CN217088476U - VFD and AHP combined operation system for severe cold area - Google Patents
VFD and AHP combined operation system for severe cold area Download PDFInfo
- Publication number
- CN217088476U CN217088476U CN202220441736.2U CN202220441736U CN217088476U CN 217088476 U CN217088476 U CN 217088476U CN 202220441736 U CN202220441736 U CN 202220441736U CN 217088476 U CN217088476 U CN 217088476U
- Authority
- CN
- China
- Prior art keywords
- air
- pipeline
- heat pump
- source heat
- branch
- 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.)
- Active
Links
Images
Landscapes
- Air Conditioning Control Device (AREA)
Abstract
The utility model provides a VFD and AHP combined operation system for severe cold areas, which comprises a frequency converter, wherein the frequency converter is communicated with a first air inlet pipeline and a first air outlet pipeline, and the first air outlet pipeline is communicated with and connected with an adjustable first air outlet branch and a second air outlet branch; the air source heat pump unit is provided with a second air inlet pipeline and a second air outlet pipeline in a communicated manner, the second air inlet pipeline is provided with a first air volume adjusting device, and the first air outlet branch is communicated and connected with the second air inlet pipeline between the first air volume adjusting device and the air source heat pump unit; and the air source heat pump unit is also communicated with a water outlet pipeline and a water return pipeline. Through the utility model discloses, can simplify warm logical system form to can preheat the use as air source heat pump set's air inlet with the operation calorific capacity of converter, improve air source heat pump set's the efficiency ratio that heats.
Description
Technical Field
The utility model relates to a severe cold district VFD and AHP combined operation field, especially a VFD and AHP combined operation system for severe cold district.
Background
When a frequency converter (VFD) runs, the heating value is about 1 to 5 percent of rated power, an air-cooled high-voltage frequency converter is mostly adopted by a condensate pump of a thermal power plant, the rated capacity is usually more than 2000kV & A, and therefore, the indoor cooling load in summer between the frequency converters of the centralized control building is usually not lower than 100 kW. The working environment requirements of the air-cooled high-voltage frequency converter are different due to different manufacturers, the temperature is mostly in the range of minus 10 ℃ and 40 ℃, the relative humidity range of air is 20 percent and 90 percent, and the service life of the frequency converter is greatly influenced by the operating environment beyond the range.
Although the service life of the air source heat pump unit (AHP) is slightly influenced by the operating environment, the operating temperature range is wide and can be from-25 ℃ to 45 ℃, but the influence of the change of the environmental temperature on the energy efficiency ratio of the unit is large. Taking a heating working condition as an example, under the condition of ensuring that the temperature of outlet water is not changed at 40 ℃, one unit can operate at the COP value of 4.1 under the condition that the temperature of outdoor dry bulb is 15 ℃, and when the temperature of outdoor dry bulb is reduced to-20 ℃, the COP value is less than 1.8.
Therefore, the energy efficiency ratio of the air source heat pump unit is improved properly under the heating condition, or the operating environment temperature of the air source heat pump unit is reduced properly under the cooling condition, so that the electric energy consumption is reduced, and the aim of reducing CO2 emission is fulfilled.
The centralized control building is an electrical building in a thermal power plant, is generally arranged near a steam turbine room, is provided with important electrical equipment rooms such as a storage battery room, a power distribution device room, a frequency converter room, a relay room and a direct current screen room, and is also provided with production and life auxiliary rooms such as an equipment overhaul room, an engineer station, an on-duty room, a conference room, a restaurant and an office. The large-scale electrical equipment arranged in the centralized control building needs to release heat outwards during operation, and from the design angle of heating ventilation specialties, when the summer cold load of the electrical equipment rooms is calculated, not only the heat transmitted into the rooms through the enclosure structure but also the heat productivity of the electrical equipment need to be considered fully in order to ensure the normal operation of the equipment. In addition, in order to meet the thermal comfort requirements of workers in different seasons, an air source heat pump unit is usually arranged to serve production and living auxiliary rooms in a centralized control building.
In the ventilation design among the frequency converters, in the aspect of air exhaust, the conventional design scheme among the frequency converters is to arrange a switching valve on an air exhaust pipeline of a frequency converter body so as to realize the function of keeping the heat dissipation of equipment indoors in winter and directly exhausting the equipment outdoors in summer. In fact, even in winter, the heat load between the frequency converters is far less than the operation heat productivity of the frequency converter body, so that most of the body exhaust air of the frequency converter needs to be led outdoors in most cases even in severe cold areas, and the part participating in the recirculation only accounts for less than 10 percent of the total exhaust air of the frequency converter body; in the aspect of air inlet, because the temperature and humidity requirements of the frequency converter on the working environment need to set an air processor, outdoor fresh air is preheated in winter (in severe cold areas), and cooled in summer (for some areas with small temperature difference of outdoor dry and wet balls, the outdoor fresh air also needs to be subjected to dehumidification processing). The processed fresh air can be directly connected with an air inlet of the body of the frequency converter through a fresh air pipeline (scheme 1); or the air can be directly sent into the room without a pipeline, and the indoor air between the frequency converters is sucked when the frequency converters run (scheme 2).
In the aspect of air conditioner design between frequency converters, when the ventilation scheme 1 is adopted between frequency converters, the air exhaust temperature of the frequency converter body is generally used for performing feedback control and regulation on the output of the compressor of the air processor. An air conditioner is additionally arranged between the frequency converters and is used for bearing cold loads caused by heat transfer of the enclosure structure, illumination heat dissipation, latent heat generated in various moisture dissipation processes and the like; when the scheme 2 is adopted, the air handler needs to simultaneously bear equipment heat dissipation, building enclosure heat transfer, illumination heat dissipation capacity, latent heat generated in various moisture dissipation processes and the like of the frequency converter, and the output of the compressor is generally adjusted in a combined manner by using the indoor temperature and the exhaust temperature of the frequency converter body. If the indoor temperature is taken as a priority regulated parameter, when the frequency converter operates with higher output, an ultra-temperature area is possibly present in the cabinet body of the frequency converter; if the temperature of the discharged air of the frequency converter body is taken as a priority regulated parameter, when the frequency converter operates with high output, the phenomenon that the indoor temperature is lower than the design requirement possibly occurs, thereby causing the waste of energy.
In the aspect of heating design among frequency converters, when a ventilation scheme 1 is adopted among the frequency converters, the heating capacity of the air processor is often subjected to feedback regulation by using the cabinet body air inlet temperature of the frequency converters, and meanwhile, the water flow of a hot water radiator is subjected to feedback regulation by using the indoor temperature; when ventilation scheme 2 is selected for use, the air inlet temperature of the cabinet body of the frequency converter is the indoor temperature between the frequency converters, and the parameter can carry out feedback regulation on the hot water flow of the radiator and the heating capacity of the air processor.
In the aspects of air conditioning and heating design of production and living auxiliary rooms, the summer cold and transition season heat demand of the production and living auxiliary rooms of the centralized control building is usually met by adopting an air source heat pump. Under the background of double carbon, most thermal power plants in China need to reduce the total consumption of heating hot water in plant areas so as to realize the capacity expansion of the total external heat supply amount. Therefore, most thermal power plants are performing clean modification on the heating system of the buildings in the plant, and the air source heat pump unit is used to cover the heating requirement. In cold regions, the attenuation degree of the air source heat pump unit is still within an acceptable range, and in some severe cold regions, the heating energy efficiency ratio of the air source heat pump unit is close to the power consumption level of electric boiler heating, so that the economical efficiency is poor.
Therefore, a comprehensive operation system which can be applied to a severe cold area and has a simplified heating and ventilation design and can improve the heating efficiency ratio of an air source heat pump unit is needed.
SUMMERY OF THE UTILITY MODEL
The utility model provides a technical problem provide a VFD and AHP combined operation system for severe cold district promptly, simplify the warm system form that leads to can preheat the use as air source heat pump set's air inlet with the operation calorific capacity of converter, improve air source heat pump set's the efficiency ratio that heats.
The utility model discloses the technical means who adopts as follows:
a VFD and AHP combined operation system for severe cold regions comprises a frequency converter, wherein the frequency converter is communicated with a first air inlet pipeline and a first air outlet pipeline, and the first air outlet pipeline is communicated and connected with an adjustable first air outlet branch and a second air outlet branch; the air source heat pump unit is provided with a second air inlet pipeline and a second air outlet pipeline in a communicated manner, the second air inlet pipeline is provided with a first air volume adjusting device, and the first air outlet branch is communicated and connected with the second air inlet pipeline between the first air volume adjusting device and the air source heat pump unit; and the air source heat pump unit is also communicated with a water outlet pipeline and a water return pipeline, one ends of the water outlet pipeline and the water return pipeline, which are far away from the air source heat pump unit, are respectively connected with an air treatment device, a fan coil and a hot water radiator, and the air treatment device is arranged in the first air inlet pipeline.
Preferably, the first air outlet branch and the second air outlet branch are respectively provided with a second air volume adjusting device and a third air volume adjusting device; and the second air outlet branch and the second air outlet pipeline are communicated and connected with an air exhaust vertical shaft.
Preferably, one end of the first air inlet pipeline, which is far away from the frequency converter, is provided with a first air blower, and the air treatment device is positioned in the first air inlet pipeline between the first air blower and the frequency converter; and a second air feeder is arranged at one end of the second air inlet pipeline, which is far away from the air source heat pump unit, and the first air volume adjusting device is positioned between the second air feeder and the air source heat pump unit.
Preferably, a first temperature measuring device and a second temperature measuring device are respectively arranged in a first air inlet pipeline between the air treatment device and the first blower and a first air inlet pipeline between the air treatment device and the frequency converter, and a third temperature measuring device and a fourth temperature measuring device are respectively arranged in a second air inlet pipeline between the first air volume regulating device and the second blower and a second air inlet pipeline between the first air volume regulating device and the air source heat pump unit; a fifth temperature measuring device is arranged in the first air outlet pipeline, and a sixth temperature measuring device is arranged in the second air outlet pipeline; and a humidity measuring device is also arranged in the first air inlet pipeline between the air treatment device and the frequency converter.
Preferably, the water outlet pipeline is communicated and connected with the air treatment device through a first water outlet branch, the water return pipeline is communicated and connected with the air treatment device through a first water return branch, and the first water outlet branch and the first water return branch are respectively provided with a first flow regulating device and a second flow regulating device.
Preferably, the water outlet pipeline is also communicated and connected with a second water outlet branch and a third water outlet branch, and the water return pipeline is also communicated and connected with a second water return branch and a third water return branch; one ends of the second water outlet branch and the second water return branch, which are far away from the air source heat pump unit, are connected with the fan coil; one ends of the third water outlet branch and the third water return branch, which are far away from the air source heat pump unit, are connected with a hot water radiator; a third flow regulating device and a fourth flow regulating device are respectively arranged on the second water outlet branch and the second water return branch, and a fifth flow regulating device and a sixth flow regulating device are respectively arranged on the third water outlet branch and the third water return branch; and a seventh temperature measuring device is arranged outside the fan coil, and an eighth temperature measuring device is arranged outside the hot water radiator.
A control and regulation method of a VFD and AHP combined operation system for severe cold areas at least comprises a summer working condition: air source heat pump set refrigeration, the converter heat extraction, fan coil opens, and the hot water radiator is closed, wherein: the opening degrees of a second air volume adjusting device arranged on the first air outlet branch, a fifth flow adjusting device arranged on a third water outlet branch between the hot water radiator and the air source heat pump unit and a sixth flow adjusting device arranged on a third water return branch are 0; the opening degrees of a third air volume adjusting device arranged on a second air outlet branch, a fourth flow adjusting device arranged on a second water return branch between the fan coil and the air source heat pump unit and a second flow adjusting device arranged on a first water return branch between the air treatment device and the air source heat pump unit are 1; the opening degree of the first air volume adjusting device and the rotating speed of a second air feeder arranged at one end of the second air inlet pipeline, which is far away from the air source heat pump unit, are adjusted by the output feedback of the air source heat pump unit; the output of the air source heat pump unit is jointly fed back and regulated by a third flow regulating device arranged on a second water outlet branch between the fan coil and the air source heat pump unit and the opening degree of a first flow regulating device arranged on a first water outlet branch between the air treatment device and the air source heat pump unit, and the priority of the feedback regulation of the first flow regulating device and the priority of the feedback regulation of the third flow regulating device are the same; the opening degree of the third flow regulating device is regulated by temperature feedback measured by a seventh temperature measuring device arranged outside the fan coil; the opening degree of the first flow regulating device is jointly fed back and regulated by the humidity measured by a humidity measuring device arranged in a first air inlet pipeline between the air processing device and the frequency converter and the temperature measured by a fifth temperature measuring device arranged in the first air outlet pipeline, and the priority of the feedback regulation of the humidity measuring device and the fifth temperature measuring device is the same; the rotating speed of a first air feeder arranged at one end of the first air inlet pipeline, which is far away from the frequency converter, is regulated by temperature feedback measured by a fifth temperature measuring device arranged on the first air outlet pipeline.
Preferably, the method also comprises a transition season condition: air source heat pump set heats, and the converter heat extraction, fan coil open, and hot water radiator opens, wherein: the opening degrees of the first flow regulating device and the second flow regulating device are 0; the opening degrees of the fourth flow regulating device and the sixth flow regulating device are 1; the opening degree of the third air volume adjusting device is jointly fed back and adjusted by the opening degree of the second air volume adjusting device and the rotating speed of the first air blower, and the priority of the feedback adjustment of the second air volume adjusting device and the priority of the feedback adjustment of the first air blower are the same; the rotating speed of the first air feeder is regulated by the temperature feedback measured by the fifth temperature measuring device; the opening degrees of the first air volume adjusting device and the second air volume adjusting device and the rotating speed of the second blower are all regulated by the output feedback of the air source heat pump unit, wherein the priority of the signal output of the opening degree increase of the second air volume adjusting device, the opening degree decrease of the first air volume adjusting device and the rotating speed decrease of the second blower is higher than the priority of the signal output of the opening degree decrease of the second air volume adjusting device, the opening degree increase of the first air volume adjusting device and the rotating speed increase of the second blower; the output of the air source heat pump unit is jointly fed back and regulated by the opening degrees of the third flow regulating device and the fifth flow regulating device, and the feedback regulation priorities of the third flow regulating device and the fifth flow regulating device are the same; the opening degree of the third flow regulating device is regulated by the temperature feedback measured by the seventh temperature measuring device; the opening degree of the fifth flow regulating device is regulated by the temperature feedback measured by the eighth temperature measuring device.
Preferably, the winter condition is also included: air source heat pump set heats, and the converter heat extraction, the fan pipeline is opened, and hot water radiator opens, wherein: the opening degrees of the second flow regulating device, the fourth flow regulating device and the sixth flow regulating device are 1; the opening degree of the third air volume adjusting device is subjected to combined feedback adjustment by the opening degree of the second air volume adjusting device and the rotating speed of the first air blower, and the priority of the feedback adjustment of the second air volume adjusting device and the priority of the feedback adjustment of the first air blower are the same; the rotating speed of the first air feeder is regulated by the temperature feedback measured by the fifth temperature measuring device; the opening degrees of the first air volume adjusting device and the second air volume adjusting device and the rotating speed of the second blower are all regulated by the output feedback of the air source heat pump unit, and the priority of the signal output of the opening degree increase of the second air volume adjusting device, the opening degree decrease of the first air volume adjusting device and the rotating speed decrease of the second blower is higher than the priority of the signal output of the opening degree decrease of the second air volume adjusting device, the opening degree increase of the first air volume adjusting device and the rotating speed increase of the second blower; the output of the air source heat pump unit is subjected to combined feedback regulation by the opening degrees of the first flow regulating device, the third flow regulating device and the fifth flow regulating device, and the feedback regulation priorities of the first flow regulating device, the third flow regulating device and the fifth flow regulating device are the same; the opening degree of the first flow regulating device is regulated by temperature feedback measured by a second temperature measuring device arranged on a first air inlet pipeline in front of the air treatment device and the frequency converter; the opening degree of the third flow regulating device is regulated by the temperature feedback measured by the seventh temperature measuring device; the opening degree of the fifth flow regulating device is regulated by the temperature feedback measured by the eighth temperature measuring device.
Compared with the prior art, the utility model has the advantages of as follows:
1. from a system form perspective: VFD and AHP combined operation system can make the warm system form of leading to of centralized control building simplify, cancels the air handler of converter air inlet, integrates it as in the utility model discloses partly in the system of establishing.
2. From the heating and ventilation design perspective: in summer, the required refrigerating capacity and the air volume of cooling of converter air inlet fall wet all can be by the utility model discloses the system that establishes is responsible for providing, and consequently each part in the converter room gets the heat and does not have the interference each other, and its cold load calculates the calculation method as an organic whole with other public building rooms, and the work load that reducible load calculated.
3. From the perspective of energy conservation: winter, the utility model discloses the system established, it is used as air source heat pump set's air inlet preheating to allocate the operation calorific capacity of converter, improves air source heat pump set's the efficiency ratio of heating to reduce heating power consumption and CO2 emission.
4. From a cleaning heat supply perspective: the establishment of the VFD and AHP combined operation system can improve the evaporation temperature of the air source heat pump unit, expand the application prospect of the air source heat pump unit in severe cold areas and provide a technical route for clean heat supply transformation of thermal power plants in the areas.
5. From a system operational perspective: the utility model discloses a VFD and AHP combined operation system provide the operation regulation method under 3 kinds of different work condition, provide the feasibility for its popularization and application at engineering practice angle.
Drawings
Fig. 1 is a schematic structural diagram of a VFD and AHP combined operation system for severe cold regions of the present invention.
Wherein, 1 an air source heat pump unit, 2 a frequency converter, 3 a first air inlet pipeline, 4 a first air outlet pipeline, 5 a second air inlet pipeline, 6 a second air outlet pipeline, 7 a first air outlet branch, 8 a second air outlet branch, 9 a first air blower, 10 a second air blower, 11 an air exhaust shaft, 12 a first air volume adjusting device, 13 a second air volume adjusting device, 14 a third air volume adjusting device, 15 an air processing device, 16 a fan coil, 17 a hot water radiator, 18 an water outlet pipeline, 19 a water return pipeline, 20 a first water outlet branch, 21 a first water return branch, 22 a second water outlet branch, 23 a second water return branch, 24 a third water outlet branch, 25 a third water return branch, 26 a first flow adjusting device, 27 a second flow adjusting device, 28 a third flow adjusting device, 29 a fourth flow adjusting device, 30 a fifth flow adjusting device, 31 a sixth flow adjusting device and 32 a first temperature measuring device, 33 a second temperature measuring device, 34 a third temperature measuring device, 35 a fourth temperature measuring device, 36 a fifth temperature measuring device, 37 a sixth temperature measuring device, 38 a seventh temperature measuring device, 39 an eighth temperature measuring device and 40 a humidity measuring device.
Detailed Description
In the embodiment shown in fig. 1, a VFD and AHP combined operation system for severe cold regions includes a frequency converter 2, the frequency converter 2 is provided with a first air inlet pipeline 3 in a communicating manner, the frequency converter 2 is also provided with a first air outlet pipeline 4 in a communicating manner, and the first air outlet pipeline 4 is connected with an adjustable first air outlet branch 7 and a second air outlet branch 8 in a communicating manner; the air source heat pump unit 1 is arranged, the air source heat pump unit 1 is provided with a second air inlet pipeline 5 and a second air outlet pipeline 6 in a communicated mode, a first air volume adjusting device 12 is arranged on the second air inlet pipeline 5, and a first air outlet branch 7 is connected to the second air inlet pipeline 5 between the first air volume adjusting device 12 and the air source heat pump unit 1 in a communicated mode; and the air source heat pump unit 1 is also provided with a water outlet pipeline 18 and a water return pipeline 19 in a communicated manner, one ends of the water outlet pipeline 18 and the water return pipeline 19, which are far away from the air source heat pump unit 1, are respectively connected with an air treatment device 15, a fan coil 16 and a hot water radiator 17, and the air treatment device 15 is arranged in the first air inlet pipeline 3.
The first air outlet branch 7 and the second air outlet branch 8 are respectively provided with a second air volume adjusting device 13 and a third air volume adjusting device 14; and the second air outlet branch 8 and the second air outlet pipeline 6 are communicated and connected with an air exhaust vertical shaft 11.
Wherein, one end of the first air inlet pipeline 3 far away from the frequency converter 2 is provided with a first blower 9, and an air treatment device 15 is positioned in the first air inlet pipeline 3 between the first blower 9 and the frequency converter 2; and a second blower 10 is arranged at one end of the second air inlet pipeline 5 far away from the air source heat pump unit 1, and the first air volume adjusting device 12 is positioned between the second blower 10 and the air source heat pump unit 1.
Wherein, a first temperature measuring device 32 and a second temperature measuring device 33 are respectively arranged in the first air inlet pipeline 3 between the air processing device 15 and the first blower 9 and in the first air inlet pipeline 3 between the air processing device 15 and the frequency converter 2, and a third temperature measuring device 34 and a fourth temperature measuring device 35 are respectively arranged in the second air inlet pipeline 5 between the first air volume adjusting device 12 and the second blower 10 and in the second air inlet pipeline 5 between the first air volume adjusting device 12 and the air source heat pump unit 1; a fifth temperature measuring device 36 is arranged in the first air outlet pipeline 4, and a sixth temperature measuring device 37 is arranged in the second air outlet pipeline 6; and a humidity measuring device 40 is also arranged in the first air inlet pipeline 3 between the air processing device 15 and the frequency converter 2.
The water outlet pipeline 18 is in communication connection with the air treatment device 15 through a first water outlet branch 20, the water return pipeline 19 is in communication connection with the air treatment device 15 through a first water return branch 21, and the first water outlet branch 20 and the first water return branch 21 are respectively provided with a first flow regulating device 26 and a second flow regulating device 27.
The water outlet pipeline 18 is also communicated and connected with a second water outlet branch 22 and a third water outlet branch 24, and the water return pipeline 19 is also communicated and connected with a second water return branch 23 and a third water return branch 25; one ends of the second water outlet branch 22 and the second water return branch 23, which are far away from the air source heat pump unit 1, are connected with the fan coil 16; one ends of the third water outlet branch 24 and the third water return branch 25, which are far away from the air source heat pump unit 1, are connected with the hot water radiator 17; a third flow regulating device 28 and a fourth flow regulating device 29 are respectively arranged on the second water outlet branch 22 and the second water return branch 23, and a fifth flow regulating device 30 and a sixth flow regulating device 31 are respectively arranged on the third water outlet branch 24 and the third water return branch 25; and a seventh temperature measuring device 38 is arranged outside the fan coil 16, and an eighth temperature measuring device 39 is arranged outside the hot water radiator 17. The seventh temperature measuring device 38 and the eighth temperature measuring device 39 are respectively disposed in the room in which the fan coil 16 and the hot water radiator 17 are located, and are used for monitoring and measuring the temperature in the room.
With reference to fig. 1, a control and regulation method for a VFD and AHP combined operation system in a severe cold area is provided, which at least includes a summer condition: 1 refrigeration of air source heat pump set, 2 heat extractions of converter, fan coil 16 open, and hot water radiator 17 closes, wherein: the opening degrees of a second air volume adjusting device 13 arranged on the first air outlet branch 7, a fifth flow adjusting device 30 arranged on a third water outlet branch 24 between the hot water radiator 17 and the air source heat pump unit 1 and a sixth flow adjusting device 31 arranged on a third water return branch 25 are 0; the opening degrees of a third air volume adjusting device 14 arranged on the second air outlet branch 8, a fourth flow adjusting device 29 arranged on a second water return branch 23 between the fan coil 16 and the air source heat pump unit 1 and a second flow adjusting device 27 arranged on a first water return branch 21 between the air treatment device 15 and the air source heat pump unit 1 are 1, wherein the opening degree is 0 when the air treatment device is fully closed and is 1 when the air treatment device is fully opened; the opening degree of the first air volume adjusting device 12 and the rotating speed of a second blower 10 arranged at one end of the second air inlet pipeline 5 far away from the air source heat pump unit 1 are adjusted by the output feedback of the air source heat pump unit 1; the output of the air source heat pump unit 1 is jointly feedback-regulated by the opening degrees of a third flow regulating device 28 arranged on a second water outlet branch 22 between the fan coil 16 and the air source heat pump unit 1 and a first flow regulating device 26 arranged on a first water outlet branch 20 between the air treatment device 15 and the air source heat pump unit 1, and the feedback-regulated priorities of the first flow regulating device 26 and the third flow regulating device 28 are the same; the opening degree of the third flow regulating device 28 is regulated by the temperature feedback measured by a seventh temperature measuring device 38 arranged outside the fan coil 16; the opening degree of the first flow regulating device 26 is jointly fed back and regulated by the humidity measured by a humidity measuring device 40 arranged in the first air inlet pipeline 3 between the air processing device 15 and the frequency converter 2 and the temperature measured by a fifth temperature measuring device 36 arranged in the first air outlet pipeline 4, and the priority of the feedback regulation of the humidity measuring device 40 and the fifth temperature measuring device 36 is the same; the rotating speed of the first blower 9 arranged at one end of the first air inlet pipeline 3 far away from the frequency converter 2 is regulated by the temperature feedback measured by the fifth temperature measuring device 36 arranged on the first air outlet pipeline 4.
And, further comprising a transition season condition: air source heat pump set 1 heats, 2 heat extractions of converter, and fan coil 16 opens, and hot water radiator 17 opens, wherein: the opening degrees of the first flow rate adjustment device 26 and the second flow rate adjustment device 27 are 0; the opening degrees of the fourth flow rate adjustment device 29 and the sixth flow rate adjustment device 31 are 1; the opening degree of the third air volume adjusting device 14 is jointly feedback-regulated by the opening degree of the second air volume adjusting device 13 and the rotating speed of the first blower 9, and the priority of the feedback regulation of the second air volume adjusting device 13 and the first blower 9 is the same; the rotating speed of the first blower 9 is feedback-regulated by the temperature measured by the fifth temperature measuring device 36; the opening degrees of the first air volume adjusting device 12 and the second air volume adjusting device 13 and the rotating speed of the second blower 10 are all regulated by the output feedback of the air source heat pump unit 1, wherein the priority of the signal output of the opening degree increase of the second air volume adjusting device 13, the opening degree decrease of the first air volume adjusting device 12 and the rotating speed decrease of the second blower 10 is higher than the priority of the signal output of the opening degree decrease of the second air volume adjusting device 13, the opening degree increase of the first air volume adjusting device 12 and the rotating speed increase of the second blower 10; the output of the air source heat pump unit 1 is jointly fed back and regulated by the opening degrees of the third flow regulating device 28 and the fifth flow regulating device 30, and the priority of the feedback regulation of the third flow regulating device 28 and the fifth flow regulating device 30 is the same; the opening degree of the third flow regulating device 28 is feedback-regulated by the temperature measured by the seventh temperature measuring device 38; the opening degree of the fifth flow rate adjusting device 30 is feedback-adjusted by the temperature measured by the eighth temperature measuring device 39.
And, also includes a winter condition: air source heat pump set 1 heats, 2 heat extractions of converter, and the fan pipeline is opened, and hot water radiator 17 opens, wherein: the opening degrees of the second flow rate adjusting device 27, the fourth flow rate adjusting device 29 and the sixth flow rate adjusting device 31 are 1; the opening degree of the third air volume adjusting device 14 is jointly feedback-regulated by the opening degree of the second air volume adjusting device 13 and the rotating speed of the first blower 9, and the priority of the feedback regulation of the second air volume adjusting device 13 and the first blower 9 is the same; the rotating speed of the first blower 9 is feedback-regulated by the temperature measured by the fifth temperature measuring device 36; the opening degrees of the first air volume adjusting device 12 and the second air volume adjusting device 13 and the rotating speed of the second blower 10 are all adjusted by the output feedback of the air source heat pump unit 1, and the priority of the signal output of the opening degree increase of the second air volume adjusting device 13, the opening degree decrease of the first air volume adjusting device 12 and the rotating speed decrease of the second blower 10 is higher than the priority of the signal output of the opening degree decrease of the second air volume adjusting device 13, the opening degree increase of the first air volume adjusting device 12 and the rotating speed increase of the second blower 10, namely when the output feedback of the air source heat pump unit 1 needs to increase the efficiency, the opening degree of the second air volume adjusting device 13 is preferentially increased; the output of the air source heat pump unit 1 is jointly feedback-regulated by the opening degrees of the first flow regulating device 26, the third flow regulating device 28 and the fifth flow regulating device 30, and the feedback-regulated priorities of the first flow regulating device 26, the third flow regulating device 28 and the fifth flow regulating device 30 are the same; the opening degree of the first flow regulating device 26 is feedback-regulated by the temperature measured by a second temperature measuring device 33 arranged on the first air inlet pipeline 3 before the air treatment device 15 and the frequency converter 2; the opening degree of the third flow regulating device 28 is feedback-regulated by the temperature measured by the seventh temperature measuring device 38; the opening degree of the fifth flow rate adjusting device 30 is feedback-adjusted by the temperature measured by the eighth temperature measuring device 39.
According to a VFD and AHP combined operation system for severe cold regions shown in fig. 1, the following embodiment is provided: a checking, drying, and making, zhengzhen of the sibarda of the union of the sillimania at the inner Mongolian autonomous region of a certain thermal power plant. In winter, the outdoor temperature of the heating room is-25.2 ℃, the outdoor temperature of the ventilation room is-18.8 ℃, the outdoor temperature of the air conditioner is-27.8 ℃ and the outdoor calculated humidity is 72 percent; in summer, the air conditioner calculates the outdoor dry bulb temperature of 31.1 ℃, the air conditioner calculates the outdoor wet bulb temperature of 19.9 ℃, the ventilation outdoor calculated temperature of 26.0 ℃, the ventilation outdoor calculated humidity of 44%, the total building area of the centralized control building of 2598.89m2 and the heating heat load in winter of 115 kW.
The equipment setting parameters are as follows:
1. air source heat pump set 1: nominal refrigeration/heating capacity is 225.6kW and 170.3kW respectively, and when the outdoor dry bulb temperature is 7 ℃, the heating COP is about 2.9; when the outdoor dry bulb temperature is-20 ℃, the heating COP is 1.35, and the COP attenuation correction curve can be regarded as linear.
2. And a frequency converter 2: the rated capacity is 3000kV & A, the heating value is 150kW when the engine runs under full load, and the temperature and humidity ranges of the working environment are required to be-10 ℃,40 ℃ and 20% and 90%.
3. Air treatment device 15: the design heat exchange capacity is 50 kW.
4. The first blower 9: the air volume is 40000m3/h, the rotating speed is 1450r/min, the total pressure is 690Pa, and the power is 9.0kW.
5. Second blower 10: as well as the first blower 9.
With reference to fig. 1, the operating parameters are as follows:
the temperature measured by the first temperature measuring device 32 is-12.5 ℃, the temperature measured by the second temperature measuring device 33 is-7 ℃, and the running air volume of the first blower 9 is 2 multiplied by 104m 3 H, the actual heating capacity of the air treatment device 15 is 30.67kW, the running output of the frequency converter 2 is 67 percent, the heating capacity is 100.5kW, the exhaust air temperature of the first exhaust air pipeline 4 of the frequency converter 2 is 11 ℃, the output of the air source heat pump unit 1 is 79 percent, and the running air capacity of the second air blower 10 is 1.16 multiplied by 104m 3 And h, the temperature measured by the fourth temperature measuring device 35 on the second air inlet pipeline 5 connected with the fourth temperature measuring device is 2.37 ℃.
Combine the equipment lectotype of this embodiment and relevant parameter setting, with air source heat pump set 1 external roofing, the 2 bodies of converter generate heat and directly arrange to outdoor traditional form and compare, the utility model discloses the system established can make air source heat pump set 1's COP value promote to 2.63 by 1.78, and whole heating season can practice thrift the power consumptive 88665.9 degree of heating, reduces CO2 and discharges 85.12t (coal-fired electricity generation).
Through the utility model discloses, can make the heating and ventilation system form of centralized control building simplify to and this system can allocate the operation calorific capacity of converter as air source heat pump set's air inlet and preheat usefulness, improve air source heat pump set's heating energy efficiency ratio, in order to reduce heating power consumption and CO2 emission, and this system can improve air source heat pump set's evaporating temperature, expand its application prospect in severe cold district, provide the technical route for the clean heat supply transformation of the steam power plant in these areas; the utility model provides an operation regulation method under 3 kinds of different operating modes also provides the feasibility for its popularization and application at engineering practice angle.
Claims (6)
1. A VFD and AHP combined operation system for severe cold areas is characterized by comprising a frequency converter (2), wherein the frequency converter (2) is communicated with a first air inlet pipeline (3), the frequency converter (2) is also communicated with a first air outlet pipeline (4), and the first air outlet pipeline (4) is communicated and connected with an adjustable first air outlet branch (7) and a second air outlet branch (8); the air source heat pump unit (1) is arranged, the air source heat pump unit (1) is provided with a second air inlet pipeline (5) and a second air outlet pipeline (6) in a communicated manner, the second air inlet pipeline (5) is provided with a first air volume adjusting device (12), and the first air outlet branch (7) is connected to the second air inlet pipeline (5) between the first air volume adjusting device (12) and the air source heat pump unit (1) in a communicated manner; and the air source heat pump unit (1) is also communicated with a water outlet pipeline (18) and a water return pipeline (19), one ends of the water outlet pipeline (18) and the water return pipeline (19) far away from the air source heat pump unit (1) are respectively connected with an air treatment device (15), a fan coil (16) and a hot water radiator (17), and the air treatment device (15) is arranged in the first air inlet pipeline (3).
2. The VFD and AHP combined operation system for severe cold regions as claimed in claim 1, wherein a second air volume adjusting device (13) and a third air volume adjusting device (14) are respectively arranged on the first air outlet branch (7) and the second air outlet branch (8); and the second air outlet branch (8) and the second air outlet pipeline (6) are communicated and connected with an air exhaust vertical shaft (11).
3. A VFD and AHP combined operation system for severe cold regions according to claim 1, wherein one end of the first air intake pipeline (3) far away from the frequency converter (2) is provided with a first air blower (9), the air treatment device (15) is positioned in the first air intake pipeline (3) between the first air blower (9) and the frequency converter (2); and one end of the second air inlet pipeline (5) far away from the air source heat pump unit (1) is provided with a second air feeder (10), and the first air volume adjusting device (12) is positioned between the second air feeder (10) and the air source heat pump unit (1).
4. A VFD and AHP combined operation system for severe cold regions according to claim 3, wherein a first temperature measuring device (32) and a second temperature measuring device (33) are respectively arranged in the first air inlet pipeline (3) between the air treatment device (15) and the first blower (9) and in the first air inlet pipeline (3) between the air treatment device (15) and the frequency converter (2), and a third temperature measuring device (34) and a fourth temperature measuring device (35) are respectively arranged in the second air inlet pipeline (5) between the first air volume adjusting device (12) and the second blower (10) and in the second air inlet pipeline (5) between the first air volume adjusting device (12) and the air source heat pump unit (1); a fifth temperature measuring device (36) is arranged in the first air outlet pipeline (4), and a sixth temperature measuring device (37) is arranged in the second air outlet pipeline (6); and a humidity measuring device (40) is also arranged in the first air inlet pipeline (3) between the air processing device (15) and the frequency converter (2).
5. The VFD and AHP combined operation system for severe cold regions as claimed in claim 1, wherein said water outlet pipeline (18) and said air treatment device (15) are connected through a first water outlet branch (20), said water return pipeline (19) and said air treatment device (15) are connected through a first water return branch (21), said first water outlet branch (20) and said first water return branch (21) are respectively provided with a first flow rate adjusting device (26) and a second flow rate adjusting device (27).
6. The VFD and AHP combined operation system for severe cold regions as claimed in claim 5, wherein said water outlet pipeline (18) is further connected in communication with a second water outlet branch (22) and a third water outlet branch (24), and said water return pipeline (19) is further connected in communication with a second water return branch (23) and a third water return branch (25); one ends of the second water outlet branch (22) and the second water return branch (23) far away from the air source heat pump unit (1) are connected with the fan coil (16); one ends of the third water outlet branch (24) and the third water return branch (25) far away from the air source heat pump unit (1) are connected with a hot water radiator (17); a third flow regulating device (28) and a fourth flow regulating device (29) are respectively arranged on the second water outlet branch (22) and the second water return branch (23), and a fifth flow regulating device (30) and a sixth flow regulating device (31) are respectively arranged on the third water outlet branch (24) and the third water return branch (25); and a seventh temperature measuring device (38) is arranged outside the fan coil (16), and an eighth temperature measuring device (39) is arranged outside the hot water radiator (17).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220441736.2U CN217088476U (en) | 2022-03-01 | 2022-03-01 | VFD and AHP combined operation system for severe cold area |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220441736.2U CN217088476U (en) | 2022-03-01 | 2022-03-01 | VFD and AHP combined operation system for severe cold area |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN217088476U true CN217088476U (en) | 2022-07-29 |
Family
ID=82547691
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202220441736.2U Active CN217088476U (en) | 2022-03-01 | 2022-03-01 | VFD and AHP combined operation system for severe cold area |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN217088476U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114760806A (en) * | 2022-03-01 | 2022-07-15 | 中国电力工程顾问集团华北电力设计院有限公司 | VFD and AHP combined operation system for severe cold area and control and adjustment method thereof |
-
2022
- 2022-03-01 CN CN202220441736.2U patent/CN217088476U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114760806A (en) * | 2022-03-01 | 2022-07-15 | 中国电力工程顾问集团华北电力设计院有限公司 | VFD and AHP combined operation system for severe cold area and control and adjustment method thereof |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110748970B (en) | Air conditioning system and control method thereof | |
| CN101440984B (en) | Airflow adjustment method for communication base station air conditioning unit | |
| CN201387087Y (en) | Energy-saving low-temperature high-humidity air supply air-conditioning unit | |
| CN201589376U (en) | Central air-conditioning variable water volume and variable air volume whole group-control energy saving system | |
| CN111947275A (en) | Energy-saving optimization method of feng shui linkage in subway stations | |
| CN108834366B (en) | Air conditioning system of data machine room | |
| CN103245036B (en) | A kind of system and method for micro-process air conditioning | |
| CN107588510A (en) | Subway public domain transition season energy environmental control system and its control method | |
| CN201100721Y (en) | Phase change temperature difference energy-saving air-conditioner | |
| CN217088476U (en) | VFD and AHP combined operation system for severe cold area | |
| CN101881495A (en) | Cold Storage Radiant Air Conditioning System Based on Evaporative Cooling | |
| CN113803773A (en) | Double-source multi-connection heating and ventilation system and control method thereof | |
| CN113483395A (en) | Low-energy-consumption residential environment control all-in-one machine and control method thereof | |
| CN106152318A (en) | A kind of varying duty regulation integral system based on cooling water bus and operation method | |
| CN2926891Y (en) | Ventilating and dehumidifying air-conditioner | |
| CN110440355A (en) | Power station temperature adjusting and dehumidifying air-conditioning system and its operation method | |
| CN217082833U (en) | Proportion-adjustable secondary return air conditioning system with reheater | |
| CN103196196A (en) | Temperature and humidity conditioning system combining phase-change temperature regulation with independent fresh air | |
| CN115654617A (en) | Residential fifth-constant method based on central heating | |
| CN210463336U (en) | Temperature-adjusting dehumidifying air-conditioning system for hydropower station | |
| CN203413763U (en) | Micro-processing air-conditioning system | |
| CN210345762U (en) | Multi-split system suitable for southern building inner zone | |
| CN111780302A (en) | Humidity control device and method for reheating by using chilled water | |
| CN206018862U (en) | A kind of cold and hot dual-purpose varying duty based on cooling water bus adjusts integral system | |
| CN208504603U (en) | New hospital energy conserving system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |