CN113432336B - Enhanced vapor injection air source heat pump system and dynamic exhaust superheat degree control method - Google Patents
Enhanced vapor injection air source heat pump system and dynamic exhaust superheat degree control method Download PDFInfo
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- 238000002347 injection Methods 0.000 title claims abstract description 29
- 239000007924 injection Substances 0.000 title claims abstract description 29
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- 239000000523 sample Substances 0.000 claims abstract description 33
- 239000007788 liquid Substances 0.000 claims description 30
- 238000012937 correction Methods 0.000 claims description 10
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- 230000007613 environmental effect Effects 0.000 claims description 8
- YCKRFDGAMUMZLT-UHFFFAOYSA-N Fluorine atom Chemical compound [F] YCKRFDGAMUMZLT-UHFFFAOYSA-N 0.000 claims description 6
- 229910052731 fluorine Inorganic materials 0.000 claims description 6
- 239000011737 fluorine Substances 0.000 claims description 6
- 230000009286 beneficial effect Effects 0.000 abstract description 2
- 239000003507 refrigerant Substances 0.000 description 16
- 239000003921 oil Substances 0.000 description 13
- 238000010438 heat treatment Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 229920006395 saturated elastomer Polymers 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000002156 mixing Methods 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 238000011160 research Methods 0.000 description 2
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- 238000013461 design Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
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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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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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
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential heat
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
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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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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Abstract
The invention discloses an enhanced vapor injection air source heat pump system and a dynamic exhaust superheat degree control method, wherein the enhanced vapor injection air source heat pump system comprises a water-side heat exchanger and an ambient temperature acquisition device, and a water outlet temperature probe is arranged at a water outlet of the water-side heat exchanger; and acquiring the outlet water temperature through the outlet water temperature probe, and acquiring the ambient temperature through the ambient temperature acquiring device. The beneficial effects of the invention are: the energy efficiency of the ultralow-temperature air source heat pump system under different working conditions of environment temperature and water temperature is optimal in a dynamic control mode of the system exhaust superheat degree.
Description
Technical Field
The invention relates to the technical field of exhaust superheat degree control, in particular to an enhanced vapor injection air source heat pump system and a dynamic exhaust superheat degree control method.
Background
In northern areas of China, the outdoor temperature is low in winter, and the conventional air source heat pump is difficult to adapt to the low-temperature working condition of the outdoor environment, and the main reason is that the normal operation of the air source heat pump is influenced by overhigh exhaust temperature of a compressor when the air source heat pump works under the low-temperature working condition of the outdoor environment. Particularly, when the ambient temperature is lower than 0 ℃, the exhaust temperature of the compressor is even higher than 130 ℃, the exhaust temperature of the compressor is too high, so that the lubricating oil becomes thin, the lubricating condition is deteriorated, and even the phenomena of carbonization of the lubricating oil, cylinder pulling and the like are caused. Therefore, the common air source heat pump cannot normally operate below 0 ℃.
In order to improve the heating efficiency of the air source heat pump and solve the problems of high compression ratio and high exhaust temperature of the traditional air source heat pump caused by too low outdoor environment temperature, an enhanced vapor injection technology is provided. The enhanced vapor injection technology adopts an economizer cycle design, and solves the problems of high compression ratio and high exhaust temperature by the principle of quasi-two-stage compression intercooling, so that the air source heat pump can still normally operate under the working condition of the lowest temperature of-25 ℃ in the outdoor environment. The control core of the enhanced vapor injection technology is that the exhaust temperature of a compressor is stabilized within an ideal target range by adjusting the flow of a refrigerant at an air injection port of the compressor, so that the stability of system operation and comprehensive energy efficiency are improved.
The theoretical formula of the exhaust temperature in the prior art is as follows: exhaust temperature = exhaust superheat + saturated condensing temperature (converted from high pressure).
Because the linear relation between the high-pressure of the system and the outlet water temperature is consistent, the saturated condensing temperature can be converted by the outlet water temperature instead of the exhaust temperature;
the above formula can therefore be equivalent to: exhaust temperature = exhaust superheat degree + effluent temperature;
in the existing scheme, exhaust superheat degree is replaced by heating temperature difference, heating temperature difference is used as an adjustable parameter, and 35 ℃ is defaulted. At the moment, the control scheme realizes that the exhaust temperature is continuously changed along with the continuous change of the outlet water temperature, so that the stable operation of the system under different working conditions is ensured.
However, with the continuous research on ultra-low temperature air source heat pump systems, it is found that the same exhaust superheat degree is controlled under different working conditions, and the system energy efficiency cannot be exerted to the maximum extent, that is, the exhaust superheat degree should be continuously changed along with the change of the operation working conditions, so that the system energy efficiency maximization under each working condition can be realized.
Disclosure of Invention
The invention provides an enhanced vapor injection air source heat pump system and a dynamic exhaust superheat degree control method, which can solve the problems that the same exhaust superheat degree is controlled under different working conditions in the prior art, the system energy efficiency cannot be exerted to the maximum extent, and the exhaust superheat degree is not constantly changed along with the change of the operating working conditions.
In order to solve the above problems, in a first aspect, the invention provides an enhanced vapor injection air source heat pump system, which includes a water-side heat exchanger and an ambient temperature acquisition device, wherein a water outlet temperature probe is arranged at a water outlet of the water-side heat exchanger;
and acquiring the outlet water temperature through the outlet water temperature probe, and acquiring the ambient temperature through the ambient temperature acquiring device.
The system also comprises a compressor, a four-way valve, an air measuring heat exchanger, an economizer and a liquid storage device;
the fluorine inlet of the water side heat exchanger is connected to the first oil port of the four-way valve, the second oil port of the four-way valve is connected to one end of the air side heat exchanger, the other end of the air side heat exchanger is connected to the first interface and the second interface of the economizer, the third interface of the economizer is connected to one end of the liquid accumulator, the other end of the liquid accumulator is connected to the fluorine inlet of the water side heat exchanger, the interface of the compressor is connected to the fourth interface of the economizer, and the air suction port and the air exhaust port of the compressor are respectively connected to the third oil port and the fourth oil port of the four-way valve.
The device also comprises an air suction pressure probe, a low-pressure switch, a gas-liquid separator and an air suction temperature probe;
one end of the gas-liquid separator is connected with the air suction port of the compressor, the other end of the gas-liquid separator is connected with the third oil port of the four-way valve, the air suction pressure probe and the low-pressure switch are connected between the air suction port of the compressor and the gas-liquid separator, and the air suction temperature probe is connected between the third oil port of the four-way valve and the gas-liquid separator.
The system also comprises an exhaust temperature probe and a high-voltage switch which are connected between the exhaust port of the compressor and the fourth oil port of the four-way valve.
The device also comprises a fin temperature probe, a dry filter, a main circuit electronic expansion valve and an auxiliary circuit electronic expansion valve;
the other end of the air side heat exchanger is connected to one end of the drying filter, the fin temperature probe is connected between the air side heat exchanger and the drying filter, the other end of the drying filter is connected to one end of the main path electronic expansion valve, the other end of the main path electronic expansion valve is connected to one end of the auxiliary path electronic expansion valve and the first interface of the economizer, and the other end of the auxiliary path electronic expansion valve is connected to the second interface of the economizer.
In a second aspect, a dynamic exhaust superheat degree control method is provided, which is implemented by using the enhanced vapor injection air source heat pump system as described above, and the dynamic exhaust superheat degree control method includes:
acquiring the outlet water temperature through the outlet water temperature probe, and acquiring the ambient temperature through the ambient temperature acquisition device;
acquiring dynamic exhaust superheat degree according to the environment temperature;
and acquiring and correcting the exhaust temperature according to the outlet water temperature and the exhaust superheat degree.
The acquiring of the dynamic exhaust superheat degree according to the environment temperature comprises the following steps:
y＝Ax 2 +Bx+C
wherein y is the exhaust superheat degree, x is the ambient temperature, and A, B and C are preset parameters.
The acquiring of the dynamic exhaust superheat degree according to the environment temperature further comprises:
setting a range of the ambient temperature;
judging whether the acquired environmental temperature is out of the range;
if the acquired environmental temperature is not outside the range, acquiring the exhaust superheat degree according to the acquired environmental temperature;
if the acquired environment temperature is out of the range, continuously judging that the acquired environment temperature is greater than the upper limit value of the range or the acquired environment temperature is less than the lower limit value of the range;
if the acquired environmental temperature is larger than the upper limit value of the range, acquiring the exhaust superheat degree according to the upper limit value;
and if the acquired environment temperature is smaller than the lower limit value of the range, acquiring the exhaust superheat degree according to the lower limit value.
The step of obtaining and correcting the exhaust temperature according to the outlet water temperature and the exhaust superheat degree comprises the following steps:
judging whether the outlet water temperature is smaller than a preset temperature threshold value or not;
if not, then
z＝y+D+F
Wherein z is the exhaust temperature, D is the effluent temperature, and F is a preset correction formula;
if so, then
z＝y+D。
The correction formula is as follows:
F＝(D-G)×H/I
and G is the preset temperature threshold, and H/I indicates that the H DEG C correction is generated when the water temperature changes by I DEG C.
The beneficial effects of the invention are:
the energy efficiency of the ultralow-temperature air source heat pump system under different working conditions of environment temperature and water temperature is optimal in a dynamic control mode of the system exhaust superheat degree. The enhanced vapor injection control of the ultralow-temperature air source heat pump system is upgraded from the traditional fixed exhaust superheat control mode to the dynamic exhaust superheat control mode, so that the heating capacity and the comprehensive energy efficiency of a unit are effectively improved.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
Fig. 1 is a schematic structural diagram of an enhanced vapor injection air source heat pump system provided by the present invention.
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.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on those shown in the drawings, merely for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention. Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.
In the present invention, the word "exemplary" is used to mean "serving as an example, instance, or illustration. Any embodiment described herein as "exemplary" is not necessarily to be construed as preferred or advantageous over other embodiments. The following description is presented to enable any person skilled in the art to make and use the invention. In the following description, details are set forth for the purpose of explanation. It will be apparent to one of ordinary skill in the art that the present invention may be practiced without these specific details. In other instances, well-known structures and processes are not shown in detail to avoid obscuring the description of the invention with unnecessary detail. Thus, the present invention is not intended to be limited to the embodiments shown, but is to be accorded the widest scope consistent with the principles and features disclosed herein.
Referring to fig. 1, fig. 1 is a schematic structural diagram of an enhanced vapor injection air source heat pump system provided by the present invention, which includes a water-side heat exchanger 3, an ambient temperature obtaining device (not shown), a compressor 1, a four-way valve 2, an air-side heat exchanger 9, an economizer 5, a liquid reservoir 4, an air suction pressure probe 17, a low-pressure switch 18, a gas-liquid separator 10, an air suction temperature probe 16, an exhaust temperature probe 11, a high-pressure switch 12, a fin temperature probe 15, a drying filter 8, a main-path electronic expansion valve 6, and an auxiliary-path electronic expansion valve 7.
In this embodiment, the enhanced vapor injection air source heat pump system is also called an economizer 5 (or flash evaporator, intercooler) system, and the cycle schematic diagram is shown in fig. 1. The process comprises the following steps: high-temperature and high-pressure refrigerant gas is condensed and cooled through the water side heat exchanger 3, heat released by condensation is transferred to tail-end circulating water, and the circulating water absorbing heat and raising temperature is used for heating. The condensed refrigerant loop is divided into two paths: the main loop is a refrigeration loop, and the auxiliary loop is a jet loop. In fig. 1, the flow of the refrigerant during heating is indicated by solid arrows, the flow of the refrigerant during cooling is indicated by dashed arrows, and the flow of the refrigerant during power failure of the four-way valve 2 is indicated by the direction of the working condition of the cooling water.
An outlet temperature probe 14 is arranged at the water outlet of the water side heat exchanger 3; the outlet water temperature is obtained by the outlet water temperature probe 14, and the ambient temperature is obtained by the ambient temperature obtaining device (not shown), obviously, the ambient temperature obtaining device is disposed in the environment where the enhanced vapor injection air source heat pump system is located. A fluorine inlet of the water-side heat exchanger 3 is connected to a first oil port of the four-way valve 2, a second oil port of the four-way valve 2 is connected to one end of the wind-side heat exchanger 9, the other end of the wind-side heat exchanger 9 is connected to a first interface and a second interface of the economizer 5, a third interface of the economizer 5 is connected to one end of a liquid accumulator 4, the other end of the liquid accumulator 4 is connected to a fluorine outlet of the water-side heat exchanger 3, an interface of the compressor 1 is connected to a fourth interface of the economizer 5, and an air suction port and an air exhaust port of the compressor 1 are respectively connected to the third oil port and the fourth oil port of the four-way valve 2. One end of the gas-liquid separator 10 is connected to the suction port of the compressor 1, the other end of the gas-liquid separator 10 is connected to the third oil port of the four-way valve 2, the suction pressure probe 17 and the low-pressure switch 18 are connected between the suction port of the compressor 1 and the gas-liquid separator 10, and the suction temperature probe 16 is connected between the third oil port of the four-way valve 2 and the gas-liquid separator 10. An exhaust temperature probe 11 and a high-pressure switch 12 are connected between the exhaust port of the compressor 1 and the fourth port of the four-way valve 2. The other end of the wind side heat exchanger 9 is connected to one end of the dry filter 8, the fin temperature probe 15 is connected between the wind side heat exchanger 9 and the dry filter 8, the other end of the dry filter 8 is connected to one end of the main circuit electronic expansion valve 6, the other end of the main circuit electronic expansion valve 6 is connected to one end of the auxiliary circuit electronic expansion valve 7 and the first interface of the economizer 5, and the other end of the auxiliary circuit electronic expansion valve 7 is connected to the second interface of the economizer 5.
In this embodiment, the refrigerant liquid in the auxiliary circuit is depressurized to a certain intermediate pressure by the auxiliary electronic expansion valve 7 and then becomes a medium pressure gas-liquid mixture, and the medium pressure gas-liquid mixture and the refrigerant liquid from the main circuit with higher temperature undergo heat exchange in the economizer 5, and the refrigerant liquid in the auxiliary circuit absorbs heat and becomes gas, and the gas is supplemented into the working cavity of the compressor 1 through the auxiliary air inlet of the compressor 1; meanwhile, the refrigerant in the main circuit is supercooled, and the supercooled refrigerant passes through the main circuit electronic expansion valve 6 and then enters the air-side heat exchanger 9.
In the wind side heat exchanger 9, the refrigerant of the main loop absorbs the heat in the low temperature environment and turns into low-pressure gas to enter the suction cavity of the compressor 1, after a section of internal compression, the refrigerant of the main loop and the refrigerant of the auxiliary loop are mixed in the working cavity of the compressor 1, then the two parts of refrigerants are mixed while being compressed along with the rotation of the working cavity until the mixing process is finished, and the mixed refrigerant is further compressed by the compressor 1 and then discharged out of the compressor 1 to form a complete closed cycle.
The enhanced vapor injection compressor 1 adopts a two-stage throttling middle vapor injection technology, and adopts an economizer 5 to carry out gas-liquid separation, thereby realizing the enhanced vapor injection effect. The air displacement of the compressor 1 is improved by mixing and cooling compression and air injection at medium and low pressure and then normal compression at high pressure, so that the purpose of improving the heating capacity in a low-temperature environment is achieved.
The functional description of each component above is as follows:
the dynamic exhaust superheat degree control method is realized by adopting the enhanced vapor injection air source heat pump system, and comprises the following steps of S1-S3:
s1, acquiring an outlet water temperature through the outlet water temperature probe 14, and acquiring an environment temperature through the environment temperature acquisition device;
s2, acquiring dynamic exhaust superheat degree according to the environment temperature; step S2 includes steps S21-S27:
s21, calculating the exhaust superheat degree according to the following formula:
y＝Ax 2 +Bx+C
wherein y is the exhaust superheat degree, x is the ambient temperature, and A, B and C are preset parameters.
In this embodiment, the theoretical formula of the exhaust temperature in the prior art is: exhaust temperature = exhaust superheat degree + saturated condensing temperature (converted from high pressure).
Because the linear relation between the high-pressure of the system and the outlet water temperature is consistent, the saturated condensing temperature can be converted from the outlet water temperature instead of the exhaust temperature;
the above theoretical formula can therefore be equivalent to: exhaust temperature = exhaust superheat degree + effluent temperature;
generally, the exhaust superheat value of the compressor 1 is considered to be stable and unchanged, but with the continuous research on an ultralow-temperature air source heat pump system, the fact that the same exhaust superheat value is controlled under different working conditions is found, the system energy efficiency cannot be exerted to the maximum extent, namely the exhaust superheat value is required to be changed continuously along with the change of the operation working conditions, and thus the system energy efficiency under each working condition can be maximized. Practice proves that the auxiliary loop of the enhanced vapor injection system is subjected to flow control, the exhaust superheat degree of the compressor 1 can be effectively controlled within an ideal range, and therefore a control scheme of the dynamic exhaust superheat degree becomes a key element for improving comprehensive energy efficiency of the system under various working conditions.
According to the above formula: exhaust temperature = exhaust superheat + effluent temperature, defining the exhaust superheat value as "y", and by data accumulation and statistics of a large number of experiments, the conclusion is drawn: the "y value" has the above function relation with the change of the ambient temperature. A. B and C are adjustable parameters respectively, default A =0.01, B = -0.75 and C =40, and parameter adjustment is carried out on A, B and C according to different unit configurations.
And S22, setting the range of the ambient temperature.
In this embodiment, the ambient temperature is calculated by rounding down in the range of-30 ℃ to 17 ℃.
S23, judging whether the acquired environment temperature is out of the range;
s24, if the obtained environment temperature is not out of the range, obtaining the exhaust superheat degree according to the obtained environment temperature;
s25, if the acquired environment temperature is out of the range, continuously judging that the acquired environment temperature is greater than the upper limit value of the range or the acquired environment temperature is less than the lower limit value of the range;
s26, if the acquired environment temperature is larger than the upper limit value of the range, acquiring the exhaust superheat degree according to the upper limit value;
and S27, if the acquired environment temperature is smaller than the lower limit value of the range, acquiring the exhaust superheat degree according to the lower limit value.
In this example, the ambient temperature was below-30 ℃ as calculated at-30 ℃ and above 17 ℃ as calculated at 17 ℃.
And S3, acquiring and correcting the exhaust temperature according to the outlet water temperature and the exhaust superheat degree. Step S3 includes steps S31-S33:
s31, judging whether the outlet water temperature is smaller than a preset temperature threshold value;
in this embodiment, the temperature threshold is set to 30 ℃.
S32, if not, then
z＝y+D+F
Wherein z is the exhaust temperature, D is the effluent temperature, and F is a preset correction formula; wherein, the correction formula is:
F＝(D-G)×H/I
and G is the preset temperature threshold, and H/I indicates that the H DEG C correction is generated when the water temperature changes by I DEG C.
In this embodiment, when the outlet water temperature is equal to or greater than 30 ℃, the exhaust temperature = Y + the outlet water temperature + (outlet water temperature-30) × 2/5, where "2/5" indicates that 2 degrees of correction is generated every time the outlet water temperature changes by 5 degrees.
S33, if yes, then
z＝y+D。
In this embodiment, when the effluent temperature is less than 30 ℃, the exhaust temperature = Y + the effluent temperature; the target upper limit value of the exhaust temperature is 116.0 ℃.
Therefore, the control mode of the exhaust superheat degree is dynamic control, and the dynamic exhaust superheat degree control logic is realized.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention.
Claims (2)
1. A dynamic exhaust superheat degree control method is realized by adopting an enhanced vapor injection air source heat pump system, wherein the enhanced vapor injection air source heat pump system comprises a water-side heat exchanger and an ambient temperature acquisition device, and a water outlet temperature probe is arranged at a water outlet of the water-side heat exchanger;
acquiring the outlet water temperature through the outlet water temperature probe, and acquiring the ambient temperature through the ambient temperature acquisition device;
the enhanced vapor injection air source heat pump system also comprises a compressor, a four-way valve, an air measuring heat exchanger, an economizer and a liquid storage device;
a fluorine inlet of the water side heat exchanger is connected to a first oil port of the four-way valve, a second oil port of the four-way valve is connected to one end of the air side heat exchanger, the other end of the air side heat exchanger is connected to a first interface and a second interface of the economizer, a third interface of the economizer is connected to one end of a liquid accumulator, the other end of the liquid accumulator is connected to a fluorine outlet of the water side heat exchanger, an interface of the compressor is connected to a fourth interface of the economizer, and an air suction port and an air exhaust port of the compressor are respectively connected to the third oil port and the fourth oil port of the four-way valve;
the enhanced vapor injection air source heat pump system also comprises an air suction pressure probe, a low-pressure switch, a gas-liquid separator and an air suction temperature probe;
one end of the gas-liquid separator is connected to the air suction port of the compressor, the other end of the gas-liquid separator is connected to the third oil port of the four-way valve, the air suction pressure probe and the low-pressure switch are connected between the air suction port of the compressor and the gas-liquid separator, and the air suction temperature probe is connected between the third oil port of the four-way valve and the gas-liquid separator;
the enhanced vapor injection air source heat pump system also comprises an exhaust temperature probe and a high-pressure switch which are connected between an exhaust port of the compressor and a fourth oil port of the four-way valve;
the enhanced vapor injection air source heat pump system also comprises a fin temperature probe, a drying filter, a main electronic expansion valve and an auxiliary electronic expansion valve;
the other end of the air side heat exchanger is connected to one end of the drying filter, the fin temperature probe is connected between the air side heat exchanger and the drying filter, the other end of the drying filter is connected to one end of the main circuit electronic expansion valve, the other end of the main circuit electronic expansion valve is connected to one end of the auxiliary circuit electronic expansion valve and a first interface of the economizer, and the other end of the auxiliary circuit electronic expansion valve is connected to a second interface of the economizer;
the method is characterized by comprising the following steps:
acquiring the outlet water temperature through an outlet water temperature probe, and acquiring the ambient temperature through an ambient temperature acquisition device;
acquiring dynamic exhaust superheat degree according to the ambient temperature; the acquiring of the dynamic exhaust superheat degree according to the environment temperature comprises the following steps:
y＝Ax 2 +Bx+C
wherein y is the exhaust superheat degree, x is the ambient temperature, and A, B and C are preset parameters;
acquiring and correcting the exhaust temperature according to the outlet water temperature and the exhaust superheat degree; the step of obtaining and correcting the exhaust temperature according to the outlet water temperature and the exhaust superheat degree comprises the following steps:
judging whether the outlet water temperature is smaller than a preset temperature threshold value or not;
if not, then
z＝y+D+F
Wherein z is the exhaust temperature, D is the effluent temperature, and F is a preset correction formula;
if so, then
z＝y+D
The correction formula is as follows:
F＝(D-G)×H/I
and G is the preset temperature threshold, and H/I indicates that the correction of H DEG C is generated when the water temperature changes by I DEG C.
2. The dynamic exhaust superheat degree control method according to claim 1, wherein the obtaining of the dynamic exhaust superheat degree in accordance with the ambient temperature further comprises:
setting a range of the ambient temperature;
judging whether the acquired environmental temperature is out of the range or not;
if the acquired environmental temperature is not outside the range, acquiring the exhaust superheat degree according to the acquired environmental temperature;
if the acquired environment temperature is out of the range, continuously judging that the acquired environment temperature is greater than the upper limit value of the range or the acquired environment temperature is less than the lower limit value of the range;
if the obtained ambient temperature is greater than the upper limit value of the range, obtaining the exhaust superheat degree according to the upper limit value;
and if the acquired environmental temperature is smaller than the lower limit value of the range, acquiring the exhaust superheat degree according to the lower limit value.
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