CN111637612B - Temperature and humidity separately-controlled centralized air conditioning system - Google Patents
Temperature and humidity separately-controlled centralized air conditioning system Download PDFInfo
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- CN111637612B CN111637612B CN202010161463.1A CN202010161463A CN111637612B CN 111637612 B CN111637612 B CN 111637612B CN 202010161463 A CN202010161463 A CN 202010161463A CN 111637612 B CN111637612 B CN 111637612B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/46—Improving electric energy efficiency or saving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/64—Electronic processing using pre-stored data
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/65—Electronic processing for selecting an operating mode
Abstract
The invention belongs to the heating and ventilation field, and discloses a temperature and humidity separately controlled centralized air conditioning system, which comprises a centralized cold and heat source host; the hydraulic module comprises a primary side pipeline, a heat exchanger and a secondary side pipeline, the primary side pipeline is connected with the concentrated cold and heat source host pipeline, and the heat exchanger is used for exchanging heat between the cold and heat source of the primary side pipeline and water of the secondary side pipeline; the system is arranged at the tail end of the user end, is communicated with the secondary side pipeline and is used for processing the indoor sensible heat load of the user end; the fresh air handling unit is arranged at a user end and comprises a pre-cooling section and a cooling and dehumidifying section, the pre-cooling section is communicated with the secondary side pipeline and used for pre-cooling fresh air, and the cooling and dehumidifying section is used for carrying out isothermal dehumidification on the pre-cooled fresh air. The double-cold-source fresh air unit is adopted, so that deep dehumidification can be realized, and the dehumidification effect is improved; the central cold and heat source host machine does not need to consider the dehumidification capacity, so that the host machine can adopt medium-temperature chilled water as a cold source, the evaporation temperature of the host machine is increased, and the energy efficiency of the system is obviously improved.
Description
Technical Field
The invention relates to the field of heating ventilation, in particular to a temperature and humidity separately controlled centralized air conditioning system.
Background
In the existing centralized residential air conditioning system with temperature and humidity control terminals, an air conditioning host is generally adopted to generate cold water to be supplied to a radiation terminal and a centralized fresh air system in summer, and meanwhile, the heat and humidity loads of a building are solved. However, the sensible heat tail end of the system adopts a radiation system, and the cooling speed is slow under the condition of instantaneous large load; due to the influences of factors such as pipeline temperature rise, hydraulic unbalance, extreme hot and humid outdoor conditions and the like, the dehumidification effect is difficult to guarantee by adopting the centralized single cold source, and the thermal comfort is seriously influenced.
Disclosure of Invention
The invention aims to provide a temperature and humidity separately-controlled centralized air conditioning system, which improves the operation efficiency of the system, reduces energy consumption, ensures a hot and humid environment and improves indoor comfort while ensuring the dehumidification capability of the system.
The technical scheme provided by the invention is as follows:
a temperature and humidity separately controlled centralized air conditioning system comprising:
a centralized cold and heat source host;
the hydraulic module comprises a primary side pipeline, a heat exchanger and a secondary side pipeline, the primary side pipeline is connected with the concentrated cold and heat source host pipeline, and the heat exchanger is used for exchanging heat between a cold and heat source in the primary side pipeline and water in the secondary side pipeline;
the system is arranged at the tail end of the user side, communicated with the secondary side pipeline and used for processing the indoor sensible heat load of the user side;
the fresh air handling unit is arranged at a user end and comprises a pre-cooling section and a cooling and dehumidifying section, the pre-cooling section is communicated with the secondary side pipeline and used for pre-cooling the entering fresh air, and the cooling and dehumidifying section is used for carrying out isothermal dehumidification on the pre-cooled fresh air.
In the scheme, the tail end is adopted to process the sensible heat load, and the fresh air handling unit is used for solving a temperature and humidity independent system of the fresh air load and the humidity load. The fresh air handling unit adopts double cold sources, precooling is carried out through a precooling section connected with a secondary side pipeline under the working condition of summer, then deep dehumidification of fresh air is realized through an independent low-temperature cold source system (a cooling dehumidification section), and the dehumidification effect under the conditions of high-temperature environment and hydraulic unbalance is fully ensured; the concentrated cold and heat source host can adopt medium-temperature chilled water to discharge water, and compared with the conventional water discharged at 7 ℃, the concentrated cold and heat source host improves the evaporation temperature and the host energy efficiency.
By adopting the building type hydraulic module, compared with a primary pump system, the primary and secondary side water paths are isolated through the heat exchanger, so that hydraulic balance is facilitated; compared with a household hydraulic module system, the system investment cost, the maintenance cost and the installation space are obviously reduced, and the implementation of charging and metering is more convenient.
Further preferably, the system also comprises a variable frequency water pump;
the variable frequency water pump is arranged on a water return pipe of the concentrated cold and heat source host and a secondary side pipeline of the hydraulic module.
In this scheme, the variable frequency water pump variable flow operation is all adopted to the one secondary side delivery pump of water conservancy module, further promotes and carries the energy consumption.
Further preferably, in the refrigeration mode, the water supply temperature of the concentrated cold and heat source host is 11 ℃, and the return water temperature is 17 ℃;
in the heating mode, the water supply temperature of the concentrated cold and heat source host is 40 ℃, and the water return temperature is 34 ℃.
In the scheme, through the 11 ℃ water outlet temperature and the unit water supply and return temperature difference system demonstration, the determination system adopts a 6 ℃ water supply and return temperature difference (water supply and return temperature 11/17 ℃), and compared with the 5 ℃ water supply and return temperature difference (7/12 ℃) working condition of a conventional system, the cold water conveying energy consumption is saved, the conveying scheme is more efficient, and the conveying energy consumption is saved.
Further preferably, the water separator and the water collector are further included;
the number of the hydraulic modules is multiple, and the multiple hydraulic modules are respectively arranged in different buildings;
the concentrated cold and heat source host comprises a water supply pipe and a water return pipe;
the water inlet of the water separator is communicated with the water supply pipe, and the water outlet of the water separator is communicated with the water inlet ends of the primary side pipelines of the plurality of hydraulic modules respectively;
the water inlet of the water collector is communicated with the water outlet ends of the primary side pipelines of the hydraulic modules, and the water outlet of the water collector is communicated with the water return pipe.
In the scheme, the water dividing and collecting device is arranged, so that the primary side hydraulic balance and the guarantee can be improved.
Further preferably, the tip comprises a radiating tip;
the radiation tail end is communicated with a secondary side pipeline of the hydraulic module;
and/or;
the tip includes a fan coil;
and the fan coil is communicated with a secondary side pipeline of the hydraulic module.
In this scheme, the sensible heat treatment end can adopt the nimble configuration form of dry-type fan coil + capillary radiant tube, need the space of quick heat extraction cooling at the sitting room lamp, arranges capillary and fan coil simultaneously, opens simultaneously, realizes rapid cooling, reaches the settlement temperature after, closes fan coil, only moves capillary system, maintains the settlement temperature. In the rooms with overlarge loads on the west side and the south side, the dry type fan coil is additionally arranged on the basis of the capillary system to meet peak loads. Compared with a conventional radiation system, the system is more flexible to operate and higher in comfort guarantee.
Further preferably, the method further comprises the following steps:
the primary metering device is arranged on a water supply and return main pipe of the concentrated cold and heat source host machine and is used for metering the total cold/heat supplied by the concentrated cold and heat source host machine;
the secondary metering device is arranged on a primary side pipeline of the hydraulic module and used for metering the cold/heat consumption of the building where the hydraulic module is located;
and the three-level metering device is arranged at the user side and used for metering the opening time and the opening area of the tail end of the user side, the operation time of the fresh air handling unit and the corresponding air volume gear information.
In the scheme, a three-level metering system is adopted, so that the defects that the metering of a user side is difficult to be calibrated and the maintenance cost of a metering instrument is high are avoided; meanwhile, the balance of the cold and hot supplies is more facilitated. The primary metering device meters the whole cold and heat output quantity of the system, the metered value is used as the total charging amount, and the secondary metering device arranged at the front end of the building hydraulic module meters the cold and heat supplied to the building and is used as the quantitative basis for the charging of the cold and heat in the building level; the three-level metering device is arranged at a user side, the running time of the fresh air handling unit in the refrigeration and heating modes, the corresponding air quantity gear information and the terminal opening time are metered and used as quantitative basis for apportioning the charging inside the building, and the running control and data acquisition of the equipment are realized through the intelligent control system.
Further preferably, the metering model for calculating the user-side cost according to the metering data of the primary metering device, the secondary metering device and the tertiary metering device is as follows:
LTk＝La·αk；
wherein L is the apportionment cost/ten thousand yuan; alpha is an energy supply season sharing coefficient; q is energy flow/MWH; a is the open radiation end pavement area/m2(ii) a t is opening time/h; subscript T is total radiation and fresh air system identification; subscript fc is the dry air panel identification; subscript OA is a fresh air label; subscript R is the radiation system identification; subscript a is an annual identification; subscript k is an energy supply quaternary mark; subscript i is a building identification; subscript j is a user identification; subscript L is a low gear identification; subscript M is a middle gear mark; subscript H is a high-grade mark; the subscript t is the metering period identification.
Further preferably, the primary metering device and the secondary metering device are both electromagnetic heat meters.
Further preferably, the fresh air handling unit further comprises a filtering section, a reheating section, a humidifying section and a fan section;
the filtering section, the pre-cooling section, the cooling and dehumidifying section, the reheating section, the humidifying section and the fan section are sequentially arranged along the fresh air inlet direction.
In this scheme, fresh air handling unit has functions such as refrigeration, dehumidification, ventilation, heating, humidification. In a refrigeration mode, medium-temperature cold water provided by a centralized machine room is used as a high-temperature cold source to pre-cool fresh air entering the machine room, and meanwhile, an independent low-temperature cold source system (a cooling and dehumidifying section) is arranged on a fresh air handling unit and is used for deep dehumidification so as to ensure the requirement of air supply humidity; meanwhile, the reheating section recycles the condensation heat of the independent low-temperature system (cooling and dehumidifying section) through the heat exchanger to realize heating and temperature rise of the supplied air. Under the heating mode, hot water provided by the centralized machine room is used as a heat source to heat and enter fresh air, and meanwhile, humidification is performed through the humidification section, so that the humidity requirement of air supply is met. In the ventilation mode, the radiation end and the fan coil are both in a closed state, and only the fresh air handling unit operates to provide ventilation inside the room.
Further preferably, the device further comprises a controller;
the controller is arranged at the user side and is in communication connection with the concentrated cold and heat source host, and the operation of the tail end and the fresh air handling unit is controlled according to the operation state of the concentrated cold and heat source host.
In the scheme, equipment control and data transmission are realized in a communication mode, hardware cost is reduced, real-time monitoring of data is realized, and compared with the existing system, collection and processing of background data are increased, and a control system is optimized; and automatically operating the equipment according to the indoor load state, and optimizing user operation.
The invention has the technical effects that: the fresh air is precooled by secondary side water of the hydraulic module and then dehumidified by an independent cooling and dehumidifying system by adopting the double-cold-source fresh air unit, so that deep dehumidification can be realized, and the dehumidifying effect under the conditions of high-temperature environment and hydraulic unbalance can be fully guaranteed; and the dehumidification of the fresh air handling unit mainly depends on the cooling dehumidification section, and the pre-cooling section only plays a pre-cooling role, so that the central cold and heat source host can adopt the medium-temperature chilled water as a cold source without considering the dehumidification capacity, for example, the central cold and heat source host can adopt the medium-temperature chilled water outlet at 11 ℃ in summer, compared with the conventional water outlet at 7 ℃, the evaporation temperature of the central cold and heat source host is increased, and the system energy efficiency is obviously improved. In addition, the concentrated cold and heat source host simultaneously supplies to the tail end and serves as a high-temperature cold source of the fresh air handling unit, and the service efficiency of the system is improved.
Drawings
The invention is described in further detail below with reference to the following figures and detailed description:
FIG. 1 is a schematic structural diagram of a temperature and humidity control centralized air conditioning system according to the present invention;
fig. 2 is a schematic diagram of the inside of a user side of a temperature and humidity separately controlled centralized air conditioning system according to the present invention;
FIG. 3 is a schematic structural diagram of a fresh air handling unit of a temperature and humidity separately controlled centralized air conditioning system according to the present invention;
FIG. 4 is a flow chart of three-stage metering of a temperature and humidity controlled air conditioning system according to the present invention;
FIG. 5 is a schematic diagram of the metering of the radiant end of a temperature and humidity controlled air conditioning system of the present invention;
FIG. 6 is a schematic view of the metering at the end of the fan coil of a temperature and humidity controlled air conditioning system of the present invention;
fig. 7 is a metering schematic diagram of a fresh air handling unit of the temperature and humidity separately controlled air conditioning system according to the present invention.
The reference numbers illustrate:
1. a centralized cold and heat source host; 11. a water supply pipe; 12. a water return pipe; 2. a hydraulic module; 21. a primary side pipe; 22. a heat exchanger; 23. a secondary side pipeline; 231. a secondary side water supply pipe; 232. a secondary side water return pipe; 3. a fresh air handling unit; 31. a pre-cooling section; 32. a cooling dehumidification section; 33. a filtration section; 34. a reheating section; 35. a humidification stage; 36. a fan section; 37. an air supply outlet; 4. a user side; 5. a building; 61. a radiating tip; 62. a fan coil; 7. a variable frequency water pump; 81. a water separator; 82. a water collector; 91. a primary metering device; 92. and a secondary metering device.
Detailed Description
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
For the sake of simplicity, the drawings only schematically show the parts relevant to the present invention, and they do not represent the actual structure as a product. In addition, in order to make the drawings concise and understandable, components having the same structure or function in some of the drawings are only schematically illustrated or only labeled. In this document, "one" means not only "only one" but also a case of "more than one".
It should be further understood that the term "and/or" as used in this specification and the appended claims refers to and includes any and all possible combinations of one or more of the associated listed items.
In this context, it is to be understood that, unless otherwise explicitly stated or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In addition, in the description of the present application, the terms "first", "second", and the like are used only for distinguishing the description, and are not intended to indicate or imply relative importance.
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following description will be made with reference to the accompanying drawings. It is obvious that the drawings in the following description are only some examples of the invention, and that for a person skilled in the art, other drawings and embodiments can be derived from them without inventive effort.
The invention provides a temperature and humidity separately controlled centralized air conditioning system, which comprises a centralized cold and heat source host 1, a hydraulic module 2, a tail end and a fresh air handling unit 3, as shown in figures 1 to 3. The hydraulic module 2 comprises a primary side pipeline 21, a heat exchanger 22 and a secondary side pipeline 23, wherein the primary side pipeline 21 is in pipeline connection with the concentrated cold and heat source host 1, and the heat exchanger 22 is used for exchanging heat between a cold and heat source in the primary side pipeline 21 and water in the secondary side pipeline 23.
The tail end is arranged at the user end 4 and is communicated with the secondary side pipeline 23 for processing the sensible heat load in the user end chamber. The fresh air handling unit 3 is arranged at the user end 4, the fresh air handling unit 3 comprises a pre-cooling section 31 and a cooling and dehumidifying section 32, the pre-cooling section 31 is communicated with the secondary side pipeline 23 and used for pre-cooling the entering fresh air, and the cooling and dehumidifying section 32 is used for carrying out isothermal dehumidification on the pre-cooled fresh air.
Specifically, the central cold and heat source host 1 may use various forms such as an air-cooled heat pump, a ground source heat pump, a chiller, a boiler, and a municipal heating system. The concentrated cold and heat source host 1 is arranged in an outdoor or concentrated air-conditioning room according to the system installation requirement; the concentrated cold and hot water is prepared by the concentrated cold and heat source host 1.
The hydraulic module 2 is positioned in the building 5; the cold and heat source supply and return pipelines are connected to one side of the hydraulic module 2 and generate secondary cold and heat water through the plate heat exchanger to supply to the tail end and the fresh air handling unit 3. Hydraulic module 2 is the box structure, and simultaneously at the inside multiplicable heat preservation of box, it is thermal-insulated to keep warm to whole heat transfer system part, prevents to lead to equipment, pipeline surface temperature low because equipment is inside to lead to cold water under the refrigeration operating mode in summer, the phenomenon of equipment and pipeline surface dewfall appears, reduces the outside heat transfer loss of hydraulic module 2 in winter and summer simultaneously.
The tip is located in the user side 4 chamber for handling sensible heat load in the chamber, and may include a radiant tip 61 and/or a fan coil 62; the radiation end 61 is communicated with the secondary side pipeline 23 of the hydraulic module 2; the fan coil 62 is communicated with the secondary side pipeline 23 of the hydraulic module 2, the secondary side pipeline 23 comprises a secondary side water supply pipe 231 and a secondary side water return pipe 232, and the tail ends of the secondary side water supply pipe 231 and the secondary side water return pipe 232 are respectively connected with the secondary side water supply pipe 231 and the secondary side water return pipe 232 in a pipeline mode. The tail ends can be flexibly arranged according to building load, functions and investment cost requirements, the fan coil 62 is arranged in a living room needing to quickly remove heat and reduce indoor temperature, the load is large, the west side room and the south side room which are difficult to meet the requirements are adopted by the radiation tail end 61, and the installation position can be top installation or ground installation (local plate lowering treatment is needed). The specific location should be arranged in the main functional area while direct blow to the human body should be avoided.
Fresh air handling unit 3 sets up in user 4 indoor, and fresh air handling unit 3 includes precooling section 31 and cooling dehumidification section 32, and precooling section 31 communicates with hydraulic module 2's secondary side pipeline 23, under the refrigeration mode, precools the new trend as the high temperature cold source through hydraulic module 2's secondary side moderate temperature cold water, and fresh air handling unit 3 is from taking one set of refrigerating system simultaneously, cools off dehumidification section 32 promptly, carries out degree of depth dehumidification to the new trend after the precooling to guarantee the humidity requirement of air supply. The fresh air handling unit 3 is arranged at the user side, so that the adjustment of the user side is conveniently realized, the adjustment flexibility is improved, and the energy waste is avoided.
According to the invention, the fresh air unit 3 adopts double cold sources, the fresh air is pre-cooled by secondary side water of the hydraulic module 2, and then the fresh air is dehumidified by an independent cooling and dehumidifying system, so that deep dehumidification can be realized, and the dehumidifying effect under the conditions of high-temperature environment and hydraulic unbalance can be fully guaranteed; and the dehumidification of the fresh air handling unit 3 mainly depends on the cooling dehumidification section 32, the precooling section 31 only plays a precooling role, and the cold water requirement temperature in summer of the radiation system is higher, so the central cold and heat source host 1 can not consider the dehumidification capability, so that the central cold and heat source host 1 can adopt the medium-temperature chilled water as a cold source, and compared with the conventional water outlet at 7 ℃, the evaporation temperature of the central cold and heat source host 1 is increased, thereby the system energy efficiency is obviously improved. In addition, the concentrated cold and heat source host 1 is simultaneously supplied to the tail end and serves as a high-temperature cold source of the fresh air handling unit 3, and the service efficiency of the system is improved.
The operation of the tail end and the fresh air unit 3 is controlled by an indoor controller, the operation mode and the operation state of the concentrated cold and heat source host 1 are sent to the indoor controller by the machine room of the concentrated cold and heat source host 1 in an RS485 communication or TCP communication mode, and the controller determines whether the indoor system allows the refrigeration and heating mode to be started or only the ventilation mode to be operated according to the operation state of the concentrated cold and heat source host 1.
The indoor controller measures the running time of a loop corresponding to the radiation tail end 61 by monitoring the opening state of an indoor radiation tail end loop valve; by monitoring the corresponding high, medium and low gear running states of the fan coil 62 when the valve is opened, the running time corresponding to the high, medium and low gears of the fan coil 62 when the valve is opened is measured; and the equipment use duration of the corresponding user is read in real time in a communication mode through a machine room management system or a background management system of the concentrated cold and heat source host 1, and corresponding cost data is calculated according to unit price.
As shown in fig. 1, in some embodiments of the present invention, the temperature and humidity separately controlled centralized air conditioning system further includes a variable frequency water pump 7, and the variable frequency water pump 7 is disposed on the water return pipe of the centralized cold and heat source host 1 and the secondary side pipeline 23 of the hydraulic module 2. The frequency conversion water pump 7 is adopted for conveying the chilled water of the concentrated cold and heat source host 1, so that the energy consumption of the water pump is reduced, and the energy efficiency of the system is further improved. The secondary side of the hydraulic module 2 adopts a variable frequency water pump 7, the secondary side flow is adjusted according to the temperature difference of the supply return water of the secondary side, the efficient conveying of cold and hot water is ensured, and the energy consumption of the secondary side water pump is reduced.
Preferably, in the refrigeration mode, the water supply temperature of the concentrated cold and heat source host 1 is 11 ℃, and the return water temperature is 17 ℃; in the heating mode, the water supply temperature of the concentrated cold and heat source host 1 is 40 ℃, and the water return temperature is 34 ℃. Compared with the conventional 7/12 ℃ 5 ℃ water supply and return temperature difference, the 6 ℃ large temperature difference variable flow conveying mode is adopted, the water supply and return temperature difference is improved, and the flow of chilled water is reduced.
As shown in fig. 1, in some embodiments of the present invention, the temperature and humidity separately controlled centralized air conditioning system further includes a water separator 81 and a water collector 82; the number of the hydraulic modules 2 is multiple, and the multiple hydraulic modules 2 are respectively arranged on different buildings 5; the concentrated cold and heat source host 1 comprises a water supply pipe 11 and a water return pipe 12; the water inlet of the water separator 81 is communicated with the water supply pipe 11, and the water outlet of the water separator 81 is communicated with the water inlet ends of the primary side pipelines 21 of the plurality of hydraulic modules 2; the water inlet of the water collector 82 is communicated with the water outlet ends of the primary side pipelines 21 of the plurality of hydraulic modules 2, and the water outlet of the water collector 82 is communicated with the water return pipe 12. The cold and heat sources in the water supply pipe 11 of the concentrated cold and heat source host 1 are distributed to a plurality of hydraulic modules 2 of different buildings 5 through the water distributor 81, and the system backwater is collected through the water collector 82.
As shown in fig. 1, in some embodiments of the present invention, the temperature and humidity separately controlled centralized air conditioning system further includes a primary metering device 91, a secondary metering device 92, and a tertiary metering device, wherein the primary metering device 91 is disposed on a water supply and return main pipe of the centralized cold and heat source host 1, and is used for metering the total cold/heat supplied by the centralized cold and heat source host 1; the secondary metering device 92 is arranged on the primary side pipeline 21 of the hydraulic module 2 and is used for metering the cold/heat consumption of the building 5 where the hydraulic module 2 is positioned; the three-level metering device is arranged at the user end 4 and used for metering the starting time and the starting area of the tail end of the user end 4, the running time of the fresh air unit 3 and corresponding air volume gear information.
Specifically, in the embodiment, a three-level metering mode is adopted to meter the apportioned cost of the user side; the three-stage metering is a centralized cooling and heating metering system set based on an on-off time area method. The system is provided with three-level metering, wherein the first-level metering is arranged at a concentrated cold and heat source host machine end and is installed at the front end of a water distributor 81 and the rear end of a water collector 82 and is used for metering the overall energy supply (cooling and heating) of the system, a first-level metering device 91 adopts a heat meter, and because the primary cold and hot water have the cooling and heating consumption in the conveying process, and meanwhile, the metering precision is considered, a second-level metering device 92 is installed in front of each building 5 hydraulic module 2, the second-level metering device 92 adopts a heat meter and is used for metering the cooling and heating consumption of the whole building, and the total cooling and heating amount of the system is shared among the buildings through each building energy meter; according to the installation requirement, enough straight pipe sections are reserved in the front and the back of the watch. For the user-side system, considering the disadvantages of small flow, poor measurement accuracy, large installation quantity, high initial investment and maintenance cost and the like, the three-level measurement adopts an on-off time area method to measure, and the operation time of the fresh air handling unit 3 and the tail end cooling and heating modes is measured respectively. Because the system of the user end 4 using the public energy comprises a capillary radiation end, a dry type fan coil end, a household fresh air handling unit and the like, and the fresh air volume is adjustable in consideration of high, medium and low gears, under the cooling/dehumidifying and heating modes, a weighting time method is adopted, and the fresh air gears perform time weighting assignment according to the air volumes of different gears. And the radiation and fresh air system is weighted and assigned according to the ratio of the maximum sensible heat load to the fresh air load.
The primary metering is used for metering the total energy supply to obtain the total cost, the metering value is used as a charging amount, the secondary metering is used for distributing the cold and heat consumption of the building, and the tertiary metering is used for distributing the cold and heat consumption of the building to users. Compared with the metering and charging of the user end, the metering system avoids the problems of poor metering precision, cold and heat collection and difficulty in balancing caused by limited installation conditions of a heat meter of the user end, small flow and other factors, and simultaneously greatly reduces the investment and maintenance cost of the metering instrument. The specific metering principle is shown in fig. 4.
The specific metering model for expense allocation is as follows:
LTk＝La·αk；
wherein L is the apportionment cost/ten thousand yuan; alpha is an energy supply season sharing coefficient; q is energy flow/MWH; a is the open radiation end pavement area/m2(ii) a t is opening time/h; subscript T is the total (radiation and fresh air system) designation; subscript fc is the dry air panel identification; subscript OA is a fresh air label; subscript R is the radiation system identification; subscript a is an annual identification; subscript k is an energy supply quaternary mark; subscript i is a building identification; subscript j is a user identification; subscript L is a low gear identification; subscript M is a middle gear mark; subscript H is a high-grade mark; the subscript t is the metering period identification.
When the tail end comprises the radiation tail end 61, the metering logic of the radiation tail end 61 is as shown in fig. 5, meanwhile, the weighting coefficient S of the area corresponding to each radiation area is recorded according to the system, and after the weighting coefficient S and the radiation running time are weighted, the energy consumption metering of the system is recorded. When the tip includes a fan coil 62, the fan coil 62 metering logic is as shown in FIG. 6.
The metering logic of the fresh air handling unit 3 is as shown in fig. 7, and the dehumidification condition of the fresh air handling unit 3 is considered to operate under the system refrigeration condition, so the dehumidification condition is counted into the refrigeration condition, and the ventilation mode does not need a cold and heat source and does not count into metering. And the measurement of the radiation terminal 61, the fan coil 62 and the fresh air handling unit 7 is collected to obtain the measurement result of the three-stage measurement device.
As shown in fig. 3, in some embodiments of the present invention, the fresh air handling unit 3 further comprises a filtration section 33, a reheating section 34, a humidification section 35, and a fan section 36; the filtering section 33, the pre-cooling section 31, the cooling and dehumidifying section 32, the reheating section 34, the humidifying section 35 and the fan section 36 are sequentially arranged along the fresh air entering direction, and an air supply opening 37 is further arranged at one end, close to the fan section 36, of the fresh air handling unit 3. The filtering section 33 is used for filtering and dedusting fresh air entering the fresh air unit 3; the pre-cooling section 31 is used for pre-cooling the filtered fresh air in a refrigeration mode; the cooling dehumidification section 32 is an independent cooling dehumidification system and is used for deeply dehumidifying the precooled fresh air; the reheating section 34 is used for reheating the deeply dehumidified fresh air to reach the air supply temperature; the humidifying section 35 is used for humidifying fresh air in a heating mode; the fan section 36 is used for air supply, the fan rotating speed of the fan section 36 is adjustable, and high-air-volume, medium-air-volume and low-air-volume air supply can be realized. The fresh air supply outlet of the fresh air unit 3 can adopt various modes such as ground air supply, skirting line air supply and top air diffuser air supply according to installation conditions, space functions and load characteristics, and preferentially adopts ground air supply and skirting line air supply according to the superiority and inferiority of airflow organization so as to realize the airflow organization effect of replacement ventilation.
In the refrigeration/dehumidification mode, the working process of the temperature and humidity separately-controlled centralized air-conditioning system is as follows:
the concentrated cold and heat source host 1 adopts 11 ℃ medium temperature outlet water, the outlet water is conveyed by the variable frequency water pump 7, the temperature difference of supply and return water is 11/17 ℃, and the variable flow large temperature difference operation of the system is realized. And the secondary side cold water is prepared through the building type hydraulic module 2. And (3) preparing cold water at 16 ℃ through a plate heat exchanger in the hydraulic module 2, supplying the cold water to the tail end and serving as a high-temperature cold source to supply the cold water to the household fresh air handling unit 3 for fresh air precooling. The secondary side adopts a variable frequency water pump 7 to provide system driving power to carry out variable flow operation. The water path after the water in the secondary side pipeline 23 enters the user terminal 4 is divided into two paths, one path is used for supplying a radiation terminal 61 and a fan coil 62, and the indoor sensible heat load is treated. The other path is introduced into a fresh air unit 3 to be used as a fresh air precooling high-temperature cold source. The fresh air is further deeply dehumidified by the independent cooling and dehumidifying system (the cooling and dehumidifying section 32), the air is cooled to 10-12 ℃, and meanwhile, the condensation heat of the independent cooling and dehumidifying system is used for reheating the fresh air in the reheating section 34, so that the reheating energy is saved. The air supply with the temperature of 16-18 ℃ is realized by adjusting the air supply gear of a proper air supply blower in the fan section 36.
In the heating mode, the central cold and heat source host 1 prepares hot water at 40 ℃, the variable-flow operation of the hot water at the primary side is realized through the variable-frequency water pump 7, and the preparation of the hot water at the secondary side is realized through the building hydraulic module 2. Hot water at 38 ℃ is prepared through a heat exchanger 22 in the hydraulic module 2 to provide hot water for the capillary radiation tail end, the dry type fan coil and the fresh air handling unit 3. The independent cooling dehumidification system (cooling dehumidification section) and the reheating section are both in a closed state, and the humidifying section 35 is opened for fresh air humidification. The blower of the fan section 36 realizes the air supply with proper air quantity through gear adjustment.
In the ventilation mode, all cold and hot preparation and conveying facilities are in a closed state, including the concentrated cold and heat source host 1, the primary and secondary side variable frequency water pump 7, the hydraulic module 2, the radiation terminal 61 and the fan coil 62 are in a closed state, and only the fresh air fan in the fresh air unit 3 is started to send fresh air which passes through the filtration.
The user end part of the temperature and humidity separately controlled centralized air conditioning system of the invention is adjustable in different rooms, the radiation tail end 61 is adjusted by the temperature control panel adjusting switch arranged in each room, and the specific operation mode is as follows:
A. the system is started, in a refrigeration mode, the dew point temperature is lower than the radiation water supply temperature and is within a dew point protection safety value, and when the current area temperature T-set target temperature Ts is greater than a preset value Delta T, the area radiation valve is started; when the target temperature Ts-the current area temperature T is greater than a preset value delta T, closing the area radiation valve;
B. the system is started, and in the heating mode, when the target temperature Ts-the current area temperature T is greater than a preset value delta T, the area radiation valve is started; when the current area temperature T-set target temperature Ts is greater than a preset value delta T, closing the area radiation valve;
C. and (4) closing the system, or in a dew point protection state in a refrigeration mode, or in a ventilation mode, closing the radiation valve.
When the terminal includes fan coil 62 equipment, the operation of the corresponding fan coil 62 is controlled according to a fan coil 62 control panel.
The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, various modifications and decorations can be made without departing from the principle of the present invention, and these modifications and decorations should also be regarded as the protection scope of the present invention.
Claims (9)
1. A temperature and humidity separately controlled centralized air conditioning system is characterized by comprising:
a centralized cold and heat source host;
the hydraulic module comprises a primary side pipeline, a heat exchanger and a secondary side pipeline, the primary side pipeline is connected with the concentrated cold and heat source host pipeline, and the heat exchanger is used for exchanging heat between a cold and heat source in the primary side pipeline and water in the secondary side pipeline;
the system is arranged at the tail end of the user side, communicated with the secondary side pipeline and used for processing the indoor sensible heat load of the user side;
the fresh air handling unit is arranged at a user end and comprises a pre-cooling section and a cooling and dehumidifying section, the pre-cooling section is communicated with the secondary side pipeline and is used for pre-cooling the entering fresh air, and the cooling and dehumidifying section is used for carrying out isothermal dehumidification on the pre-cooled fresh air;
the primary metering device is arranged on a water supply and return main pipe of the concentrated cold and heat source host machine and is used for metering the total cold/heat supplied by the concentrated cold and heat source host machine;
the secondary metering device is arranged on a primary side pipeline of the hydraulic module and used for metering the cold/heat consumption of the building where the hydraulic module is located;
and the three-level metering device is arranged at the user side and used for metering the opening time and the opening area of the tail end of the user side, the operation time of the fresh air handling unit and the corresponding air volume gear information.
2. The centralized air-conditioning system with temperature and humidity control as claimed in claim 1,
the device also comprises a variable frequency water pump;
the variable frequency water pump is arranged on a water return pipe of the concentrated cold and heat source host and a secondary side pipeline of the hydraulic module.
3. The centralized air-conditioning system with temperature and humidity control according to claim 2,
in a refrigeration mode, the water supply temperature of the concentrated cold and heat source host is 11 ℃, and the water return temperature is 17 ℃;
in the heating mode, the water supply temperature of the concentrated cold and heat source host is 40 ℃, and the water return temperature is 34 ℃.
4. The centralized air-conditioning system with temperature and humidity control as claimed in claim 1,
the device also comprises a water separator and a water collector;
the number of the hydraulic modules is multiple, and the multiple hydraulic modules are respectively arranged in different buildings;
the concentrated cold and heat source host comprises a water supply pipe and a water return pipe;
the water inlet of the water separator is communicated with the water supply pipe, and the water outlet of the water separator is communicated with the water inlet ends of the primary side pipelines of the plurality of hydraulic modules respectively;
the water inlet of the water collector is communicated with the water outlet ends of the primary side pipelines of the hydraulic modules, and the water outlet of the water collector is communicated with the water return pipe.
5. The centralized air-conditioning system with temperature and humidity control as claimed in claim 1,
the tip comprises a radiating tip;
the radiation tail end is communicated with a secondary side pipeline of the hydraulic module;
and/or;
the tip includes a fan coil;
and the fan coil is communicated with a secondary side pipeline of the hydraulic module.
6. The centralized air-conditioning system with temperature and humidity control as claimed in claim 1,
calculating a metering model of the user side cost according to the metering data of the first-stage metering device, the second-stage metering device and the third-stage metering device, wherein the metering model comprises the following steps:
LTk＝La·αk；
wherein L is the apportionment cost/ten thousand yuan; alpha is an energy supply season sharing coefficient; q is energy flow/MWH; a is the open radiation end pavement area/m2(ii) a t is opening time/h; subscript T is total radiation and fresh air system identification; subscript fc is the dry air panel identification; subscript OA is a fresh air label; subscript R is the radiation system identification; subscript a is an annual identification; subscript k is an energy supply quaternary mark; subscript i is a building identification; subscript j is a user identification; subscript L is a low gear identification; subscript M is a middle gear mark; subscript H is a high-grade mark; the subscript t is the metering period identification.
7. The centralized air-conditioning system with temperature and humidity control as claimed in claim 1,
the primary metering device and the secondary metering device are both electromagnetic heat meters.
8. The centralized air-conditioning system with temperature and humidity control as claimed in claim 1,
the fresh air handling unit also comprises a filtering section, a reheating section, a humidifying section and a fan section;
the filtering section, the pre-cooling section, the cooling and dehumidifying section, the reheating section, the humidifying section and the fan section are sequentially arranged along the fresh air inlet direction.
9. The centralized air-conditioning system with temperature and humidity control as claimed in claim 1,
the device also comprises a controller;
the controller is arranged at the user side and is in communication connection with the concentrated cold and heat source host, and the operation of the tail end and the fresh air handling unit is controlled according to the operation state of the concentrated cold and heat source host.
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| CN202010161463.1A CN111637612B (en) | 2020-03-10 | 2020-03-10 | Temperature and humidity separately-controlled centralized air conditioning system |
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| CN202010161463.1A CN111637612B (en) | 2020-03-10 | 2020-03-10 | Temperature and humidity separately-controlled centralized air conditioning system |
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| CN111637612B true CN111637612B (en) | 2021-10-22 |
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| CN201488157U (en) * | 2009-06-15 | 2010-05-26 | 张茂勇 | Cryogenic independent-dehumidification ground-source water air-conditioner integration device |
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