CN1485588A - Dual-purpose multiple operating mode self-defrosting type heat pump air-conditioner and automatic defrosting process thereof - Google Patents
Dual-purpose multiple operating mode self-defrosting type heat pump air-conditioner and automatic defrosting process thereof Download PDFInfo
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- 238000010257 thawing Methods 0.000 title claims abstract description 99
- 238000000034 method Methods 0.000 title claims abstract description 23
- 239000003507 refrigerant Substances 0.000 claims abstract description 164
- 239000007788 liquid Substances 0.000 claims abstract description 62
- 238000004378 air conditioning Methods 0.000 claims abstract description 45
- 238000010438 heat treatment Methods 0.000 claims description 54
- 239000002918 waste heat Substances 0.000 claims description 38
- 238000006243 chemical reaction Methods 0.000 claims description 25
- 230000000694 effects Effects 0.000 claims description 10
- 238000011010 flushing procedure Methods 0.000 claims description 8
- 238000001514 detection method Methods 0.000 claims description 6
- 238000012806 monitoring device Methods 0.000 claims description 5
- 238000010992 reflux Methods 0.000 claims description 4
- 230000009977 dual effect Effects 0.000 claims description 3
- 238000005086 pumping Methods 0.000 abstract 2
- 238000004519 manufacturing process Methods 0.000 abstract 1
- 238000012544 monitoring process Methods 0.000 abstract 1
- 239000000700 radioactive tracer Substances 0.000 abstract 1
- 238000005057 refrigeration Methods 0.000 description 9
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 6
- 238000005485 electric heating Methods 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000001816 cooling Methods 0.000 description 4
- 239000007789 gas Substances 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 238000013461 design Methods 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000002457 bidirectional effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 239000010726 refrigerant oil Substances 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
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Abstract
The invention relates to a dual-purpose multiple operating mode self-defrosting type thermal pumping air-conditioning unit which comprises a compressor, a four-way switching valve set, a second heat exchanger, a liquid return cushioning device and a first heat exchanger having a draught fan, wherein a residual heat tracer pipe, a temperature monitoring apparatus and a humidity supervisory instrument are arranged on the first heat exchanger, a pipe line switching device, a controlled throttle apparatus a temperature and moisture detecting device, a four-way switching valve set, a draught fan, and the electrically controlled portion of the controlled throttle device are arranged in the refrigerant pipe connection between the first and the second heat exchanger. The invention also discloses the automatic defrosting method for the thermal pumping air-conditioning unit which can substantially improve the heat-production performance of the heat pump air-conditioning unit and realize automatic defrosting.
Description
Technical Field
The invention belongs to the field of heating and refrigerating combined systems, and particularly relates to a compression type heat pump air conditioning device.
Background
The air conditioner is widely used for various large central air conditioning devices for centralized cooling and heating in office buildings, hotels and residential districts in northern China, and a large or medium-sized compression type refrigerating unit is generally used for completing the refrigerating function; because the existing large and medium-sized compression refrigerating units can not perform heating (the flow direction of a refrigerant is difficult to control arbitrarily), the large air conditioning device can only complete the heating function of an air conditioning system by an external heating source (usually adopting a steam heating mode) in winter, so that the utilization rate of refrigerating equipment is low, and the operating cost of a user is high.
The inventor of the present invention discloses a dual-effect dual-temperature central air conditioning device in chinese patent ZL 02213198.1 published on 8/1/2003. The double-control throttling expansion device comprises a compressor, a first heat exchanger and a second heat exchanger, wherein a refrigerant supply pipe of the compressor is connected with refrigerant heat exchange pipes of the first heat exchanger and the second heat exchanger through a refrigerant reversing valve group, a refrigerant return pipe of the compressor is connected with the refrigerant heat exchange pipes of the first heat exchanger and the second heat exchanger through a buffer and the refrigerant reversing valve group, and a two-way double-control throttling expansion device is connected between the refrigerant heat exchange pipes communicated with the first heat exchanger and the second heat exchanger in series. The patent adopts the switching of a refrigerant reversing valve group and a bidirectional double-control throttling expansion device, and realizes the functions of double effects of refrigeration and heating and double temperature ranges of large and medium-sized refrigerating units. However, the heat exchanger still has a defect that when the heat exchanger is used in northern areas of China in winter, a first heat exchanger (an outdoor heat exchanger) is easy to frost and freeze, the heat exchange efficiency of the whole device is influenced, and when the outdoor temperature is lower than-5 ℃, the output temperature of a second heat exchanger cannot meet the temperature requirement specified by related heating specifications.
Chinese patent ZL 00248597.4 published in 8/22/2001 discloses a "heat pipe heat pump cooling and heating air conditioner", which is characterized in that an auxiliary heating heat pipe collector is arranged between a compressor and an indoor heat exchanger, and the secondary heating is performed on refrigerant vapor discharged from the compressor, so as to increase the enthalpy value of the molecules of the refrigerant vapor, thereby achieving the purpose of improving the heat quantity released by the indoor heat exchanger. The patent is still a method for increasing heat quantity indoors by electric heating, needs to provide energy for an air conditioning system additionally, and has high electric heating cost, so that the defrosting problem of an outdoor heat exchanger cannot be solved.
Chinese patent application 97123401.9, published 6.1.1999, discloses a defrosting apparatus and method for an air conditioner, which judges whether an outdoor unit is frosted by comparing the temperature of the outdoor heat exchanger, the outdoor temperature and the operation time of a compressor when heating, and starts defrosting operation if the temperature of the outdoor heat exchanger is lower than a predetermined temperature within a predetermined time and the operation of the compressor exceeds the predetermined time, by comparing the outdoor temperature with the outdoor temperature; and if the temperature of the outdoor heat exchanger exceeds the preset temperature and the defrosting operation exceeds the preset time, stopping the defrosting operation and entering the heating operation. However, in the whole defrosting operation stage, the actual air conditioner works under the refrigerating working condition, the output temperature of the indoor heat exchanger is influenced, whether the frosting on the outdoor heat exchanger is completely removed cannot be judged in time by simply measuring the temperature, and the frosting and the icing on the outdoor heat exchanger cannot be rapidly removed for large and medium-sized air conditioners.
Disclosure of Invention
The invention aims to solve the technical problem of providing a double-effect multi-working condition self-defrosting heat pump air conditioner and an automatic defrosting method thereof, which can normally heat and heat a large or medium-sized heat pump type air conditioner under the condition of lower temperature environment without adopting an electric heating mode, have the functions of automatic defrosting and deicing, and have high defrosting and deicing speed and good effect.
The technical scheme of the invention is as follows: the double-effect multi-working condition self-defrosting heat pump air conditioner comprises a compressor, a four-way conversion valve group, a second heat exchanger, a liquid return buffer device and a first heat exchanger with a fan, wherein the compressor, the four-way conversion valve group, the second heat exchanger, the liquid return buffer device and the first heat exchanger are sequentially connected through a refrigerant pipeline; a refrigerant heat exchange tube of the first heat exchanger is provided with a temperature monitoring device and a humidity detection device; a pipeline switching device and a controllable throttling device connected with the pipeline switching device are arranged on a refrigerant connecting pipe between the first heat exchanger and the second heat exchanger; one ends of the refrigerant heat exchange tubes of the first heat exchanger and the second heat exchanger are respectively connected with one end of the four-way conversion valve bank; the other end of the first heat exchanger refrigerant heat exchange tube is connected with the other end of the second heat exchanger refrigerant heat exchange tube through the pipeline switching device and the controllable throttling device; two ends of the first heat exchanger waste heat tracing pipe are connected with the pipeline switching device; the temperature monitoring device and the humidity detection device are electrically connected with the four-way conversion valve group, the fan, the pipeline switching device and the electric control part of the controllable throttling device.
The pipeline switching device comprises control valves F11-F16, wherein one ends of the control valves F11 and F14 are connected in parallel to form an r end of the pipeline switching device and are connected with the other end of the refrigerant heat exchange tube of the second heat exchanger; the other end of the control valve F11 and one end of the control valve F12 are connected in parallel to form an o end of the pipeline switching device and connected with one end of the controllable throttling device; the other end of the control valve F12 and one end of the control valve F15 are connected in parallel to form an m end of the pipeline switching device and are connected with one end of the first heat exchanger waste heat tracing pipe; one ends of the control valves F13 and F16 are connected in parallel to form the end I of the pipeline switching device and are connected with the other end of the first heat exchanger refrigerant heat exchange pipe; the other ends of the control valves F13 and F15 are connected in parallel to form the n end of the pipeline switching device and are connected with the other end of the controllable throttling device; the other ends of the control valves F14 and F16 are connected in parallel to form a k end of the pipeline switching device and are connected with the other end of the first heat exchanger waste heat tracing pipe.
The controllable throttling device can adopt a structural form consisting of two groups of one-way controllable throttling units DJ1 and DJ2 which are reversely connected in series, two control valves f3 and f4 and a liquid collecting tank, wherein each one-way controllable throttling unit is formed by connecting one-way throttling expansion valve j1 or j2 and one control valve f1 or f2 in series, the liquid collecting tank is provided with a liquid outlet pipe and two air inlet pipes, the tail end opening of the liquid outlet pipe is positioned at the lower part of the liquid collecting tank, the tail end opening of the air inlet pipe is positioned at the upper part of the liquid collecting tank, and the bottom of the liquid collecting tank is provided with an oil drain valve; one end of the one-way controllable throttling unit DJ1 and one end of the control valve f3 are connected in parallel to form a q end of the controllable throttling device and connected with an o end of the pipeline switching device; one end of the unidirectional controllable throttling unit DJ2 and one end of the control valve f4 are connected in parallel to form a p end of the controllable throttling device and connected with an n end of the pipeline switching device; the other ends of the unidirectional controllable throttling units DJ1 and DJ2 are connected in parallel and then are connected with a liquid outlet pipe of the liquid collecting tank; the other ends of the control valves f3 and f4 are respectively correspondingly connected with two air inlet pipes of the liquid collecting tank.
The controllable throttling device can also adopt a structural form consisting of two groups of one-way controllable throttling units DJ3 and DJ4 which are reversely connected in parallel, each one-way controllable throttling unit is formed by connecting one-way throttling expansion valve j3 or j4 and one control valve f5 or f6 in series, wherein one end of the control valve f5 and one end of the one-way throttling expansion valve j4 are connected in parallel and then connected with the q end forming the controllable throttling device and the o end of the pipeline switching device; one end of the control valve f6 and the other end of the one-way throttle expansion valve j3 are connected in parallel and then connected with the p end which forms a controllable throttle device and the n end of the pipeline switching device.
The fan that above-mentioned first heat exchanger was taken is the variable speed fan, and when air conditioner device worked in the defrosting operating mode, the fan motor was operated under the rotational speed that is higher than 1000 revolutions per minute.
The invention also provides an automatic defrosting method of the double-effect multi-working-condition self-defrosting heat pump air conditioner, which comprises the following steps:
(1) when the air conditioning device operates in a heating working condition, detecting the temperature of a refrigerant heat exchange tube of a first heat exchanger positioned outdoors;
(2) when the air conditioning device operates in a heating working condition, detecting the humidity outside a refrigerant heat exchange tube of a first heat exchanger;
(3) when the temperature or the humidity of the refrigerant heat exchange tube of the first heat exchanger reaches a defrosting action set value, the air conditioning device enters a temperature difference compensation defrosting working condition, and the refrigerant passing through the second heat exchanger enters the refrigerant heat exchange tube of the first heat exchanger after passing through the waste heat tracing tube of the first heat exchanger and the controllable throttling device through the switching of the pipeline switching device and the controllable throttling device to perform defrosting operation;
(4) and when the temperature or the humidity of the heat exchange tube of the first heat exchanger reaches a defrosting ending set value, the conventional heating working condition is recovered through the switching of the pipeline switching device and the controllable throttling device.
The invention also provides an automatic defrosting method of the double-effect multi-working-condition self-defrosting heat pump air conditioner, which comprises the following steps:
(1) when the air conditioning device operates in a heating working condition, detecting the temperature of a refrigerant heat exchange tube of a first heat exchanger positioned outdoors;
(2) when the air conditioning device operates in a heating working condition, detecting the humidity outside a refrigerant heat exchange tube of a first heat exchanger;
(3) when the temperature and the humidity of the refrigerant heat exchange tube of the first heat exchanger reach a defrosting action set value, the air conditioning device enters a backflow defrosting working condition, and the refrigerant passing through the second heat exchanger directly enters the waste heat tracing tube and the refrigerant heat exchange tube of the first heat exchanger through the switching of the pipeline switching device and the controllable throttling device to perform defrosting operation;
(4) and when the temperature and the humidity of the refrigerant heat exchange tube of the first heat exchanger reach defrosting ending set values, the conventional heating working condition is recovered through the switching of the pipeline switching device and the controllable throttling device.
When the reflux defrosting condition is started, the fan attached to the first heat exchanger can enter a high-speed running state under the control of the control circuit, the fan motor of the fan runs at the rotating speed higher than 1000 revolutions per minute, and the frost attached to the refrigerant heat exchange tube of the first heat exchanger is quickly removed by means of high-speed airflow generated by the variable speed fan; and when the defrosting operation working condition is finished, the fan resumes the operation in the conventional rotating speed control mode.
The invention also provides another automatic defrosting method of the double-effect multi-working-condition self-defrosting heat pump air conditioner, which comprises the following steps:
(1) when the air conditioning device operates in a heating working condition, detecting the temperature of a refrigerant heat exchange tube of a first heat exchanger positioned outdoors;
(2) when the air conditioning device operates in a heating working condition, detecting the humidity outside a refrigerant heat exchange tube of a first heat exchanger;
(3) when the temperature and the humidity of the refrigerant heat exchange tube of the first heat exchanger reach a defrosting action set value, the air conditioning device enters a back flushing quick defrosting working condition, and a high-temperature and high-pressure refrigerant supplied by a compressor directly enters a waste heat tracing tube and the refrigerant heat exchange tube of the first heat exchanger through the switching of a four-way conversion valve group, a pipeline switching device and a controllable throttling device to perform automatic defrosting and deicing operation;
(4) and when the temperature and the humidity of the heat exchange tube of the first heat exchanger reach defrosting ending set values, the conventional heating working condition is recovered through the switching of the four-way conversion valve bank, the pipeline switching device and the controllable throttling device.
When the back flushing quick defrosting operation working condition is started, a fan attached to the first heat exchanger enters a high-speed operation state under the control of a control circuit of the fan, a fan motor of the fan runs at the rotating speed higher than 1000 revolutions per minute, and frost and ice attached to a refrigerant heat exchange tube of the first heat exchanger are quickly removed by means of high-speed airflow generated by a variable speed fan; and when the defrosting operation working condition is finished, the fan resumes the operation in the conventional rotating speed control mode.
Compared with the prior art, the invention has the advantages that:
1. the high-temperature refrigerant of the refrigerant circulating system is utilized for defrosting, so that the problem that the heating of the heat pump type air conditioner in winter only depends on auxiliary electric heating and electric defrosting is solved;
2. the automatic and quick defrosting and deicing functions can be realized without stopping and assisting an electric heating device, and the functions are timely, effective, automatic and convenient;
3. the first heat exchanger (namely the outdoor heat exchanger) with the double-pipe parallel structure is adopted, so that the heating effect of the heat pump type air conditioner can be improved, and the heat pump type air conditioner is efficient and energy-saving;
4. the heating performance of various large and medium-sized heat pump type air conditioners under the condition of lower temperature can be obviously improved by only adding a few parts without changing the overall structure and the main configuration of the existing air conditioning system, so that the energy is saved, and the economic benefit is good;
5. the four-way switching valve group, the pipeline switching device and the controllable throttling device are arranged and switched, so that the existing large and medium-sized heat pump type air conditioning device can realize various working conditions such as refrigeration, heating, temperature difference compensation, backflow defrosting, back flushing quick defrosting and the like, has multiple functions, is convenient to operate and manage, has a simple design structure, and fully saves one-time investment and daily operation and maintenance cost of users.
Drawings
FIG. 1 is a schematic view of the apparatus structure and piping connection of the present invention;
FIG. 2 is a block diagram of the electrical connections of the electrical control portion of the present invention;
FIG. 3 is a schematic diagram of the structure and piping connection of the piping switching device according to the embodiment of the present invention;
FIG. 4 is a schematic view of the structure and piping connection of an embodiment of the controllable throttle device of the present invention;
FIG. 5 is a schematic view of another embodiment of a controllable throttle device according to the present invention;
FIG. 6 is a schematic view of an equivalent structure and piping connection of an embodiment of the present invention;
FIG. 7 is a schematic view of an equivalent structure and piping connection of another embodiment of the present invention;
fig. 8 is an equivalent structure and piping connection diagram of yet another embodiment of the present invention.
Detailed Description
The invention is further elucidated with reference to the figures and embodiments.
In fig. 1, a refrigerant supply pipe a of a compressor 1 is connected with refrigerant heat exchange pipelines of a first heat exchanger 6 and a second heat exchanger 4 through a four-way conversion valve group 3, and a refrigerant return pipe b of the compressor is connected with the refrigerant heat exchange pipelines of the first heat exchanger and the second heat exchanger through a liquid return buffer device 2 and the four-way conversion valve group; a pipeline switching device 5 and a controllable throttling device 9 connected with the pipeline switching device are arranged on a refrigerant connecting pipeline between the first heat exchanger and the second heat exchanger.
The first heat exchanger is a double-tube heat exchanger, one of which is a refrigerant heat exchange pipeline 7, and the other is a waste heat tracing pipe 8, and the two pipes are arranged in parallel.
The h end and the t end of the refrigerant heat exchange tubes of the first heat exchanger and the second heat exchanger are respectively and correspondingly connected with the e end and the d end of the four-way conversion valve bank; the end g of the first heat exchanger refrigerant heat exchange tube is connected with the end s of the second heat exchanger refrigerant heat exchange tube through the end l and the end r of the pipeline switching device and a controllable throttling device connected with the end l and the end r; two ends j and i of the first heat exchanger waste heat tracing pipe are correspondingly connected with the k end and the m end of the pipeline switching device respectively.
The u end and the v end of the heat exchange pipe of the second heat exchanger are connected with a user pipe network (air conditioning water or air conditioning air).
The first heat exchanger is provided with a variable speed fan 12, the motor of which runs at a speed of more than 1000 rpm when the air conditioning unit is operating in defrost mode.
In fig. 2, the temperature monitoring device and the humidity detecting device are electrically connected to the fan control circuit and the valve control circuits of the four-way switching valve set, the pipeline switching device and the controllable throttling device, respectively, the fan control circuit is connected to the fan motor, and each valve control circuit is connected to the control circuit of each control valve.
In fig. 3, the pipeline switching device comprises control valves F11-F16, wherein one ends of the control valves F11 and F14 are connected in parallel to form an end r of the pipeline switching device and are connected with the other end s of the refrigerant heat exchange pipeline of the second heat exchanger; the other end of the control valve F11 and one end of the control valve F12 are connected in parallel to form an o end of the pipeline switching device and connected with one end q of the controllable throttling device; the other end of the control valve F12 and one end of the control valve F15 are connected in parallel to form an m end of the pipeline switching device and are connected with one end i of the first heat exchanger waste heat tracing pipe; one ends of the control valves F13 and F16 are connected in parallel to form the end I of the pipeline switching device and are connected with the other end g of the first heat exchanger refrigerant heat exchange pipe; the other ends of the control valves F13 and F15 are connected in parallel to form the n end of the pipeline switching device and are connected with the other end p of the controllable throttling device; the other ends of the control valves F14 and F16 are connected in parallel to form a k end of the pipeline switching device and are connected with the other end j of the first heat exchanger waste heat tracing pipe.
In fig. 4, the controllable throttling device adopts a structural form consisting of two groups of one-way controllable throttling units DJ1 and DJ2 which are connected in series in an opposite direction, two control valves f3 and f4 and a liquid collecting tank 10, wherein each one-way controllable throttling unit is formed by connecting one-way throttling expansion valve j1 (or j2) and one control valve f1 (or f2) in series.
Wherein, collection liquid jar is provided with a drain pipe and two intake pipes, and the end opening of drain pipe is located the lower part of collection liquid jar, and the end opening of intake pipe is located the upper portion of collection liquid jar, and the bottom of collection liquid jar sets up the fuel outlet valve, utilizes the difference of refrigerant and lubricating oil proportion, separates and discharges the lubricating oil of sneaking into in the refrigerant, improves the heat exchange efficiency of refrigerant.
One end of the one-way controllable throttling unit DJ1 and one end of the control valve f3 are connected in parallel to form a q end of the controllable throttling device and connected with an o end of the pipeline switching device; one end of the unidirectional controllable throttling unit DJ2 and one end of the control valve f4 are connected in parallel to form a p end of the controllable throttling device and connected with an n end of the pipeline switching device; the other ends of the unidirectional controllable throttling units DJ1 and DJ2 are connected in parallel and then are connected with a liquid outlet pipe of the liquid collecting tank; the other ends of the control valves f3 and f4 are respectively connected with two air inlet pipes of the liquid collecting tank.
The control valve is used for adjusting the flow of the refrigerant passing through the one-way throttle expansion valve; when one group of one-way controllable throttling units works, the control valve in the other group of one-way controllable throttling units is in a closed state, so that the function of two-way double control is achieved.
The purpose of setting up the collection liquid jar is that the refrigerant that comes out from the second heat exchanger carries out gas-liquid separation, prevents to supply liquid uneven, causes unstability to the evaporimeter operating mode, when whole device work in backward flow defrosting operating mode, will open for control valve f3 and f4 simultaneously, provides the route for the refrigerant directly gets into first heat exchanger.
In fig. 5, the controllable throttling device may also adopt a structural form consisting of two sets of one-way controllable throttling units DJ3 and DJ4 which are connected in parallel in an opposite direction, each one-way controllable throttling unit is formed by connecting one-way throttling expansion valve j3 or j4 and one control valve f5 or f6 in series, wherein, one end of the control valve f5 and one end of the one-way throttling expansion valve j4 are connected in parallel and then connected with the q end forming the controllable throttling device and the o end of the pipeline switching device; one end of the control valve f6 and the other end of the one-way throttle expansion valve j3 are connected in parallel and then connected with the p end which forms a controllable throttle device and the n end of the pipeline switching device.
Depending on the user's requirement for the minimum allowable outdoor temperature at which the entire apparatus is operated, one of the two controllable throttling devices shown in fig. 4 and 5 may be selected.
Example 1:
the system configuration shown in fig. 1, the electric control system shown in fig. 2, the pipeline switching device shown in fig. 3 and the controllable throttle device shown in fig. 5 are adopted.
(1) Normal refrigeration condition:
when the heat pump air conditioner works under a normal refrigeration working condition, the first heat exchanger serves as a condenser, the second heat exchanger serves as an evaporator, the control valves F1 and F4 in the four-way switching valve group are opened, the control valves F11, F15 and F16 in the pipeline switching device are opened, the control valve F6 in the controllable throttling device is opened, and the other control valves are closed.
The refrigerant passes through the end of the refrigerant supply pipe a of the compressor 1 → the control valve F4 → the h end of the first heat exchanger refrigerant heat exchange pipe 7 → the g end of the first heat exchanger refrigerant heat exchange pipe 7 → the control valve F16 → the j end of the first heat exchanger waste heat tracing pipe 8 → the i end of the first heat exchanger waste heat tracing pipe 8 → the control valve F15 → the p end of the controllable throttling device 9 → the control valve F6 → the one-way throttling expansion valve j4 → the q end of the controllable throttling device 9 → the control valve F11 → the s end of the second heat exchanger 4 refrigerant heat exchange pipe → the t end of the second heat exchanger 4 refrigerant heat exchange pipe → the control valve F1 → the liquid returning buffer device 2 → the end of the refrigerant return pipe b of the compressor 1.
In the process, the compressor sends the gaseous refrigerant into the first heat exchanger through the four-way conversion valve bank, the gaseous refrigerant exchanges heat with outdoor air under the action of air flow generated by the fan, the gaseous refrigerant is throttled and expanded through the controllable throttling device, the refrigerant is cooled and condensed into a liquid state, the liquid refrigerant enters the second heat exchanger and absorbs a large amount of heat contained in air conditioning water or air conditioning air, the liquid refrigerant is rapidly boiled and evaporated into a gaseous state, the gaseous refrigerant passes through the four-way conversion valve bank and enters the compressor again after being subjected to gas-liquid separation through the liquid return buffer device, and a refrigeration cycle is completed.
In the process, the refrigerant in the second heat exchanger continuously absorbs a large amount of heat contained in the air conditioning water or the air conditioning air, and then the heat is radiated to an external heat exchange medium (outdoor air for the air-cooled compressor unit) through the first heat exchanger, so that the purpose of taking the heat out of the room is achieved.
In the working condition, the refrigerant heat exchange tube and the waste heat tracing tube of the first heat exchanger are connected in series to form a whole, so that the surface area of the heat exchange tube of the condenser is increased, the heat exchange effect is improved, and the heat exchange efficiency is improved.
(2) Normal heating working condition:
when the heat pump air conditioner works under the normal heating working condition, the first heat exchanger serves as an evaporator, the second heat exchanger serves as a condenser, the control valves F2 and F3 in the four-way switching valve group are opened, the control valves F11 and F13 in the pipeline switching device are opened, the control valve F5 in the controllable throttling device is opened, and the rest control valves are closed.
The refrigerant flows from the end of the refrigerant supply pipe a of the compressor 1 → the control valve F2 → the t end of the refrigerant heat exchange tube of the second heat exchanger 4 → the s end of the refrigerant heat exchange tube of the second heat exchanger 4 → the control valve F11 → the q end of the controllable throttling device 9 → the control valve F5 → the one-way throttling expansion valve j3 → the p end of the controllable throttling device 9 → the control valve F13 → the g end of the refrigerant heat exchange tube 7 of the first heat exchanger → the h end of the refrigerant heat exchange tube 7 of the first heat exchanger → the control valve F3 → the liquid returning buffer device 2 → the b end of the refrigerant return pipe of the compressor 1.
In the above process, the high-pressure high-temperature refrigerant gas compressed by the compressor enters the second heat exchanger through the four-way conversion valve bank, releases heat to air conditioning water or air conditioning air to be cooled into high-pressure liquid, enters the controllable throttling device through the pipeline switching device to be throttled and expanded into low-pressure liquid, the liquid refrigerant enters the refrigerant pipe of the first heat exchanger to be evaporated, absorbs heat in an external heat exchange medium (air with outdoor environment temperature for the air-cooled compressor unit) in the evaporation process, is evaporated into low-pressure steam, and the low-pressure refrigerant steam enters the compressor through the four-way conversion valve bank and the liquid return buffer device to be compressed into high-pressure gas and continues to perform the next cycle.
In the process, the refrigerant in the first heat exchanger continuously absorbs external heat, then the heat is transferred to air conditioning water or air conditioning air through the second heat exchanger, and the heat is transmitted to the indoor through the air conditioning water or the air conditioning air, so that the aim of heating the indoor is fulfilled.
In the working condition, no flowing refrigerant exists in the waste heat tracing pipe of the first heat exchanger.
(3) Temperature difference compensation defrosting condition:
when the heat pump air conditioner works under the temperature difference compensation defrosting working condition, the first heat exchanger serves as an evaporator, the second heat exchanger serves as a condenser, the control valves F2 and F3 in the four-way conversion valve group are opened, the control valves F12, F13 and F14 in the pipeline switching device are opened, the control valve F5 in the controllable throttling device is opened, the other control valves are closed, and the equivalent structure and the pipeline connection relation are shown in fig. 6.
The refrigerant passes through the end of the refrigerant supply pipe a of the compressor 1 → the control valve F2 → the end t of the refrigerant heat exchange pipe of the second heat exchanger 4 → the end s of the refrigerant heat exchange pipe of the second heat exchanger 4 → the control valve F14 → the end j of the heat tracing pipe for the waste heat of the first heat exchanger 8 → the end i of the heat tracing pipe for the waste heat of the first heat exchanger 8 → the control valve F12 → the end q of the controllable throttling device → the control valve F5 → the one-way throttling expansion valve j3 → the end p of the controllable throttling device → the control valve F13 → the end g of the refrigerant heat exchange pipe 7 of the first heat exchanger → the end h of the refrigerant heat exchange pipe 7 of the first heat exchanger → the control valve F3 → the liquid returning buffer device 2 → the.
When a common large or medium-sized heat pump type air conditioner is used in winter, if the external environment temperature is too low, the temperature difference between the outdoor environment temperature and the pipe wall of the first heat exchanger (an evaporator in the heating operation working condition) is small, and the refrigerant can basically not absorb heat from the outside, the heat which is taken as a heat pump to enter an indoor pump is also little, and the heating effect is poor or basically has no heating effect. Therefore, the minimum outdoor use environment temperature of the common conventional heat pump type air conditioner is not lower than-5 ℃.
When the outdoor environment temperature is too low and heat supply is needed, the control valves F12, F13 and F14 in the pipeline switching device are opened, and the residual heat compensation passage is automatically opened. At the moment, high-pressure high-temperature refrigerant gas is compressed by the compressor and then enters the second heat exchanger (indoor) through the four-way conversion valve group, and is cooled into high-pressure liquid after heat is discharged. Because the indoor temperature is higher, the refrigerant passing through the second heat exchanger still has higher temperature (relative to the low outdoor temperature), the refrigerant liquid with higher temperature firstly enters the waste heat tracing pipe 8 of the first heat exchanger (outdoor) 6 through the control valve F12, the waste heat contained in the refrigerant liquid is conducted to the refrigerant heat exchange pipe 7 in the first heat exchanger through the metal radiating fins of the first heat exchanger, and then is throttled and expanded into low-pressure liquid through the controllable throttling device 9, and then enters the refrigerant heat exchange pipe 7 to be evaporated into low-pressure steam, and the heat in the air and the heat released by the waste heat tracing pipe conducted through the metal radiating fins are absorbed in the evaporation process. The low-pressure refrigerant vapor enters the compressor again through the four-way switching valve group and is compressed into high-pressure gas.
When the air conditioner operates in a heating working condition, the temperature and the humidity of a refrigerant heat exchange tube of a first heat exchanger positioned outdoors are detected, when the detected value of the temperature or the humidity reaches a defrosting action set value, the air conditioner enters a temperature difference compensation defrosting working condition, and the refrigerant passing through a second heat exchanger enters the refrigerant heat exchange tube of the first heat exchanger after passing through a waste heat tracing tube of the first heat exchanger and a controllable throttling device through the switching of a pipeline switching device and the controllable throttling device to perform temperature difference compensation and defrosting operation; and when the temperature or the humidity of the heat exchange tube of the first heat exchanger reaches a defrosting ending set value, the conventional heating working condition is recovered through the switching of the pipeline switching device and the controllable throttling device.
Because the refrigerant liquid with higher temperature firstly passes through the waste heat tracing pipe 8 of the outdoor heat exchanger 6, the waste heat tracing pipe 8 and the refrigerant heat exchange pipe 7 are arranged in parallel, and a heat transfer/heat exchange process exists between the waste heat tracing pipe 8 and the refrigerant heat exchange pipe 7, the output temperature of the second heat exchanger can be effectively improved and the frosting of the first heat exchanger can be dissolved by adopting the working conditions of the process.
Example 2:
the system configuration shown in fig. 1, the electric control system shown in fig. 2, the pipeline switching device shown in fig. 3 and the controllable throttle device shown in fig. 4 are adopted.
(1) And (3) a reflux defrosting working condition:
when the heat pump air conditioner works in a reflux defrosting condition, the first heat exchanger serves as an evaporator, the second heat exchanger serves as a condenser, the control valves F2 and F3 in the four-way switching valve group are opened, the control valves F11, F15 and F16 in the pipeline switching device are opened, the control valves F3 and F4 in the controllable throttling device are opened, the other control valves are closed, and the equivalent structure and the pipeline connection relation are shown in FIG. 7.
The refrigerant passes through the end of the refrigerant supply pipe a of the compressor 1 → the control valve F2 → the end of the refrigerant heat exchange pipe of the second heat exchanger 4 → the control valve F11 → the end of the controllable throttling device q → the control valve F3 → the liquid collecting tank 10 → the control valve F4 → the end of the controllable throttling device p → the control valve F15 → the end of the first heat exchanger waste heat tracing pipe 8 i → the end of the first heat exchanger waste heat tracing pipe 8 j → the control valve F16 → the end of the first heat exchanger refrigerant heat exchange pipe 7 g → the end of the first heat exchanger refrigerant heat exchange pipe 7 h → the control valve F3 → the liquid returning buffer device 2 → the end of the refrigerant return pipe b of the compressor 1.
In the above process, the refrigerant still having a higher temperature after passing through the second heat exchanger directly enters the waste heat tracing pipe 8 and the refrigerant heat exchange pipe 7 of the first heat exchanger through the passages of the control valve f3, the liquid collection tank 10 and the control valve f4 without throttling, and then returns to the compressor through the four-way conversion valve group and the liquid return buffer device.
The purpose of setting up the collection liquid jar is that carry out gas-liquid separation with the refrigerant that comes out from the second heat exchanger, prevents to cause the damage because of the liquid impact to the compressor.
When the air conditioner operates in a heating working condition, the temperature and the humidity of a refrigerant heat exchange tube of a first heat exchanger positioned outdoors are detected, when the temperature and the humidity detection values of the refrigerant heat exchange tube of the first heat exchanger reach defrosting action set values, the air conditioner enters a backflow defrosting working condition, and the refrigerant passing through a second heat exchanger directly enters a waste heat tracing tube and the refrigerant heat exchange tube of the first heat exchanger through the switching of a pipeline switching device and a controllable throttling device to perform backflow defrosting operation; and when the temperature and the humidity of the refrigerant heat exchange tube of the first heat exchanger reach defrosting ending set values, the conventional heating working condition is recovered through the switching of the pipeline switching device and the controllable throttling device.
When the back flow defrosting condition is started, the fan 12 attached to the first heat exchanger can enter a high-speed running state under the control of the control circuit, and the fan motor runs at the rotating speed higher than 1000 rpm. The ice frost attached to the refrigerant heat exchange tube of the first heat exchanger is quickly removed by means of high-speed airflow (compared with the air quantity and the air speed of a conventional fan) generated by a variable-speed fan; meanwhile, the heat exchange amount of air is increased by using the air flow which flows in an accelerating way, and more heat and energy are provided by using the heat generated by the friction of the high-speed air flow with the heat exchanger pipeline and the heat exchange sheet.
And when the defrosting operation working condition is finished, the fan resumes the operation in the conventional rotating speed control mode.
By adopting the working condition flow scheme, the frosting on the first heat exchanger pipeline can be melted and removed rapidly and effectively.
The logical relationship between the valve opening and closing and the pipeline connection relationship under the normal refrigeration and heating working conditions in the embodiment are the same as those in the embodiment 1, and are not repeated here.
Example 3:
the system configuration shown in fig. 1, the electric control system shown in fig. 2, the pipeline switching device shown in fig. 3 and the controllable throttling device shown in fig. 4 or fig. 5 are adopted.
(1) The working condition of back flushing and quick box removal is as follows:
when the heat pump air conditioner works in a backflushing quick defrosting working condition, control valves F1 and F4 in the four-way switching valve group are opened, control valves F11, F15 and F16 in the pipeline switching device are opened, control valves F3 and F4 (the controllable throttling device adopts the structural form of FIG. 5) or F6 (the controllable throttling device adopts the structural form of FIG. 4) in the controllable throttling device are opened, the rest control valves are closed, and the equivalent structure and the pipeline connection relation are shown in FIG. 8.
The refrigerant is guided to the end of the refrigerant supply pipe a of the compressor 1 → the control valve F4 → the first heat exchanger refrigerant heat exchange pipe 7 → the control valve F16 → the first heat exchanger waste heat tracing pipe 8 → the control valve F15 → the controlled throttling device 9 → the control valve F11 → the second heat exchanger 4 refrigerant heat exchange pipe → the control valve F1 → the liquid returning buffer device 2 → the end of the refrigerant returning pipe b of the compressor 1.
When the air conditioner runs in a heating working condition, the temperature and the humidity of a refrigerant heat exchange tube of a first heat exchanger positioned outdoors are detected, when the temperature and humidity detection values reach defrosting action set values, the air conditioner enters a back flushing quick defrosting working condition, and high-temperature and high-pressure refrigerant supplied by a compressor directly enters a waste heat tracing tube and a refrigerant heat exchange tube of the first heat exchanger through the switching of a four-way conversion valve bank, a pipeline switching device and a controllable throttling device, so that the refrigerant heat exchange tube and the waste heat tracing tube are quickly heated, and frost or ice attached to the surface of the refrigerant heat exchange tube and the waste heat tracing tube are quickly burst and melted. Meanwhile, the fan attached to the first heat exchanger enters a high-speed running state under the control of the control circuit, the fan motor runs at the rotating speed higher than 1000 rpm, and frost and ice attached to the refrigerant heat exchange tube of the first heat exchanger are quickly removed by means of high-speed airflow generated by the variable-speed fan.
When the temperature and the humidity of the heat exchange tube of the first heat exchanger reach defrosting ending set values, the conventional heating working condition is recovered through the switching of the four-way conversion valve bank, the pipeline switching device and the controllable throttling device; meanwhile, the fan resumes the normal speed control mode.
Because whole air conditioning equipment is equivalent to work under the anti-heating (refrigeration) operating mode in fact in this operating mode, so the operating time of this operating mode should not be the overlength to avoid influencing the output temperature of second heat exchanger.
The logical relationship between the valve opening and closing and the pipeline connection relationship under the normal refrigeration and heating working conditions in the embodiment are the same as those in the embodiment 1, and are not repeated here.
The invention utilizes the high-temperature refrigerant of the refrigerant circulating system to defrost, can obviously improve the heating performance of various large and medium-sized heat pump type air conditioners under the condition of lower temperature, realizes the functions of automatic quick defrosting and deicing, ensures that the conventional large and medium-sized heat pump type air conditioners can realize various working conditions of refrigeration, heating, temperature difference compensation, backflow defrosting, back flushing quick defrosting and the like, has multiple functions, one machine and multiple functions, is convenient to operate and manage, has simple design structure, fully saves one-time investment and daily operation and maintenance cost of users, saves energy and has good economic benefit.
The invention can be widely used for various large and medium-sized compression heat pump air-conditioning units and can also be used for the reconstruction of household unit type cooling and heating air conditioners. Can be widely used for central heating and cooling air-conditioning systems in various markets, office buildings, hospitals, hotels and residential districts.
Claims (10)
1. The utility model provides a double-effect multiplex condition is from defrosting formula heat pump air conditioner, includes compressor, four-way conversion valves, second heat exchanger, liquid buffer and the first heat exchanger that has the fan that connects gradually through the refrigerant pipeline, and wherein the refrigerant delivery pipe of compressor is through four-way conversion valves and the refrigerant heat exchange tube hookup of first heat exchanger and second heat exchanger, and its refrigerant back flow is through liquid buffer and the refrigerant heat exchange tube hookup of four-way conversion valves and first heat exchanger and second heat exchanger, characterized by:
a waste heat tracing pipe is arranged on the first heat exchanger;
a refrigerant heat exchange tube of the first heat exchanger is provided with a temperature monitoring device and a humidity detection device;
a pipeline switching device and a controllable throttling device connected with the pipeline switching device are arranged on a refrigerant connecting pipe between the first heat exchanger and the second heat exchanger; wherein,
one end of the refrigerant heat exchange tube of the first heat exchanger and one end of the refrigerant heat exchange tube of the second heat exchanger are respectively connected with one end of the four-way conversion valve bank;
the other end of the first heat exchanger refrigerant heat exchange tube is connected with the other end of the second heat exchanger refrigerant heat exchange tube through the pipeline switching device and the controllable throttling device;
two ends of the first heat exchanger waste heat tracing pipe are connected with the pipeline switching device;
the temperature monitoring device and the humidity detection device are electrically connected with the four-way conversion valve group, the fan, the pipeline switching device and the electric control part of the controllable throttling device.
2. The dual effect multi-operation self-defrosting heat pump air conditioner according to claim 1, wherein the pipe switching device comprises control valves F11-F16, wherein,
one ends of the control valves F11 and F14 are connected in parallel to form an r end of the pipeline switching device and are connected with the other end of the refrigerant heat exchange tube of the second heat exchanger;
the other end of the control valve F11 and one end of the control valve F12 are connected in parallel to form an o end of the pipeline switching device and connected with one end of the controllable throttling device;
the other end of the control valve F12 and one end of the control valve F15 are connected in parallel to form an m end of the pipeline switching device and are connected with one end of the first heat exchanger waste heat tracing pipe;
one ends of the control valves F13 and F16 are connected in parallel to form the end I of the pipeline switching device and are connected with the other end of the first heat exchanger refrigerant heat exchange pipe;
the other ends of the control valves F13 and F15 are connected in parallel to form the n end of the pipeline switching device and are connected with the other end of the controllable throttling device;
the other ends of the control valves F14 and F16 are connected in parallel to form a k end of the pipeline switching device and are connected with the other end of the first heat exchanger waste heat tracing pipe.
3. The double effect multiple working condition self defrosting heat pump air conditioner according to claim 1 or 2 wherein the controllable throttling device comprises two sets of one way controllable throttling unit DJ1, DJ2, two control valves f3, f4 and liquid collecting tank connected in series in reverse direction, each one way controllable throttling unit is composed of one way throttling expansion valve j1 or j2 and one control valve f1 or f2 connected in series, wherein,
the liquid collecting tank is provided with a liquid outlet pipe and two air inlet pipes, the tail end opening of the liquid outlet pipe is positioned at the lower part of the liquid collecting tank, the tail end opening of the air inlet pipe is positioned at the upper part of the liquid collecting tank, and the bottom of the liquid collecting tank is provided with an oil drain valve;
one end of the one-way controllable throttling unit DJ1 and one end of the control valve f3 are connected in parallel to form a q end of the controllable throttling device and connected with an o end of the pipeline switching device;
one end of the unidirectional controllable throttling unit DJ2 and one end of the control valve f4 are connected in parallel to form a p end of the controllable throttling device and connected with an n end of the pipeline switching device;
the other ends of the unidirectional controllable throttling units DJ1 and DJ2 are connected in parallel and then are connected with a liquid outlet pipe of the liquid collecting tank;
the other ends of the control valves f3 and f4 are respectively correspondingly connected with two air inlet pipes of the liquid collecting tank.
4. The double effect multiple working condition self defrosting heat pump air conditioner according to claim 1 or 2 wherein the controllable throttling device comprises two sets of one way controllable throttling unit DJ3 and DJ4 connected in reverse parallel, each one way controllable throttling unit is composed of one way throttling expansion valve j3 or j4 and one control valve f5 or f6 connected in series, wherein,
one end of a control valve f5 and one end of a one-way throttle expansion valve j4 are connected in parallel and then connected with a q end forming a controllable throttle device and an o end of a pipeline switching device;
one end of the control valve f6 and the other end of the one-way throttle expansion valve j3 are connected in parallel and then connected with the p end which forms a controllable throttle device and the n end of the pipeline switching device.
5. The dual effect multi operating mode self defrosting heat pump air conditioner according to claim 1 wherein the fan associated with the first heat exchanger is a variable speed fan and the fan motor operates at a speed greater than 1000 rpm when the air conditioner is operating in the defrost mode.
6. The automatic defrosting method of the double-effect multi-working condition self-defrosting heat pump air conditioner as claimed in claim 1, comprising the following steps:
(1) when the air conditioning device operates in a heating working condition, detecting the temperature of a refrigerant heat exchange tube of a first heat exchanger positioned outdoors;
(2) when the air conditioning device operates in a heating working condition, detecting the humidity outside a refrigerant heat exchange tube of a first heat exchanger;
(3) when the temperature or the humidity of the refrigerant heat exchange tube of the first heat exchanger reaches a defrosting action set value, the air conditioning device enters a temperature difference compensation defrosting working condition, and the refrigerant passing through the second heat exchanger enters the refrigerant heat exchange tube of the first heat exchanger after passing through the waste heat tracing tube of the first heat exchanger and the controllable throttling device through the switching of the pipeline switching device and the controllable throttling device to perform defrosting operation;
(4) and when the temperature or the humidity of the heat exchange tube of the first heat exchanger reaches a defrosting ending set value, the conventional heating working condition is recovered through the switching of the pipeline switching device and the controllable throttling device.
7. The automatic defrosting method of the double-effect multi-working condition self-defrosting heat pump air conditioner as claimed in claim 1, comprising the following steps:
(1) when the air conditioning device operates in a heating working condition, detecting the temperature of a refrigerant heat exchange tube of a first heat exchanger positioned outdoors;
(2) when the air conditioning device operates in a heating working condition, detecting the humidity outside a refrigerant heat exchange tube of a first heat exchanger;
(3) when the temperature and the humidity of the refrigerant heat exchange tube of the first heat exchanger reach a defrosting action set value, the air conditioning device enters a backflow defrosting working condition, and the refrigerant passing through the second heat exchanger directly enters the waste heat tracing tube and the refrigerant heat exchange tube of the first heat exchanger through the switching of the pipeline switching device and the controllable throttling device to perform defrosting operation;
(4) and when the temperature and the humidity of the refrigerant heat exchange tube of the first heat exchanger reach defrosting ending set values, the conventional heating working condition is recovered through the switching of the pipeline switching device and the controllable throttling device.
8. The automatic defrosting method of a double effect multiple working condition self-defrosting heat pump air conditioner according to claim 7, characterized in that at the beginning of the reflux defrosting working condition, the fan attached to the first heat exchanger can be put into a high speed operation state under the control of the control circuit, the fan motor thereof is operated at a rotating speed higher than 1000 rpm, and the frost attached to the refrigerant heat exchange tube of the first heat exchanger is rapidly removed by means of the high speed airflow generated by the variable speed fan; and when the defrosting operation working condition is finished, the fan resumes the operation in the conventional rotating speed control mode.
9. The automatic defrosting method of the double-effect multi-working condition self-defrosting heat pump air conditioner as claimed in claim 1, comprising the following steps:
(1) when the air conditioning device operates in a heating working condition, detecting the temperature of a refrigerant heat exchange tube of a first heat exchanger positioned outdoors;
(2) when the air conditioning device operates in a heating working condition, detecting the humidity outside a refrigerant heat exchange tube of a first heat exchanger;
(3) when the temperature and the humidity of the refrigerant heat exchange tube of the first heat exchanger reach a defrosting action set value, the air conditioning device enters a back flushing quick defrosting working condition, and a high-temperature and high-pressure refrigerant supplied by a compressor directly enters a waste heat tracing tube and the refrigerant heat exchange tube of the first heat exchanger through the switching of a four-way conversion valve group, a pipeline switching device and a controllable throttling device to perform automatic defrosting and deicing operation;
(4) and when the temperature and the humidity of the heat exchange tube of the first heat exchanger reach defrosting ending set values, the conventional heating working condition is recovered through the switching of the four-way conversion valve bank, the pipeline switching device and the controllable throttling device.
10. The automatic defrosting method of the double effect multi-working condition self-defrosting heat pump air conditioner according to claim 9, characterized in that at the beginning of the back flushing fast defrosting operation, the fan attached to the first heat exchanger enters a high speed operation state under the control of the control circuit, the fan motor thereof operates at a rotation speed higher than 1000 rpm, and the frost and ice attached to the refrigerant heat exchange tube of the first heat exchanger are removed fast by means of the high speed airflow generated by the variable speed fan; and when the defrosting operation working condition is finished, the fan resumes the operation in the conventional rotating speed control mode.
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| CN 03143232 CN1485588B (en) | 2003-07-29 | 2003-07-29 | Dual-purpose multiple operating mode self-defrosting type heat pump air-conditioner and automatic defrosting process thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101187517B (en) * | 2006-11-17 | 2010-05-12 | 海尔集团公司 | Air-conditioner defrosting method |
| CN101382365B (en) * | 2005-08-05 | 2010-12-15 | 松下电器产业株式会社 | Air conditioner |
| CN101694314B (en) * | 2009-10-23 | 2012-07-25 | 清华大学 | Air handling device with natural heating and humidity control |
| CN104236004A (en) * | 2013-06-19 | 2014-12-24 | 广东美的制冷设备有限公司 | Defrosting control method and device for heat pump system |
| CN107728673A (en) * | 2017-11-23 | 2018-02-23 | 深圳市共享能源技术有限公司 | Temperature control regulating system |
| CN108036556A (en) * | 2017-12-22 | 2018-05-15 | 珠海恩盛能源科技有限公司 | One kind defrosting and the relevant heat pump control mode of ambient temperature and humidity |
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| CN109556234A (en) * | 2018-10-22 | 2019-04-02 | 珠海格力电器股份有限公司 | Defrosting control method, device, equipment and medium |
| CN110726206A (en) * | 2019-10-10 | 2020-01-24 | 珠海格力电器股份有限公司 | Drying device and defrosting control method thereof |
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| FR2743408B1 (en) * | 1996-01-08 | 1998-02-13 | Martin Jean Antoine | AIR CONDITIONING PROCESS FOR COLLECTIVE HOUSING BUILDINGS |
| CN2290823Y (en) * | 1997-03-03 | 1998-09-09 | 刘仕英 | Automatic defrost heat pump |
| CN1128316C (en) * | 1999-07-05 | 2003-11-19 | 清华同方股份有限公司 | Cold and heat accumulation type air conditioner with heat pump |
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| CN1133046C (en) * | 2000-09-21 | 2003-12-31 | 丛旭日 | Bipolar heat pump type air conditioner |
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| CN101187517B (en) * | 2006-11-17 | 2010-05-12 | 海尔集团公司 | Air-conditioner defrosting method |
| CN101694314B (en) * | 2009-10-23 | 2012-07-25 | 清华大学 | Air handling device with natural heating and humidity control |
| CN104236004A (en) * | 2013-06-19 | 2014-12-24 | 广东美的制冷设备有限公司 | Defrosting control method and device for heat pump system |
| CN104236004B (en) * | 2013-06-19 | 2017-02-15 | 广东美的制冷设备有限公司 | Defrosting control method and device for heat pump system |
| CN107728673A (en) * | 2017-11-23 | 2018-02-23 | 深圳市共享能源技术有限公司 | Temperature control regulating system |
| CN108036556A (en) * | 2017-12-22 | 2018-05-15 | 珠海恩盛能源科技有限公司 | One kind defrosting and the relevant heat pump control mode of ambient temperature and humidity |
| CN108826799A (en) * | 2018-07-24 | 2018-11-16 | 广州市热道节能科技有限公司 | A kind of interactive heat pump drying and dehumidification system of heat source each other |
| CN109556234A (en) * | 2018-10-22 | 2019-04-02 | 珠海格力电器股份有限公司 | Defrosting control method, device, equipment and medium |
| CN113661364A (en) * | 2019-04-18 | 2021-11-16 | 三菱电机株式会社 | Control device for air conditioner, outdoor unit, relay unit, heat source unit, and air conditioner |
| CN110726206A (en) * | 2019-10-10 | 2020-01-24 | 珠海格力电器股份有限公司 | Drying device and defrosting control method thereof |
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| CN115038916B (en) * | 2020-02-03 | 2023-06-16 | Lg电子株式会社 | Air conditioner |
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