precooled through the first heat exchanger 2, one part of the precooled fresh air is dehumidified through the second heat exchanger 3, the other part of the precooled fresh air directly passes through the bypass air valve 18, the two parts of the precooled fresh air and the bypass air valve are mixed and then reheated through the third heat exchanger 4, and the mixed fresh air is sent into the room after reaching the temperature and humidity requirements of the supplied air.
Example 3
This example describes the operation of a dual-evaporation fresh air handling unit in isothermal dehumidification mode. In the isothermal dehumidification mode, the second solenoid valve 11 is closed, the first electronic expansion valve 12, the first solenoid valve 10 and the fourth electronic expansion valve 15 are opened, wherein the first electronic expansion valve 12 and the fourth electronic expansion valve 15 are opened in the second path. The first four-way selector valve 8 and the second four-way selector valve 9 are still in the cooling mode, as in embodiments 1 and 2. After the high-temperature and high-pressure refrigerant steam from the first four-way reversing valve 8 and the second four-way reversing valve 9 are combined, one part of the combined refrigerant steam enters the outdoor heat exchanger 6, passes through the first electronic expansion valve 12, the liquid reservoir 7 and the first electromagnetic valve 10, and the other part of the combined refrigerant steam passes through the fourth electronic expansion valve 15 and enters the third heat exchanger 4 for heat exchange, part of condensation heat is recovered, and fresh air from the second heat exchanger 3 is reheated, wherein the reheating quantity is larger than that in the embodiment 2. The flow rate of the refrigerant entering the third heat exchanger 4 can be controlled and regulated by the combination of the first electronic expansion valve 12 and the fourth electronic expansion valve 15. The refrigerant discharged from the third heat exchanger 4 is mixed with the refrigerant discharged from the accumulator 7, and then introduced into the first heat exchanger 2 and the second heat exchanger 3, and the flow process is the same as in embodiments 1 and 2.
For the indoor fresh air, the fresh air is firstly precooled through the first heat exchanger 2, one part of the precooled fresh air is dehumidified through the second heat exchanger 3, the other part of the precooled fresh air directly passes through the bypass air valve 18, the two parts of the precooled fresh air and the bypass air valve are mixed and then reheated through the third heat exchanger 4, and the mixed fresh air is sent into the room after reaching the temperature and humidity requirements of the supplied air.
Example 4
The embodiment describes the operation condition of the double-evaporation fresh air unit in the heating mode. In the heating mode, the first four-way reversing valve 8 and the second four-way reversing valve 9 are switched to the heating mode, the second electromagnetic valve 11 and the first electronic expansion valve 12 are opened, the first electronic expansion valve 12 opens the first drift diameter to be used as a throttle valve, and the first electromagnetic valve 10, the fourth electronic expansion valve 15 and the bypass air valve 18 are closed.
After the refrigerant passes through the double-evaporation-temperature compressor 1, high-temperature and high-pressure refrigerant steam is discharged from the exhaust cavity and divided into two paths, one path of the refrigerant enters the first heat exchanger 2 through the second four-way reversing valve 9 for condensation, fresh air is preheated to become low-temperature and high-pressure liquid refrigerant, and the low-temperature and high-pressure liquid refrigerant passes through the first one-way valve 16. The other path of the refrigerant enters the second heat exchanger 3 through the first four-way reversing valve 8 for condensation, and then the fresh air is reheated and changed into a low-temperature high-pressure liquid refrigerant, and then the refrigerant passes through the second one-way valve 17. The refrigerant is mixed with the low-temperature high-pressure liquid refrigerant output by the first check valve 16, and then enters the third heat exchanger 4 for heat exchange, fresh air is reheated, the liquid refrigerant is subcooled to further reduce the temperature, and then passes through the second electromagnetic valve 11 and the liquid reservoir 7, is throttled by the first electronic expansion valve 12 to become low-temperature low-pressure refrigerant liquid, and then passes through the outdoor heat exchanger 6 to exchange heat with the outside, so that the low-temperature low-pressure refrigerant vapor is changed, one part of the low-temperature low-pressure refrigerant vapor enters the low-pressure suction cavity b of the double-evaporation temperature compressor 1 through the first four-way reversing valve 8, and the other part of the low-pressure. After being compressed by the evaporation temperature compressor 1, the high-temperature and high-pressure refrigerant vapor is mixed and discharged from the same exhaust cavity, and the heating cycle is performed in such a way of circulating and reciprocating.
And as for the indoor fresh air, the fresh air sequentially passes through the first heat exchanger 2, the second heat exchanger 3 and the third heat exchanger 4 to heat the fresh air, and the fresh air is sent into the room after the air supply requirement is met.
The foregoing detailed description of the preferred embodiments of the invention has been presented. It should be understood that numerous modifications and variations could be devised by those skilled in the art in light of the present teachings without departing from the inventive concepts. Therefore, the technical solutions available to those skilled in the art through logic analysis, reasoning and limited experiments based on the prior art according to the concept of the present invention should be within the scope of protection defined by the claims.
Claims (6)
1. A double-evaporation fresh air unit comprises a compressor, an outdoor heat exchanger, a liquid storage device and an indoor unit, and is characterized in that the indoor unit comprises a first heat exchanger, a second heat exchanger, a third heat exchanger and a blower, fresh air is enabled to sequentially pass through the first heat exchanger and the second heat exchanger,
the air outlet of the compressor is respectively connected with a first four-way reversing valve and a second four-way reversing valve, the output ends of the first four-way reversing valve and the second four-way reversing valve are connected together and then divided into a first branch and a second branch, wherein the first branch is provided with the outdoor heat exchanger, a first throttling device and the liquid storage device which are sequentially connected, the outlet of the liquid storage device is divided into a third branch and a fourth branch, the third branch is respectively connected with one end of the first heat exchanger, one end of the second heat exchanger and one end of the third heat exchanger through a first electromagnetic valve, a second throttling device is arranged between the first heat exchanger and the first electromagnetic valve, and a third throttling device is arranged between the second heat exchanger and the first electromagnetic valve; the fourth branch is sequentially connected with a second electromagnetic valve and the other end of the third heat exchanger; the second branch is sequentially connected with a fourth throttling device and the other end of the third heat exchanger; the third branch and the fourth branch are respectively connected with an air suction port of the compressor through the first four-way reversing valve and the second four-way reversing valve to form a loop;
the double-evaporation fresh air handling unit at least comprises the following three working modes, namely a first working mode, a second working mode and a third working mode:
in the first operating mode, the first throttling means and the first solenoid valve are open, and the second solenoid valve and the fourth throttling means are closed, so that the refrigerant coming out of the compressor flows through the first heat exchanger and the second heat exchanger, respectively;
in the second operation mode, the first throttling device and the second electromagnetic valve are opened, and the first electromagnetic valve and the fourth throttling device are closed, so that the refrigerant flowing out of the compressor flows through the third heat exchanger and then flows into the first heat exchanger and the second heat exchanger respectively;
in the third operation mode, the first throttle device, the first solenoid valve, and the fourth throttle device are opened, and the second solenoid valve is closed, so that a part of the refrigerant flowing out of the compressor flows through the third heat exchanger, and another part of the refrigerant flows through the accumulator, and then the refrigerant flowing out of the third heat exchanger is mixed with the refrigerant flowing out of the accumulator and flows through the first heat exchanger and the second heat exchanger.
2. The dual evaporative fresh air handling unit as recited in claim 1 wherein the compressor uses a dual evaporative temperature compressor.
3. The dual evaporation fresh air handling unit of claim 1, wherein the first throttling device and the fourth throttling device are each a first electronic expansion valve, the first electronic expansion valve having a first diameter and a second diameter, the first diameter having a greater flow resistance than the second diameter.
4. A dual evaporation fresh air handling unit according to any of claims 1 to 3, wherein the first throttling means and the second throttling means are both second electronic expansion valves, and the second electronic expansion valves have only one passage.
5. A dual evaporative fresh air handling unit as claimed in any one of claims 1 to 3, wherein the indoor unit further includes a bypass damper.
6. A dual evaporation fresh air handling unit according to any one of claims 1 to 3, wherein a humidity sensor is provided at an outlet portion of the indoor unit, and the operating frequency of the compressor is reduced after a predetermined humidity is reached.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910104679.1A CN109882939B (en) | 2019-02-01 | 2019-02-01 | Dual-evaporation fresh air handling unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910104679.1A CN109882939B (en) | 2019-02-01 | 2019-02-01 | Dual-evaporation fresh air handling unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109882939A CN109882939A (en) | 2019-06-14 |
| CN109882939B true CN109882939B (en) | 2021-05-11 |
Family
ID=66927780
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910104679.1A Active CN109882939B (en) | 2019-02-01 | 2019-02-01 | Dual-evaporation fresh air handling unit |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109882939B (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110410902A (en) * | 2019-07-22 | 2019-11-05 | 南京天加环境科技有限公司 | It is a kind of can total heat recovery and accurately adjust recuperation of heat amount air-conditioning system |
| CN110332614A (en) * | 2019-08-01 | 2019-10-15 | 南京天加环境科技有限公司 | A kind of air-conditioning coil arrangement of variable wind path |
| CN110411059B (en) * | 2019-08-28 | 2024-01-23 | 珠海格力电器股份有限公司 | Double-evaporation-temperature heat pump system, air conditioner and control method |
| CN112361484A (en) * | 2020-11-10 | 2021-02-12 | 珠海格力电器股份有限公司 | Double-cold-source multi-runner temperature and humidity adjusting system and refrigerating equipment |
| CN113776220B (en) * | 2021-08-24 | 2022-09-09 | 清华大学 | Room air conditioner and control method thereof |
| CN114893851A (en) * | 2022-05-24 | 2022-08-12 | 上海理工大学 | Laboratory fresh air handling unit based on double-evaporation-temperature refrigerating system |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004101154A (en) * | 2002-09-13 | 2004-04-02 | Mitsubishi Electric Corp | Air-conditioner operating method, and air-conditioner |
| CN102937308A (en) * | 2012-11-14 | 2013-02-20 | 合肥天鹅制冷科技有限公司 | Dehumidification air conditioner capable of supplying air with multiple temperature parameters |
| CN106642448A (en) * | 2016-10-19 | 2017-05-10 | 上海朗绿建筑科技股份有限公司 | Ultra-efficient direct expansion heat recovery type dehumidification fresh air machine |
| CN108775664B (en) * | 2018-08-13 | 2024-02-27 | 珠海格力电器股份有限公司 | Air conditioner system and air conditioner with same |
-
2019
- 2019-02-01 CN CN201910104679.1A patent/CN109882939B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN109882939A (en) | 2019-06-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN109882939B (en) | Dual-evaporation fresh air handling unit | |
| CN112503680B (en) | Full-working-condition efficient fresh air fan for heat recovery of multistage heat pump | |
| CN111998565B (en) | Double-temperature air conditioning system and control method thereof | |
| CN108679747B (en) | Fresh air dehumidifying air conditioning system | |
| CN107975869B (en) | Air conditioning system | |
| CN107940636B (en) | Air conditioning system | |
| CN107747806B (en) | Air conditioning system | |
| CN104764241A (en) | Air conditioner | |
| CN112413738B (en) | Fresh air conditioning system and heat recovery method thereof | |
| CN107726480B (en) | Semi-decoupling type graded dehumidification and cooling dehumidification heat pump system and method | |
| CN114087681A (en) | Single-channel fresh air dehumidification air treatment system | |
| CN108106045A (en) | A kind of air-conditioning refrigerator combined system of central refrigerating split cooling | |
| CN207584898U (en) | Air-conditioning system | |
| CN106403421A (en) | Air conditioning device | |
| CN207471736U (en) | Air-conditioning system | |
| CN107676902B (en) | Air conditioning system | |
| CN213090173U (en) | Air conditioning system | |
| CN212362480U (en) | Double-temperature air conditioning system | |
| CN114034183A (en) | Totally-enclosed high-precision temperature and humidity independent control heat pump drying system | |
| CN210832603U (en) | Air conditioner | |
| CN112082284A (en) | Heat pump system with double suction and exhaust functions and control method | |
| JPH078999Y2 (en) | Air source heat pump | |
| CN112361504A (en) | Integral fresh air dehumidification all-in-one | |
| CN207471789U (en) | Air-conditioning system | |
| CN112432381A (en) | Air conditioning system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |