CN112629084A - Defrosting operation determination method and defrosting system - Google Patents
Defrosting operation determination method and defrosting system Download PDFInfo
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- CN112629084A CN112629084A CN202011530694.1A CN202011530694A CN112629084A CN 112629084 A CN112629084 A CN 112629084A CN 202011530694 A CN202011530694 A CN 202011530694A CN 112629084 A CN112629084 A CN 112629084A
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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
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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
- 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
- F25B39/00—Evaporators; Condensers
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
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- Heat-Pump Type And Storage Water Heaters (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention relates to the technical field of defrosting, and particularly discloses a defrosting operation judgment method which is characterized by comprising the following judgment steps: s1, detecting the change of the outdoor environment temperature Ta in real time; s2, detecting the change of the pressure of the heat pump pipeline of the compressor and the difference value between the ambient temperature and the temperature of the fins in real time through a system pressure sensor; and judging the defrosting effect in the defrosting operation. By the defrosting operation judging method, the frosting thickness of the heat pump outdoor tube fin type heat exchanger can be accurately detected to effectively defrost, so that the problems that the defrosting is not clean, and the defrosting wastes heat when no frost exists are solved; meanwhile, by combining the defrosting operation judgment method, the defrosting system can quickly defrost under the condition of optimizing the process.
Description
Technical Field
The invention relates to the technical field of heat pump defrosting, in particular to a defrosting operation judgment method and a defrosting system.
Background
The heat pump defrosting technology has diversified solutions. In order to solve the problem that an outdoor heat exchanger can improve defrosting effect during heating operation and ensure that the outdoor heat exchanger does not have any attenuation influence on cooling operation, the patent document discloses a defrosting device, a heat pump machine and a defrosting method of the defrosting device (CN 103954087B). The patent document divides the outdoor heat exchanger into a first functional part and a second functional part by performing segmented treatment on the outdoor heat exchanger, wherein the first functional part (preferably the upper part) of the outdoor heat exchanger can perform sensible heat releasing operation on passing fluid, and the second functional part (preferably the lower part) of the outdoor heat exchanger can perform supercooling heat releasing operation on passing fluid (preferably refrigerant), so that when a control valve is in a first state, a compressor is started, refrigerant steam output by a fluid outlet of the compressor sequentially passes through the first functional part and the second functional part, sensible heat releasing operation is performed, and, Thereby the supercooling is exothermic to dispel the heat, after the lower refrigerant of the temperature that has given off heat gets into indoor heat exchanger, can absorb the heat in the indoor heat exchanger comparatively high-efficiently, thereby can reach better refrigeration effect indoor, outdoor heat exchanger after having guaranteed from this to the segmentation does not have any decay influence to the refrigeration operation, and simultaneously, when heating the operation, the second functional part can carry out the operation of heat release of condensation, the first functional part can carry out the evaporation heat absorption operation, the heat of second functional part release can satisfy outdoor heat exchanger and improve the effect of defrosting when heating the operation.
In the prior art, a defrosting determination method (CN106052021B) is also disclosed, which aims to solve the problem that the specific temperature or temperature difference determination value changes depending on the ambient temperature, humidity, and heat pump operating state, so that erroneous determination is easily caused, and the situation of erroneous defrosting is caused. The fluctuation interference caused by the change of the working state of the system is eliminated through the temperature difference starting point selecting step, the fact that the temperature difference starting point is not selected in a wave trough or a wave crest of a temperature difference fluctuation curve along with time is guaranteed, whether an air conditioning system frosts or not and whether frosting begins or not are judged through the temperature difference change rate, the interference caused by fluctuation caused by the change of the working state in the air conditioning running process is filtered, and whether defrosting is required or not can be judged more accurately.
However, the drawbacks of the above existing solutions at least include:
(1) the frosted thickness of the outdoor heat exchanger and more effective defrosting cannot be accurately detected, so that the defrosting is not clean; defrosting is also carried out when frost is absent, so that the problem of heat waste is caused;
(2) the defrosting water collector can not be guaranteed to collect the water that flows down and can not freeze after outdoor ambient temperature is less than 0 ℃, if the water that the water collector collects freezes, the ice sheet can constantly grow under ambient temperature is less than 0 ℃ to block partial outdoor heat exchanger heat transfer, lead to the heating effect to worsen.
Disclosure of Invention
In order to overcome the above-mentioned drawbacks, the present invention provides a defrosting operation determining method and a defrosting system.
The technical scheme provided by the invention is as follows:
the defrosting operation judgment method comprises the following judgment steps:
s1, detecting the change of outdoor environment temperature Ta in real time, preliminarily judging that the outdoor tube fin type heat exchanger is likely to frost when Ta is less than 12 ℃, and entering next judgment if frosting is likely to occur, wherein if frosting is not likely to occur, the defrosting system continues to operate, and related actions of defrosting are not performed; after the defrosting system meets the condition of primary frost formation, the judgment of step S2 is started;
s2, detecting the change of the pressure of the heat pump pipeline of the compressor and the difference value between the environmental temperature and the temperature of the fins of the finned tube heat exchanger in real time through a system pressure sensor;
pressure change PLx ═ PLn-PLn + 1;
tae ═ Ta (ambient temperature) -Te (tube-fin heat exchanger fin temperature);
wherein, the relation between the change situation of pressure and the difference between ambient temperature and the finned tube heat exchanger fin temperature includes:
(1) when PLx is less than or equal to 0.10 and Tae is less than or equal to 10, the fins of the tube fin type heat exchanger may not frost;
(2) when PLx is more than 0.10 and PLx is less than or equal to 0.30, Tae is more than or equal to 10 and Tae is less than or equal to 12, the fins of the tube-fin heat exchanger can be frosted, but the frosting speed is slower;
(3) when PLx is more than 0.30 and Tae is more than 12, the finned tube heat exchanger has frosting and frosting speed is high.
Preferably, the step S3 and S3 are further included, and the determining of the frosting condition of the tube fin type heat exchanger fin through the accumulated calculation of the step S1 and the step S2 comprises the following steps:
(1) the fins of the tube fin type heat exchanger may not be frosted at first, and after the operation, the repeated calculation result is unchanged, so that the fins of the tube fin type heat exchanger can be obtained to be frosted;
(2) the method comprises the following steps that firstly, fins of the tube fin type heat exchanger may not be frosted at first but run, the possibility that the fins of the tube fin type heat exchanger are frosted is repeatedly calculated, and the fins are judged to be slightly frosted;
(3) the fins of the tube fin type heat exchanger are frosted, but the frosting speed is slow;
(4) the fins of the tube fin type heat exchanger are frosted, and the frosting speed is high;
s4, judging the defrosting effect in the defrosting operation:
s41, detecting the change value of the temperature at the bottom of the heat pump outdoor tube fin type heat exchanger in real time:
TEx-TE 0 (pre-defrost temperature) -TEn (real-time temperature detection).
When the TEx is more than 35 ℃, the defrosting effect is better;
when the temperature TEx is more than or equal to 20 ℃ and less than 35 ℃, the defrosting effect is general;
when the TEx is less than 20 ℃, the defrosting effect is poor;
s42, detecting the change of the pressure of the refrigerant of the heat pump pipeline in real time;
PHx PH0 (pre-defrost pressure) -PHn (real-time pressure detection).
When PHx is less than 28bar, the defrosting effect is better;
when PHx is more than or equal to 28bar and TEx is less than 31bar, the defrosting effect is general;
when PHx is more than or equal to 31bar, the defrosting effect is poor;
s43, calculating the defrosting consumption time of the defrosting system in real time:
when the Time02 is less than 4 minutes, the defrosting effect is better;
when the Time02 is more than or equal to 4 and the Time02 is less than 7 minutes, the defrosting effect is general;
when the Time02 is more than or equal to 7 minutes, the defrosting effect is poor.
Preferably, in step S1, the process proceeds to step S2 after the defrosting system satisfies the preliminary frost condition Time01 is 30 minutes.
Preferably, in step S2, the system pressure sensor detects the change of the heat pump pipeline pressure and the difference between the ambient temperature and the fin temperature of the tube fin heat exchanger in real time every two minutes.
Preferably, in step S3, the fin frosting is determined by the accumulation calculation of steps S1 and S2 as follows:
(1) the fins of the tube-fin heat exchanger may not frost at first, and after the running Time01 is 30 minutes, the repeated calculation results are unchanged, so that the fins of the tube-fin heat exchanger can be obtained to be free of frost;
(2) after the fins of the tube-fin heat exchanger may not frost at first but the running Time01 is 30 minutes, the possibility of frosting of the tube-fin heat exchanger fins is repeatedly calculated, and the fins of the tube-fin heat exchanger are judged to be slightly frosted.
Preferably, in step S41, the temperature change value of the bottom of the heat pump outdoor tube fin type heat exchanger is detected every 10 seconds;
in step S42, the change value of the heat pump pipeline refrigerant pressure is detected in real time every 10 seconds.
Preferably, in steps S41, S42, and S43: when any two items belong to better defrosting effect, the defrosting effect of the defrosting system is judged to be better; when any two items belong to general defrosting effects, judging that the defrosting effect of the defrosting system is general; and when any two items belong to poor defrosting effects, judging that the defrosting effect of the defrosting system is poor.
Preferably, the defrosting system comprises one or more compressors connected in parallel and a defrosting circuit for refrigerant, wherein a pressure sensor is arranged on the defrosting circuit, and the defrosting circuit comprises a tube fin type heat exchanger, a four-way reversing valve, a water side heat exchanger connected to a heat source and a water pan for connecting defrosting water discharge;
preferably, two pipe orifices of the four-way reversing valve are respectively connected with an air outlet of the compressor and an air inlet of the water-side heat exchanger, and the other two pipe orifices of the four-way reversing valve are respectively connected with an air inlet of the compressor and an air outlet of the tube fin type heat exchanger;
the four connectors of a plate heat exchanger are respectively connected with the middle air supplement port of the compressor, the first throttle valve, the filter and the outlet branch pipe of the water side heat exchanger;
the defrosting branch of the tube fin type heat exchanger comprises a second throttling valve and a defrosting capillary tube which are connected, a first check valve is arranged between the second throttling valve and the filter, a second check valve is arranged between the second throttling valve and the water side heat exchanger, and a third check valve is arranged between the defrosting capillary tube and the tube fin type heat exchanger.
Preferably, the tube fin type heat exchanger is provided with a temperature probe and an outdoor temperature probe, and the heat source of the water side heat exchanger is air.
Preferably, the water receiving tray comprises a horizontally arranged spacing flat plate, end plates are arranged at two ends of the spacing flat plate, a first fin mounting inclined plate and a second fin mounting inclined plate which are bent obliquely downwards are respectively arranged at two sides of the spacing flat plate, a first water tank straight side plate which is bent vertically downwards is arranged at one side of the first fin mounting inclined plate, and the first water tank straight side plate is perpendicular to the spacing flat plate;
a first water tank inclined bottom plate which is bent upwards in an inclined mode is arranged on one side of the first water tank straight side plate, the first water tank inclined bottom plate and the first water tank straight side plate are perpendicular to each other, the first water tank inclined bottom plate and the spacing flat plate are not parallel to each other, and an included angle formed by the first water tank inclined bottom plate and the spacing flat plate in a downward inclined mode is formed; one end of the first water tank inclined bottom plate is provided with a first drainage pipe;
one side of the first water tank inclined bottom plate is provided with a first water tank inclined side plate which is bent upwards in an inclined manner, one side of the second fin installation inclined plate is provided with a second water tank straight side plate which is bent downwards in a vertical manner, and the second water tank straight side plate is perpendicular to the spacing flat plate; one side of the second water tank straight side plate is provided with a second water tank inclined bottom plate bent in an inclined upward direction, the second water tank inclined bottom plate is perpendicular to the second water tank straight side plate, the second water tank inclined bottom plate is not parallel to the spacing flat plate, the second water tank inclined bottom plate and the spacing flat plate are provided with an included angle inclined downward, one end of the second water tank inclined bottom plate is provided with a second drain pipe, and one side of the second water tank inclined bottom plate is provided with a second water tank inclined side plate bent in an inclined upward direction.
Compared with the prior art, the invention has the beneficial effects that:
by the defrosting operation judging method, the frosting thickness of the heat pump outdoor tube fin type heat exchanger can be accurately detected to effectively defrost, so that the problems that the defrosting is not clean, and the defrosting wastes heat when no frost exists are solved; meanwhile, by combining the defrosting operation judgment method, the defrosting system can quickly defrost under the condition of optimizing the process.
The defrosting system can accelerate the speed of the defrosting process by adjusting an electronic expansion valve of the refrigerating system and the like, and meanwhile, the defrosting work of the system cannot be influenced when any one of the outdoor temperature probe, the pressure sensor and the temperature probe of the tube-fin heat exchanger is in a problem. Through the optimization channel design of defrosting water collector, can discharge the defrosting water fast, the water collector of outdoor heat exchanger can collect the defrosting water fast, guarantees that the defrosting water can flow away fast to it leads to the heat exchanger to heat the effect and worsens to have avoided the defrosting water to freeze the problem at the water collector.
Drawings
FIG. 1 is a schematic view showing the structure and operation of the defrosting operation determining method and defrosting system according to the present invention;
FIG. 2 is a schematic view of the structure of the water pan of the present invention;
FIG. 3 is an enlarged view of the water pan of the present invention;
FIG. 4 is a schematic view of the installation structure between the water pan and the fins of the tube fin type heat exchanger.
In the figure: 1. the third check valve 2, the pressure sensor 3, the compressor 4, the temperature probe 5, the outdoor temperature probe 6, the tube fin type heat exchanger 7, the four-way reversing valve 8, the water side heat exchanger 9, the water receiving disc 10, the plate type heat exchanger 11, the first throttle valve 12, the filter 13, the second throttle valve 14, the defrosting capillary tube 15, the first check valve 16, the second check valve 17, the partition plate 18, the first fin mounting inclined plate 19, the second fin mounting inclined plate 20, the first water tank straight side plate 21, the first water tank inclined bottom plate 22, the first water discharge pipe 23, the first water tank inclined side plate 24, the second water tank straight side plate 25, the second water tank inclined bottom plate 26, the second water discharge pipe 27, the second water tank inclined side plate 28, the end plate 29 and the fins.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
As shown in fig. 1, the defrosting operation determining method includes the following determining steps:
step S1, detecting the change of outdoor environment temperature Ta in real time, when Ta is less than 12 ℃, preliminarily judging that the outdoor tube fin type heat exchanger 6 is likely to frost, if frosting is likely to occur, entering the next judgment, if frosting is not likely to occur, continuously operating the defrosting system, and not performing related actions of defrosting; after the defrosting system meets the condition of primary frost formation, the judgment of step S2 is started;
step S2, detecting the change of the pressure of the heat pump pipeline of the compressor 3 and the difference value between the environmental temperature and the temperature of the fins of the tube fin type heat exchanger 6 in real time through the system pressure sensor 2;
pressure change PLx ═ PLn-PLn + 1;
tae ═ Ta (ambient temperature) -Te (fin temperature of tube-fin heat exchanger 6);
wherein, the relation between the change situation of pressure and the difference between ambient temperature and the fin temperature of the tube fin type heat exchanger 6 includes:
(1) when PLx is less than or equal to 0.10 and Tae is less than or equal to 10, the fins of the tube-fin heat exchanger 6 may not frost;
(2) when PLx is more than 0.10, PLx is less than or equal to 0.30, Tae is more than or equal to 10, and Tae is less than or equal to 12, the fins of the tube-fin heat exchanger 6 may have frost, but the frosting speed is slower;
(3) when PLx is more than 0.30 and Tae is more than 12, the fins of the tube fin type heat exchanger 6 have frost and the frost formation speed is very high.
The step S3 of determining the fin frosting condition of the tube-fin heat exchanger 6 through the accumulation calculation of the steps S1 and S2 includes:
(1) the fins of the tube fin type heat exchanger 6 may not be frosted at first, and after the operation, the repeated calculation result is unchanged, so that the fins can be obtained to be frosted-free;
(2) the fins of the tube fin type heat exchanger 6 may not be frosted at first but are operated, the possibility of frosting of the fins is repeatedly calculated, and the fins are judged to be slightly frosted;
(3) the fins of the tube fin type heat exchanger 6 are frosted, but the frosting speed is slow;
(4) the fins of the tube fin type heat exchanger 6 are frosted, and the frosting speed is high;
step S4, defrosting effect determination during defrosting operation:
step S41, detecting a variation value of the temperature at the bottom of the heat pump outdoor tube fin heat exchanger 6 in real time:
TEx-TE 0 (pre-defrost temperature) -TEn (real-time temperature detection).
When the TEx is more than 35 ℃, the defrosting effect is better;
when the temperature TEx is more than or equal to 20 ℃ and less than 35 ℃, the defrosting effect is general;
when the TEx is less than 20 ℃, the defrosting effect is poor;
step S42, detecting the change of the pressure of the refrigerant of the heat pump pipeline in real time;
PHx PH0 (pre-defrost pressure) -PHn (real-time pressure detection).
When PHx is less than 28bar, the defrosting effect is better;
when PHx is more than or equal to 28bar and TEx is less than 31bar, the defrosting effect is general;
when PHx is more than or equal to 31bar, the defrosting effect is poor;
step S43, calculating the defrosting consumption time of the defrosting system in real time:
when the Time02 is less than 4 minutes, the defrosting effect is better;
when the Time02 is more than or equal to 4 and the Time02 is less than 7 minutes, the defrosting effect is general;
when the Time02 is more than or equal to 7 minutes, the defrosting effect is poor.
As an example, in step S1, after the condition Time01 that the defrost system satisfies the preliminary frost is 30 minutes, the process starts to enter step S2.
As an embodiment:
in step S2, the system pressure sensor 2 detects the pressure change of the heat pump pipeline and the difference between the ambient temperature and the fin temperature of the tube fin heat exchanger 6 every two minutes.
In step S3, it is determined by the accumulation calculation in steps S1 and S2 that the fin frosting of the tube-fin heat exchanger 6 is as follows:
(1) after the fins of the tube-fin heat exchanger 6 may not frost at first and the operation Time01 is 30 minutes, the result of repeated calculation is unchanged, so that the fins of the tube-fin heat exchanger may not frost;
(2) after the fins of the tube-fin heat exchanger 6 may not frost at first but the operation Time01 is 30 minutes, the possibility of frost formation of the fins of the tube-fin heat exchanger 6 is repeatedly calculated, and the fins of the tube-fin heat exchanger 6 are judged to be slightly frosted.
In step S41, detecting a change value of the temperature of the bottom of the heat pump outdoor tube fin heat exchanger 6 every 10 seconds;
in step S42, the change value of the heat pump pipeline refrigerant pressure is detected in real time every 10 seconds.
In steps S41, S42, and S43: when any two items belong to better defrosting effect, the defrosting effect of the defrosting system is judged to be better; when any two items belong to general defrosting effects, judging that the defrosting effect of the defrosting system is general; and when any two items belong to poor defrosting effects, judging that the defrosting effect of the defrosting system is poor.
The defrosting system comprises one or more compressors 3 connected in parallel and a defrosting loop for a refrigerant, wherein a pressure sensor 2 is arranged on the defrosting loop, and the defrosting loop comprises a tube fin type heat exchanger 6, a four-way reversing valve 7, a water side heat exchanger 8 connected to a heat source and a water pan 9 connected with defrosting water discharge;
two pipe orifices of the four-way reversing valve 7 are respectively connected with the air outlet of the compressor 3 and the air inlet of the water-side heat exchanger 8, and the other two pipe orifices of the four-way reversing valve 7 are respectively connected with the air inlet of the compressor 3 and the air outlet of the tube fin type heat exchanger 6;
the pressure sensor 2 is arranged on a pipeline connected with the four-way reversing valve 7 and the air inlet of the compressor 3, and four connecting ports of a plate type heat exchanger 10 are respectively connected with a middle air supplement port of the compressor 3, a first throttle valve 11, a filter 12 and an outlet branch pipe of a water side heat exchanger 8;
the defrosting branch of the tube fin type heat exchanger 6 comprises a second throttling valve 13 and a defrosting capillary tube 14 which are connected, a first one-way valve 15 is arranged between the second throttling valve 13 and the filter 12, a second one-way valve 16 is arranged between the second throttling valve 13 and the water side heat exchanger 8, and a third one-way valve 1 is arranged between the defrosting capillary tube 14 and the tube fin type heat exchanger 6.
The tube fin type heat exchanger 6 is connected with a temperature probe 4 and an outdoor temperature probe 5, and the heat source of the water side heat exchanger 8 is air.
During defrosting, as shown by the dotted arrow in fig. 1, high-temperature and high-pressure refrigerant gas is discharged through the compressor 3, then enters the tube fin type heat exchanger 6 through the four-way reversing valve 7 to be defrosted and condensed into low-temperature and high-pressure liquid, then is divided into two paths to pass through the third one-way valve 1 and the defrosting capillary tube 14 respectively and then enters the water inlet side heat exchanger 8 to exchange heat, so that low-temperature and low-pressure refrigerant gas is formed, then sequentially passes through the four-way reversing valve 7 and finally enters the compressor 3 to be compressed, and thus the compression cycle is completed; and the other path of the refrigerant gas passes through a second throttling valve 13 and a second one-way valve 16 and then enters a water side heat exchanger 8 for heat exchange to form low-temperature and low-pressure refrigerant gas, and then passes through a four-way reversing valve 7 in sequence and finally enters a compressor 3 for compression to complete the compression cycle.
By the defrosting operation judging method, the frosting thickness of the heat pump outdoor tube fin type heat exchanger 6 can be accurately detected to effectively defrost, so that the problems that the defrosting is not clean, and the defrosting wastes heat when no frost exists are solved; meanwhile, by combining the defrosting operation judgment method, the defrosting system can quickly defrost under the condition of optimizing the process.
The defrosting system can accelerate the speed of the defrosting process by adjusting an electronic expansion valve of the refrigerating system and the like, and meanwhile, the defrosting work of the system cannot be influenced when any one of the outdoor temperature probe 5, the pressure sensor 2 and the temperature probe 4 of the tube fin type heat exchanger 6 is in a problem.
Referring to fig. 2-3, the water pan 9 includes a horizontally disposed partition plate 17, end plates 29 are disposed at two ends of the partition plate 17, a first fin installation inclined plate 18 and a second fin installation inclined plate 19 bent obliquely downward are disposed at two sides of the partition plate 17, a first water tank straight side plate 20 bent vertically downward is disposed at one side of the first fin installation inclined plate 18, and the first water tank straight side plate 20 is perpendicular to the partition plate 17;
one side of the first water tank straight side plate 20 is provided with a first water tank inclined bottom plate 21 which is bent upwards in an inclined mode, the first water tank inclined bottom plate 21 is perpendicular to the first water tank straight side plate 20, the first water tank inclined bottom plate 21 is not parallel to the spacing flat plate 17, and the first water tank inclined bottom plate 21 and the spacing flat plate 17 form an included angle which inclines downwards; one end of the first water tank inclined bottom plate 21 is provided with a first drainage pipe 22;
one side of the first water tank inclined bottom plate 21 is provided with a first water tank inclined side plate 23 which is bent upwards in an inclined manner, one side of the second fin installation inclined plate 19 is provided with a second water tank straight side plate 24 which is bent downwards in a vertical manner, and the second water tank straight side plate 24 is perpendicular to the spacing flat plate 17; one side of the second water tank straight side plate 24 is provided with a second water tank inclined bottom plate 25 which is bent upwards in an inclined mode, the second water tank inclined bottom plate 25 is perpendicular to the second water tank straight side plate 24, the second water tank inclined bottom plate 25 is not parallel to the spacing plate 17, the second water tank inclined bottom plate 25 and the spacing plate 17 are provided with an included angle which is inclined downwards, one end of the second water tank inclined bottom plate 25 is provided with a second water drainage pipe 26, and one side of the second water tank inclined bottom plate 25 is provided with a second water tank inclined side plate 27 which is bent upwards in an inclined mode.
Through the optimized channel design between 6 fins 38 of defrosting water collector 9 pipe fin type heat exchanger, can discharge defrosting water fast, and defrosting water can be collected fast to outdoor heat exchanger's water collector 9, guarantees that defrosting water can flow away fast to avoided defrosting water to freeze the problem at water collector 9 and lead to the heat exchanger effect of heating to worsen, through draining off wind side heat exchanger comdenstion water fast effectively, guaranteed going on more smoothly of defrost system.
Those not described in detail in this specification are within the skill of the art. Although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that various changes in the embodiments and/or modifications of the invention can be made, and equivalents and modifications of some features of the invention can be made without departing from the spirit and scope of the invention.
Claims (10)
1. The defrosting operation judgment method is characterized by comprising the following judgment steps:
s1, detecting the change of outdoor environment temperature Ta in real time, preliminarily judging that the outdoor tube fin type heat exchanger is likely to frost when Ta is less than 12 ℃, and entering next judgment if frosting is likely to occur, wherein if frosting is not likely to occur, the defrosting system continues to operate, and related actions of defrosting are not performed; after the defrosting system meets the condition of primary frost formation, the judgment of step S2 is started;
s2, detecting the change of the pressure of the heat pump pipeline of the compressor and the difference value between the ambient temperature and the temperature of the fins in real time through a system pressure sensor;
pressure change PLx ═ PLn-PLn + 1;
tae ═ Ta (ambient temperature) -Te (fin temperature of tube-fin heat exchanger);
wherein, the relation between the change situation of pressure and the difference between ambient temperature and the fin temperature of the finned tube heat exchanger includes:
(1) when PLx is less than or equal to 0.10 and Tae is less than or equal to 10, the fins of the tube fin type heat exchanger may not frost;
(2) when PLx is more than 0.10 and PLx is less than or equal to 0.30, Tae is more than or equal to 10 and Tae is less than or equal to 12, the fins of the tube-fin heat exchanger can be frosted, but the frosting speed is slower;
(3) when PLx is more than 0.30 and Tae is more than 12, the fins of the tube fin type heat exchanger have frost and the frost formation speed is very high.
2. The defrosting operation determination method according to claim 1, comprising the steps of:
s3, judging the fin frosting condition of the tube fin type heat exchanger through the accumulation calculation of the step S1 and the step S2 comprises the following steps:
(1) the fins of the tube fin type heat exchanger may not be frosted at first, and after the operation, the repeated calculation result is unchanged, so that the fins can be obtained to be frosted-free;
(2) the method comprises the following steps that firstly, fins of the tube fin type heat exchanger may not be frosted at first but run, the possibility that the fins are frosted is repeatedly calculated, and the fins are judged to be slightly frosted;
(3) the fins of the tube fin type heat exchanger are frosted, but the frosting speed is slow;
(4) the fins of the tube fin type heat exchanger are frosted, and the frosting speed is high;
s4, judging the defrosting effect in the defrosting operation:
s41, detecting the change value of the temperature at the bottom of the heat pump outdoor tube fin type heat exchanger in real time:
TEx-TE 0 (pre-defrost temperature) -TEn (real-time temperature detection).
When the TEx is more than 35 ℃, the defrosting effect is better;
when the temperature TEx is more than or equal to 20 ℃ and less than 35 ℃, the defrosting effect is general;
when the TEx is less than 20 ℃, the defrosting effect is poor;
s42, detecting the change of the pressure of the refrigerant of the heat pump pipeline in real time;
PHx PH0 (pre-defrost pressure) -PHn (real-time pressure detection).
When PHx is less than 28bar, the defrosting effect is better;
when PHx is more than or equal to 28bar and TEx is less than 31bar, the defrosting effect is general;
when PHx is more than or equal to 31bar, the defrosting effect is poor;
s43, calculating the defrosting consumption time of the defrosting system in real time:
when the Time02 is less than 4 minutes, the defrosting effect is better;
when the Time02 is more than or equal to 4 and the Time02 is less than 7 minutes, the defrosting effect is general;
when the Time02 is more than or equal to 7 minutes, the defrosting effect is poor.
3. The defrosting operation determination method according to claim 2, characterized in that:
in step S1, when the defrosting system satisfies the preliminary frost condition Time01 is 30 minutes, the flow proceeds to step S2.
4. The defrosting operation determination method according to claim 3, characterized in that:
in step S2, the system pressure sensor detects the pressure change of the heat pump pipeline and the difference between the ambient temperature and the fin temperature of the finned tube heat exchanger in real time every two minutes.
5. The defrosting operation determination method according to claim 4, characterized in that:
in step S3, it is determined by the accumulation calculation of steps S1 and S2 that the tube-fin heat exchanger fin is frosted as follows:
(1) the fins of the tube-fin heat exchanger may not frost at first, and after the running Time01 is 30 minutes, the repeated calculation results are unchanged, so that the fins of the tube-fin heat exchanger can be obtained to be free of frost;
(2) after the fins of the tube-fin heat exchanger may not frost at first but the running Time01 is 30 minutes, the possibility of frosting of the fins of the tube-fin heat exchanger is repeatedly calculated, and the fins of the tube-fin heat exchanger are judged to be slightly frosted.
6. The defrosting operation determination method according to claim 5, characterized in that:
in step S41, detecting the change value of the temperature of the bottom of the heat pump outdoor tube fin type heat exchanger every 10 seconds;
in step S42, the change value of the heat pump pipeline refrigerant pressure is detected in real time every 10 seconds.
7. The defrosting operation determination method according to claim 6, characterized in that: in steps S41, S42, and S43:
when any two items belong to better defrosting effect, the defrosting effect of the defrosting system is judged to be better;
when any two items belong to general defrosting effects, judging that the defrosting effect of the defrosting system is general;
and when any two items belong to poor defrosting effects, judging that the defrosting effect of the defrosting system is poor.
8. Defrost system according to any of the claims 1-7, characterized in that:
the defrosting system comprises one or more compressors connected in parallel and a defrosting loop for a refrigerant, wherein a pressure sensor is arranged on the defrosting loop, and the defrosting loop comprises a tube fin type heat exchanger, a four-way reversing valve, a water side heat exchanger and a water receiving disc, wherein the tube fin type heat exchanger, the four-way reversing valve, the water side heat exchanger and the water receiving disc are connected in a circulating mode to form a loop, and the water receiving disc is used for connecting defrosting water to be discharged.
9. The defrost system of claim 8, wherein:
two pipe orifices of the four-way reversing valve are respectively connected with an air outlet of the compressor and an air inlet of the water-side heat exchanger, and the other two pipe orifices of the four-way reversing valve are respectively connected with an air inlet of the compressor and an air outlet of the tube fin type heat exchanger;
the four connectors of a plate heat exchanger are respectively connected with a middle air supplement port of the compressor, a first throttle valve, a filter and an outlet branch pipe of a water side heat exchanger;
the defrosting branch of the tube fin type heat exchanger comprises a second throttling valve and a defrosting capillary tube which are connected, a first one-way valve is arranged between the second throttling valve and the filter, a second one-way valve is arranged between the second throttling valve and the water side heat exchanger, and a third one-way valve is arranged between the defrosting capillary tube and the tube fin type heat exchanger;
the tube fin type heat exchanger is provided with a temperature probe and an outdoor temperature probe, and the heat source of the water side heat exchanger is air.
10. The defrost system of claim 9, wherein:
the water pan comprises a horizontally arranged spacing flat plate, end plates are arranged at two ends of the spacing flat plate, a first fin mounting inclined plate and a second fin mounting inclined plate which are bent obliquely downwards are respectively arranged at two sides of the spacing flat plate, a first water tank straight side plate which is bent vertically downwards is arranged at one side of the first fin mounting inclined plate, and the first water tank straight side plate is perpendicular to the spacing flat plate;
a first water tank inclined bottom plate which is bent upwards in an inclined mode is arranged on one side of the first water tank straight side plate, the first water tank inclined bottom plate and the first water tank straight side plate are perpendicular to each other, the first water tank inclined bottom plate and the spacing flat plate are not parallel to each other, and an included angle formed by the first water tank inclined bottom plate and the spacing flat plate in a downward inclined mode is formed; one end of the first water tank inclined bottom plate is provided with a first drainage pipe;
one side of the first water tank inclined bottom plate is provided with a first water tank inclined side plate which is bent upwards in an inclined manner, one side of the second fin installation inclined plate is provided with a second water tank straight side plate which is bent downwards in a vertical manner, and the second water tank straight side plate is perpendicular to the spacing flat plate; one side of the second water tank straight side plate is provided with a second water tank inclined bottom plate bent in an inclined upward direction, the second water tank inclined bottom plate is perpendicular to the second water tank straight side plate, the second water tank inclined bottom plate is not parallel to the spacing flat plate, the second water tank inclined bottom plate and the spacing flat plate are provided with an included angle inclined downward, one end of the second water tank inclined bottom plate is provided with a second drain pipe, and one side of the second water tank inclined bottom plate is provided with a second water tank inclined side plate bent in an inclined upward direction.
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