CN113432336A - 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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- CN113432336A CN113432336A CN202110452489.6A CN202110452489A CN113432336A CN 113432336 A CN113432336 A CN 113432336A CN 202110452489 A CN202110452489 A CN 202110452489A CN 113432336 A CN113432336 A CN 113432336A
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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 29
- 238000012937 correction Methods 0.000 claims description 9
- 238000001035 drying Methods 0.000 claims description 7
- 230000007613 environmental effect Effects 0.000 claims description 7
- 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
- 229920006395 saturated elastomer Polymers 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000009833 condensation Methods 0.000 description 3
- 230000005494 condensation Effects 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 238000011160 research Methods 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 238000003763 carbonization Methods 0.000 description 1
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- 239000000498 cooling water Substances 0.000 description 1
- 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
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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
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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
- F25B41/30—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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- Engineering & Computer Science (AREA)
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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 invention has the beneficial effects that: 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 traditional 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. Especially 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, the lubricating oil becomes thin, the lubricating condition is deteriorated, and the phenomena of carbonization of the lubricating oil, cylinder pulling and the like are even 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 air injection enthalpy increasing technology adopts an economizer cycle design, and solves the problems of high compression ratio and high exhaust temperature through the principle of quasi-secondary 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 discharge temperature of the compressor is stabilized in an ideal target range by adjusting the flow of the refrigerant at the air injection port of the compressor, so that the stability of the system operation and the comprehensive energy efficiency are improved.
The theoretical formula of the exhaust temperature in the prior art is as follows: the exhaust temperature is exhaust superheat degree + saturated condensation temperature (obtained by conversion according to 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 formula can therefore be equivalent to: the exhaust temperature is exhaust superheat degree plus water outlet temperature;
in the existing scheme, exhaust superheat degree is replaced by heating temperature difference, heating temperature difference is 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 and deep 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, namely, the exhaust superheat degree is required to be continuously changed along with the change of the operating working conditions, so that the system energy efficiency under each working condition can be maximized.
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 problem 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, namely the exhaust superheat degree does not change continuously 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 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 system also comprises an exhaust temperature probe and a high-pressure 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 ambient 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＝Ax2+Bx+C
wherein y is the exhaust superheat degree, x is the ambient temperature, and A, B, C is a preset parameter.
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 larger than the upper limit value of the range or the acquired environment temperature is smaller than the lower limit value of the range;
if the obtained environmental temperature is larger than the upper limit value of the range, obtaining 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 correction of H DEG C is generated when the water temperature changes by I DEG C.
The invention has the beneficial effects that:
the energy efficiency of the ultralow temperature air source heat pump system is optimal under different working conditions of environment temperature and water temperature by a dynamic control mode of the system exhaust superheat degree. The air injection enthalpy gain control of the ultralow-temperature air source heat pump system is upgraded from a traditional fixed exhaust superheat degree control mode to a dynamic exhaust superheat degree 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 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 that other drawings can be obtained according to the drawings without creative efforts.
Fig. 1 is a schematic structural diagram of an enhanced vapor injection air source heat pump system provided by the invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying 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 inventive exercise, are within the 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", and the like, indicate orientations or positional relationships based on those shown in the drawings, and are used merely for convenience of description and for simplicity of description, and do not indicate or imply that the device or element being 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, features defined as "first" and "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 disclosure, 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 view of a structure 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-voltage switch 18, a gas-liquid separator 10, an air suction temperature probe 16, an exhaust temperature probe 11, a high-voltage 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 referred to as 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. The fluorine inlet of the water side heat exchanger 3 is connected to the first oil port of the four-way valve 2, the second oil port of the four-way valve 2 is connected to one end of the air side heat exchanger 9, the other end of the air side heat exchanger 9 is connected to the first interface and the second interface of the economizer 5, the third interface of the economizer 5 is connected to one end of the liquid storage device 4, the other end of the liquid storage device 4 is connected to the fluorine outlet of the water side heat exchanger 3, the interface of the compressor 1 is connected to the fourth interface of the economizer 5, and the air suction port and the 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 exchanges heat with the refrigerant liquid with a higher temperature from the main circuit in the economizer 5, and the refrigerant liquid in the auxiliary circuit absorbs heat and becomes gas, and the gas is supplied to 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, the low-pressure gas enters the air suction cavity of the compressor 1, after being compressed for a period of time, 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 the refrigerants are mixed while being compressed along with the rotation of the working cavity until the mixing process is finished, the mixed refrigerant is further compressed by the compressor 1 and then is discharged out of the compressor 1, and a complete closed cycle is formed.
The enhanced vapor injection compressor 1 adopts a two-stage throttling middle vapor injection technology and an economizer 5 for gas-liquid separation, so that the enhanced vapor injection effect is realized. The compressor 1 is compressed and mixed cooled by air injection at medium and low pressure, and then normally compressed at high pressure, so that the air displacement of the compressor is increased, and the purpose of improving the heating capacity in a low-temperature environment is achieved.
The function of each component is described in the following table:
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 the outlet water temperature through the outlet water temperature probe 14, and acquiring the 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＝Ax2+Bx+C
wherein y is the exhaust superheat degree, x is the ambient temperature, and A, B, C is a preset parameter.
In this embodiment, the theoretical formula of the exhaust temperature in the prior art is: the exhaust temperature is equal to the exhaust superheat degree + saturated condensation temperature (obtained by conversion according to the 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: the exhaust temperature is exhaust superheat degree plus water outlet temperature;
generally, the exhaust superheat value of the compressor 1 is considered to be stable and unchanged, but with the continuous and deep research on the 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 therefore 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 the control scheme of the dynamic exhaust superheat degree becomes a key element for improving the comprehensive energy efficiency of the system under various working conditions.
According to the above formula: the exhaust gas temperature is exhaust superheat degree + water outlet temperature, the exhaust superheat degree value is defined as y, and a conclusion is obtained through data accumulation and statistics of a large number of experiments: the "y value" has the above functional relationship with the change of the ambient temperature. A. B, C are adjustable parameters, default A is 0.01, default B is-0.75, default C is 40, and A, B, C adjusts the parameters according to different unit configurations.
And S22, setting the range of the environment temperature.
In this example, 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 outside 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 larger than the upper limit value of the range or the acquired environment temperature is smaller than the lower limit value of the range;
s26, if the obtained environment temperature is larger than the upper limit value of the range, obtaining 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 the present 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 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.
In this embodiment, when the outlet water temperature is equal to or higher than 30 ℃, the exhaust temperature is Y + outlet water temperature + (outlet water temperature-30) × 2/5, where "2/5" indicates that 2 degrees of correction is generated every 5 degrees of change in the outlet water temperature.
S33, if yes, then
z＝y+D。
In this embodiment, when the effluent temperature is less than 30 ℃, the exhaust temperature is Y + the effluent temperature; the target upper limit of the exhaust temperature is 116.0 ℃.
Therefore, the exhaust superheat degree control mode 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 (10)
1. An enhanced vapor injection air source heat pump system is characterized by comprising 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.
2. The enhanced vapor injection air source heat pump system of claim 1, further comprising a compressor, a four-way valve, an anemometer heat exchanger, an economizer and a reservoir;
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 outlet 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.
3. The enhanced vapor injection air source heat pump system according to claim 2, further comprising 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.
4. The enhanced vapor injection air source heat pump system of claim 2, further comprising an exhaust temperature probe and a high pressure switch connected between an exhaust port of the compressor and a fourth port of the four-way valve.
5. The enhanced vapor injection air source heat pump system according to claim 2, further comprising a fin temperature probe, a dry 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 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.
6. A dynamic exhaust superheat degree control method is realized by adopting the enhanced vapor injection air source heat pump system as claimed in claim 1, and 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;
and acquiring and correcting the exhaust temperature according to the outlet water temperature and the exhaust superheat degree.
7. The dynamic exhaust superheat control method of claim 6 wherein said deriving a dynamic exhaust superheat as a function of said ambient temperature comprises:
y＝Ax2+Bx+C
wherein y is the exhaust superheat degree, x is the ambient temperature, and A, B, C is a preset parameter.
8. The dynamic exhaust superheat degree control method according to claim 7, 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;
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 environment temperature is smaller than the lower limit value of the range, acquiring the exhaust superheat degree according to the lower limit value.
9. The dynamic exhaust superheat degree control method according to claim 7, wherein the obtaining and correcting the exhaust temperature according to the leaving water temperature and the exhaust superheat degree comprises:
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。
10. The dynamic exhaust superheat degree control method according to claim 9, wherein the modified equation is:
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.
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