CN112414163A - Heat exchanger, hot water making circulating unit and control method thereof - Google Patents
Heat exchanger, hot water making circulating unit and control method thereof Download PDFInfo
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- CN112414163A CN112414163A CN202011238565.5A CN202011238565A CN112414163A CN 112414163 A CN112414163 A CN 112414163A CN 202011238565 A CN202011238565 A CN 202011238565A CN 112414163 A CN112414163 A CN 112414163A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
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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
- 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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02731—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one three-way valve
Abstract
The present disclosure provides a heat exchanger, a hot water circulating unit and a control method thereof, wherein the heat exchanger includes: the heat exchange fin is arranged on the heat exchange tube in a penetrating manner, and the heat exchange fins are at least two and at least two heat exchange fins to form a group of heat exchange fin groups; in two adjacent groups of heat exchange fin groups, the distance between the heat exchange fin close to the second group of heat exchange fin group in the first group of heat exchange fin group and the heat exchange fin close to the first group of heat exchange fin group in the second group of heat exchange fin group is gradually reduced along the airflow flowing direction, and the distance is the distance vertical to the airflow flowing direction. According to the multi-functional water heater, the distance between the fins is gradually reduced along the airflow flowing direction, the large fin distance is formed, the air speed is increased, the air quantity is increased, the heat exchange capacity of the heat exchange fins is improved, the defrosting capacity is improved, the large temperature operation range of the multi-functional water heater can be effectively met, and the working condition application range is improved.
Description
Technical Field
The disclosure relates to the technical field of air conditioners, in particular to a heat exchanger, a hot water making circulating unit and a control method of the hot water making circulating unit.
Background
The heating operation range of the multifunctional water heater is generally 35-35 ℃, but 35-7 ℃, the multifunctional water heater can not enter a frequent defrosting state and can operate for a long time. However, abnormal conditions exist, for example, in the Yangtze river coastal areas of China, the humidity is too high, a large amount of frost is generated when the temperature is lower than 0 ℃, the defrosting load of the whole machine is very large at the moment, the load output of the whole machine is very large, and the problems of unclean defrosting, frequent defrosting and the like are also caused.
From another aspect, when the external environment temperature is-7 to-35 ℃, a large amount of frost is formed on the fins, and the ventilation of the whole fins is difficult due to the fact that the fin spacing is too small, the tube spacing is too small, and the frost thickness is thick; the defrosting difficulty is greatly increased due to the fact that the circulation temperature is too low and the heat exchange capability is greatly reduced due to the difficulty in ventilation; the risk of the operation of the whole machine is increased, and faults such as high voltage, low voltage and the like easily occur at the time.
If fatal problems such as low temperature liquid carrying and the like occur, the compressor can be damaged irreversibly, so that the service life of the whole machine is shortened, and the reliability of the whole machine is threatened, which are problems caused by the original scheme of the current machine set.
From the above problems, the existing high heat exchange performance fin only suitable for the normal temperature section cannot meet the problem of continuously enlarging the operation range of the multifunctional water heater.
Because the high heat exchange performance fin of the heat exchanger only suitable for the normal temperature section in the prior art can not meet the technical problems of large temperature operation range, smaller working condition application range and the like of the multifunctional water heater, the heat exchanger, the hot water making circulating unit and the control method thereof are researched and designed in the disclosure.
Disclosure of Invention
Therefore, the technical problem to be solved by the present disclosure is to overcome the defects that the high heat exchange performance fin of the heat exchanger suitable for the normal temperature section in the prior art cannot meet the requirements of the multifunctional water heater on a large temperature operation range and a small working condition application range, so as to provide a heat exchanger, a hot water making circulating unit and a control method thereof.
In order to solve the above problem, the present disclosure provides a heat exchanger, including:
the heat exchange fin is arranged on the heat exchange tube in a penetrating manner, and the heat exchange fins are at least two and at least two heat exchange fins to form a group of heat exchange fin groups; in two adjacent groups of heat exchange fin groups, the distance between the heat exchange fin close to the second group of heat exchange fin group in the first group of heat exchange fin group and the heat exchange fin close to the first group of heat exchange fin group in the second group of heat exchange fin group is gradually reduced along the airflow flowing direction, and the distance is the distance vertical to the airflow flowing direction.
In some embodiments, the heat exchange fins of the first group of heat exchange fin groups close to the second group of heat exchange fin groups and the heat exchange fins of the second group of heat exchange fin groups close to the first group of heat exchange fin groups are arranged at an angle θ, and the angle θ is 0 < θ < 45 °.
In some embodiments, the heat exchanging fin group includes a first heat exchanging fin and a third heat exchanging fin, the upstream side in the airflow flowing direction, the windward end of the first heat exchanging fin and the windward end of the third heat exchanging fin are connected, and the downstream side in the airflow flowing direction, the leeward end of the first heat exchanging fin and the leeward end of the third heat exchanging fin are spaced.
In some embodiments, the heat exchanging fin group further includes a second heat exchanging fin located between the first heat exchanging fin and the third heat exchanging fin, and the upstream side of the airflow flowing direction, the windward end of the second heat exchanging fin, the windward end of the first heat exchanging fin, and the windward end of the third heat exchanging fin are all connected.
In some embodiments, the leeward ends of the second heat exchanger fins are spaced from the leeward ends of the first heat exchanger fins on the downstream side in the direction of airflow flow, while the leeward ends of the second heat exchanger fins are also spaced from the leeward ends of the third heat exchanger fins.
In some embodiments, the heat exchange surface of the second heat exchange fin is arranged perpendicular to the axial direction of the heat exchange tube; and/or the second heat exchange fin and the heat exchange tube are fixedly arranged; and/or an air volume sensor is arranged on the upstream side of the second heat exchange fin along the airflow flowing direction.
The present disclosure further provides a heating water circulation unit, which includes any one of the heat exchangers, where the heat exchanger is a first heat exchange device, and further includes a second heat exchange device, a compressor, a third heat exchange device, and a control valve, where the first heat exchange device and the second heat exchange device are connected in parallel, the control valve is disposed at a position of a pipeline where the first heat exchange device and the second heat exchange device intersect, and by controlling the control valve, one of the first heat exchange device and the second heat exchange device can be controlled to be opened, and the other one of the first heat exchange device and the second heat exchange device can be controlled to be closed, and a working temperature range of the first heat exchange device is less than or equal to a working temperature range of the second heat exchange device.
In some embodiments, the working temperature range of the hot water making circulating unit is (a ℃, b ℃), the working temperature range of the first heat exchange device is (a ℃, n ℃), the working temperature range of the second heat exchange device is (n ℃, b ℃), wherein a is less than n and less than b, the outdoor environment temperature is detected to be TE, when a is less than TE and less than n, the first heat exchange device is opened and the second heat exchange device is closed by controlling the control valve, when n is less than TE and less than b, the second heat exchange device is opened and the first heat exchange device is closed by controlling the control valve, and the value of n is a switching temperature point.
In some embodiments, the control valve is a three-way valve:
when a is larger than TE and is smaller than or equal to n, controlling the three-way valve to be switched to an ON state;
and when n is more than TE and less than or equal to b, controlling the three-way valve to be switched to an OFF state.
In some embodiments, the switching temperature point n is calculated as follows:
in the formula:
tw is the actual defrosting temperature, and 0-t 1 is the data return time of the defrosting sensor.
In some embodiments, when an angle θ is sandwiched between the heat exchange fin close to the second group of heat exchange fin groups in the first group of heat exchange fin groups and the heat exchange fin close to the first group of heat exchange fin groups in the second group of heat exchange fin groups, and the angle is 0 < θ < 45 °, the angle at which the air volume is maximum is θ 1;
setting rated air quantity as Q, fin length as L, fin spacing as L1, fin width as L2 and fin number as m;
the rated inlet wind speed V1 is calculated as: v1 ═ Q/((m-1) × L1 × L2)
The actual inlet air speed V is calculated as:
V＝Q/((m-1)*(L1-2*L*sinθ)*L2)
the wind speed difference Δ V-V1 is calculated as follows
In some embodiments, when an angle θ is sandwiched between the heat exchange fin close to the second group of heat exchange fin groups in the first group of heat exchange fin groups and the heat exchange fin close to the first group of heat exchange fin groups in the second group of heat exchange fin groups, and the angle θ is 0 < θ < 45 °, the angle at which the air volume is maximum is θ 1;
setting rated air quantity as Q, fin length as L, fin spacing as L1, fin width as L2 and fin number as m;
the air inlet speed V when the air quantity is maximum is calculated as:
V2＝Q/((m-1)*(L1-2*L*sinθ1)*L2)
after the low-temperature heat exchange device is started, the angle of the fins is directly adjusted to theta 1 to operate for 3 min; the angle θ is then adjusted every t1s, the adjustment being calculated as follows:
θ ═ θ 1 × (V/V2) was further calculated as follows
The present disclosure also provides a control method of the heating water circulation unit according to any one of the preceding claims, wherein: the working operation range of the hot water making circulating unit is (a ℃, b ℃), the working temperature range of the first heat exchange device (3) is (a ℃, n ℃), the working temperature range of the second heat exchange device (4) is (n ℃, b ℃), wherein a is more than n and less than b, and the outdoor environment temperature is TE:
when the a is larger than TE and is less than or equal to n, controlling the control valve to open the first heat exchange device and close the second heat exchange device; and when n is larger than TE and smaller than b, controlling the control valve to open the second heat exchange device and close the first heat exchange device, wherein the value of n is a switching temperature point.
The heat exchanger, the hot water circulating unit and the control method thereof have the following beneficial effects:
the air speed is effectively improved, the air quantity is effectively improved, the heat exchange capacity of the heat exchange fins is further improved, the ventilation among the heat exchange fins is ensured to be normal, the defrosting capacity is effectively improved, the large temperature operation range of the multifunctional water heater can be effectively met, and the working condition application range is improved; the included angle theta between the fins of the heat exchange device is controlled according to different operation working conditions (outdoor environment temperature) at the beginning of operation, so that the air volume is increased under the condition of not increasing the power, the heat exchange quantity of the fins is increased, and the load of a compressor in overtemperature operation is reduced; the whole machine control system is combined, a control strategy is designed, the external working condition of the whole machine is combined, the automatic mode switching and the demand adjusting capacity are corresponding to the low-temperature heat exchange device, and therefore the unit can meet the requirement of large-range operation; therefore, the problem of frequent defrosting is eliminated, the problems of high-low pressure faults or low-temperature liquid carrying and the like are avoided, the redundant starting times of the compressor are reduced, the service life of the compressor is prolonged, and the running reliability of the whole machine is improved; guarantee the unit even running, continuously to indoor input heat assurance user's use travelling comfort.
Drawings
Fig. 1 is a system configuration diagram of a hot water circulating unit of the present disclosure;
FIG. 2 is a corresponding graph of included angle θ between heat exchange fins and heat exchange capacity (air volume) according to the present disclosure;
fig. 3 is a schematic top view of the heat exchange fins of the present disclosure when an included angle θ exists therebetween.
The reference numerals are represented as:
1. a heat exchange pipe; 2. heat exchange fins; 21. a first heat exchange fin; 22. a second heat exchange fin; 23. a third heat exchange fin; 3. a first heat exchange means; 4. a second heat exchange means; 5. a compressor; 6. a third heat exchange means; 7. a control valve; 8. a gas-liquid separator; 9. a fan.
Detailed Description
As shown in fig. 1-3, the present disclosure provides a heat exchanger comprising:
the heat exchange fin 2 is arranged on the heat exchange tube 1 in a penetrating manner, and the heat exchange fins 2 are at least two heat exchange fins 2, and at least two heat exchange fins 2 form a group of heat exchange fin group; in two adjacent groups of heat exchange fin groups, the distance between the heat exchange fin close to the second group of heat exchange fin group in the first group of heat exchange fin group and the heat exchange fin close to the first group of heat exchange fin group in the second group of heat exchange fin group is gradually reduced along the airflow flowing direction, and the distance is the distance vertical to the airflow flowing direction.
According to the air-conditioning system, at least two heat exchange fins are arranged to be one heat exchange fin group, the distance between the heat exchange fins in the two adjacent heat exchange fin groups and the heat exchange fins in the first heat exchange fin group, which are close to the second heat exchange fin group, and the distance between the heat exchange fins in the second heat exchange fin group, which are close to the first heat exchange fin group, are gradually reduced along the airflow flowing direction, the distance between the formed fins is gradually reduced along the airflow flowing direction, and a large fin distance is formed, so that the air speed is effectively improved, the air volume is effectively improved, the heat exchange capacity of the heat exchange fins is further improved, the ventilation among the heat exchange fins is ensured to be normal, the defrosting capacity is effectively improved, the large temperature operating range of the multifunctional water heater can be effectively met, and the working condition application range is improved.
In some embodiments, the heat exchange fins of the first group of heat exchange fin groups close to the second group of heat exchange fin groups and the heat exchange fins of the second group of heat exchange fin groups close to the first group of heat exchange fin groups are arranged at an angle θ, and the angle θ is 0 < θ < 45 °.
The included angle theta between the fins of the heat exchange device is controlled according to different operation working conditions (outdoor environment temperature) at the beginning of operation, so that the air quantity is increased under the condition of not increasing power, the heat exchange quantity of the fins is increased, and the load of a compressor in overtemperature operation is reduced; the whole machine control system is combined, a control strategy is designed, the external working condition of the whole machine is combined, the automatic mode switching and the demand adjusting capacity are corresponding to the low-temperature heat exchange device, and therefore the unit can meet the requirement of large-range operation; therefore, the problem of frequent defrosting is eliminated, the problems of high-low pressure faults or low-temperature liquid carrying and the like are avoided, the redundant starting times of the compressor are reduced, the service life of the compressor is prolonged, and the running reliability of the whole machine is improved; guarantee the unit even running, continuously to indoor input heat assurance user's use travelling comfort.
The existing air-conditioning field generally uses parallel fins, and the heat exchange capacity is limited. The angle theta of the fin is increased, so that the air inlet speed can be increased, a low-pressure area is manufactured on the inner side of the whole machine, and the air quantity is continuously sucked from the outside, so that the heat exchange capacity of the low-temperature condenser is enhanced;
it is worth noting that the range of theta is 0-45 degrees, and a highest air volume point theta 1 is arranged between theta, namely theta is large and cannot be used (wind resistance is suddenly increased due to large theta, and comprehensive air volume is influenced), and theta is small and cannot be used (wind speed and air volume are difficult to be increased due to small theta is close to parallel fins).
In some embodiments, the heat exchanging fin group includes a first heat exchanging fin 21 and a third heat exchanging fin 23, a windward end of the first heat exchanging fin 21 and a windward end of the third heat exchanging fin 23 are connected on an upstream side in the airflow flowing direction, and a leeward end of the first heat exchanging fin 21 and a leeward end of the third heat exchanging fin 23 are spaced apart on a downstream side in the airflow flowing direction. The first heat exchange fin and the third heat exchange fin are arranged at the upstream end (windward end) of airflow and are separated at the downstream end (leeward end) of the airflow, so that the heat exchange fin group can form a shape of a cross along the airflow flowing direction, an airflow flowing space between two adjacent heat exchange fin groups forms a structure with the airflow flowing area gradually reduced, the airflow speed is gradually increased, the air volume is pushed to be gradually increased, and the heat exchange capacity between the airflow and the heat exchange fins is improved.
In some embodiments, the heat exchanging fin group further includes a second heat exchanging fin 22, the second heat exchanging fin 22 is located between the first heat exchanging fin 21 and the third heat exchanging fin 23, and the upstream side of the airflow flowing direction, the windward end of the second heat exchanging fin 22, the windward end of the first heat exchanging fin 21, and the windward end of the third heat exchanging fin 23 are all connected. The heat exchange fin group is further optimized in structural form, the three heat exchange fins form the heat exchange fin group through the arrangement of the second heat exchange fins, the windward ends of the three fins are connected, the structural strength of the heat exchange fin group is effectively improved, one fin is changed into three fins to form a reinforced fin effect, and the heat exchange capacity can be improved.
Fig. 3 is a partial schematic view showing that the fin pitch is not parallel in the development at present, wherein 3 fins are processed by a special process to connect the 3 fins into a group, wherein the first heat exchange fin 21 and the third heat exchange fin 23 can be controlled by an adjusting mechanism to change with a side fin theta, wherein the second heat exchange fin 2 is a fin fixed on a refrigerant copper pipe, and the change of theta is sensed and adjusted by negative feedback control by adding an air volume sensor and a control device to meet the maximum air volume requirement.
In some embodiments, the leeward end of the second heat exchanging fin 22 is spaced apart from the leeward end of the first heat exchanging fin 21 on the downstream side in the airflow flowing direction, while the leeward end of the second heat exchanging fin 22 is also spaced apart from the leeward end of the third heat exchanging fin 23. Through the setting of the leeward end of the second heat exchange fin, the leeward end of the second heat exchange fin is spaced from the leeward end of the first heat exchange fin, and meanwhile, the leeward end of the second heat exchange fin is also spaced from the leeward end of the third heat exchange fin, so that the leeward end between the first heat exchange fin and the third heat exchange fin can be effectively opened, the included angle between two adjacent heat exchange fin groups is larger, the effect of improving the wind speed is better and obvious, and the wind quantity is further improved.
In some embodiments, the heat exchange surface of the second heat exchange fin 22 is arranged perpendicular to the axial direction of the heat exchange tube 1; and/or the second heat exchange fin 22 is fixedly arranged with the heat exchange tube 1; and/or an air volume sensor is arranged on the upstream side of the second heat exchange fin 22 along the airflow flowing direction. This is disclosed through the perpendicular setting of the axis direction of the heat transfer face of second heat transfer fin and heat exchange tube, can guarantee its and the heat exchange tube between firm combination length, fixed setting can guarantee that second heat transfer fin reduces to rock, forms good fixed effect to first and third heat transfer fin, can detect the amount of wind that obtains the fin windward side through air sensor, has improved the amount of wind, has improved heat transfer effect for current parallel arrangement's fin.
The present disclosure further provides a heating water circulation unit, which includes any one of the heat exchangers described above, where the heat exchanger is a first heat exchange device 3 (preferably, an outdoor low-temperature heat exchanger), and further includes a second heat exchange device 4 (preferably, an outdoor normal-temperature heat exchanger), a compressor 5, a third heat exchange device 6 (preferably, an indoor heating water heat exchanger), and a control valve 7, where the first heat exchange device 3 and the second heat exchange device 4 are arranged in parallel, the control valve 7 is arranged at a pipeline position where the first heat exchange device 3 and the second heat exchange device 4 intersect, and by controlling the control valve 7, one of the first heat exchange device 3 and the second heat exchange device 4 can be controlled to be opened, and the other can be closed, and a working temperature range of the first heat exchange device 3 is less than or equal to a working temperature range of the second heat exchange device 4.
According to the invention, a controllable low-temperature condenser is connected in parallel beside a normal-temperature condenser, the design of the low-temperature condenser adopts a large tube pitch and a large fin pitch, so that the high frosting condition during ultralow-temperature operation is adapted, the normal ventilation of a unit is ensured, and the sufficient defrosting capacity is still provided; the fins of the condenser are controlled by using a braking structure, so that the air quantity is increased under the condition of not increasing the power, the heat exchange quantity of the fins is increased, and the load of a compressor during the ultralow-temperature operation is reduced; the whole machine control system is combined, a control strategy is designed, the external working condition of the whole machine is combined, the automatic mode switching and the demand regulation capacity are corresponding to the low-temperature condenser, and therefore the unit can meet the requirement of large-range operation; therefore, the problem of frequent defrosting is eliminated, the problems of high-low pressure faults or low-temperature liquid carrying and the like are avoided, the redundant starting times of the compressor are reduced, the service life of the compressor is prolonged, and the running reliability of the whole machine is improved; guarantee the unit even running, continuously to indoor input heat assurance user's use travelling comfort.
In some embodiments, the working temperature range of the hot water making circulating unit is (a ℃, b ℃), the working temperature range of the first heat exchange device 3 is (a ℃, n ℃), the working temperature range of the second heat exchange device 4 is (n ℃, b ℃), wherein a is less than n and less than b, the outdoor environment temperature is detected to be TE, when a is less than TE and less than n, the first heat exchange device is opened and the second heat exchange device is closed by controlling the control valve, when n is less than TE and less than b, the second heat exchange device is opened and the first heat exchange device is closed by controlling the control valve, and n is a switching temperature point.
In some embodiments, the control valve is a three-way valve:
when a is larger than TE and is smaller than or equal to n, controlling the three-way valve to be switched to an ON state;
and when n is more than TE and less than or equal to b, controlling the three-way valve to be switched to an OFF state.
In some embodiments, the switching temperature point n is calculated as follows:
in the formula:
tw is the actual defrosting temperature, and 0-t 1 is the data return time of the defrosting sensor; the lower the Te is, the larger the difference value between the Te and the Te is, so that the coefficient is increased, the worse the running condition of the whole machine is, the more serious the frosting is, so that the temperature of a switching point is increased, and the unit enters a low-temperature running mode in advance, so that the running reliability of the whole machine is protected;
in some embodiments, the fin angle theta is set to be in the range of 0-45 degrees, and the optimal air volume angle theta 1 is set;
when an angle theta is formed between the heat exchange fin close to the second heat exchange fin group in the first heat exchange fin group and the heat exchange fin close to the first heat exchange fin group in the second heat exchange fin group, and the angle is more than 0 and less than 45 degrees, the angle when the air volume is maximum is theta 1;
setting rated air quantity as Q, fin length as L, fin spacing as L1, fin width as L2 and fin number as m;
the rated inlet wind speed V1 is calculated as: v1 ═ Q/((m-1) × L1 × L2)
The actual inlet air speed V is calculated as:
V＝Q/((m-1)*(L1-2*L*sinθ)*L2)
the wind speed difference Δ V-V1 is calculated as follows
In some embodiments, when an angle θ is sandwiched between the heat exchange fin close to the second group of heat exchange fin groups in the first group of heat exchange fin groups and the heat exchange fin close to the first group of heat exchange fin groups in the second group of heat exchange fin groups, and the angle θ is 0 < θ < 45 °, the angle at which the air volume is maximum is θ 1;
setting rated air quantity as Q, fin length as L, fin spacing as L1, fin width as L2 and fin number as m;
the air inlet speed V when the air quantity is maximum is calculated as:
V2＝Q/((m-1)*(L1-2*L*sinθ1)*L2)
after the low-temperature heat exchange device is started, the angle of the fins is directly adjusted to theta 1 to operate for 3 min; the angle θ is then adjusted every t1s, the adjustment being calculated as follows:
θ ═ θ 1 × (V/V2) was further calculated as follows
The present disclosure further provides a control method of the water heating cycle unit according to any one of the preceding items, wherein the operating range of the water heating cycle unit is (a ℃, b ℃), the operating temperature range of the first heat exchange device 3 is (a ℃, n ℃), the operating temperature range of the second heat exchange device 4 is (n ℃, b ℃), wherein a is greater than n is less than b, and the outdoor environment temperature is TE:
when the a is larger than TE and is less than or equal to n, controlling the control valve to open the first heat exchange device and close the second heat exchange device; and when n is larger than TE and smaller than b, controlling the control valve to open the second heat exchange device and close the first heat exchange device, wherein the value of n is a switching temperature point.
According to the invention, a controllable low-temperature condenser (a first heat exchange device 3) is connected in parallel beside a normal-temperature condenser (a second heat exchange device 4), the low-temperature condenser is designed to adopt a large tube pitch and a large fin pitch so as to adapt to the high frosting condition during ultralow-temperature operation, the normal ventilation of a unit is ensured, and the unit still has enough defrosting capacity; the fins of the condenser are controlled by using a braking structure, so that the air quantity is increased under the condition of not increasing the power, the heat exchange quantity of the fins is increased, and the load of a compressor during the ultralow-temperature operation is reduced; the control system of the whole machine is combined, a control strategy is designed, the external working condition of the whole machine is combined, the mode is automatically switched (when a is more than TE and less than n, the control valve is controlled to open the first heat exchange device, and close the second heat exchange device; when n is more than TE and less than b, the control valve is controlled to open the second heat exchange device, and close the first heat exchange device), and the adjustment demand capacity corresponds to the low-temperature condenser, so that the unit can meet the demand of large-range operation; therefore, the problem of frequent defrosting is eliminated, the problems of high-low pressure faults or low-temperature liquid carrying and the like are avoided, the redundant starting times of the compressor are reduced, the service life of the compressor is prolonged, and the running reliability of the whole machine is improved; guarantee the unit even running, continuously to indoor input heat assurance user's use travelling comfort.
The above description is only exemplary of the present disclosure and should not be taken as limiting the disclosure, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present disclosure should be included in the scope of the present disclosure. The foregoing is only a preferred embodiment of the present disclosure, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present disclosure, and these modifications and variations should also be regarded as the protection scope of the present disclosure.
Claims (13)
1. A heat exchanger, characterized by: the method comprises the following steps:
the heat exchange fin comprises a heat exchange tube (1) and heat exchange fins (2), wherein the heat exchange fins (2) are arranged on the heat exchange tube (1) in a penetrating mode, and the heat exchange fins (2) are at least two and at least two heat exchange fins (2) to form a group of heat exchange fin groups; in two adjacent groups of heat exchange fin groups, the distance between the heat exchange fin close to the second group of heat exchange fin group in the first group of heat exchange fin groups and the heat exchange fin close to the first group of heat exchange fin groups in the second group of heat exchange fin groups is gradually reduced along the airflow flowing direction, and the distance is the distance vertical to the airflow flowing direction.
2. The heat exchanger of claim 1, wherein:
an angle theta is formed between the heat exchange fin close to the second heat exchange fin group in the first heat exchange fin group and the heat exchange fin close to the first heat exchange fin group in the second heat exchange fin group, and the angle theta is more than 0 and less than 45 degrees.
3. The heat exchanger according to claim 1 or 2, wherein:
the heat exchange fin group comprises a first heat exchange fin (21) and a third heat exchange fin (23), the upstream side of the airflow flowing direction, the windward end of the first heat exchange fin (21) and the windward end of the third heat exchange fin (23) are connected, and the downstream side of the airflow flowing direction, the leeward end of the first heat exchange fin (21) and the leeward end of the third heat exchange fin (23) are separated.
4. The heat exchanger of claim 3, wherein:
the heat exchange fin group further comprises second heat exchange fins (22), the second heat exchange fins (22) are located between the first heat exchange fins (21) and the third heat exchange fins (23), and the upstream side of the airflow flowing direction, the windward ends of the second heat exchange fins (22), the windward ends of the first heat exchange fins (21) and the windward ends of the third heat exchange fins (23) are connected.
5. The heat exchanger of claim 4, wherein:
on the downstream side in the airflow flowing direction, the leeward end of the second heat exchange fin (22) is spaced from the leeward end of the first heat exchange fin (21), and the leeward end of the second heat exchange fin (22) is also spaced from the leeward end of the third heat exchange fin (23).
6. The heat exchanger of claim 4 or 5, wherein:
the heat exchange surface of the second heat exchange fin (22) is perpendicular to the axial direction of the heat exchange tube (1); and/or the second heat exchange fin (22) and the heat exchange tube (1) are fixedly arranged; and/or an air volume sensor is arranged on the upstream side of the second heat exchange fin (22) along the airflow flowing direction.
7. A heating water circulation unit is characterized in that: the heat exchanger comprises the heat exchanger as claimed in any one of claims 1 to 6, and is a first heat exchange device (3), and further comprises a second heat exchange device (4), a compressor (5), a third heat exchange device (6), and a control valve (7), wherein the first heat exchange device (3) and the second heat exchange device (4) are arranged in parallel, the control valve (7) is arranged at a pipeline position where the first heat exchange device (3) and the second heat exchange device (4) intersect, one of the first heat exchange device (3) and the second heat exchange device (4) can be controlled to be opened and the other can be closed by controlling the control valve (7), and the working temperature range of the first heat exchange device (3) is less than or equal to that of the second heat exchange device (4).
8. The heating water circulation unit according to claim 7, wherein:
the working temperature range of the hot water making circulating unit is (a ℃, b ℃), the working temperature range of the first heat exchange device (3) is (a ℃, n ℃), the working temperature range of the second heat exchange device (4) is (n ℃, b ℃), wherein a is more than n and less than b, the outdoor environment temperature is detected to be TE, when a is more than TE and less than n, the first heat exchange device is opened and the second heat exchange device is closed by controlling the control valve, when n is more than TE and less than b, the second heat exchange device is opened and the first heat exchange device is closed by controlling the control valve, and n is a switching temperature point.
9. The heating water circulation unit according to claim 8, wherein:
the control valve is a three-way valve:
when a is larger than TE and is smaller than or equal to n, controlling the three-way valve to be switched to an ON state;
and when n is more than TE and less than or equal to b, controlling the three-way valve to be switched to an OFF state.
10. The heating water circulation unit according to claim 8, wherein:
the switching temperature point n is calculated as follows:
in the formula:
tw is the actual defrosting temperature, and 0-t 1 is the data return time of the defrosting sensor.
11. The heating water circulation unit according to claim 8, wherein:
when an angle theta is formed between the heat exchange fin close to the second heat exchange fin group in the first heat exchange fin group and the heat exchange fin close to the first heat exchange fin group in the second heat exchange fin group, and the angle is more than 0 and less than 45 degrees, the angle when the air volume is maximum is theta 1;
setting rated air quantity as Q, fin length as L, fin spacing as L1, fin width as L2 and fin number as m;
the rated inlet wind speed V1 is calculated as: v1 ═ Q/((m-1) × L1 × L2)
The actual inlet air speed V is calculated as:
V＝Q/((m-1)*(L1-2*L*sinθ)*L2)
the wind speed difference Δ V-V1 is calculated as follows
12. The heating water circulation unit according to claim 8, wherein:
when an angle theta is formed between the heat exchange fin close to the second heat exchange fin group in the first heat exchange fin group and the heat exchange fin close to the first heat exchange fin group in the second heat exchange fin group, and the angle is more than 0 and less than 45 degrees, the angle with the largest air volume is theta 1;
setting rated air quantity as Q, fin length as L, fin spacing as L1, fin width as L2 and fin number as m;
the air inlet speed V when the air quantity is maximum is calculated as:
V2＝Q/((m-1)*(L1-2*L*sinθ1)*L2)
after the low-temperature heat exchange device is started, the angle of the fins is directly adjusted to theta 1 to operate for 3 min; the angle θ is then adjusted every t1s, the adjustment being calculated as follows:
θ ═ θ 1 × (V/V2) was further calculated as follows
13. A control method of the heating water circulation unit according to any one of claims 7 to 12, characterized in that: the working operation range of the hot water making circulating unit is (a ℃, b ℃), the working temperature range of the first heat exchange device (3) is (a ℃, n ℃), the working temperature range of the second heat exchange device (4) is (n ℃, b ℃), wherein a is more than n and less than b, and the outdoor environment temperature is TE:
when the a is larger than TE and is less than or equal to n, controlling the control valve to open the first heat exchange device and close the second heat exchange device; and when n is larger than TE and smaller than b, controlling the control valve to open the second heat exchange device and close the first heat exchange device, wherein the value of n is a switching temperature point.
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| CN202011238565.5A CN112414163B (en) | 2020-11-09 | 2020-11-09 | Heat exchanger, hot water making circulating unit and control method thereof |
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| CN202011238565.5A CN112414163B (en) | 2020-11-09 | 2020-11-09 | Heat exchanger, hot water making circulating unit and control method thereof |
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202660814U (en) * | 2012-04-16 | 2013-01-09 | 海信科龙电器股份有限公司 | Heat exchanging fin for air conditioning heat exchanger and combined heat exchanging fin |
| US20150211807A1 (en) * | 2014-01-29 | 2015-07-30 | Trane International Inc. | Heat Exchanger with Fluted Fin |
| CN205372843U (en) * | 2016-01-12 | 2016-07-06 | 广东美的制冷设备有限公司 | Heat exchanger and air condensing units of air conditioner |
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2020
- 2020-11-09 CN CN202011238565.5A patent/CN112414163B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202660814U (en) * | 2012-04-16 | 2013-01-09 | 海信科龙电器股份有限公司 | Heat exchanging fin for air conditioning heat exchanger and combined heat exchanging fin |
| US20150211807A1 (en) * | 2014-01-29 | 2015-07-30 | Trane International Inc. | Heat Exchanger with Fluted Fin |
| CN205372843U (en) * | 2016-01-12 | 2016-07-06 | 广东美的制冷设备有限公司 | Heat exchanger and air condensing units of air conditioner |
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