CN111426090A - Control device, air-conditioning heat pump system and control method thereof - Google Patents
Control device, air-conditioning heat pump system and control method thereof Download PDFInfo
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- CN111426090A CN111426090A CN202010214384.2A CN202010214384A CN111426090A CN 111426090 A CN111426090 A CN 111426090A CN 202010214384 A CN202010214384 A CN 202010214384A CN 111426090 A CN111426090 A CN 111426090A
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 39
- 238000000034 method Methods 0.000 title claims abstract description 37
- 239000003507 refrigerant Substances 0.000 claims abstract description 65
- 239000007788 liquid Substances 0.000 claims abstract description 22
- 238000010257 thawing Methods 0.000 claims description 32
- 238000010438 heat treatment Methods 0.000 claims description 24
- 230000001965 increasing effect Effects 0.000 claims description 15
- 230000017525 heat dissipation Effects 0.000 claims description 6
- 238000005057 refrigeration Methods 0.000 claims description 6
- 230000000694 effects Effects 0.000 description 13
- 238000004781 supercooling Methods 0.000 description 12
- 238000001816 cooling Methods 0.000 description 8
- 238000010586 diagram Methods 0.000 description 8
- 238000004590 computer program Methods 0.000 description 5
- 238000004891 communication Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 238000012545 processing Methods 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 2
- 229910052802 copper Inorganic materials 0.000 description 2
- 239000010949 copper Substances 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000003287 optical effect Effects 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 230000000203 accumulation affect Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000003672 processing method Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 230000000007 visual effect Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- 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
- F24F11/42—Defrosting; Preventing freezing of outdoor units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
- F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
- F25B2313/0252—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units with bypasses
- F25B2313/02522—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units with bypasses during defrosting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention relates to a control device, an air-conditioning heat pump system and a control method thereof. The air-conditioning heat pump system comprises a compressor, a gas-liquid separator, an intermediate heat exchanger, an outdoor heat exchanger and an indoor heat exchanger which are connected through a refrigerant pipeline, wherein the intermediate heat exchanger comprises a first heat exchange pipeline and a second heat exchange pipeline, a first electronic expansion valve is arranged on a main pipeline of the refrigerant pipeline, the indoor heat exchanger is provided with a second electronic expansion valve, the outdoor heat exchanger comprises a first part and a second part arranged on a bypass branch, a first side of the bypass branch is connected between a first end of the first heat exchange pipeline and the second electronic expansion valve, a second side of the bypass branch is connected to a first end of the second heat exchange pipeline, and a second end of the second heat exchange pipeline is connected to an enthalpy-increasing port and/or the gas-liquid separator of the compressor; the bypass branch is provided with a valve and a third electronic expansion valve. Through the arrangement, the overall performance of the air-conditioning heat pump system can be improved.
Description
Technical Field
The invention relates to the technical field of air conditioning, in particular to a control device, an air conditioning heat pump system and a control method thereof.
Background
An air-conditioning heat pump system (e.g., an air-cooling type air-conditioning heat pump system) generally has a cooling mode and a heating mode, and air with a suitable temperature can be supplied to a room by circulating a refrigerant through a circuit formed by a compressor-an outdoor heat exchanger (generally referred to as a condenser) -a throttling part (e.g., an electronic expansion valve or a capillary tube, etc.) -an indoor heat exchanger (generally referred to as an evaporator) -a compressor. In case that the air conditioner is in the heating mode, the outdoor heat exchanger may be frosted. Specifically, when the evaporation temperature is lower than the dew point temperature corresponding to the outdoor environment temperature, the coil of the outdoor unit of the air conditioner begins to frost, and when the frost layer on the outer wall of the coil of the outdoor unit of the air conditioner is formed to a certain thickness, the heating capacity of the air conditioner is reduced to deteriorate. It is necessary to defrost the outdoor heat exchanger of the outdoor unit of the air conditioner in time.
For example, in the case of a commercial multi-split air conditioner in an air conditioning heat pump system, since the area of the outdoor heat exchanger is large, particularly for the bottom of the outdoor heat exchanger, condensed water may flow down, or defrosting water cannot be removed in time during defrosting, which may cause the bottom of the outdoor heat exchanger to be frozen, and if the multi-split air conditioner is operated for a long time under such a situation, the performance of the whole machine may be affected. Therefore, if the defrosting mechanism is performed uniformly for the entire outdoor heat exchanger, there is a problem that the performance of the entire machine is degraded due to bottom frost formation.
In order to solve this problem, the current processing method includes: 1. part of coil pipes at the bottom of the outdoor heat exchanger are used as subcoolers, and the medium-temperature refrigerant flowing back from the indoor side firstly flows through the subcoolers at the bottom (for example, the subcoolers are composed of copper pipes and fins) and then enters the evaporator through the electronic expansion valve and the liquid distributor, so that the problem of bottom frosting is avoided; 2. a few coil pipes at the bottom of the outdoor heat exchanger are directly blocked, and no refrigerant flows in the coil pipes, so that no cold energy exchange is realized during heating, and the frosting is inhibited in such a way. However, for the first treatment method, because the supercooled pipe has the defect of large pressure loss, the treatment method of bottom supercooling inevitably affects the performance of the whole machine while avoiding frosting; moreover, the fins and the copper pipes have strong heat transfer effect, so that the phenomenon of icing and frosting at the bottom is difficult to ensure. For the second approach, the problem of wasting effective heat exchange area obviously exists in a few coils blocking the bottom of the outdoor heat exchanger.
Accordingly, there is a need in the art for a new solution to the above problems.
Disclosure of Invention
Technical problem
In view of this, the present invention is directed to solve the problem of timely and effective defrosting of an outdoor heat exchanger of an air conditioning heat pump system.
Solution scheme
The invention provides an air-conditioning heat pump system, which comprises a compressor, a gas-liquid separator, an intermediate heat exchanger, at least one outdoor heat exchanger and at least one indoor heat exchanger which are connected through a refrigerant pipeline, wherein the intermediate heat exchanger comprises a shell, and a first heat exchange pipeline and a second heat exchange pipeline which are arranged in the shell and can exchange heat, and the refrigerant pipeline comprises: the indoor heat exchanger is connected with the outdoor heat exchanger through the main path, a first electronic expansion valve is arranged on the main path, the indoor heat exchanger is provided with a second electronic expansion valve, and a first end and a second end of the first heat exchange pipeline are respectively connected with the first electronic expansion valve and the second electronic expansion valve; the outdoor heat exchanger comprises a first part and a second part which are arranged up and down, the second part is arranged on the bypass branch, the first side of the bypass branch is connected to the position, between the first end of the first heat exchange pipeline and the second electronic expansion valve, of the main pipeline, the second side of the bypass branch is connected to the first end of the second heat exchange pipeline, and the second end of the second heat exchange pipeline is connected to the enthalpy increasing port of the compressor and/or the gas-liquid separator; the bypass branch is provided with a valve at the position, close to the first side, of the second part, and the bypass branch is provided with a third electronic expansion valve at the position, close to the second side, of the second part.
By adding the bypass pipeline and combining the technology of intermediate supercooling and air-supplying enthalpy increase, different processing can be performed on the refrigerants flowing through the first part at the top and the second part at the bottom of the outdoor heat exchanger, and when the heat pump system is in a heating mode, because the bypass branch is provided with the continuously circulating medium-temperature refrigerant, the second part can be ensured not to frost during heating.
On the premise, when the heat pump system is in a defrosting mode, the defrosting effect of the first part is ensured by ensuring the refrigerant circulation quantity of the first part, and finally, the defrosting of the outdoor heat exchanger is effectively realized. Compared with the bottom supercooling mode, the method can avoid pressure loss caused by arrangement of the subcooler, thereby improving the overall performance of the air-conditioning heat pump system. Compared with the method of directly plugging the bottom coil, the method has the advantages that the intermediate heat exchanger is combined, on one hand, the second part of the bottom can be thoroughly prevented from frosting, on the other hand, the supercooling degree of a main refrigerant of the system can be improved, and therefore the overall performance of the heat pump system is improved.
With regard to the air-conditioning heat pump system, in a possible implementation manner, the refrigerant pipeline includes a first branch pipe and a second branch pipe, and a second end of the second heat exchange pipeline is connected to the enthalpy increasing port of the compressor and the gas-liquid separator through the first branch pipe and the second branch pipe, where the first branch pipe and the second branch pipe are respectively provided with a first valve and a second valve.
By such an arrangement, the connection state of the plate heat exchanger can be adjusted more flexibly, and a better enthalpy-increasing effect can be obtained.
With regard to the air conditioning heat pump system described above, in one possible embodiment, the intermediate heat exchanger is a plate heat exchanger.
With the air conditioning heat pump system described above, in one possible embodiment, the heat dissipation area of the first portion is larger than the heat dissipation area of the second portion.
Through the arrangement, the effective heat exchange area of the outdoor heat exchanger can be influenced as little as possible on the premise of ensuring that the second part is not frosted all the time, so that the heat exchange performance of the outdoor heat exchanger is enhanced as much as possible on the premise of ensuring the defrosting reliability.
For example, in order to ensure an effective heat exchange area of the outdoor heat exchanger, the heat exchange area of the first portion should be substantially larger than that of the second portion. As an example, the second portion of the bottom includes 2-3 rows of coils.
In combination with the difference between the heat exchange areas of the first part and the second part, the first heat exchange tube of the plate heat exchanger should be understood as a main path and the second heat exchange tube should be understood as a secondary path by referring to the flow distribution of the refrigerant in the first heat exchange tube and the second heat exchange tube of the plate heat exchanger. Taking the heating mode as an example, the second electronic expansion valve is connected with an inlet of the main path (the first end of the first heat exchange tube), an outlet of the main path (the second end of the first heat exchange tube) is connected with the first electronic expansion valve, the third electronic expansion valve is connected with an inlet of the auxiliary path (the first end of the second heat exchange tube), and an outlet of the auxiliary path (the second end of the second heat exchange tube) is connected with the enthalpy increasing port of the compressor and/or the inlet of the gas-liquid separator.
The second aspect of the present invention provides a control method for an air-conditioning heat pump system, the control method comprising: acquiring an operation mode of the air-conditioning heat pump system; selectively opening at least the valve and adjusting an opening degree of the third electronic expansion valve according to the operation mode; wherein, the air-conditioning heat pump system is any one of the air-conditioning heat pump systems.
With regard to the above control method, in a possible implementation manner, the refrigerant pipeline includes a first branch pipe and a second branch pipe, the second end of the second heat exchange pipeline is connected to an enthalpy increasing port of the compressor and the gas-liquid separator through the first branch pipe and the second branch pipe, respectively, and the first branch pipe and the second branch pipe are provided with a first valve and a second valve, respectively, and the "selectively opening at least the valves and adjusting the opening degree of the third electronic expansion valve according to the operation mode" specifically includes: selectively opening the valve, the first valve, the second valve, and adjusting an opening degree of the third electronic expansion valve.
By such an arrangement, the enthalpy increasing effect can be reliably obtained.
With regard to the above control method, in a possible embodiment, the "selectively opening at least the valve and adjusting the opening degree of the third electronic expansion valve according to the operation mode" specifically includes: and when the operation mode is the defrosting mode, closing the valve and the third electronic expansion valve.
With this arrangement, since the heat pump system is substantially in the cooling mode at this time, there is no possibility that the second portion itself will be frosted, and the defrosting effect of the first portion due to the insufficient refrigerant circulation amount can be prevented from being affected after the valve and the third electronic expansion valve are closed.
With regard to the above control method, in a possible embodiment, "selectively opening at least the valve and adjusting the opening degree of the third electronic expansion valve according to the operation mode" specifically includes: and when the operation mode is a heating mode, opening the valve and adjusting the opening degree of the third electronic expansion valve to ensure that the second part does not frost. Meanwhile, the running performance of the heat pump system is improved.
With regard to the above control method, in a possible embodiment, "selectively opening at least the valve and adjusting the opening degree of the third electronic expansion valve according to the operation mode" specifically includes: and when the operation mode is a refrigeration mode, opening the valve and adjusting the opening degree of the third electronic expansion valve according to the refrigeration requirement. Meanwhile, the running performance of the heat pump system is improved.
In the cooling mode and the heating mode, the opening degree of the third electronic expansion valve can be controlled according to the superheat degree of the branch refrigerant before and after flowing through the plate heat exchanger. Such as: in order to protect the compressor and ensure performance, the degree of superheat should generally be controlled between 0 and 2, it being understood that the specific values may be determined and adjusted in connection with the actual product.
A third aspect of the present invention provides a control apparatus including a memory storing a program capable of executing the steps of the method for controlling an air-conditioning heat pump system according to any one of the preceding claims, and a processor capable of calling the program and executing the steps of the method according to any one of the preceding claims.
The control device has all the technical effects of the control method of the air-conditioning heat pump system, and the details are not repeated herein.
The invention can be seen from the fact that the technology of improving supercooling by skillfully utilizing the plate heat exchanger enables the medium-temperature refrigerant to firstly flow through the second part at the bottom of the heat exchanger in the heating mode, so that the frosting of the second part at the bottom can be effectively prevented during the heating period, and the second part can continuously participate in heat exchange. On the basis, the performance of the heat pump system is further improved by combining the air-supplying and enthalpy-increasing technology. Specifically, a bypass branch is additionally arranged between a refrigerant pipeline between the intermediate heat exchanger and a second electronic expansion valve corresponding to the indoor heat exchanger and the enthalpy increasing port/gas-liquid separator of the compressor, the refrigerant in the refrigerant pipeline is divided into a main pipeline and a branch pipeline, the main pipeline leads to a first part at the top of the outdoor heat exchanger, and the branch pipeline passes through a second part at the bottom of the outdoor heat exchanger through the bypass branch pipeline. The bypass branch is communicated in the heating mode, so that the second part at the bottom is prevented from frosting, and the defrosting effect of the first part is ensured in the mode that the bypass branch is closed in the defrosting mode. On the premise that the defrosting quality of the outdoor heat exchanger is guaranteed, the overall performance of the air-conditioning heat pump system is improved.
Drawings
Embodiments of the present invention will be described below with reference to the accompanying drawings in which:
FIG. 1 is a schematic diagram of a multi-split air conditioner according to a first embodiment of the present invention;
FIG. 2 is a schematic diagram of a multi-split air conditioner according to a second embodiment of the present invention;
FIG. 3 is a schematic diagram of a multi-split air conditioner according to a third embodiment of the present invention;
fig. 4 is a flowchart illustrating a control method of a multi-split air conditioner according to a first embodiment of the invention;
fig. 5 is a schematic view illustrating a flow direction of refrigerant in a multi-split air conditioner in a cooling mode according to a first embodiment of the present invention;
fig. 6 is a schematic flow direction of a refrigerant in a heating mode of a multi-split air conditioner according to a first embodiment of the present invention; and
fig. 7 is a schematic diagram illustrating a refrigerant flow direction of a multi-split air conditioner in a defrost mode according to a first embodiment of the present invention.
List of reference numerals:
1. an outdoor heat exchanger; 11. a first portion; 12. a second portion; 2. an indoor heat exchanger; 3. a compressor; 31. an enthalpy increasing port; 4. a four-way valve; 5. a gas-liquid separator; 6. a main road; 71. a first electronic expansion valve; 72. a second electronic expansion valve; 73. a third electronic expansion valve; 74. an electromagnetic valve; 8. a bypass branch; 9. a plate heat exchanger; 911. a first end of a first heat exchange line; 912. a second end of the first heat exchange line; 921. a first end of a second heat exchange line; 922. a second end of the second heat exchange line; 101. a first branch pipe; 102. a second branch pipe; 111. a first solenoid valve; 112. a second solenoid valve.
Detailed Description
For the purpose of facilitating understanding of the present invention, the present invention will be described more fully and in detail below with reference to the accompanying drawings and examples, but it will be understood by those skilled in the art that these embodiments are merely illustrative of the technical principles of the present invention and are not intended to limit the scope of the present invention. Although the present embodiment is described with respect to a multi-split air conditioner including one outdoor unit and a plurality of indoor units, it is obvious that the multi-split air conditioner may be in other forms, such as a plurality of outdoor units.
In the description of the present invention, a "module" or "processor" may include hardware, software, or a combination of both. A module may comprise hardware circuitry, various suitable sensors, communication ports, memory, may comprise software components such as program code, or may be a combination of software and hardware. The processor may be a central processing unit, microprocessor, image processor, digital signal processor, or any other suitable processor. The processor has data and/or signal processing functionality. The processor may be implemented in software, hardware, or a combination thereof. Non-transitory computer readable storage media include any suitable medium that can store program code, such as magnetic disks, hard disks, optical disks, flash memory, read-only memory, random-access memory, and the like. The term "a and/or B" denotes all possible combinations of a and B, such as a alone, B alone or a and B. The term "at least one A or B" or "at least one of A and B" means similar to "A and/or B" and may include only A, only B, or both A and B. The singular forms "a", "an" and "the" may include the plural forms as well.
It should be noted that in the description of the present invention, the terms of direction or positional relationship indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, which are merely for convenience of description, and do not indicate or imply that the device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
The air conditioner generally includes an outdoor unit and an indoor unit, the outdoor unit is mainly provided with a compressor, an outdoor fan and an outdoor heat exchanger (generally called condenser), the indoor unit is mainly provided with an indoor heat exchanger (generally called evaporator), and the compressor, the condenser, the evaporator and the compressor form a refrigerant circulation loop. When the refrigerant circulates along the compressor → the outdoor heat exchanger → the indoor heat exchanger → the compressor, the air conditioner is in a refrigerating cycle. When the refrigerant circulates along the compressor → the indoor heat exchanger → the outdoor heat exchanger → the compressor, the air conditioner is in a heating cycle. In the case where the air conditioner is in a heating cycle, there is a possibility that the outdoor heat exchanger is frosted. If defrosting/defrosting is not performed in time, the heating performance of the air conditioner is affected.
Compared with the traditional air conditioner, on one hand, the outdoor unit of the multi-split air conditioner has the characteristic of large area of the outdoor heat exchanger, and on the other hand, once the outdoor heat exchanger of the outdoor unit of the multi-split air conditioner is not subjected to timely and effective defrosting operation, the performance of the indoor units of the multi-split air conditioner can be influenced. Based on the premise, the inventor analyzes the outdoor heat exchanger of the multi-split air conditioner in the following way: when the outdoor heat exchanger is defrosted, if defrosting water cannot be discharged at the bottom in time, the defrosting water is easy to freeze to cause incomplete defrosting at the bottom, and frost layer accumulation affects the heat exchange effect of the outdoor unit of the air conditioner after long-time operation, so that the performance of the whole machine is reduced.
The prior art, recognizing this phenomenon, typically makes such improvements to the coil at the bottom of the outdoor heat exchanger: and the coil pipe at the bottom is used as a supercooling pipe or the coil pipe at the bottom is directly plugged. For the coil pipe at the bottom as the supercooling pipe, the middle temperature refrigerant flowing through the supercooling pipe can not frost the bottom, but is limited by the size of the outdoor heat exchanger, the flow area of the supercooling pipe is quite limited, and the large pressure loss is generally caused, so that the problem is caused: in order to prevent the arrangement of frosting from generating adverse effect which influences the performance of the whole machine. Obviously, this is a problem of overall performance that arises in the process of solving an overall performance problem, and the solved problem and the newly arising problem are not very different. For the direct plugging of the coil pipe at the bottom, the problem of frosting and icing cannot be thoroughly solved, and the effective area of the outdoor heat exchanger is wasted.
Based on such a situation, the present invention has been made in consideration of the difference between the regions to which defrosting is applied, and particularly, needs to be intensively improved with respect to the bottom region of the outdoor heat exchanger.
Referring to fig. 1, fig. 1 is a schematic structural diagram of a multi-split air conditioner according to a first embodiment of the present invention. As shown in fig. 1, the multi-split air conditioner includes an outdoor unit 1 and a plurality of indoor units 2, wherein the outdoor heat exchanger is divided into a first portion (as a main heat exchanger) 11 at the top and a second portion (as a bypass heat exchanger) 12 at the bottom, it is understood that the division is not strictly, such as: the outer shell is divided into two cavities by a partition plate, and the first part and the second part are respectively arranged in the two cavities. But mainly aims at the division of pipeline communication, namely the corresponding communication targets of the liquid inlet side and the liquid outlet side of the first part and the second part are different. In other words, in the present invention, the division of the outdoor heat exchanger into the first part and the second part should be understood as selectively dividing the two regions at the visual level on the basis of the definition of the corresponding communication targets of the liquid inlet side and the liquid outlet side of the first part and the second part. On the one hand, the second part of the bottom is ensured not to frost in the process of heating the outdoor heat exchanger; on the other hand, in the process of defrosting the outdoor heat exchanger, the first part is ensured to have enough refrigerant circulation quantity, so that the defrosting effect of the first part is ensured. Through the matching of the mechanisms in the two aspects, the integral defrosting effect of the outdoor heat exchanger is ensured. Specifically, the bypass branch is configured for the second part, and when in the heating mode, the medium-temperature refrigerant continuously flows in the second part, so that the frosting phenomenon cannot occur. In the defrosting mode, the refrigerant does not flow in the bypass branch, so that the defrosting effect of the first part is ensured. In the two modes, the heat exchange area of the outdoor heat exchanger is mainly converted into the heat dissipation area of the first part, so that in order to ensure the heat exchange performance of the outdoor heat exchanger, the heat dissipation area of the first part should be obviously larger than that of the second part, for example, 2-3 rows of coils at the bottommost part of the outdoor heat exchanger are usually used as the second part.
Specifically, the multi-split air conditioner comprises an outdoor heat exchanger 1, a plurality of indoor heat exchangers 2, a compressor 3, a four-way valve 4, a gas-liquid separator 5 and an intermediate heat exchanger which are connected through a refrigerant pipeline, if the intermediate heat exchanger is a plate heat exchanger 9, if the intermediate heat exchanger 9 comprises a shell and two rows of heat exchange tubes arranged in the shell, specifically, the multi-split air conditioner comprises a first heat exchange pipeline and a second heat exchange pipeline which can exchange heat, the plurality of indoor heat exchangers are connected with the outdoor heat exchanger through a main pipeline 6 after being gathered, a first electronic expansion valve 71 is arranged on the main pipeline 6, each indoor heat exchanger is provided with a second electronic expansion valve 72, a first end 911 and a second end 912 of the first heat exchange pipeline are respectively connected with the first electronic expansion valve and the second electronic expansion valve, the outdoor heat exchanger comprises a first part 11 and a second part 12, the second part is provided with a bypass branch 8, and the first side (the left side in fig. 1) A position between the ends and the second expansion valve, a second side (right side in fig. 1) is connected to a first end 921 of the second heat exchange line, and a second end 922 of the second heat exchange line is connected to the enthalpy addition port 31 of the compressor. The bypass branch is provided with a third electronic expansion valve 73 at a position near the second side of the second portion, and a valve, such as a solenoid valve 74, is provided at a position near the first side of the second portion.
Referring to fig. 2, fig. 2 is a schematic structural diagram of a multiple online unit according to a second embodiment of the invention. As shown in fig. 2, on the premise that the basic structure is substantially the same as that of fig. 1, the main difference is the connection manner of the second side of the bypass branch, and specifically, in the case that the compressor is not provided with the enthalpy increasing port, the second side of the bypass branch is connected to the gas-liquid separator 5.
Referring to fig. 3, fig. 3 is a schematic structural diagram of a multi-split air conditioner according to a third embodiment of the present invention. As shown in fig. 3, on the premise that the basic structure is substantially the same as that of fig. 1 and 2, the main difference is the connection manner of the second side of the bypass branch, specifically, the refrigerant pipeline includes a first branch pipe 101 and a second branch pipe 102, and in the case that the compressor is provided with the enthalpy increasing port, the second side of the bypass branch is connected to the enthalpy increasing port 31 of the compressor and the gas-liquid separator 5 through the first branch pipe 101 and the second branch pipe 102, respectively. Wherein, the first branch pipe is provided with a first valve, such as a first solenoid valve 111, and the second branch pipe is provided with a second valve, such as a second solenoid valve 112. Thus, such control can be performed as follows: and judging whether the running state of the compressor is in an enthalpy increasing state, if so, opening the first electromagnetic valve, closing the second electromagnetic valve, and communicating the second side of the bypass branch with the enthalpy increasing port of the compressor. If not, the first electromagnetic valve is closed, the second electromagnetic valve is opened, and the second side of the bypass branch is communicated with the gas-liquid separator.
Referring to fig. 4, fig. 4 is a flowchart illustrating a control method of a multi-split air conditioner according to a first embodiment of the present invention. As shown in fig. 4, based on the first embodiment, i.e. the structure shown in fig. 1, the control method of the multi-split air conditioner of the present invention mainly includes the following steps:
s1, acquiring the operation mode of the multi-split air conditioner;
and S2, selectively opening the electromagnetic valve and adjusting the opening degree of the third electronic expansion valve according to the operation mode.
Referring to fig. 4 and 5, fig. 5 is a schematic view illustrating a flow direction of a refrigerant in a cooling mode of a multi-split air conditioner according to a first embodiment of the present invention. As shown in fig. 4 and 5, when any air conditioning indoor unit is in the cooling mode, S2 specifically includes: and opening the electromagnetic valve and adjusting the opening degree of the third electronic expansion valve according to the refrigeration requirement, for example, adjusting the opening degree of the third electronic expansion valve according to the superheat degree of the branch refrigerant so as to meet the refrigeration requirement and simultaneously improve the running performance of the pump system. In the cooling mode: the high-temperature high-pressure gaseous refrigerant discharged from the exhaust port of the compressor firstly flows through the first part of the outdoor heat exchanger to be condensed and released, then the refrigerant completely enters the plate heat exchanger through the second end of the first heat exchange pipeline, and flows out of the first end of the first heat exchange pipeline and then is divided into a main path and a branch path, wherein the refrigerant in the main path flows to an indoor unit of the air conditioner to be refrigerated, the refrigerant in the branch path firstly flows through the second part at the bottom of the outdoor heat exchanger so that the supercooling degree of the refrigerant in the branch path is improved, and the refrigerant in the main path in the first heat exchange pipeline enters the plate heat exchanger through the first end of the second heat exchange pipeline after being throttled by the electronic expansion valve to exchange heat with the refrigerant in the main path in the first heat exchange pipeline, so that the supercooling degree of the refrigerant in the main path.
It should be understood that the main path and the branch path are understood as the distribution ratio of the refrigerant. Specifically, the first part at the top of the outdoor heat exchanger has an effective heat exchange area in various modes, so that the heat exchange area of the first part is obviously larger than that of the second part, and the refrigerant corresponding to the first part is the refrigerant in the main path.
Referring to fig. 4 and 6, fig. 6 is a schematic view illustrating a flow direction of a refrigerant in a heating mode of a multi-split air conditioner according to a first embodiment of the present invention. As shown in fig. 4 and 6, when any air conditioning indoor unit is in the heating mode, S2 specifically includes: and opening the electromagnetic valve and adjusting the opening degree of the third electronic expansion valve to ensure that the second part does not frost, and adjusting the opening degree of the third electronic expansion valve according to the superheat degree of the branch refrigerant to ensure that the second part does not frost and improve the running performance of the heat pump system. In the heating mode: the medium temperature refrigerant flowing back from the indoor heat exchanger is divided into a main path and a branch path before entering the plate heat exchanger, the refrigerant in the main path enters the intermediate heat exchanger through the first end of the first heat exchange pipeline and exchanges heat with the refrigerant in the branch path in the second heat exchange pipeline, and therefore the supercooling degree of the refrigerant in the main path is improved. And then, the main path refrigerant flows out through the second end of the first heat exchange pipeline, flows through the first electronic expansion valve, flows to the first part of the outdoor heat exchanger, is evaporated, and returns to the compressor. The refrigerant in the branch firstly flows through the second part at the bottom of the outdoor heat exchanger, then enters the intermediate heat exchanger through the first end of the second heat exchange pipeline after being throttled by the third electronic expansion valve of the bypass branch, exchanges heat with the refrigerant in the main pipeline in the first heat exchange pipeline to become superheated gas, and finally is sprayed into the enthalpy-increasing port of the compressor.
Referring to fig. 4 and 7, fig. 7 is a schematic diagram illustrating a refrigerant flow direction of the multi-split air conditioner in the defrost mode according to the first embodiment of the present invention. As shown in fig. 4 and 7, when any air conditioning indoor unit is in the defrosting mode, S2 specifically includes: the solenoid valve and the third electronic expansion valve are closed. This is because, in the defrosting mode, the inner and outer fans both stop operating, and the refrigerant circulation volume itself in the system is small, and if the refrigerant is still divided into the main path and the branch path, the problem of insufficient refrigerant circulation volume may occur in the defrosting process. Therefore, in order to prevent the defrosting effect of the first portion of the top from being affected due to the insufficient refrigerant circulation amount, the refrigerant does not pass through the second portion corresponding to the bypass branch. In fact, as can be seen from the foregoing description of the heating mode, the present invention can ensure that the second portion does not frost during heating, and therefore, it is not necessary to circulate the refrigerant in the bypass branch during defrosting. Thus, effective defrosting of the outdoor heat exchanger is achieved.
It should be noted that, although the foregoing embodiments describe each step in a specific sequence, those skilled in the art will understand that, in order to achieve the effect of the present invention, different steps do not necessarily need to be executed in such a sequence, and they may be executed simultaneously (in parallel) or in other sequences, and these changes are all within the protection scope of the present invention.
In a control device of the present invention, processing functions of the respective steps of the aforementioned method are included. In one embodiment, the control device at least comprises a processor and a memory, wherein the memory stores a program capable of executing the control method of the multi-split air conditioner, and the processor calls the corresponding program in the memory and executes the corresponding steps of the method according to different operation modes.
It will be understood by those skilled in the art that all or part of the flow of the method according to the above-described embodiment may be implemented by a computer program, which may be stored in a computer-readable storage medium and used to implement the steps of the above-described embodiments of the method when the computer program is executed by a processor. Wherein the computer program comprises computer program code, which may be in the form of source code, object code, an executable file or some intermediate form, etc. The computer-readable medium may include: any entity or device capable of carrying said computer program code, media, usb disk, removable hard disk, magnetic diskette, optical disk, computer memory, read-only memory, random access memory, electrical carrier wave signals, telecommunication signals, software distribution media, etc. It should be noted that the computer readable medium may contain content that is subject to appropriate increase or decrease as required by legislation and patent practice in jurisdictions, for example, in some jurisdictions, computer readable media does not include electrical carrier signals and telecommunications signals as is required by legislation and patent practice.
So far, the technical solution of the present invention has been described with reference to one embodiment shown in the drawings, but it is easily understood by those skilled in the art that the scope of the present invention is obviously not limited to these specific embodiments. Equivalent changes or substitutions of related technical features can be made by those skilled in the art without departing from the principle of the invention, and the technical scheme after the changes or substitutions can fall into the protection scope of the invention.
Claims (10)
1. An air-conditioning heat pump system is characterized in that the air-conditioning heat pump system comprises a compressor, a gas-liquid separator, an intermediate heat exchanger, at least one outdoor heat exchanger and at least one indoor heat exchanger which are connected through a refrigerant pipeline,
the intermediate heat exchanger comprises a shell, a first heat exchange pipeline and a second heat exchange pipeline which are arranged in the shell and can exchange heat,
the refrigerant pipeline includes:
the indoor heat exchanger is connected with the outdoor heat exchanger through the main path, a first electronic expansion valve is arranged on the main path, the indoor heat exchanger is provided with a second electronic expansion valve, and a first end and a second end of the first heat exchange pipeline are respectively connected with the first electronic expansion valve and the second electronic expansion valve; and
the outdoor heat exchanger comprises a first part and a second part which are arranged up and down, the second part is arranged on the bypass branch, the first side of the bypass branch is connected to the position, between the first end of the first heat exchange pipeline and the second electronic expansion valve, of the main pipeline, the second side of the bypass branch is connected to the first end of the second heat exchange pipeline, and the second end of the second heat exchange pipeline is connected to the enthalpy increasing port and/or the gas-liquid separator of the compressor;
the bypass branch is provided with a valve at the position, close to the first side, of the second part, and the bypass branch is provided with a third electronic expansion valve at the position, close to the second side, of the second part.
2. An air-conditioning heat pump system according to claim 1, characterized in that the refrigerant pipeline comprises a first branch pipe and a second branch pipe, the second end of the second heat exchange pipeline is connected to the enthalpy increasing port of the compressor and the gas-liquid separator through the first branch pipe and the second branch pipe respectively,
wherein the first branch pipe and the second branch pipe are respectively provided with a first valve and a second valve.
3. An air conditioning heat pump system according to claim 1 or 2, wherein the intermediate heat exchanger is a plate heat exchanger.
4. An air conditioning heat pump system according to claim 1, wherein the heat dissipation area of the first portion is larger than the heat dissipation area of the second portion.
5. A control method of an air conditioner heat pump system is characterized by comprising the following steps:
acquiring an operation mode of the air-conditioning heat pump system;
selectively opening at least the valve and adjusting an opening degree of the third electronic expansion valve according to the operation mode;
wherein the air-conditioning heat pump system is the air-conditioning heat pump system of any one of claims 1 to 4.
6. A control method for an air-conditioning heat pump system according to claim 5, wherein the refrigerant pipeline comprises a first branch pipe and a second branch pipe, the second end of the second heat exchange pipeline is connected to the enthalpy increasing port of the compressor and the gas-liquid separator through the first branch pipe and the second branch pipe, respectively, the first branch pipe and the second branch pipe are provided with a first valve and a second valve, respectively, and the "selectively opening at least the valves and adjusting the opening degree of the third electronic expansion valve according to the operation mode" specifically comprises:
selectively opening the valve, the first valve, the second valve, and adjusting an opening degree of the third electronic expansion valve.
7. A control method for an air conditioning heat pump system according to claim 5 or 6, wherein the "selectively opening at least the valve and adjusting the opening degree of the third electronic expansion valve according to the operation mode" specifically comprises:
and when the operation mode is the defrosting mode, closing the valve and the third electronic expansion valve.
8. The method for controlling an air-conditioning heat pump system according to claim 5 or 6, wherein the "selectively opening at least the valve and adjusting the opening degree of the third electronic expansion valve according to the operation mode" specifically includes:
and when the operation mode is a heating mode, opening the valve and enabling the second part not to frost by adjusting the opening degree of the third electronic expansion valve.
9. The method for controlling an air-conditioning heat pump system according to claim 5 or 6, wherein the "selectively opening at least the valve and adjusting the opening degree of the third electronic expansion valve according to the operation mode" specifically includes:
and when the operation mode is a refrigeration mode, opening the valve and adjusting the opening degree of the third electronic expansion valve according to the refrigeration requirement.
10. A control apparatus characterized by comprising a memory storing a program capable of executing the steps of the control method of the air-conditioning heat pump system according to any one of claims 5 to 9, and a processor capable of calling the program and executing the steps of the method according to any one of claims 5 to 9.
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