CN108775664B - Air conditioner system and air conditioner with same - Google Patents
Air conditioner system and air conditioner with same Download PDFInfo
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- CN108775664B CN108775664B CN201810918132.0A CN201810918132A CN108775664B CN 108775664 B CN108775664 B CN 108775664B CN 201810918132 A CN201810918132 A CN 201810918132A CN 108775664 B CN108775664 B CN 108775664B
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- heat exchanger
- way valve
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- 238000004891 communication Methods 0.000 claims description 36
- 238000010438 heat treatment Methods 0.000 abstract description 50
- 238000010257 thawing Methods 0.000 abstract description 28
- 239000003570 air Substances 0.000 description 183
- 239000003507 refrigerant Substances 0.000 description 105
- 238000001704 evaporation Methods 0.000 description 25
- 239000007788 liquid Substances 0.000 description 25
- 230000008020 evaporation Effects 0.000 description 20
- 238000001816 cooling Methods 0.000 description 13
- 238000007791 dehumidification Methods 0.000 description 12
- 230000006835 compression Effects 0.000 description 8
- 238000007906 compression Methods 0.000 description 8
- 238000010586 diagram Methods 0.000 description 8
- 230000009977 dual effect Effects 0.000 description 8
- 238000000034 method Methods 0.000 description 6
- 238000005057 refrigeration Methods 0.000 description 6
- 238000011084 recovery Methods 0.000 description 5
- 239000012080 ambient air Substances 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 2
- 239000000155 melt Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000003303 reheating Methods 0.000 description 1
- 230000001502 supplementing effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/41—Defrosting; Preventing freezing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
- F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention provides an air conditioner system and an air conditioner with the same. The exhaust port of the compressor is selectively communicated with the inlet end of the first heat exchanger or the inlet end of the third heat exchanger through the first valve body; the exhaust port of the compressor is selectively communicated with the inlet end of the first heat exchanger or the inlet end of the second heat exchanger through the second valve body; the outlet end of the third heat exchanger is selectively communicated with the inlet end of the first heat exchanger or the outlet end of the fourth heat exchanger; the outlet end of the first heat exchanger is selectively communicated with the air inlet of the compressor or the air inlet of the fourth heat exchanger; the outlet end of the second heat exchanger is selectively communicated with the inlet end of the fourth heat exchanger or the outlet end of the fourth heat exchanger, and the outlet end of the fourth heat exchanger is selectively communicated with the air inlet of the compressor. The problem of the air conditioner system when defrosting operation, the heating operation of air conditioner system stops, causes the user to use and experience poor is solved. The use experience of the user is effectively improved.
Description
Technical Field
The invention relates to the technical field of air conditioner equipment, in particular to an air conditioner system and an air conditioner with the same.
Background
The traditional fresh air dehumidifier generally adopts vapor compression cooling for dehumidification, and uses an evaporation temperature to treat the sensible heat and the latent heat load of the fresh air. The evaporation temperature of the fresh air dehumidifier is usually lower due to the requirement of the temperature of the air outlet dew point, so that the energy consumption of a unit is high, the energy efficiency is low, and the refrigeration energy efficiency is generally not more than 3.0.
In the prior art, although the energy efficiency of the fresh air dehumidifier is improved by combining double evaporation temperatures with exhaust heat recovery, the energy efficiency is mainly improved by aiming at consumption reduction in the refrigerating and dehumidifying operation, the energy efficiency is not related to a heating technical scheme, the functions of double-temperature evaporation heating, defrosting continuous heating and the like cannot be realized in the prior art, the problem that the indoor temperature fluctuates due to frosting-defrosting of an evaporator in heating cannot be solved, and the problem that the air conditioner in the prior art is poor in comfortableness in use is solved.
Furthermore, in the prior art, it is also proposed that frostless heating can be realized by exhaust heat recovery during heating operation, and the problem of poor comfort caused by defrosting is solved. However, in practical application, these schemes are difficult to realize frostless heating, for the following reasons:
1. in order to ensure the indoor positive pressure requirement, the exhaust air quantity is always smaller than the fresh air quantity, and the heat recovered from the exhaust air is limited.
2. The outdoor fresh air temperature in winter is usually lower, the temperature in many places is usually lower than 10 ℃, and the temperature rise of the fresh air before and after heating is large (usually more than 20 ℃). On the exhaust heat recovery side, in order to ensure that the evaporator does not frost, the temperature of the refrigerant needs to be controlled above a certain temperature, so that the temperature drop of the exhaust air before and after passing through the evaporator is limited (usually not more than 20 ℃), and the absolute value of the temperature drop of the exhaust air is not more than the absolute value of the temperature rise of fresh air.
3. The temperature in winter is low, the moisture content of air is small, the dew point temperature is low, and the amount of recoverable latent heat is limited. Therefore, in winter heating, the evaporator in the exhaust channel is used independently to recover exhaust heat and ensure that the evaporator is not frosted, and the outdoor evaporator is not used for supplementing heat, so that the fresh air supply temperature and the heating quantity are difficult to ensure, and the comfort is poorer.
Disclosure of Invention
The invention mainly aims to provide an air conditioner system and an air conditioner with the same, so as to solve the problem of poor comfort of the air conditioner in the prior art.
In order to achieve the above object, according to one aspect of the present invention, there is provided an air conditioner system including a compressor, a first heat exchanger, a second heat exchanger, a third heat exchanger, and a fourth heat exchanger, which are connected; the exhaust port of the compressor is selectively communicated with the inlet end of the first heat exchanger or the inlet end of the third heat exchanger through the first valve body; the exhaust port of the compressor is selectively communicated with the inlet end of the first heat exchanger or the inlet end of the second heat exchanger through the second valve body; the outlet end of the third heat exchanger is selectively communicated with the inlet end of the first heat exchanger or the outlet end of the fourth heat exchanger; the outlet end of the first heat exchanger is selectively communicated with the air inlet of the compressor or the air inlet of the fourth heat exchanger; the outlet end of the second heat exchanger is selectively communicated with the inlet end of the fourth heat exchanger or the outlet end of the fourth heat exchanger, and the outlet end of the fourth heat exchanger is selectively communicated with the air inlet of the compressor.
Further, the air inlet of the compressor comprises a first air inlet and a second air inlet, the compressor is provided with a first working cavity and a second working cavity, the first air inlet is communicated with the first working cavity, the second air inlet is communicated with the second working cavity, the outlet end of the first heat exchanger can be communicated with at least one of the first air inlet and the second air inlet, and the outlet end of the fourth heat exchanger can be communicated with at least one of the first air inlet and the second air inlet.
Further, the first valve body and the second valve body are four-way valves, the S end of the first valve body is communicated with the exhaust port of the compressor, the E end of the first valve body is communicated with the inlet end of the third heat exchanger, the D end of the first valve body is communicated with the first air inlet, the C end of the first valve body is communicated with the C end of the second valve body, the S end of the second valve body is communicated with the exhaust port of the compressor, the E end of the second valve body is communicated with the outlet end of the second heat exchanger, and the D end of the second valve body is communicated with the second air inlet.
Further, the outlet end of the fourth heat exchanger is communicated with a pipeline between the C end of the first valve body and the C end of the second valve body, the inlet end of the first heat exchanger is communicated with a pipeline between the C end of the first valve body and the C end of the second valve body through a first branch, the inlet end of the first heat exchanger is communicated with the outlet end of the third heat exchanger through a second branch, or the inlet end of the first heat exchanger is communicated with the E end of the first valve body through a third branch, the outlet end of the first heat exchanger is optionally communicated with a pipeline between the C end of the first valve body and the C end of the second valve body through a first three-way valve, or the outlet end of the first heat exchanger is optionally communicated with the inlet end of the fourth heat exchanger through a first three-way valve.
Further, a first one-way valve is arranged on the first branch, the inlet end of the first one-way valve is communicated with a pipeline between the C end of the first valve body and the C end of the second valve body, and the outlet end of the first one-way valve is communicated with the inlet end of the first heat exchanger.
Further, a first throttle valve is arranged on the second branch, and a solenoid valve is arranged on the third branch.
Further, a second three-way valve is arranged on a pipeline between the inlet end of the first heat exchanger and the outlet end of the fourth heat exchanger, the h end of the second three-way valve is communicated with the inlet end of the first heat exchanger, the k end of the second three-way valve is communicated with a pipeline communicated between the first throttle valve and the electromagnetic valve, and the j end of the second three-way valve is communicated with a pipeline communicated between the outlet end of the fourth heat exchanger and the outlet end of the second heat exchanger.
Further, a third three-way valve is arranged on a pipeline between the outlet end of the fourth heat exchanger and the C end of the first valve body and the C end of the second valve body, a fourth three-way valve is arranged on a pipeline between the outlet end of the fourth heat exchanger and the outlet end of the second heat exchanger, the d end of the third three-way valve is communicated with the outlet end of the fourth heat exchanger, the f end of the third three-way valve is communicated with a pipeline between the C end of the first valve body and the C end of the second valve body, the e end of the third three-way valve is communicated with the p end of the fourth three-way valve, the m end of the fourth three-way valve is communicated with a pipeline between the j end of the fourth three-way valve and the outlet end of the second heat exchanger, and the n end of the fourth three-way valve is communicated with a pipeline between the inlet end of the first three-way valve and the fourth heat exchanger.
Further, the air conditioner system further includes: and the inlet end of the fifth heat exchanger is communicated with a pipeline which is communicated between the outlet end of the first heat exchanger and the inlet end of the fourth heat exchanger, and the outlet end of the fifth heat exchanger is communicated with a pipeline which is communicated between the m end of the fourth three-way valve and the outlet end of the second heat exchanger.
Further, a proportional control valve is arranged on a pipeline communicated with the inlet end of the fifth heat exchanger.
Further, the first heat exchanger is used for exchanging heat with outdoor air flow, the second heat exchanger, the third heat exchanger and the fifth heat exchanger are used for exchanging heat with fresh air flow when entering the room, and the fourth heat exchanger is used for exchanging heat with air flow when exiting the room.
Further, a second one-way valve is arranged on a pipeline between the end D communicated with the first valve body and the first air inlet, the inlet end of the second one-way valve is communicated with the end D of the first valve body, and the outlet end of the second one-way valve is communicated with the first air inlet.
Further, a fifth three-way valve is arranged on a pipeline between the outlet end of the fourth heat exchanger and the C end of the first valve body and the C end of the second valve body, the g end of the fifth three-way valve is selectively communicated with the outlet end of the first three-way valve or the fourth heat exchanger, the q end of the fifth three-way valve is communicated with the outlet end of the second one-way valve, and the t end of the fifth three-way valve is communicated with a pipeline between the C end of the first valve body and the C end of the second valve body.
Further, the air conditioner system further comprises a sixth three-way valve, wherein the end a of the first three-way valve is communicated with the outlet end of the first heat exchanger, the end c of the first three-way valve is communicated with a pipeline communicated with the inlet end of the fourth heat exchanger, the end b of the first three-way valve is communicated with the end u of the sixth three-way valve, the end w of the sixth three-way valve is communicated with a pipeline communicated between the end g of the fifth three-way valve and the outlet end of the fourth heat exchanger, and the end v of the sixth three-way valve is communicated with a pipeline communicated between the end D of the second valve body and the second air inlet.
Further, the first working chamber and the second working chamber work independently.
According to another aspect of the present invention, there is provided an air conditioner including an air conditioner system, the air conditioner system being the air conditioner described above.
By applying the technical scheme of the invention, the air conditioner system adopts the first valve body structure, the second valve body structure and the plurality of heat exchangers, and the plurality of heat exchangers are communicated with the compressor through the first valve body structure and the second valve body structure, so that the air conditioner system can realize the function of uninterrupted defrosting when defrosting is needed after the heat exchangers used as external machines are frosted, namely the air conditioner system can realize defrosting operation and heating operation at the same time, and the problem of poor user experience caused by stopping the heating operation of the air conditioner system when the air conditioner system performs defrosting operation in the prior art is solved. By adopting the air conditioner system, the stability of the indoor environment temperature can be effectively ensured, and the use experience of a user is effectively improved.
Drawings
The accompanying drawings, which 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. In the drawings:
fig. 1 shows a schematic structural view of a first embodiment of an air conditioner system according to the present invention;
fig. 2 shows a schematic refrigerant flow diagram of a dual temperature evaporation heating mode of a first embodiment of an air conditioner system according to the present invention;
FIG. 3 is a schematic view showing a refrigerant flow direction in a non-stop heating mode of a first embodiment of an air conditioner system according to the present invention;
fig. 4 shows a schematic refrigerant flow diagram of a cooling mode of a first embodiment of an air conditioner system according to the present invention;
FIG. 5 is a schematic refrigerant flow diagram of a reheat dehumidification mode of a first embodiment of an air conditioner system according to the present disclosure;
fig. 6 shows a schematic structural view of a second embodiment of an air conditioner system according to the present invention;
fig. 7 shows a schematic refrigerant flow diagram of a dual temperature evaporation heating mode according to a second embodiment of the air conditioner system of the present invention;
FIG. 8 is a schematic diagram showing a refrigerant flow direction in a non-stop heating mode of a second embodiment of an air conditioner system according to the present invention;
Fig. 9 is a schematic refrigerant flow diagram of a cooling mode of a second embodiment of an air conditioner system according to the present invention;
fig. 10 shows a refrigerant flow diagram of a reheat dehumidification mode of a second embodiment of an air conditioner system according to the present invention.
Wherein the above figures include the following reference numerals:
1. a compressor; 2. a liquid storage tank; 3. a liquid storage tank; 4. a first valve body; 5. a second valve body; 6. a first one-way valve; 7. a first heat exchanger; 8. a first three-way valve; 9. a third three-way valve; 10. a fourth three-way valve; 11. a second three-way valve; 12. a first throttle valve; 13. a second throttle valve; 14. an electromagnetic valve; 15. a proportional control valve; 16. a fifth heat exchanger; 17. a second heat exchanger; 18. a third heat exchanger; 19. a fourth heat exchanger; 20. an exhaust motor; 21. a fresh air motor; 22. a second one-way valve; 23. a fifth three-way valve; 24. a sixth three-way valve;
31. a first branch; 32. a second branch; 33. and a third branch.
Detailed Description
It should be noted that, in the case of no conflict, the embodiments and features in the embodiments may be combined with each other. The invention will be described in detail below with reference to the drawings in connection with embodiments.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
It should be noted that the terms "first," "second," and the like in the description and claims of this application and the accompanying drawings are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the terms so used are interchangeable under appropriate circumstances such that the embodiments of the application described herein are, for example, capable of operation in sequences other than those illustrated or otherwise described herein. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
Exemplary embodiments according to the present application will now be described in more detail with reference to the accompanying drawings. These exemplary embodiments may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. It should be understood that these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the concept of these exemplary embodiments to those skilled in the art, that in the drawings, it is possible to enlarge the thicknesses of layers and regions for clarity, and that identical reference numerals are used to designate identical devices, and thus descriptions thereof will be omitted.
As shown in connection with fig. 1 to 10, according to an embodiment of the present invention, an air conditioner system is provided.
Specifically, as shown in fig. 1 to 5, the air conditioner system includes a compressor 1, a first heat exchanger 7, a second heat exchanger 17, a third heat exchanger 18, and a fourth heat exchanger 19, which are in communication. The exhaust port of the compressor 1 is selectively communicated with the inlet end of the first heat exchanger 7 or the inlet end of the third heat exchanger 18 through the first valve body 4. The exhaust port of the compressor 1 is selectively communicated with the inlet end of the first heat exchanger 7 or the inlet end of the second heat exchanger 17 through the second valve body 5. The outlet end of the third heat exchanger 18 is optionally in communication with the inlet end of the first heat exchanger 7 or the outlet end of the fourth heat exchanger 19. The outlet end of the first heat exchanger 7 is optionally in communication with the inlet of the compressor 1 or the inlet of the fourth heat exchanger 19. The outlet end of the second heat exchanger 17 is optionally in communication with the inlet end of the fourth heat exchanger 19 or the outlet end of the fourth heat exchanger 19, and the outlet end of the fourth heat exchanger 19 is optionally in communication with the inlet of the compressor 1.
In this embodiment, the first valve body structure, the second valve body structure and the plurality of heat exchangers are adopted in the air conditioner system, the plurality of heat exchangers are communicated with the compressor through the first valve body structure and the second valve body structure, so that the air conditioner system can realize that when defrosting is needed after the heat exchangers serving as external machines are frosted, the air conditioner system can also realize the function of continuous defrosting, namely, the air conditioner system can realize defrosting operation and heating operation at the same time, and the problem that in the prior art, when the air conditioner system performs defrosting operation, the heating operation of the air conditioner system is stopped, and the user experience is poor is solved. By adopting the air conditioner system, the stability of the indoor environment temperature can be effectively ensured, and the use experience of a user is effectively improved.
Wherein the air inlet of the compressor 1 comprises a first air inlet and a second air inlet, the compressor 1 is provided with a first working cavity and a second working cavity, the first air inlet is communicated with the first working cavity, the second air inlet is communicated with the second working cavity, the outlet end of the first heat exchanger 7 can be communicated with at least one of the first air inlet and the second air inlet, and the outlet end of the fourth heat exchanger 19 can be communicated with at least one of the first air inlet and the second air inlet. This arrangement can effectively improve the performance of the compressor.
Preferably, the first valve body 4 and the second valve body 5 are four-way valves, the S end of the first valve body 4 is communicated with the exhaust port of the compressor 1, the E end of the first valve body 4 is communicated with the inlet end of the third heat exchanger 18, the D end of the first valve body 4 is communicated with the first air inlet, the C end of the first valve body 4 is communicated with the C end of the second valve body 5, the S end of the second valve body 5 is communicated with the exhaust port of the compressor 1, the E end of the second valve body 5 is communicated with the outlet end of the second heat exchanger 17, and the D end of the second valve body 5 is communicated with the second air inlet.
The outlet end of the fourth heat exchanger 19 is in communication with the conduit between the C-end of the first valve body 4 and the C-end of the second valve body 5, and the inlet end of the first heat exchanger 7 is in communication with the conduit between the C-end of the first valve body 4 and the C-end of the second valve body 5 via the first branch 31. The inlet end of the first heat exchanger 7 may be in communication with the outlet end of the third heat exchanger 18 via the second branch 32, or the inlet end of the first heat exchanger 7 may be in communication with the E end of the first valve body 4 via the third branch 33, the outlet end of the first heat exchanger 7 may be in communication with a pipeline between the C end of the first valve body 4 and the C end of the second valve body 5 via the first three-way valve 8, or the outlet end of the first heat exchanger 7 may be in communication with the inlet end of the fourth heat exchanger 19 via the first three-way valve 8.
Further, the first branch 31 is provided with a first check valve 6. The inlet end of the first one-way valve 6 is communicated with a pipeline between the C end of the first valve body 4 and the C end of the second valve body 5, and the outlet end of the first one-way valve 6 is communicated with the inlet end of the first heat exchanger 7. The second branch 32 is provided with the first throttle valve 12, and the third branch 33 is provided with the solenoid valve 14.
Specifically, a second three-way valve 11 is arranged on the pipeline between the inlet end of the first heat exchanger 7 and the outlet end of the fourth heat exchanger 19. The h end of the second three-way valve 11 is communicated with the inlet end of the first heat exchanger 7, the k end of the second three-way valve 11 is communicated with a pipeline communicated between the first throttle valve 12 and the electromagnetic valve 14, and the j end of the second three-way valve 11 is communicated with a pipeline communicated between the outlet end of the fourth heat exchanger 19 and the outlet end of the second heat exchanger 17.
A third three-way valve 9 is arranged on a pipeline which is communicated between the outlet end of the fourth heat exchanger 19 and the C end of the first valve body 4 and the C end of the second valve body 5. A fourth three-way valve 10 is arranged on a pipeline between the outlet end of the fourth heat exchanger 19 and the outlet end of the second heat exchanger 17, the d end of the third three-way valve 9 is communicated with the outlet end of the fourth heat exchanger 19, the f end of the third three-way valve 9 is communicated with a pipeline between the C end of the first valve body 4 and the C end of the second valve body 5, the e end of the third three-way valve 9 is communicated with the p end of the fourth three-way valve 10, the m end of the fourth three-way valve 10 is communicated with a pipeline between the j end of the fourth three-way valve 11 and the outlet end of the second heat exchanger 17, and the n end of the fourth three-way valve 10 is communicated with a pipeline between the first three-way valve 8 and the inlet end of the fourth heat exchanger 19.
Further, the air conditioner system further includes a fifth heat exchanger 16. The inlet end of the fifth heat exchanger 16 is in communication with a conduit communicating between the outlet end of the first heat exchanger 7 and the inlet end of the fourth heat exchanger 19. The outlet end of the fifth heat exchanger 16 is in communication with a conduit communicating between the m-end of the fourth three-way valve 10 and the outlet end of the second heat exchanger 17. The arrangement can further improve the heating performance of the air conditioner and the practicability of the air conditioner system. Wherein, a proportional control valve 15 is arranged on a pipeline communicated with the inlet end of the fifth heat exchanger 16.
Preferably, the first heat exchanger 7 is used for heat exchange with outdoor air flow, the second heat exchanger 17, the third heat exchanger 18 and the fifth heat exchanger 16 are used for heat exchange with fresh air flow when entering the room, and the fourth heat exchanger 19 is used for heat exchange with air flow when exiting the room.
As shown in fig. 6 to 10, a second check valve 22 is arranged on a pipeline which is communicated between the end D of the first valve body 4 and the first air inlet, the inlet end of the second check valve 22 is communicated with the end D of the first valve body 4, and the outlet end of the second check valve 22 is communicated with the first air inlet. A fifth three-way valve 23 is arranged on the pipeline which communicates between the outlet end of the fourth heat exchanger 19 and the C end of the first valve body 4 and the C end of the second valve body 5. The g end of the fifth three-way valve 23 is selectively communicated with the outlet end of the first three-way valve 8 or the fourth heat exchanger 19, the q end of the fifth three-way valve 23 is communicated with the outlet end of the second one-way valve 22, and the t end of the fifth three-way valve 23 is communicated with a pipeline between the C end of the first valve body 4 and the C end of the second valve body 5.
The air conditioner system further comprises a sixth three-way valve 24, wherein the a end of the first three-way valve 8 is communicated with the outlet end of the first heat exchanger 7, the c end of the first three-way valve 8 is communicated with a pipeline communicated with the inlet end of the fourth heat exchanger 19, the b end of the first three-way valve 8 is communicated with the u end of the sixth three-way valve 24, the w end of the sixth three-way valve 24 is communicated with a pipeline communicated between the g end of the fifth three-way valve 23 and the outlet end of the fourth heat exchanger 19, and the v end of the sixth three-way valve 24 is communicated with a pipeline communicated between the D end of the second valve body 5 and the second air inlet. The first working chamber and the second working chamber operate independently. The four-way valve and the valve core of each three-way valve are controlled to realize switching connection between the pipelines, so that the refrigerant entering the compressor can realize two entering modes, namely, entering after mixing before entering into operation, or respectively entering into the working cavity through the independent pipelines to perform compression operation, and the practicability and reliability of the air conditioner system are further improved.
The air conditioner system in the above embodiment may also be used in the technical field of air conditioner devices, that is, according to another aspect of the present invention, an air conditioner is provided, including the air conditioner system, where the air conditioner system is the air conditioner in the above embodiment.
Specifically, the air conditioner is a fresh air conditioner with double evaporation temperatures, the air conditioner system of the air conditioner can realize synchronous heating operation with double evaporation temperatures by different switching combinations of components such as a three-way valve and the like and recovering exhaust heat, and different cylinder bodies of the compressor are provided with different compression ratios on the premise of ensuring sufficient heating quantity, so that heating power consumption is reduced, and meanwhile, at least 1 evaporator is ensured not to frost during heating. When defrosting is needed after the external machine frosts, the unit can also realize the function of defrosting without stopping, and can perform defrosting and heating at the same time, thereby solving the problems of interruption of heating and poor comfort in defrosting of the traditional equipment. When the air conditioner is used for refrigerating or reheating and dehumidifying, sensible heat and latent heat of fresh air are respectively processed by utilizing high and low different evaporating temperatures, so that the fresh air is cooled step by step, and meanwhile, the exhaust cooling capacity is recovered through the condenser, so that the energy efficiency of the whole fresh air dehumidifier is greatly improved.
The air conditioning system comprises 1 compressor with double air suction ports (two independent compression cavities), 2 liquid storage tanks (the liquid storage tank 2 and the liquid storage tank 3), 2 four-way valves, 5 heat exchangers, 2 throttle valves, 1 electromagnetic valve, 1 proportional control valve, 6 three-way valves, 2 one-way valves and 2 fans (an air exhaust motor 20 and a fresh air motor 21). Through the different control combinations of components such as four-way valve, three-way valve, proportional control valve and choke valve, the unit can realize different operation modes such as dual temperature evaporation heating operation, non-stop defrosting heating operation, dual evaporation temperature refrigeration operation and reheat dehumidification operation. The energy efficiency and the comfort of the unit are integrally improved through the cold/heat recovery of exhaust air and the grading treatment of fresh air.
Specifically, through the SE switch-on and the CD switch-on of the first valve body 4 and the second valve body 5, the ab path, the df path, the mn path, the hk path, the gq path and the uv path of each three-way valve are switched on, the electromagnetic valve 14 is closed, the proportional control valve 15 is closed, the dual-evaporation-temperature heating is realized, the evaporation temperatures of the evaporators in different use environments are changed, not only at least 1 evaporator is ensured to be frosted, but also two cylinder body refrigerants in the compressor have different compression ratios, and the heating efficiency of a unit is improved.
According to the air conditioner system, exhaust heat is recovered, double-temperature evaporation is performed, at least 1 evaporator is guaranteed not to be frosted when being heated, therefore, when the evaporator in an outdoor environment is frosted, through SE connection and CD connection of the first valve body 4 and the second valve body 5, ab paths, df paths, mn paths, hk paths, tg paths and uw paths of all three-way valves are connected, the electromagnetic valve 14 is opened, the proportional control valve 15 is closed, and the function of defrosting without stopping is achieved.
Through SC switch-on, DE switch-on of first valve body 4 and second valve body 5, each three way valve ac way, DE way, mp way and jk way switch on, solenoid valve 14 is closed, and proportional control valve 15 is closed, realizes two evaporation temperature refrigeration, carries out the hierarchical processing to fresh air, retrieves the exhaust air cooling capacity simultaneously, improves system refrigeration efficiency.
Through the different control combinations of components and parts such as three-way valve, the fresh air is reheated after being cooled and dehumidified through grading treatment, so that not only is energy-saving, but also the air supply comfort is improved, wherein the broken line part in the system diagram is indicated as a refrigerant non-passage.
1. Dual temperature evaporation heating operation mode: in the dual-temperature evaporation heating mode, SE of the first valve body 4 and the second valve body 5 is connected, CD is connected, ab of the first three-way valve 8 is connected, df of the third three-way valve 9 is connected, mn of the fourth three-way valve 10 is connected, hk of the second three-way valve 11 is connected, gq of the fifth three-way valve 23 is connected, uv of the sixth three-way valve 24 is connected, the electromagnetic valve 14 is closed, and the proportional control valve 15 is closed. At this time, the refrigerant is separated into two paths from the compressor exhaust port, and enters the third heat exchanger 18 and the second heat exchanger 17 (as condensers) through SE paths of the first valve body 4 and the second valve body 5, where the refrigerant releases heat, and then is throttled by the first throttle valve 12 and the second throttle valve 13 to form two paths of refrigerants with different evaporating temperatures. The low-temperature refrigerant is obtained through the first throttle valve 12, enters the first heat exchanger 7 (serving as a low-temperature evaporator) to absorb heat from the environment, and then flows out of the first three-way valve 8 and the sixth three-way valve 24 under the action of pressure difference and then returns to the compressor through the liquid storage tank 3 (the refrigerant does not flow to the second valve body 5 and returns to the first heat exchanger 7 under the action of pressure difference). The high-temperature refrigerant obtained through the second throttle valve 13 enters the fourth heat exchanger 19 (serving as a high-temperature evaporator) to absorb heat from the exhaust air, and then returns to the compressor through the third three-way valve 9, the fifth three-way valve 23 and the liquid storage tank 2, as shown in fig. 7.
At this time, the outdoor fresh air passes through the third heat exchanger 18 and the second heat exchanger 17 in sequence to be heated, and then is sent into the room. At the same time, the indoor exhaust air passes through the fourth heat exchanger 19, where the low-temperature refrigerant is heated, and then the cooled exhaust air is discharged outside. The heating operation energy efficiency of the system is improved by changing the compression ratio of the compressor and recovering exhaust heat.
2. And (3) a defrosting and heating operation mode without shutdown: after the unit operates for a period of time in the double-temperature evaporation heating mode, frosting occurs on the first heat exchanger 7, and when the thickness of the frost layer reaches a certain value, the unit needs to enter a defrosting mode to defrost the first heat exchanger 7. At this time, the unit will operate in a non-stop heating mode. In this mode, SE of the first valve body 4 and the second valve body 5 is turned on, CD is turned on, ab of the first three-way valve 8 is turned on, df of the third three-way valve 9 is turned on, mn of the fourth three-way valve 10 is turned on, hk of the second three-way valve 11 is turned on, tg of the fifth three-way valve 23 is turned on, uw of the sixth three-way valve 24 is turned on, the electromagnetic valve 14 is opened, and the proportional control valve 15 is turned off. At this time, the refrigerant is split into two paths after exiting from the compressor exhaust port, and one path of refrigerant enters the first heat exchanger 7 through the SE path of the first valve body 4, the second three-way valve 11 and the electromagnetic valve 14. The first heat exchanger 7 serves as a condenser, and the high-temperature refrigerant heats and melts frost on the heat exchanger. The other path of refrigerant directly enters the second heat exchanger 17 (serving as a condenser) through the SE of the second valve body 5 to heat fresh air, throttles through the second throttle valve 13 and enters the fourth heat exchanger 19 through the mn of the fourth three-way valve 10. The fourth heat exchanger 19 serves as an evaporator, and the refrigerant absorbs heat from the exhaust air, flows to the df path of the third three-way valve 9, and mixes with the refrigerant passing through the first three-way valve 8 and the sixth three-way valve 24 from the first heat exchanger 7. After the mixed refrigerant passes through the paths of the fifth three-way valve 23, the refrigerant is divided into two parts again, and the two parts respectively pass through the paths CD of the first valve body 4 and the second valve body 5, enter the liquid storage tank 2 and the liquid storage tank 3, and return to the compressor, as shown in figure 8. When the temperature of the tube of the first heat exchanger 7 rises to a predetermined target value (the target value is set to an arbitrary value, such as 10 c, depending on the actual situation), defrosting ends and the unit exits this mode.
At this time, the outdoor fresh air passes through the third heat exchanger 18 and the second heat exchanger 17 in sequence to be heated, and then is sent into the room. At the same time, the indoor exhaust air passes through the fourth heat exchanger 19, where the low-temperature refrigerant is heated, and then the cooled exhaust air is discharged outside.
In the mode, the first heat exchanger 7 and the second heat exchanger 17 are both used as condensers, the fourth heat exchanger 19 is used as an evaporator, the third heat exchanger 18 does not work, the characteristics of high indoor exhaust temperature and no frosting of the fourth heat exchanger 19 are utilized, the defrosting process of the first heat exchanger 7 is realized, the heating is not stopped, the problem of indoor temperature fluctuation caused by defrosting and heating stopping of the traditional fresh air conditioner is solved, and the heating comfort is improved.
3. Dual evaporating temperature refrigeration mode of operation: in the cooling mode, SC and DE of the first valve body 4 and the second valve body 5 are turned on, ac of the first three-way valve 8 is turned on, DE of the third three-way valve 9 is turned on, mp of the fourth three-way valve 10 is turned on, jk of the second three-way valve 11 is turned on, gq of the fifth three-way valve 23 is turned on, uw of the sixth three-way valve 24 is turned on, the electromagnetic valve 14 is turned off, and the proportional control valve 15 is turned off. At this time, the refrigerant is split into two paths from the compressor exhaust port, and flows through the first check valve 6 to enter the first heat exchanger 7 after being converged by the SC paths of the first valve body 4 and the second valve body 5, the first heat exchanger 7 serves as a condenser, the refrigerant exchanges heat with ambient air at the position, and then flows through the ac path of the first three-way valve 8 to enter the fourth heat exchanger 19. The fourth heat exchanger 19 acts as a condenser for recovering the cold in the indoor exhaust air, where the refrigerant will be further cooled. The cooled refrigerant passes through the de and pm paths of the third three-way valve 9 and the fourth three-way valve 10 after exiting from the fourth heat exchanger 19, and then is divided into two parts. A part of the refrigerant is throttled by the first throttle valve 12 to obtain a low-temperature refrigerant with higher temperature, and the refrigerant enters the third heat exchanger 18, so that the third heat exchanger 18 becomes a high-temperature evaporator. The other part is throttled by the second throttle valve 13 to obtain a low-temperature refrigerant with lower temperature, and the low-temperature refrigerant enters the second heat exchanger 17, so that the second heat exchanger 17 becomes a low-temperature evaporator. After the two paths of refrigerants exchange heat in the second heat exchanger 17 and the third heat exchanger 18 respectively, the two paths of refrigerants respectively pass through DE paths of the first valve body 4 and the second valve body 5 to reach the liquid storage tank 3 and the liquid storage tank 2 and return to the compressor, as shown in fig. 9. At this time, the outdoor fresh air enters and is pre-cooled by the high-temperature evaporator, namely the third heat exchanger 18, the sensible heat load of the fresh air is treated, the cooled fresh air enters the low-temperature second heat exchanger 17 for further cooling and dehumidification, the latent heat load is treated, and then the fresh air is sent into a room. At the same time, the indoor exhaust air passes through the fourth heat exchanger 19, where the high-temperature refrigerant is cooled, and the heat of the refrigerant is taken away and discharged out of the room. The fresh air is treated in a grading way, and the exhaust cooling capacity is recovered, so that the refrigerating operation energy efficiency of the system is integrally improved.
4. Remanufacturing dehumidification operation mode: in the reheat dehumidification mode, SC and DE of the first and second valve bodies 4 and 5 are turned on, ac of the first three-way valve 8 is turned on, DE of the third three-way valve 9 is turned on, mp of the fourth three-way valve 10 is turned on, kj of the second three-way valve 11 is turned on, gq of the fifth three-way valve 23 is turned on, uw of the sixth three-way valve 24 is turned on, the proportional control valve 15 is opened, and the electromagnetic valve 14 is closed. At this time, the refrigerant is split into two paths from the compressor exhaust port, and flows through the first check valve 6 to enter the first heat exchanger 7 after being converged by the SC paths of the first valve body 4 and the second valve body 5. The first heat exchanger 7 serves as a condenser where the refrigerant exchanges heat with ambient air and then passes through the ac path of the first three-way valve 8 to be split into two parts. Part of the fresh air enters a fifth heat exchanger 16 through a proportional control valve 15, and the fifth heat exchanger 16 serves as a condenser to heat the fresh air. The opening degree of the proportional regulating valve 15 is regulated by the difference between the reheated fresh air temperature and the target fresh air temperature (the target temperature may be the air outlet temperature set by the user, or may be any preset value, such as 26 ℃), so as to regulate the amount of the refrigerant entering the fifth heat exchanger 16. Another part of the refrigerant enters the fourth heat exchanger 19. The fourth heat exchanger 19 also serves as a condenser for recovering the cold in the indoor exhaust air, where the refrigerant is further cooled. The cooled refrigerant is mixed with the refrigerant from the fifth heat exchanger 16 through the de and pm paths of the third three-way valve 9 and the fourth three-way valve 10 after exiting from the fourth heat exchanger 19, and is divided into two parts, wherein one part of the refrigerant is throttled by the first throttle valve 12 to obtain a low-temperature refrigerant with higher temperature, and the low-temperature refrigerant enters the third heat exchanger 18, so that the third heat exchanger 18 becomes a high-temperature evaporator. The other part is throttled by the second throttle valve 13 to obtain a low-temperature refrigerant with lower temperature, and the low-temperature refrigerant enters the second heat exchanger 17, so that the second heat exchanger 17 becomes a low-temperature evaporator. After the two paths of refrigerants exchange heat in the second heat exchanger 17 and the third heat exchanger 18 respectively, the two paths of refrigerants respectively pass through DE paths of the first valve body 4 and the second valve body 5 to reach the liquid storage tank 3 and the liquid storage tank 2 and return to the compressor, as shown in fig. 10.
At this time, the outdoor fresh air enters and is pre-cooled by the high-temperature evaporator, namely the third heat exchanger 18, the sensible heat load of the fresh air is treated, the cooled fresh air enters the low-temperature second heat exchanger 17 again to be further cooled and dehumidified, the latent heat load is treated, and finally the fresh air is reheated to the target temperature at the fifth heat exchanger 16 and then is sent into a room. At the same time, the indoor exhaust air passes through the fourth heat exchanger 19, where the high-temperature refrigerant is cooled, and the heat of the refrigerant is taken away and discharged out of the room. The fresh air is dehumidified by grading treatment, and the exhaust air cooling capacity is recovered, so that the dehumidification energy efficiency of the system is improved, and the comfort is also improved.
In the above-described scheme, the second check valve 22, the fifth three-way valve 23, and the sixth three-way valve 24 may cancel the formation of a new system scheme. The main difference between the new scheme and the original scheme is that the double-temperature evaporation heating operation is performed. In the new scheme, the refrigerants coming out of the first heat exchanger 7 and the fourth heat exchanger 19 are mixed first and then enter the liquid storage tank 2 and the liquid storage tank 3 respectively and return to the compressor, so that the compression ratio of the refrigerants in the two cylinder bodies in the compressor is the same, while in the original scheme, the refrigerants coming out of the first heat exchanger 7 and the fourth heat exchanger 19 are not mixed and enter the liquid storage tank 2 and the liquid storage tank 3 respectively and return to the compressor, so that the compression ratio of the refrigerants in the two cylinder bodies in the compressor is different.
Specifically, according to another embodiment of the present application, 1, dual temperature evaporation heating operation: in the dual-temperature evaporation heating mode, SE and CD of the first valve body 4 and the second valve body 5 are connected, ab of the first three-way valve 8 is connected, df of the third three-way valve 9 is connected, mn of the fourth three-way valve 10 is connected, hk of the second three-way valve 11 is connected, the electromagnetic valve 14 is closed, and the proportional control valve 15 is closed. At this time, the refrigerant is separated into two paths from the compressor exhaust port, and enters the third heat exchanger 18 and the second heat exchanger 17 (as condensers) through SE paths of the first valve body 4 and the second valve body 5, where the refrigerant releases heat, and then is throttled by the first throttle valve 12 and the second throttle valve 13 to form two paths of refrigerants with different evaporating temperatures. The low-temperature refrigerant is obtained through the first throttle valve 12, and enters the first heat exchanger 7 (serving as a low-temperature evaporator) to absorb heat from the environment. The high-temperature refrigerant obtained through the second throttle valve 13 enters the fourth heat exchanger 19 (serving as a high-temperature evaporator) to absorb heat from exhaust air, then passes through the third three-way valve 9, is mixed with the low-temperature refrigerant from the first three-way valve 8, and then reaches the liquid storage tank 3 and the liquid storage tank 2 through CD paths of the first valve body 4 and the second valve body 5 respectively to return to the compressor, as shown in fig. 2.
At this time, the outdoor fresh air passes through the third heat exchanger 18 and the second heat exchanger 17 in sequence to be heated, and then is sent into the room. At the same time, the indoor exhaust air passes through the fourth heat exchanger 19, where the low-temperature refrigerant is heated, and then the cooled exhaust air is discharged outside. And the heating operation energy efficiency of the system is improved through the recovery of exhaust heat.
2. And (3) a defrosting and heating operation mode without shutdown: after the unit operates for a period of time in the double-temperature evaporation heating mode, frosting occurs on the first heat exchanger 7, and when the thickness of the frost layer reaches a certain value, the unit needs to enter a defrosting mode to defrost the first heat exchanger 7. At this time, the unit will operate in a non-stop heating mode. In this mode, SE of the first valve body 4 and the second valve body 5 is turned on, CD is turned on, ab of the first three-way valve 8 is turned on, df of the third three-way valve 9 is turned on, mn of the fourth three-way valve 10 is turned on, hk of the second three-way valve 11 is turned on, the electromagnetic valve 14 is opened, and the proportional control valve 15 is closed. At this time, the refrigerant is split into two paths after exiting from the compressor exhaust port, and one path of refrigerant enters the first heat exchanger 7 through the SE path of the first valve body 4, the electromagnetic valve 14 and the second three-way valve 11. The first heat exchanger 7 serves as a condenser, and the high-temperature refrigerant heats and melts frost on the heat exchanger. The other path of refrigerant directly enters the second heat exchanger 17 (serving as a condenser) through the SE of the second valve body 5 to heat fresh air, throttles through the second throttle valve 13 and enters the fourth heat exchanger 19 through the mn of the fourth three-way valve 10. The fourth heat exchanger 19 serves as an evaporator, and the refrigerant absorbs heat from the exhaust air, flows to the df path of the third three-way valve 9, and is mixed with the refrigerant from the first heat exchanger 7. The mixed refrigerant is divided into two parts again, and enters the liquid storage tank 2 and the liquid storage tank 3 through the CD paths of the first valve body 4 and the second valve body 5 respectively, and returns to the compressor, as shown in figure 3. When the temperature of the tube of the first heat exchanger 7 rises to a predetermined target value (the target value is set to an arbitrary value, such as 10 c, depending on the actual situation), defrosting ends and the unit exits this mode.
At this time, the outdoor fresh air passes through the third heat exchanger 18 and the second heat exchanger 17 in sequence to be heated, and then is sent into the room. At the same time, the indoor exhaust air passes through the fourth heat exchanger 19, where the low-temperature refrigerant is heated, and then the cooled exhaust air is discharged outside.
In the mode, the first heat exchanger 7 and the second heat exchanger 17 are both used as condensers, the fourth heat exchanger 19 is used as an evaporator, the third heat exchanger 18 does not work, the characteristics of high indoor exhaust temperature and no frosting of the fourth heat exchanger 19 are utilized, the defrosting process of the first heat exchanger 7 is realized, the heating is not stopped, the problem of indoor temperature fluctuation caused by defrosting and heating stopping of the traditional fresh air conditioner is solved, and the heating comfort is improved.
3. Dual evaporating temperature refrigeration mode of operation: in the cooling mode, SC and DE of the first valve body 4 and the second valve body 5 are turned on, ac of the first three-way valve 8 is turned on, DE of the third three-way valve 9 is turned on, mp of the fourth three-way valve 10 is turned on, jk of the second three-way valve 11 is turned on, the electromagnetic valve 14 is closed, and the proportional control valve 15 is closed. At this time, the refrigerant is split into two paths from the compressor exhaust port, and flows through the first check valve 6 to enter the first heat exchanger 7 after being converged by the SC paths of the first valve body 4 and the second valve body 5, the first heat exchanger 7 serves as a condenser, the refrigerant exchanges heat with ambient air at the position, and then flows through the ac path of the first three-way valve 8 to enter the fourth heat exchanger 19. The fourth heat exchanger 19 acts as a condenser for recovering the cold in the indoor exhaust air, where the refrigerant will be further cooled. The cooled refrigerant passes through the de and pm paths of the third three-way valve 9 and the fourth three-way valve 10 after exiting from the fourth heat exchanger 19, and then is divided into two parts. A part of the refrigerant is throttled by the first throttle valve 12 to obtain a low-temperature refrigerant with higher temperature, and the refrigerant enters the third heat exchanger 18, so that the third heat exchanger 18 becomes a high-temperature evaporator. The other part is throttled by the second throttle valve 13 to obtain a low-temperature refrigerant with lower temperature, and the low-temperature refrigerant enters the second heat exchanger 17, so that the second heat exchanger 17 becomes a low-temperature evaporator. After the two paths of refrigerants exchange heat in the second heat exchanger 17 and the third heat exchanger 18 respectively, the two paths of refrigerants respectively pass through DE paths of the first valve body 4 and the second valve body 5 to reach the liquid storage tank 3 and the liquid storage tank 2 and return to the compressor, as shown in fig. 4.
At this time, the outdoor fresh air enters and is pre-cooled by the high-temperature evaporator, namely the third heat exchanger 18, the sensible heat load of the fresh air is treated, the cooled fresh air enters the low-temperature second heat exchanger 17 for further cooling and dehumidification, the latent heat load is treated, and then the fresh air is sent into a room. At the same time, the indoor exhaust air passes through the fourth heat exchanger 19, where the high-temperature refrigerant is cooled, and the heat of the refrigerant is taken away and discharged out of the room. The fresh air is treated in a grading way, and the exhaust cooling capacity is recovered, so that the refrigerating operation energy efficiency of the system is integrally improved.
4. Reheat dehumidification operation
In the reheat dehumidification mode, SC and DE of the first and second valve bodies 4 and 5 are turned on, ac of the first three-way valve 8 is turned on, DE of the third three-way valve 9 is turned on, mp of the fourth three-way valve 10 is turned on, kj of the second three-way valve 11 is turned on, the proportional control valve 15 is opened, and the electromagnetic valve 14 is closed. At this time, the refrigerant is split into two paths from the compressor exhaust port, and flows through the first check valve 6 to enter the first heat exchanger 7 after being converged by the SC paths of the first valve body 4 and the second valve body 5. The first heat exchanger 7 serves as a condenser where the refrigerant exchanges heat with ambient air and then passes through the ac path of the first three-way valve 8 to be split into two parts. Part of the fresh air enters the fifth heat exchanger 16 through the proportional control valve 15, the fifth heat exchanger 16 serves as a condenser for heating the fresh air, and the opening degree of the proportional control valve 15 is adjusted through the difference between the reheated fresh air temperature and the target fresh air temperature (the target temperature can be the air outlet temperature freely set by a user or can be any preset value, such as 26 ℃), so that the amount of the refrigerant entering the fifth heat exchanger 16 is adjusted. The other part of the refrigerant enters the fourth heat exchanger 19, and at this time, the fourth heat exchanger 19 also serves as a condenser for recovering the cold in the indoor exhaust air, and the refrigerant is further cooled. The cooled refrigerant is mixed with the refrigerant from the fifth heat exchanger 16 through the de and pm paths of the third three-way valve 9 and the fourth three-way valve 10 after exiting from the fourth heat exchanger 19, and is divided into two parts, wherein one part of the refrigerant is throttled by the first throttle valve 12 to obtain a low-temperature refrigerant with higher temperature, and the low-temperature refrigerant enters the third heat exchanger 18, so that the third heat exchanger 18 becomes a high-temperature evaporator. The other part is throttled by the second throttle valve 13 to obtain a low-temperature refrigerant with lower temperature, and the low-temperature refrigerant enters the second heat exchanger 17, so that the second heat exchanger 17 becomes a low-temperature evaporator. After the two paths of refrigerants exchange heat in the second heat exchanger 17 and the third heat exchanger 18 respectively, the two paths of refrigerants respectively pass through ED paths of the first valve body 4 and the second valve body 5 to reach the liquid storage tank 3 and the liquid storage tank 2, and return to the compressor, as shown in fig. 5.
At this time, the outdoor fresh air enters and is pre-cooled by the high-temperature evaporator, namely the third heat exchanger 18, the sensible heat load of the fresh air is treated, the cooled fresh air enters the low-temperature second heat exchanger 17 again to be further cooled and dehumidified, the latent heat load is treated, and finally the fresh air is reheated to the target temperature at the fifth heat exchanger 16 and then is sent into a room. At the same time, the indoor exhaust air passes through the fourth heat exchanger 19, where the high-temperature refrigerant is cooled, and the heat of the refrigerant is taken away and discharged out of the room. The fresh air is dehumidified by grading treatment, and the exhaust air cooling capacity is recovered, so that the dehumidification energy efficiency of the system is improved, and the comfort is also improved.
In addition to the foregoing, references in the specification to "one embodiment," "another embodiment," "an embodiment," etc., mean that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment described in general terms in the application. The appearances of the phrase in various places in the specification are not necessarily all referring to the same embodiment. Further, when a particular feature, structure, or characteristic is described in connection with any embodiment, it is intended that such feature, structure, or characteristic be implemented within the scope of the invention.
In the foregoing embodiments, the descriptions of the embodiments are emphasized, and for parts of one embodiment that are not described in detail, reference may be made to related descriptions of other embodiments.
The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (16)
1. An air conditioner system is characterized by comprising a compressor (1), a first heat exchanger (7), a second heat exchanger (17), a third heat exchanger (18) and a fourth heat exchanger (19) which are communicated with each other;
the exhaust port of the compressor (1) is selectively communicated with the inlet end of the first heat exchanger (7) or the inlet end of the third heat exchanger (18) through a first valve body (4);
the exhaust port of the compressor (1) is selectively communicated with the inlet end of the first heat exchanger (7) or the inlet end of the second heat exchanger (17) through a second valve body (5);
the outlet end of the third heat exchanger (18) is selectively communicated with the inlet end of the first heat exchanger (7) or the outlet end of the fourth heat exchanger (19);
The outlet end of the first heat exchanger (7) is selectively communicated with the air inlet of the compressor (1) or the air inlet of the fourth heat exchanger (19);
the outlet end of the second heat exchanger (17) is selectively communicated with the inlet end of the fourth heat exchanger (19) or the outlet end of the fourth heat exchanger (19), and the outlet end of the fourth heat exchanger (19) is selectively communicated with the air inlet of the compressor (1);
the first heat exchanger (7) is used for carrying out heat exchange with outdoor airflow, the second heat exchanger (17) and the third heat exchanger (18) are used for carrying out heat exchange with fresh air airflow when entering a room, and the fourth heat exchanger (19) is used for carrying out heat exchange with airflow when being discharged out of the room.
2. An air conditioner system according to claim 1, wherein the air inlet of the compressor (1) comprises a first air inlet and a second air inlet, the compressor (1) has a first working chamber and a second working chamber, the first air inlet is in communication with the first working chamber, the second air inlet is in communication with the second working chamber, the outlet end of the first heat exchanger (7) is in communication with at least one of the first air inlet and the second air inlet, and the outlet end of the fourth heat exchanger (19) is in communication with at least one of the first air inlet and the second air inlet.
3. The air conditioner system according to claim 2, wherein the first valve body (4) and the second valve body (5) are four-way valves, an S end of the first valve body (4) is communicated with an exhaust port of the compressor (1), an E end of the first valve body (4) is communicated with an inlet end of the third heat exchanger (18), a D end of the first valve body (4) is communicated with the first air inlet, a C end of the first valve body (4) is communicated with a C end of the second valve body (5), an S end of the second valve body (5) is communicated with an exhaust port of the compressor (1), an E end of the second valve body (5) is communicated with an outlet end of the second heat exchanger (17), and a D end of the second valve body (5) is communicated with the second air inlet.
4. An air conditioner system according to claim 2, wherein the outlet end of the fourth heat exchanger (19) is in communication with a line between the C-end of the first valve body (4) and the C-end of the second valve body (5), the inlet end of the first heat exchanger (7) is in communication with a line between the C-end of the first valve body (4) and the C-end of the second valve body (5) through a first branch (31), the inlet end of the first heat exchanger (7) is in communication with the outlet end of the third heat exchanger (18) through a second branch (32), or the inlet end of the first heat exchanger (7) is in communication with the E-end of the first valve body (4) through a third branch (33), the outlet end of the first heat exchanger (7) is in communication with a line between the C-end of the first valve body (4) and the C-end of the second valve body (5) through a first three-way valve (8), or the inlet end of the first heat exchanger (7) is in communication with the E-end of the first valve body (7) through a third branch (33).
5. An air conditioner system according to claim 4, characterized in that the first branch (31) is provided with a first non-return valve (6), the inlet end of the first non-return valve (6) is in communication with a pipeline between the C-end of the first valve body (4) and the C-end of the second valve body (5), and the outlet end of the first non-return valve (6) is in communication with the inlet end of the first heat exchanger (7).
6. An air conditioner system according to claim 4, wherein the second branch (32) is provided with a first throttle valve (12) and the third branch (33) is provided with a solenoid valve (14).
7. An air conditioner system according to claim 6, characterized in that a second three-way valve (11) is arranged on a pipeline between the inlet end of the first heat exchanger (7) and the outlet end of the fourth heat exchanger (19), the h end of the second three-way valve (11) is communicated with the inlet end of the first heat exchanger (7), the k end of the second three-way valve (11) is communicated with a pipeline between the first throttle valve (12) and the electromagnetic valve (14), and the j end of the second three-way valve (11) is communicated with a pipeline between the outlet end of the fourth heat exchanger (19) and the outlet end of the second heat exchanger (17).
8. The air conditioner system according to claim 7, wherein a third three-way valve (9) is provided on a pipe line communicating between the outlet end of the fourth heat exchanger (19) and the C end of the first valve body (4) and the C end of the second valve body (5), a fourth three-way valve (10) is provided on a pipe line communicating between the outlet end of the fourth heat exchanger (19) and the outlet end of the second heat exchanger (17), the d end of the third three-way valve (9) is communicated with the outlet end of the fourth heat exchanger (19), the f end of the third three-way valve (9) is communicated with a pipe line communicating between the C end of the first valve body (4) and the C end of the second valve body (5), the e end of the third three-way valve (9) is communicated with the p end of the fourth three-way valve (10), and the m end of the fourth three-way valve (10) is communicated with the j end of the second three-way valve (11) and the outlet end of the fourth three-way valve (17), and the n end of the third three-way valve (8) is communicated with the inlet end of the third three-way valve (8).
9. The air conditioner system of claim 8, further comprising:
And the inlet end of the fifth heat exchanger (16) is communicated with a pipeline which is communicated between the outlet end of the first heat exchanger (7) and the inlet end of the fourth heat exchanger (19), and the outlet end of the fifth heat exchanger (16) is communicated with a pipeline which is communicated between the m end of the fourth three-way valve (10) and the outlet end of the second heat exchanger (17).
10. An air conditioner system according to claim 9, characterized in that a proportional control valve (15) is provided on the line connecting the inlet end of the fifth heat exchanger (16).
11. An air conditioner system according to claim 9, characterized in that the fifth heat exchanger (16) is arranged to exchange heat with a fresh air flow when entering a room.
12. The air conditioner system according to claim 4, wherein a second one-way valve (22) is provided on a pipe line communicating between the D end of the first valve body (4) and the first air inlet, an inlet end of the second one-way valve (22) is communicated with the D end of the first valve body (4), and an outlet end of the second one-way valve (22) is communicated with the first air inlet.
13. An air conditioner system according to claim 12, characterized in that a fifth three-way valve (23) is provided on the line communicating the outlet end of the fourth heat exchanger (19) with the C-end of the first valve body (4) and the C-end of the second valve body (5), the g-end of the fifth three-way valve (23) being in communication with the outlet end of the first three-way valve (8) or the fourth heat exchanger (19), the q-end of the fifth three-way valve (23) being in communication with the outlet end of the second one-way valve (22), the t-end of the fifth three-way valve (23) being in communication with the line between the C-end of the first valve body (4) and the C-end of the second valve body (5).
14. The air conditioner system according to claim 13, further comprising a sixth three-way valve (24), the a-end of the first three-way valve (8) being in communication with the outlet end of the first heat exchanger (7), the c-end of the first three-way valve (8) being in communication with a conduit in communication with the inlet end of the fourth heat exchanger (19), the b-end of the first three-way valve (8) being in communication with the u-end of the sixth three-way valve (24), the w-end of the sixth three-way valve (24) being in communication with a conduit in communication between the g-end of the fifth three-way valve (23) and the outlet end of the fourth heat exchanger (19), the v-end of the sixth three-way valve (24) being in communication with a conduit in communication between the D-end of the second valve body (5) and the second air inlet.
15. The air conditioner system of claim 2, wherein the first working chamber and the second working chamber operate independently.
16. An air conditioner comprising an air conditioner system, wherein the air conditioner system is the air conditioner system of any one of claims 1 to 15.
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| CN201810918132.0A CN108775664B (en) | 2018-08-13 | 2018-08-13 | Air conditioner system and air conditioner with same |
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| CN108775664B true CN108775664B (en) | 2024-02-27 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109882939B (en) * | 2019-02-01 | 2021-05-11 | 上海理工大学 | Dual-evaporation fresh air handling unit |
| CN110657505A (en) * | 2019-09-23 | 2020-01-07 | 广东芬尼克兹节能设备有限公司 | Dehumidifier system, dehumidifier and control method |
| CN112212465B (en) * | 2020-10-23 | 2021-12-14 | 珠海格力电器股份有限公司 | Anti-frosting control method and device for air conditioning unit and air conditioning system |
| CN114087739B (en) * | 2021-11-24 | 2023-10-27 | 广东美的制冷设备有限公司 | Fresh air equipment control method and device, fresh air equipment and storage medium |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02223757A (en) * | 1989-02-27 | 1990-09-06 | Toshiba Corp | Air conditioner |
| US5076346A (en) * | 1987-06-17 | 1991-12-31 | Mitsubishi Denki Kabushiki Kaisha | Air conditioner |
| CN2188184Y (en) * | 1994-04-25 | 1995-01-25 | 广东美的集团股份有限公司 | Throttle and frost-removal structure for air conditioner |
| US5493870A (en) * | 1994-04-22 | 1996-02-27 | Nippondenso Co., Ltd. | Air conditioning apparatus for vehicle |
| CN206637900U (en) * | 2017-03-21 | 2017-11-14 | 珠海格力电器股份有限公司 | Air conditioning system |
| CN208620489U (en) * | 2018-08-13 | 2019-03-19 | 珠海格力电器股份有限公司 | Air conditioner system and air conditioner with same |
-
2018
- 2018-08-13 CN CN201810918132.0A patent/CN108775664B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5076346A (en) * | 1987-06-17 | 1991-12-31 | Mitsubishi Denki Kabushiki Kaisha | Air conditioner |
| JPH02223757A (en) * | 1989-02-27 | 1990-09-06 | Toshiba Corp | Air conditioner |
| US5493870A (en) * | 1994-04-22 | 1996-02-27 | Nippondenso Co., Ltd. | Air conditioning apparatus for vehicle |
| CN2188184Y (en) * | 1994-04-25 | 1995-01-25 | 广东美的集团股份有限公司 | Throttle and frost-removal structure for air conditioner |
| CN206637900U (en) * | 2017-03-21 | 2017-11-14 | 珠海格力电器股份有限公司 | Air conditioning system |
| CN208620489U (en) * | 2018-08-13 | 2019-03-19 | 珠海格力电器股份有限公司 | Air conditioner system and air conditioner with same |
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