CN104896750A - A trans-critical CO2 heat pump water heater pressure control method and system - Google Patents
A trans-critical CO2 heat pump water heater pressure control method and system Download PDFInfo
- Publication number
- CN104896750A CN104896750A CN201510168668.1A CN201510168668A CN104896750A CN 104896750 A CN104896750 A CN 104896750A CN 201510168668 A CN201510168668 A CN 201510168668A CN 104896750 A CN104896750 A CN 104896750A
- Authority
- CN
- China
- Prior art keywords
- opt
- pressure
- water
- expulsion
- fan
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
Abstract
The invention relates to a trans-critical CO2 heat pump water heater pressure control method and system. The method comprises the steps of collecting the outlet temperature tgc of an air cooling device, an evaporation temperature te of an evaporator, a discharge pressure P of a compressor, and a water outlet temperature Tw1 of a water tank; calculating the optimal discharge pressure Popt according to tgc and te; judging whether the difference between P and Popt is within an permissible range and maintaining the current operation state if the difference is within the permissible range and performing the step S4 if the difference is not within the permissible range; by judging the difference between Tw1 and the preset water outlet temperature Tw0 and an evaporator fan rotating speed V, adjusting the water inlet flow of the air cooling device, the evaporator fan rotating speed and the electronic expansion valve opening degree according to a preferential order until the difference between P and Popt is within the permissible range. Through the preferential adjustment order, the difference between P and Popt is within the permissible range and the performance coefficient (COP) of the system reaches the maximum, so that the system stability is improved, the service life of the electronic valve is prolonged and the system reliability is improved.
Description
Technical field
The present invention relates to the controller field of heat pump water-heating machine, particularly a kind of Trans-critical cycle CO
2the control method of heat pump water-heating machine pressure and system.
Background technology
Due to environmental protection natural refrigerant CO
2nontoxic with it, to ozone layer without destruction, appearance effect can not be produced, and the advantage such as its good macroscopic property, again be subject to people's attention.Simultaneously due to Trans-critical cycle CO
2the exothermic process of circulation is in supercritical region, and there is the characteristics such as temperature glide in exothermic process, is specially adapted to heat pump water heater system.Carbon dioxide is used for Trans-critical cycle heat pump water-heating machine system, has the advantage that conventional heat pump does not possess: environmental protection and stronger hot water preparing ability.Hot water preparing ability is by force because it has obvious temperature glide being in heat release under postcritical HTHP, and this feature is just being applicable to water to be heated to higher problem.
CO 2 trans-critical heat pump hot water machine is in different operating mode running, because system input power and system heating capacity have different change curves with the pressure at expulsion of compressor, therefore the pressure at expulsion that existence one is optimum, make the coefficient of performance of CO 2 trans-critical heat pump water-heating machine system (COP) there is a maximum, now corresponding pressure is referred to as optimum pressure at expulsion P
opt.For CO 2 trans-critical heat pump water-heating machine system, the optimum pressure at expulsion P in certainty annuity running
opt, by detecting Compressor Discharge Pressure P, compare Compressor Discharge Pressure P and optimum pressure at expulsion P
optbetween relation, control the coefficient of performance (COP) of heat pump water-heating machine system, the control method of prior art, by judging Compressor Discharge Pressure P and optimum pressure at expulsion P
optbetween relation, directly control and regulate electronic expansion valve opening, the less stable of system, the frequent aperture regulating electric expansion valve, affects the service life of electronic valve and the reliability of system.
Summary of the invention
The invention provides a kind of Trans-critical cycle CO
2the control method of heat pump water-heating machine pressure and system, to solve above-mentioned control method and system directly controls and regulates electronic expansion valve opening, the technical problem that process is comparatively complicated.
In order to solve the problems of the technologies described above, the invention provides a kind of Trans-critical cycle CO
2the control method of heat pump water-heating machine pressure,
Comprise the following steps:
Step S1, gathers the air cooler outlet temperature t of water-heating machine system
gc, evaporator evaporation temperature t
e, Compressor Discharge Pressure P and water tank leaving water temperature T
w1;
Step S2, according to described air cooler outlet temperature t
gcwith described evaporator evaporation temperature t
ecalculate the optimum pressure at expulsion P of compressor
opt;
Step S3, judges described Compressor Discharge Pressure P and described optimum pressure at expulsion P
optdifference whether in allowed band, if it is keep current operating conditions; Otherwise perform step S4;
Step S4, judges the water tank leaving water temperature T gathered
w1with the water tank leaving water temperature T preset
w0absolute difference whether super preset difference value △ T, if so, then regulate air cooler flow of inlet water, return step S1; Otherwise perform step S5;
Step S5, judges the rotation speed of fan V whether V in condition and range of evaporimeter
l≤ V≤V
h, if so, then according to Compressor Discharge Pressure P and described optimum pressure at expulsion P
optregulate the rotation speed of fan of evaporimeter, return step S1; Otherwise perform step S6;
Step S6, according to Compressor Discharge Pressure P and described optimum pressure at expulsion P
optregulate the aperture of electric expansion valve;
Step S7, repeated execution of steps 1 to step 6, until realize described Compressor Discharge Pressure P and described optimum pressure at expulsion P
optdifference in allowed band.
The invention has the beneficial effects as follows: by direct-detection water tank leaving water temperature T
w1, then by water tank leaving water temperature T
w1with default leaving water temperature T
w0compare, confirm described leaving water temperature T
w1with default leaving water temperature T
w0difference whether exceed △ T in allowed band, if exceed △ T in allowed band, then connect and regulate air cooler flow of inlet water; Because heat pump final purpose is exactly to realize required hot water, after adjustment air cooler flow of inlet water, other parameters also can change accordingly, and air cooler flow of inlet water has changed, then air cooler outlet Temperature of Working can change, air cooler outlet temperature t
gc, evaporator evaporation temperature t
e, Compressor Discharge Pressure P can correspondingly change, and then by air cooler outlet temperature t
gcwith evaporator evaporation temperature t
ecalculate the optimum pressure at expulsion P of compressor
opt, confirm Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference in allowed band; If Primary regulation can not reach requirement, then system automatically again circulates and regulates air cooler flow of inlet water, makes Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference in allowed band, make the coefficient of performance of system (COP) reach comparatively large, this regulative mode is more direct, efficiently.Meanwhile, if described leaving water temperature T
w1with default leaving water temperature T
w0difference △ T in allowed band, the rotation speed of fan V of evaporimeter meets V
l≤ V≤V
h, then directly regulate the rotation speed of fan of evaporimeter, the effect of adjustment can be reached comparatively rapidly; When the rotation speed of fan V of evaporimeter does not meet V
l≤ V≤V
htime, by directly regulating the aperture of electric expansion valve.The present invention is by regulating air cooler flow of inlet water, regulating the sequencing of the aperture of the rotation speed of fan of evaporimeter and adjustment electric expansion valve, the stability of raising system, reduce the frequency regulating electronic expansion valve opening, increase the service life of electronic valve and the reliability of system.
Further, optimum pressure at expulsion P described in step S2
optcomputing formula be:
P
opt＝(2.7686-0.0147×t
e)×t
gc+(0.346×t
e-8.851)
Wherein, t
gcfor air cooler outlet temperature, t
efor evaporator evaporation temperature.
The beneficial effect of above-mentioned further scheme is adopted to be: to pass through formula
P
opt=(2.7686-0.0147 × t
e) × t
gc+ (0.346 × t
e-8.851) P, calculated
optcomparatively accurate, it is also more accurate to make with the relatively result of Compressor Discharge Pressure P, guarantees that the coefficient of performance (COP) of critical carbon dioxide heat pump water-heating machine system is larger.
Further, the P of Compressor Discharge Pressure described in step S3 and described optimum pressure at expulsion P
optdifference allowed band meet following formula: 0.95*P
opt≤ P≤1.05*P
opt.
The beneficial effect of above-mentioned further scheme is adopted to be: less Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference range, make the coefficient of performance of critical carbon dioxide heat pump water-heating machine system (COP) reach maximum.
Further, the concrete operations of air cooler flow of inlet water are regulated to be in described step S4: to judge described water tank leaving water temperature T
w1with described default water tank leaving water temperature T
w0with the magnitude relationship of preset difference value △ T,
Work as T
w1-T
w0during>=△ T, increase described air cooler flow of inlet water; Work as T
w0-T
w1during>=△ T, reduce described air cooler flow of inlet water.
The beneficial effect of above-mentioned further scheme is adopted to be: to pass through T
w1and T
w0between size increase or reduce air cooler flow of inlet water, reach and more directly, efficiently regulate object.
Further, in step S5 according to Compressor Discharge Pressure P and described optimum pressure at expulsion P
optthe concrete operations of the rotation speed of fan of adjustment evaporimeter are:
Work as P>P
opttime, reduce evaporator fan rotating speed V; Work as P<P
opttime, increase evaporator fan rotating speed V.
The beneficial effect of above-mentioned further scheme is adopted to be: ∣ T
w1-T
w0∣≤△ T and V
l≤ V≤V
hcondition under, if Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference not in allowed band, by regulating evaporator fan rotating speed V, guarantee Trans-critical cycle CO
2the Compressor Discharge Pressure P ratio of heat pump water-heating machine pressure is easier to close to and reaches optimum pressure at expulsion P
opt, thus reach regulating effect, add the validity of system fading margin.
Further, step S6 is according to Compressor Discharge Pressure P and described optimum pressure at expulsion P
optthe concrete operations of the aperture of adjustment electric expansion valve are:
Work as P>P
opttime, utilize PID to control, increase described electronic expansion valve opening; Work as P<P
opttime, utilize PID to control, reduce described electronic expansion valve opening.
The beneficial effect of above-mentioned further scheme is adopted to be: by further regulating the aperture of electric expansion valve, regulating effect can be reached comparatively rapidly, making Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference in allowed band, reach the higher coefficient of performance (COP) value.
Further, described preset difference value △ T is 0.5 DEG C to 1.5 DEG C.
The beneficial effect of above-mentioned further scheme is adopted to be: the preset difference value △ T scope of 0.5 DEG C to 1.5 DEG C, can reach good regulable control effect.
Further, described preset difference value △ T is 1 DEG C.
The beneficial effect of above-mentioned further scheme is adopted to be: preset difference value △ T is 1 DEG C, can comparatively fast reach adjustment object, meanwhile, avoids the adjustment of too much number of times, makes user's experience best results.
Further, the rotation speed of fan V of evaporimeter described in step S4 whether V in condition and range
l≤ V≤V
h, minimum speed V
lfor 80% of evaporator fan rated speed, maximum speed V
hfor 120% of evaporator fan rated speed.
The beneficial effect of above-mentioned further scheme is adopted to be: the +/-20% of setting evaporator fan rated speed is as the limited field regulating evaporator fan rotating speed V, avoid in adjustment process, have influence on evaporator fan operating limit, reasonable regulating effect can be reached simultaneously.
The present invention also provides a kind of Trans-critical cycle CO
2the control system of heat pump water-heating machine pressure,
Comprise data acquisition module, computing module, the first judge module, the second judge module, discharge adjustment module, the 3rd judge module, rotation speed of fan adjustment module and electronic valve aperture adjustment module,
Described data acquisition module, for gathering the air cooler outlet temperature t of water-heating machine system
gc, evaporator evaporation temperature t
e, Compressor Discharge Pressure P and water tank leaving water temperature T
w1;
Described computing module, for according to described air cooler outlet temperature t
gcwith described evaporator evaporation temperature t
ecalculate the optimum pressure at expulsion P of compressor
opt;
Described first judge module, for judging described Compressor Discharge Pressure P and described optimum pressure at expulsion P
optdifference whether in allowed band, if it is keep current operating conditions; Otherwise call the second judge module;
Described second judge module, for judging the water tank leaving water temperature T gathered
w1with the water tank leaving water temperature T preset
w0absolute difference whether super preset difference value △ T, if so, then call discharge adjustment module; Otherwise call described 3rd judge module;
Described 3rd judge module, for judging the rotation speed of fan V whether V in condition and range of evaporimeter
l≤ V≤V
h, if so, then call described rotation speed of fan adjustment module; Otherwise call described electronic valve aperture adjustment module;
Described discharge adjustment module, for according to water tank leaving water temperature T
w1with the water tank leaving water temperature T preset
w0relation regulate solar term coolers flow of inlet water;
Described rotation speed of fan adjustment module, for regulating the rotation speed of fan of evaporimeter according to Compressor Discharge Pressure P and described optimum pressure at expulsion Popt;
Described electronic valve aperture adjustment module, for according to Compressor Discharge Pressure P and described optimum pressure at expulsion P
optregulate the aperture of electric expansion valve.
The beneficial effect of control system of the present invention is: the optimum pressure at expulsion P calculated by computing module
opt, judge module is by Compressor Discharge Pressure P and optimum pressure at expulsion P
optcompare, finally by control module according to leaving water temperature T
w1with default leaving water temperature T
w0relation regulate air cooler flow of inlet water, comparatively fast can make Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference reach in allowed band, make the coefficient of performance of system (COP) reach larger.
Accompanying drawing explanation
Fig. 1 is Trans-critical cycle CO of the present invention
2the process control chart of the embodiment one of the control method of heat pump water-heating machine pressure;
Fig. 2 is Trans-critical cycle CO of the present invention
2the process control chart of the embodiment two of the control method of heat pump water-heating machine pressure;
Fig. 3 is Trans-critical cycle CO of the present invention
2the structured flowchart of the control system of heat pump water-heating machine pressure.
Detailed description of the invention
Below in conjunction with drawings and Examples, the present invention is further illustrated.
Trans-critical cycle CO of the present invention
2the process control chart of the embodiment one of the control method of heat pump water-heating machine pressure, see Fig. 1, comprises the following steps.
Step S1, gathers the air cooler outlet temperature t of water-heating machine system
gc, evaporator evaporation temperature t
e, Compressor Discharge Pressure P and water tank leaving water temperature T
w1.
Step S2, according to air cooler outlet temperature t
gcwith evaporator evaporation temperature t
ecalculate the optimum pressure at expulsion P of compressor
opt.
Step S3, judges Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference whether in allowed band, if it is keep current operating conditions; Otherwise perform step S4.
Step S4, judges the water tank leaving water temperature T gathered
w1with the water tank leaving water temperature T preset
w0absolute difference whether super preset difference value △ T, if so, then regulate air cooler flow of inlet water, return step S1; Otherwise perform step S5.
Step S5, judges the rotation speed of fan V whether V in condition and range of evaporimeter
l≤ V≤V
h, if so, then according to Compressor Discharge Pressure P and described optimum pressure at expulsion P
optregulate the rotation speed of fan of evaporimeter, return step S1; Otherwise perform step S6.
Step S6, according to Compressor Discharge Pressure P and optimum pressure at expulsion P
optregulate the aperture of electric expansion valve.
Step S7, repeated execution of steps 1 to step 6, until realize Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference in allowed band.
By direct-detection water tank leaving water temperature T
w1, then by water tank leaving water temperature T
w1with default leaving water temperature T
w0compare, confirm described leaving water temperature T
w1with default leaving water temperature T
w0difference whether exceed △ T in allowed band, if exceed △ T in allowed band, then connect and regulate air cooler flow of inlet water; Because heat pump final purpose is exactly to realize required hot water, after adjustment air cooler flow of inlet water, other parameters also can change accordingly, and air cooler flow of inlet water has changed, then air cooler outlet Temperature of Working can change, air cooler outlet temperature t
gc, evaporator evaporation temperature t
e, Compressor Discharge Pressure P can correspondingly change, and then by air cooler outlet temperature t
gcwith evaporator evaporation temperature t
ecalculate the optimum pressure at expulsion P of compressor
opt, confirm Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference in allowed band; If Primary regulation can not reach requirement, then system automatically again circulates and regulates air cooler flow of inlet water, makes Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference in allowed band, make the coefficient of performance of system (COP) reach comparatively large, this regulative mode is more direct, efficiently.
Meanwhile, if described leaving water temperature T
w1with default leaving water temperature T
w0difference △ T in allowed band, the rotation speed of fan V of evaporimeter meets V
l≤ V≤V
h, then directly regulate the rotation speed of fan of evaporimeter, the effect of adjustment can be reached comparatively rapidly; When the rotation speed of fan V of evaporimeter does not meet V
l≤ V≤V
htime, by directly regulating the aperture of electric expansion valve.The present invention, by regulating air cooler flow of inlet water, regulating the sequencing of the aperture of the rotation speed of fan of evaporimeter and adjustment electric expansion valve, guarantees high efficiency and the substantivity of mediation process, improves the validity of control system simultaneously.
Trans-critical cycle CO of the present invention
2the process control chart of the embodiment two of the control method of heat pump water-heating machine pressure, see Fig. 2, comprises step:
Step S1, gathers the air cooler outlet temperature t of water-heating machine system
gc, evaporator evaporation temperature t
e, Compressor Discharge Pressure P and water tank leaving water temperature T
w1.
Step S2, according to air cooler outlet temperature t
gcwith evaporator evaporation temperature t
ecalculate the optimum pressure at expulsion P of compressor
opt; Optimum pressure at expulsion P
optcomputing formula be:
P
opt＝(2.7686-0.0147×t
e)×t
gc+(0.346×t
e-8.851)。
Step S3, judges Compressor Discharge Pressure P and described optimum pressure at expulsion P
optdifference whether in allowed band, if it is keep current operating conditions; Otherwise perform step S4; Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference in allowed band be whether: 0.95*P
opt≤ P≤1.05*P
opt.
Step S4, judges the water tank leaving water temperature T gathered
w1with the water tank leaving water temperature T preset
w0absolute difference whether super preset difference value △ T, if so, then regulate air cooler flow of inlet water, return step S1; Otherwise perform step S5.
The concrete operations of air cooler flow of inlet water are regulated to be in step S4: to judge water tank leaving water temperature T
w1with the water tank leaving water temperature T preset
w0with the magnitude relationship of preset difference value △ T, work as T
w1-T
w0during>=△ T, increase air cooler flow of inlet water; Work as T
w0-T
w1during>=△ T, reduce air cooler flow of inlet water.
Step S5, judges the rotation speed of fan V whether V in condition and range of evaporimeter
l≤ V≤V
h, if so, then according to Compressor Discharge Pressure P and optimum pressure at expulsion P
optregulate the rotation speed of fan of evaporimeter, return step S1; Otherwise perform step S6.
Step S6, according to Compressor Discharge Pressure P and optimum pressure at expulsion P
optregulate the aperture of electric expansion valve; Step S6 is according to Compressor Discharge Pressure P and optimum pressure at expulsion P
optthe concrete operations of the aperture of adjustment electric expansion valve are: work as P>P
opttime, utilize PID to control, increase electronic expansion valve opening; Work as P<P
opttime, utilize PID to control, reduce electronic expansion valve opening.
Step S7, repeated execution of steps 1 to step 6, until realize described Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference in allowed band.
By regulating air cooler flow of inlet water, regulating concrete behaviour's step of the aperture of the rotation speed of fan of evaporimeter and adjustment electric expansion valve, achieve adjustment process fast and efficiently, ensure that the reliability and stability of system.
Trans-critical cycle CO of the present invention
2the structured flowchart of the control system of heat pump water-heating machine pressure, see Fig. 3, comprises data acquisition module 10, computing module 20, first judge module 03, second judge module 40, discharge adjustment module 50, the 3rd judge module 60, rotation speed of fan adjustment module 70 and electronic valve aperture adjustment module 80.
Data acquisition module 10, for gathering the air cooler outlet temperature t of water-heating machine system
gc, evaporator evaporation temperature t
e, Compressor Discharge Pressure P and water tank leaving water temperature T
w1.
Computing module 20, for according to described air cooler outlet temperature t
gcwith described evaporator evaporation temperature t
ecalculate the optimum pressure at expulsion P of compressor
opt.
First judge module 30, for judging Compressor Discharge Pressure P and described optimum pressure at expulsion P
optdifference whether in allowed band, if it is keep current operating conditions; Otherwise call the second judge module 40.
Second judge module 40, for judging the water tank leaving water temperature T gathered
w1with the water tank leaving water temperature T preset
w0absolute difference whether super preset difference value △ T, if so, then call discharge adjustment module 50; Otherwise call the 3rd judge module 60.
3rd judge module 60, for judging the rotation speed of fan V whether V in condition and range of evaporimeter
l≤ V≤V
h, if so, then call rotation speed of fan adjustment module 70; Otherwise call electronic valve aperture adjustment module 80.
Discharge adjustment module 50, for according to water tank leaving water temperature T
w1with the water tank leaving water temperature T preset
w0relation regulate solar term coolers flow of inlet water.
Rotation speed of fan adjustment module 70, for regulating the rotation speed of fan of evaporimeter according to Compressor Discharge Pressure P and optimum pressure at expulsion Popt.
Electronic valve aperture adjustment module 80, for regulating the aperture of electric expansion valve according to Compressor Discharge Pressure P and optimum pressure at expulsion Popt.
Control system provided by the invention, the optimum pressure at expulsion P calculated by computing module
opt, judge module is by Compressor Discharge Pressure P and optimum pressure at expulsion P
optcompare, finally by discharge adjustment module according to leaving water temperature T
w1with default leaving water temperature T
w0relation regulate air cooler flow of inlet water, comparatively fast can make Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference reach in allowed band, make the coefficient of performance of system (COP) reach larger.
By rotation speed of fan adjustment module according to evaporator fan rotating speed V, guarantee Trans-critical cycle CO
2the Compressor Discharge Pressure P ratio of heat pump water-heating machine pressure is easier to close to and reaches optimum pressure at expulsion P
opt, thus reach regulating effect, add the validity of system fading margin.
Regulate electronic expansion valve opening can reach regulating effect comparatively rapidly by electronic valve aperture adjustment module, reach the higher coefficient of performance (COP) value, there is higher stability.
In first embodiment of the present invention, systems axiol-ogy is to the air cooler outlet temperature t of water-heating machine system
gc=34 DEG C, evaporator evaporation temperature t
e=10 DEG C, Compressor Discharge Pressure P=76.25bar, water tank leaving water temperature T
w1=85 DEG C, preset leaving water temperature T
w0=82 DEG C; Air cooler flow of inlet water be 3.05 cubes per hour, evaporator fan rotating speed V=2500 turns, the minimum speed limits value V of evaporator fan
l=2200 turns, the maximum speed limits value V of evaporator fan
h=3000 turns; Leaving water temperature T
w1with default leaving water temperature T
w0the Systematical control value △ T=1 DEG C of difference.
By formula P
opt=(2.7686-0.0147 × t
e) × t
gc+ (0.346 × t
e-8.851) P is calculated
opt=(2.7686-0.0147 × 10) × 34+ (0.346 × 10-8.851)=83.743bar, P=76.25bar, P
opt* 0.95=83.743*0.95=79.556, P<P
opt* 0.95, T
w1-T
w0=85 DEG C-82 DEG C=3 DEG C > △ T=1 DEG C, increase air cooler flow of inlet water, be adjusted to 3.2 cubes per hour, now, t
gc=35 DEG C, evaporator evaporation temperature t
e=10 DEG C, Compressor Discharge Pressure P=84.35bar, P
opt=86.365bar, Compressor Discharge Pressure P and optimum pressure at expulsion P
optdifference in allowed band, 0.95*P
opt≤ P≤1.05*P
opt, system completes adjustment.
In a second embodiment of the present invention, systems axiol-ogy is to the air cooler outlet temperature t of water-heating machine system
gc=28 DEG C, evaporator evaporation temperature t
e=4.5 DEG C, Compressor Discharge Pressure P=77.45bar, water tank leaving water temperature T
w1=83 DEG C, preset leaving water temperature T
w0=82.5 DEG C; Air cooler flow of inlet water be 2.8 cubes per hour, evaporator fan rotating speed V=2500 turns, the minimum speed limits value V of evaporator fan
l=2200 turns, the maximum speed limits value V of evaporator fan
h=3000 turns, electronic expansion valve opening 250 step; The Systematical control value △ T=1 DEG C of leaving water temperature Tw1 and default leaving water temperature Tw0 difference.After completing adjustment by control method of the present invention, its parameter is respectively: t
gcbe 30 degree, t
ewhen being 5 degree, P
optfor 73.73bar, now rotation speed of fan 2400 turns, electronic expansion valve opening 300 step, discharge 2.8 cubes is per hour, and the coefficient of performance (COP) of its system reaches 3.9.
Above to Trans-critical cycle CO of the present invention
2control method and the system of heat pump water-heating machine pressure are described in detail, and apply specific case herein and set forth principle of the present invention and embodiment.The explanation of above embodiment just understands core concept of the present invention for helping; Meanwhile, for one of ordinary skill in the art, according to thought of the present invention, all will change in specific embodiments and applications, in sum, this description should not be construed as limitation of the present invention.
Claims (10)
1. a Trans-critical cycle CO
2the control method of heat pump water-heating machine pressure, is characterized in that, comprises the following steps:
Step S1, gathers the air cooler outlet temperature t of water-heating machine system
gc, evaporator evaporation temperature t
e, Compressor Discharge Pressure P and water tank leaving water temperature T
w1;
Step S2, according to described air cooler outlet temperature t
gcwith described evaporator evaporation temperature t
ecalculate the optimum pressure at expulsion P of compressor
opt;
Step S3, judges described Compressor Discharge Pressure P and described optimum pressure at expulsion P
optdifference whether in allowed band, if it is keep current operating conditions; Otherwise perform step S4;
Step S4, judges the water tank leaving water temperature T gathered
w1with the water tank leaving water temperature T preset
w0absolute difference whether super preset difference value △ T, if so, then regulate air cooler flow of inlet water, return step S1; Otherwise perform step S5;
Step S5, judges the rotation speed of fan V whether V in condition and range of evaporimeter
l≤ V≤V
h, if so, then according to Compressor Discharge Pressure P and described optimum pressure at expulsion P
optregulate the rotation speed of fan of evaporimeter, return step S1; Otherwise perform step S6;
Step S6, according to Compressor Discharge Pressure P and described optimum pressure at expulsion P
optregulate the aperture of electric expansion valve;
Step S7, repeated execution of steps 1 to step 6, until realize described Compressor Discharge Pressure P and described optimum pressure at expulsion P
optdifference in allowed band.
2. Trans-critical cycle CO according to claim 1
2the control method of heat pump water-heating machine pressure, is characterized in that, optimum pressure at expulsion P described in step S2
optcomputing formula be:
P
opt＝(2.7686-0.0147×t
e)×t
gc+(0.346×t
e-8.851)
Wherein, t
gcfor air cooler outlet temperature, t
efor evaporator evaporation temperature.
3. Trans-critical cycle CO according to claim 1 and 2
2the control method of heat pump water-heating machine pressure, is characterized in that, the P of Compressor Discharge Pressure described in step S3 and described optimum pressure at expulsion P
optdifference allowed band meet following formula: 0.95*P
opt≤ P≤1.05*P
opt.
4. Trans-critical cycle CO according to claim 1 and 2
2the control method of heat pump water-heating machine pressure, is characterized in that, regulates the concrete operations of air cooler flow of inlet water to be in described step S4: judge described water tank leaving water temperature T
w1with described default water tank leaving water temperature T
w0with the magnitude relationship of preset difference value △ T,
As Tw1-Tw0 >=△ T, increase described air cooler flow of inlet water; As Tw0-Tw1 >=△ T, reduce described air cooler flow of inlet water.
5. Trans-critical cycle CO according to claim 1 and 2
2the control method of heat pump water-heating machine pressure, is characterized in that, according to Compressor Discharge Pressure P and described optimum pressure at expulsion P in step S5
optthe concrete operations of the rotation speed of fan of adjustment evaporimeter are:
Work as P>P
opttime, reduce evaporator fan rotating speed V; Work as P<P
opttime, increase evaporator fan rotating speed V.
6. Trans-critical cycle CO according to claim 5
2the control method of heat pump water-heating machine pressure, is characterized in that, step S6 is according to Compressor Discharge Pressure P and described optimum pressure at expulsion P
optthe concrete operations of the aperture of adjustment electric expansion valve are:
Work as P>P
opttime, utilize PID to control, increase described electronic expansion valve opening; Work as P<P
opttime, utilize PID to control, reduce described electronic expansion valve opening.
7. Trans-critical cycle CO according to claim 1
2the control method of heat pump water-heating machine pressure, is characterized in that, described preset difference value △ T is 0.5 DEG C to 1.5 DEG C.
8. Trans-critical cycle CO according to claim 7
2the control method of heat pump water-heating machine pressure, is characterized in that, described preset difference value △ T is 1 DEG C.
9. Trans-critical cycle CO according to claim 1
2the control method of heat pump water-heating machine pressure, is characterized in that, whether the rotation speed of fan V of evaporimeter described in step S4 V in condition and range
l≤ V≤V
h, minimum speed V
lfor 80% of evaporator fan rated speed, maximum speed V
hfor 120% of evaporator fan rated speed.
10. a Trans-critical cycle CO
2the control system of heat pump water-heating machine pressure, is characterized in that, comprises data acquisition module, computing module, the first judge module, the second judge module, discharge adjustment module, the 3rd judge module, rotation speed of fan adjustment module and electronic valve aperture adjustment module,
Described data acquisition module, for gathering the air cooler outlet temperature t of water-heating machine system
gc, evaporator evaporation temperature t
e, Compressor Discharge Pressure P and water tank leaving water temperature T
w1;
Described computing module, for according to described air cooler outlet temperature t
gcwith described evaporator evaporation temperature t
ecalculate the optimum pressure at expulsion P of compressor
opt;
Described first judge module, for judging described Compressor Discharge Pressure P and described optimum pressure at expulsion P
optdifference whether in allowed band, if it is keep current operating conditions; Otherwise call the second judge module;
Described second judge module, for judging the water tank leaving water temperature T gathered
w1with the water tank leaving water temperature T preset
w0absolute difference whether super preset difference value △ T, if so, then call discharge adjustment module; Otherwise call described 3rd judge module;
Described 3rd judge module, for judging the rotation speed of fan V whether V in condition and range of evaporimeter
l≤ V≤V
h, if so, then call described rotation speed of fan adjustment module; Otherwise call described electronic valve aperture adjustment module;
Described discharge adjustment module, for according to water tank leaving water temperature T
w1with the water tank leaving water temperature T preset
w0relation regulate solar term coolers flow of inlet water;
Described rotation speed of fan adjustment module, for according to Compressor Discharge Pressure P and described optimum pressure at expulsion P
optregulate the rotation speed of fan of evaporimeter;
Described electronic valve aperture adjustment module, for according to Compressor Discharge Pressure P and described optimum pressure at expulsion P
optregulate the aperture of electric expansion valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510168668.1A CN104896750A (en) | 2015-04-10 | 2015-04-10 | A trans-critical CO2 heat pump water heater pressure control method and system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510168668.1A CN104896750A (en) | 2015-04-10 | 2015-04-10 | A trans-critical CO2 heat pump water heater pressure control method and system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104896750A true CN104896750A (en) | 2015-09-09 |
Family
ID=54029574
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510168668.1A Pending CN104896750A (en) | 2015-04-10 | 2015-04-10 | A trans-critical CO2 heat pump water heater pressure control method and system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104896750A (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105698454A (en) * | 2016-03-11 | 2016-06-22 | 西安交通大学 | Control method for optimum pressure of transcritical CO2 heat pump |
| CN107933872A (en) * | 2017-11-07 | 2018-04-20 | 珠海格力电器股份有限公司 | Electronic expansion valve control method and device for ship water chilling unit |
| CN108800562A (en) * | 2018-06-20 | 2018-11-13 | 青岛海信日立空调系统有限公司 | Heat-production control method, the apparatus and system of hot water heat pump system |
| CN108844361A (en) * | 2018-09-13 | 2018-11-20 | 珠海格力电器股份有限公司 | Dehumidification control method, device and equipment for dehumidification dryer and dehumidification dryer |
| CN109579377A (en) * | 2018-12-05 | 2019-04-05 | 西安交通大学 | A kind of CO 2 trans-critical heat pump system electronic expansion valve control method |
| CN109764570A (en) * | 2018-12-29 | 2019-05-17 | 西安交通大学 | A kind of control method of the CO 2 trans-critical heat pump system discharge pressure based on neuroid |
| CN111006425A (en) * | 2019-11-28 | 2020-04-14 | 江苏苏净集团有限公司 | Multi-parallel carbon dioxide heat pump control method based on target load control |
| CN111520907A (en) * | 2020-03-27 | 2020-08-11 | 青岛海信日立空调系统有限公司 | Heat pump water heater and control method thereof |
| CN114234450A (en) * | 2021-12-24 | 2022-03-25 | 山东雅士股份有限公司 | Variable-frequency CO2Water heater unit and control method thereof |
| CN114274729A (en) * | 2021-12-16 | 2022-04-05 | 东风汽车集团股份有限公司 | CO2Control method of heat pump system |
| CN115183508A (en) * | 2022-07-07 | 2022-10-14 | 百尔制冷(无锡)有限公司 | Novel trans-critical carbon dioxide exhaust pressure control method and control system thereof |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006132875A (en) * | 2004-11-08 | 2006-05-25 | Denso Corp | Heat pump type heating device |
| CN102313358A (en) * | 2010-07-01 | 2012-01-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Control method for exhaust pressure of carbon-dioxide heat-pump water heater |
| CN102652245A (en) * | 2009-12-09 | 2012-08-29 | 夏普株式会社 | Air conditioner, method for controlling aperture of expansion valve, and computer readable storage medium for storing program for controlling aperture of expansion valve |
| EP2543939A2 (en) * | 2006-12-28 | 2013-01-09 | Daikin Industries, Ltd. | Refrigeration apparatus |
| CN103148653A (en) * | 2013-03-20 | 2013-06-12 | 江苏苏净集团有限公司 | Temperature-range-based control method of carbon dioxide heat pump system |
-
2015
- 2015-04-10 CN CN201510168668.1A patent/CN104896750A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006132875A (en) * | 2004-11-08 | 2006-05-25 | Denso Corp | Heat pump type heating device |
| EP2543939A2 (en) * | 2006-12-28 | 2013-01-09 | Daikin Industries, Ltd. | Refrigeration apparatus |
| CN102652245A (en) * | 2009-12-09 | 2012-08-29 | 夏普株式会社 | Air conditioner, method for controlling aperture of expansion valve, and computer readable storage medium for storing program for controlling aperture of expansion valve |
| CN102313358A (en) * | 2010-07-01 | 2012-01-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Control method for exhaust pressure of carbon-dioxide heat-pump water heater |
| CN103148653A (en) * | 2013-03-20 | 2013-06-12 | 江苏苏净集团有限公司 | Temperature-range-based control method of carbon dioxide heat pump system |
Non-Patent Citations (1)
| Title |
|---|
| 彦启森等: "《空气调节用制冷技术（第三版）》", 31 January 2005 * |
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105698454B (en) * | 2016-03-11 | 2017-12-08 | 西安交通大学 | A kind of control method of transcritical CO_2 heat pump optimum pressure |
| CN105698454A (en) * | 2016-03-11 | 2016-06-22 | 西安交通大学 | Control method for optimum pressure of transcritical CO2 heat pump |
| CN107933872B (en) * | 2017-11-07 | 2020-04-24 | 珠海格力电器股份有限公司 | Electronic expansion valve control method and device for ship water chilling unit |
| CN107933872A (en) * | 2017-11-07 | 2018-04-20 | 珠海格力电器股份有限公司 | Electronic expansion valve control method and device for ship water chilling unit |
| CN108800562A (en) * | 2018-06-20 | 2018-11-13 | 青岛海信日立空调系统有限公司 | Heat-production control method, the apparatus and system of hot water heat pump system |
| CN108800562B (en) * | 2018-06-20 | 2020-06-02 | 青岛海信日立空调系统有限公司 | Heating control method, device and system of hot water heat pump system |
| CN108844361A (en) * | 2018-09-13 | 2018-11-20 | 珠海格力电器股份有限公司 | Dehumidification control method, device and equipment for dehumidification dryer and dehumidification dryer |
| CN109579377A (en) * | 2018-12-05 | 2019-04-05 | 西安交通大学 | A kind of CO 2 trans-critical heat pump system electronic expansion valve control method |
| CN109764570A (en) * | 2018-12-29 | 2019-05-17 | 西安交通大学 | A kind of control method of the CO 2 trans-critical heat pump system discharge pressure based on neuroid |
| CN111006425A (en) * | 2019-11-28 | 2020-04-14 | 江苏苏净集团有限公司 | Multi-parallel carbon dioxide heat pump control method based on target load control |
| CN111006425B (en) * | 2019-11-28 | 2021-10-29 | 江苏苏净集团有限公司 | Multi-parallel carbon dioxide heat pump control method based on target load control |
| CN111520907A (en) * | 2020-03-27 | 2020-08-11 | 青岛海信日立空调系统有限公司 | Heat pump water heater and control method thereof |
| CN114274729A (en) * | 2021-12-16 | 2022-04-05 | 东风汽车集团股份有限公司 | CO2Control method of heat pump system |
| CN114274729B (en) * | 2021-12-16 | 2023-09-05 | 东风汽车集团股份有限公司 | CO 2 Control method of heat pump system |
| CN114234450A (en) * | 2021-12-24 | 2022-03-25 | 山东雅士股份有限公司 | Variable-frequency CO2Water heater unit and control method thereof |
| CN114234450B (en) * | 2021-12-24 | 2023-09-08 | 山东雅士股份有限公司 | Variable frequency CO 2 Control method of water heater unit |
| CN115183508A (en) * | 2022-07-07 | 2022-10-14 | 百尔制冷(无锡)有限公司 | Novel trans-critical carbon dioxide exhaust pressure control method and control system thereof |
| CN115183508B (en) * | 2022-07-07 | 2023-11-17 | 百尔制冷(无锡)有限公司 | Novel transcritical carbon dioxide exhaust pressure control method and control system thereof |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104896750A (en) | A trans-critical CO2 heat pump water heater pressure control method and system | |
| CN101539151B (en) | Method and device for controlling inverter compressor | |
| CN109945454B (en) | Air conditioning system compressor control method, air conditioning controller and air conditioner | |
| CN101809372B (en) | Compressor operation control device and air conditioner using same | |
| JP5951397B2 (en) | Air conditioner | |
| CN107062556A (en) | A kind of control method of refrigerant flow of module water dispenser | |
| CN105571068A (en) | Operation control method and device for air conditioner | |
| KR20070115741A (en) | Heat pump hot water supply floor heating apparatus | |
| EP2244036A1 (en) | Refrigeration cycle device | |
| KR20100114022A (en) | Heat-pump hot-water supply apparatus | |
| CN104776633A (en) | Hybrid power refrigeration system and control method thereof | |
| CN107842897A (en) | CO2 floor heatings heat pump realizes confession, the efficient transcritical operation heat exchange enclosed circulation heating water system of the small temperature difference of backwater | |
| JP6289440B2 (en) | Heat pump water heater | |
| JP5476835B2 (en) | Air conditioning system | |
| CN102364265A (en) | Variable flow circulation type heat pump water heater | |
| JP2010236816A (en) | Heat pump type air conditioner and method of controlling heat pump type air conditioner | |
| JP7295779B2 (en) | Heat pump hot water heating system | |
| CN204574599U (en) | Hybrid power refrigeration system | |
| JP5677198B2 (en) | Air cooling heat pump chiller | |
| JP6533717B2 (en) | Hot water supply system | |
| JP2004340535A (en) | Heat pump water heater | |
| CN108317588A (en) | Compound heating device, supply control method for heat and its device | |
| JP5478403B2 (en) | Heat pump water heater | |
| JP2005140439A (en) | Heat pump water heater | |
| CN201344588Y (en) | Heat pump hot water unit capable of reliably supplying water |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20150909 |