CN109595768A - Design control method and overall control method for indoor anti-condensation risk - Google Patents
Design control method and overall control method for indoor anti-condensation risk Download PDFInfo
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- CN109595768A CN109595768A CN201811383823.1A CN201811383823A CN109595768A CN 109595768 A CN109595768 A CN 109595768A CN 201811383823 A CN201811383823 A CN 201811383823A CN 109595768 A CN109595768 A CN 109595768A
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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
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
-
- 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
- F24F11/50—Control or safety arrangements characterised by user interfaces or communication
- F24F11/52—Indication arrangements, e.g. displays
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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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Abstract
The invention discloses a design control method and an integral control method for indoor condensation prevention risks. The design control method comprises the following steps: determining a condensation influence factor of the fresh air system according to the condensation risk of the fresh air system and the influence weight of the fresh air system; determining a dry type fan coil condensation influence factor according to the dry type fan coil condensation risk and the dry type fan coil influence weight; determining a dewing influence factor of the metal radiating plate according to the dewing risk of the metal radiating plate and the influence weight of the metal radiating plate; the fresh air system dewing influence factor, the dry type fan coil dewing influence factor and the metal radiation plate dewing influence factor are the room dewing influence factor. By the invention, the indoor condensation risk can be controlled and adjusted in the design stage, and the specific operation condition can be further monitored in the operation stage.
Description
Technical field
The present invention relates to indoor temperature and humidity control fields, and in particular to a kind of design control method of interior anti-condensation risk
And whole control method.
Background technique
Perception due to human skin to temperature and humidity, people always can influence body because of the variation of temperature and humidity
Comfort level.Outdoor temperature and humidity is not artificially controlled by eco-environmental impact.And indoor temperature and humidity is just that people's emphasis closes
Note, the especially technical staff of architectural design field.
When considering indoor temperature and humidity, moisture condensation risk is the design point that technical staff pays close attention to.Moisture condensation refers in air
Steam when can reach saturation state, if environment temperature continues to decline, start oversaturated condensation vapor elutriation in air occur
Out the phenomenon that.It and include: fresh air system, dry-type fan coil and metal spoke to several aspects that indoor dew condensation phenomenon is affected
Penetrate plate.(1) fresh air system is according in closed indoor side sending fresh air to interior with special equipment, then from the other side by dedicated
Equipment will form " fresh air field of flow " to outdoor discharge indoors, to meet the needs of indoor fresh air ventilating.(2) dry type wind
Machine coil pipe is to be specifically used to provide the air conditioner end equipment of aobvious cooling capacity to room.Chilled water supply water temperature under its design conditions
The generally greater than air dew point temperature of use environment, Air-cooling Process evaporated condensation water generate, and are typical dry calibration processes.
Dry-type fan coil itself do not ensure that it is certain realize dry calibration, dry calibration be by air side air inlet dew-point temperature with
What the relativeness between chilled water supply water temperature determined.(3) metal radiant panel (also known as) heating, the 70% of heating capacity
From heat radiation.Since air hardly picks up radiant heat, so radiant heat will directly heat the surface being irradiated to, as
Face, article and its lower personnel, discharge heat to surrounding air again after heating.Illuminated surface, temperature can be higher by empty around
Temperature degree is more than 3 DEG C.Metal radiant panel itself accounts for 30% also by Convective Heating surrounding air, this partial heat.
In the prior art, the moisture condensation risk control side that can properly consider above-mentioned three kinds of influence factors is not occurred also
Formula.
Summary of the invention
The object of the present invention is to provide a kind of design control method of indoor anti-condensation risk and whole control methods, can
Indoor moisture condensation risk is preferably controlled.
Technical solution provided by the invention is as follows:
A kind of design control method of interior anti-condensation risk includes:
Fresh air system moisture condensation impact factor is determined according to the weighing factor of fresh air system moisture condensation risk and fresh air system；
Dry-type fan coil moisture condensation shadow is determined according to dry-type fan coil moisture condensation risk and dry-type fan coil weighing factor
Ring the factor；
Metal radiant panel moisture condensation impact factor is determined according to metal radiant panel moisture condensation risk and metal radiant panel weighing factor；
The fresh air system moisture condensation impact factor, the dry-type fan coil moisture condensation impact factor, the metal radiant panel
Condense impact factor, and the sum of three is room moisture condensation impact factor.
Preferably, fresh air system moisture condensation risk is determined by following algorithm:
I-th of room fresh air system moisture condensation risk RiX:
RiX=(TiX-TiL)/[min(TC1X、TC2X……TCNX)-max(TC1X、TC2X……TCNX)]；
Wherein: TCiX=TiX-TiL；Fresh air air-supply dry-bulb temperature TiX；Indoor design condition limit offset point dew-point temperature TiL；
Fresh air system weighing factor is determined by following algorithm:
I-th of room fresh air system weighing factor WiX:
WiX=Qix/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that each room of fresh air system can undertakeiXFor in the case where setting fresh air air output, newly
Wind from air-supply dry-bulb temperature TiXIt is changed to room temperature TNAfforded sensible heat amount, QiX=CMiX(TN-TiX), i=1,
2,……N；Wherein, MiXFor New atmosphere quality flow, C is air specific heat；Total sensible heat load Q in each roomZ1、QZ2……QZNIt is each
Room must heat, including according to preset condition obtain heat.
Preferably, dry-type fan coil moisture condensation risk is determined by following algorithm:
I-th of room dry-type fan coil moisture condensation risk RiP:
RiP=(TiP-TiL)/[min(TC1P、TC2P……TCNP)-max(TC1P、TC2P……TCNP)]；
Wherein: TCiP=TiP-TiL；Dry-type fan coil air-supply dry-bulb temperature TiP；Indoor design condition limit offset point dew point temperature
Spend TiL；
Dry-type fan coil weighing factor is determined by following algorithm:
I-th of room dry-type fan coil weighing factor WiP:
WiP=QiP/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that dry-type fan coil can undertake1P、Q2P……QNPFor in the case where setting air output,
Dry-type fan coil is from supply air temperature TiPIt is changed to room temperature TNAfforded sensible heat amount, QiP=CMiP(TN-TiP), i=
1,2,……N；Wherein, MiPFor dry-type fan coil air-supply mass flow, C is air specific heat；Total sensible heat load in each room
QZ1、QZ2……QZNFor each room must heat, including according to preset condition obtain heat.
Preferably, metal radiant panel moisture condensation risk is determined by following algorithm:
I-th of room metal radiant panel moisture condensation risk RiF:
RiF=(TiF-TiL)/[min(TC1F、TC2F……TCNF)-max(TC1F、TC2F……TCNF)]；
Wherein: TCiF=TiF-TiL；Metal radiant panel surface temperature TiF；Indoor design condition limit offset point dew-point temperature TiL；
Metal radiant panel weighing factor is determined by following algorithm:
I-th of room metal radiant panel weighing factor WiF:
WiF=QiF/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that metal radiant panel can undertakeiF=5 × 10-8×[(TiF+273)4-(AUST+273)4]×
A, i=1,2 ... N；Wherein, AUST is the weighted mean of the remaining surface in addition to metal radiant panel, and A is metal spoke
Penetrate plate suqare；Total sensible heat load Q in each roomZ1、QZ2……QZNFor each room must heat, including obtained according to preset condition
Heat.
Preferably, i-th of room fresh air system moisture condensation impact factor: κX=RiX·WiX×100；
I-th of room dry-type fan coil moisture condensation impact factor: κP=RiP·WiP×100；
I-th of room metal radiant panel moisture condensation impact factor: κF=RiF·WiF×100；
I-th of room moisture condensation impact factor: κ=κX+κP+κF。
Preferably, the determinating reference value of room moisture condensation impact factor κ is 0, as κ < 0, illustrates room moisture condensation risk
It is small, and negative value is smaller, risk is lower.
Preferably, fresh air system moisture condensation impact factor κXDeterminating reference value be 0, work as κXWhen < 0, illustrate the room fresh air
Condensation risk is small, and negative value is smaller, and risk is lower；
And/or
Dry-type fan coil moisture condensation impact factor κPDeterminating reference value be 0, work as κPWhen < 0, illustrate the room dry type blower
Coil pipe moisture condensation risk is small, and negative value is smaller, and risk is lower；
And/or
Metal radiant panel moisture condensation impact factor κFDeterminating reference value be 0, work as κFWhen < 0, illustrate the room metal radiant panel
The risk that condenses is small, and negative value is smaller, and risk is lower.
Preferably, indoor design condition limit offset point dew-point temperature TiLIt obtains by the following method:
Under the action of fresh air system and dry-type fan coil, the admixture point of indoor fresh air and dry-type fan coil to
Limiting condition is close；The limiting condition is the dry-type fan coil state point for not considering fresh air system and influencing；
Due to the influence of fresh air system, the admixture point of indoor fresh air and fan coil, which infinitely leans on, described is bordering on the pole
Limit state will not be overlapped with the limiting condition.
Preferably, indoor design condition limit offset point dew-point temperature TiLFurther obtain by the following method:
Three fresh air air output G are determined according to preset condition1、G2And G3, the maximum value of three is taken to determine fresh air air output Gx
=max (G1、G2、G3), the mass flow of fresh air is Mx；It is possible thereby to determine the dehumidifying effect W of fresh air system1, heat-removal capability Q1；
The heat-removal capability for determining dry-type fan coil is Q2=Mp × Δ t, in which:
The air-supply mass flow of Mp --- dry-type fan coil；
The supply air temperature difference of Δ t --- dry-type fan coil；
The admixture point of indoor fresh air and fan coil is set as O point, admixture point temperature, water capacity To, Wo；
Enable Δ Wxo=(Wo-WSx), Δ Wof=(WF- Wo), in which:
WF--- fan coil ventilation state water capacity；
Wo --- admixture point water capacity；
WSx--- fresh air ventilation state point water capacity；
Enable Δ Txo=(To-TSx), Δ Tof=(TF- Wo), in which:
TF--- fan coil ventilation state temperature；
To --- admixture point temperature；
TSx--- fresh air ventilation state point temperature；
It can thus be concluded that:
Mx Δ Txo=Mp Δ Tof,
Mx Δ Wxo=Mp Δ Wof；
Mx Δ Txo, Mx Δ Wxo is definite value in the case where fresh air air output is constant, it is assumed that Mp infinitely increases, then Δ
Wof, Δ Tof are infinitely close to 0, then admixture point is infinitely close to dry-type fan coil state point；
Flow mass M x, the indoor design condition point N of the indoor humidity load Wx, fresh air air-supply that can be undertaken according to fresh air air-supply contain
Moisture WNThe interior of calculating is related to state limit offset point NLJXWater capacity；
Indoor design condition limit offset point NLJXWater capacity be dLJX=dN+Δd；Wherein, dNIt is indoor design condition point N containing wet
Amount, Δ d are that water capacity caused by the indoor humidity load Wx of fresh air air-supply changes；
Indoor design condition limit offset point NLJXDry-bulb temperature TLJXFor pre-set value；
By TLJX、dLJXIt can determine NLJXDew-point temperature TiL。
The present invention also provides a kind of whole control methods of indoor anti-condensation risk comprising:
Design control method as the aforementioned；
It further include progress control method, the progress control method includes:
It filters out in design control method, the room of room moisture condensation impact factor >=0, and in the first temperature of room setting
Moisture probe；
Room moisture condensation impact factor instantly is calculated according to the temperature and humidity parameter of first temperature and humidity probe detection.
Preferably, it filters out in design control method, the room of fresh air system moisture condensation impact factor >=0, and in the room
Between fresh air system be arranged the second temperature and humidity pop one's head in；
According to second temperature and humidity probe detection temperature and humidity parameter calculate instantly room fresh air system moisture condensation influence because
Son.
Preferably, it filters out in design control method, the room of dry-type fan coil moisture condensation impact factor >=0, and
The dry-type fan coil setting third temperature and humidity in the room is popped one's head in；
Room dry-type fan coil moisture condensation shadow instantly is calculated according to the temperature and humidity parameter of third temperature and humidity probe detection
Ring the factor.
Preferably, it filters out in design control method, the room of metal radiant panel moisture condensation impact factor >=0, and at this
The metal radiant panel in room is arranged the 4th temperature and humidity and pops one's head in；
Calculating room metal radiant panel moisture condensation instantly according to the temperature and humidity parameter of the 4th temperature and humidity probe detection influences
The factor.
Preferably, moisture condensation impact factor in room obtains by the following method:
(1) fresh air system moisture condensation risk is determined by following algorithm:
I-th of room fresh air system moisture condensation risk RiX:
RiX=(TiX-TiL)/[min(TC1X、TC2X……TCNX)-max(TC1X、TC2X……TCNX)]；
Wherein: TCiX=TiX-TiL；Fresh air air-supply dry-bulb temperature TiX；Indoor design condition limit offset point dew-point temperature TiL；
Fresh air system weighing factor is determined by following algorithm:
I-th of room fresh air system weighing factor WiX:
WiX=Qix/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that each room of fresh air system can undertakeiXFor in the case where setting fresh air air output, newly
Wind from air-supply dry-bulb temperature TiXIt is changed to room temperature TNAfforded sensible heat amount, QiX=CMiX(TN-TiX), i=1,
2,……N；Wherein, MiXFor New atmosphere quality flow, C is air specific heat；Total sensible heat load Q in each roomZ1、QZ2……QZNIt is each
Room must heat, including according to preset condition obtain heat；
(2) dry-type fan coil moisture condensation risk is determined by following algorithm:
I-th of room dry-type fan coil moisture condensation risk RiP:
RiP=(TiP-TiL)/[min(TC1P、TC2P……TCNP)-max(TC1P、TC2P……TCNP)]；
Wherein: TCiP=TiP-TiL；Dry-type fan coil air-supply dry-bulb temperature TiP；Indoor design condition limit offset point dew point temperature
Spend TiL；
Dry-type fan coil weighing factor is determined by following algorithm:
I-th of room dry-type fan coil weighing factor WiP:
WiP=QiP/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that dry-type fan coil can undertake1P、Q2P……QNPFor in the case where setting air output,
Dry-type fan coil is from supply air temperature TiPIt is changed to room temperature TNAfforded sensible heat amount, QiP=CMiP(TN-TiP), i=
1,2,……N；Wherein, MiPFor dry-type fan coil air-supply mass flow, C is air specific heat；Total sensible heat load in each room
QZ1、QZ2……QZNFor each room must heat, including according to preset condition obtain heat；
(3) metal radiant panel moisture condensation risk is determined by following algorithm:
I-th of room metal radiant panel moisture condensation risk RiF:
RiF=(TiF-TiL)/[min(TC1F、TC2F……TCNF)-max(TC1F、TC2F……TCNF)]；
Wherein: TCiF=TiF-TiL；Metal radiant panel surface temperature TiF；Indoor design condition limit offset point dew-point temperature TiL；
Metal radiant panel weighing factor is determined by following algorithm:
I-th of room metal radiant panel weighing factor WiF:
WiF=QiF/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that metal radiant panel can undertakeiF=5 × 10-8×[(TiF+273)4-(AUST+273)4]×
A, i=1,2 ... N；Wherein, AUST is the weighted mean of the remaining surface in addition to metal radiant panel, and A is metal spoke
Penetrate plate suqare；Total sensible heat load Q in each roomZ1、QZ2……QZNFor each room must heat, including obtained according to preset condition
Heat；
I-th of room fresh air system moisture condensation impact factor: κX=RiX·WiX×100；
I-th of room dry-type fan coil moisture condensation impact factor: κP=RiP·WiP×100；
I-th of room metal radiant panel moisture condensation impact factor: κF=RiF·WiF×100；
I-th of room moisture condensation impact factor: κ=κX+κP+κF。
Preferably, fresh air system moisture condensation risk is determined by following algorithm:
I-th of room fresh air system moisture condensation risk RiX:
RiX=(TiX-TiL)/[min(TC1X、TC2X……TCNX)-max(TC1X、TC2X……TCNX)]；
Wherein: TCiX=TiX-TiL；Fresh air air-supply dry-bulb temperature TiX；Indoor design condition limit offset point dew-point temperature TiL；
Fresh air system weighing factor is determined by following algorithm:
I-th of room fresh air system weighing factor WiX:
WiX=Qix/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that each room of fresh air system can undertakeiXFor in the case where setting fresh air air output, newly
Wind from air-supply dry-bulb temperature TiXIt is changed to room temperature TNAfforded sensible heat amount, QiX=CMiX(TN-TiX), i=1,
2,……N；Wherein, MiXFor New atmosphere quality flow, C is air specific heat；Total sensible heat load Q in each roomZ1、QZ2……QZNIt is each
Room must heat, including according to preset condition obtain heat；
I-th of room fresh air system moisture condensation impact factor: κX=RiX·WiX×100。
Preferably, dry-type fan coil moisture condensation risk is determined by following algorithm:
I-th of room dry-type fan coil moisture condensation risk RiP:
RiP=(TiP-TiL)/[min(TC1P、TC2P……TCNP)-max(TC1P、TC2P……TCNP)]；
Wherein: TCiP=TiP-TiL；Dry-type fan coil air-supply dry-bulb temperature TiP；Indoor design condition limit offset point dew point temperature
Spend TiL；
Dry-type fan coil weighing factor is determined by following algorithm:
I-th of room dry-type fan coil weighing factor WiP:
WiP=QiP/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that dry-type fan coil can undertake1P、Q2P……QNPFor in the case where setting air output,
Dry-type fan coil is from supply air temperature TiPIt is changed to room temperature TNAfforded sensible heat amount, QiP=CMiP(TN-TiP), i=
1,2,……N；Wherein, MiPFor dry-type fan coil air-supply mass flow, C is air specific heat；Total sensible heat load in each room
QZ1、QZ2……QZNFor each room must heat, including according to preset condition obtain heat
I-th of room dry-type fan coil moisture condensation impact factor: κP=RiP·WiP×100。
Preferably, metal radiant panel moisture condensation risk is determined by following algorithm:
I-th of room metal radiant panel moisture condensation risk RiF:
RiF=(TiF-TiL)/[min(TC1F、TC2F……TCNF)-max(TC1F、TC2F……TCNF)]；
Wherein: TCiF=TiF-TiL；Metal radiant panel surface temperature TiF；Indoor design condition limit offset point dew-point temperature TiL；
Metal radiant panel weighing factor is determined by following algorithm:
I-th of room metal radiant panel weighing factor WiF:
WiF=QiF/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that metal radiant panel can undertakeiF=5 × 10-8×[(TiF+273)4-(AUST+273)4]×
A, i=1,2 ... N；Wherein, AUST is the weighted mean of the remaining surface in addition to metal radiant panel, and A is metal spoke
Penetrate plate suqare；Total sensible heat load Q in each roomZ1、QZ2……QZNFor each room must heat, including obtained according to preset condition
Heat；
I-th of room metal radiant panel moisture condensation impact factor: κF=RiF·WiF×100。
Preferably, when room condenses impact factor κ=0, pre-alarm is carried out；
When indoor dew-point temperature is higher than supply water temperature, alarm.
A kind of design control method of indoor anti-condensation risk provided by the invention and whole control method, can bring with
It is lower the utility model has the advantages that
1, the control of anti-condensation risk is divided into the specific control of the theoretical control and operation phase of design phase by the present invention.
(1) in the design phase, each room tail end air conditioner Condensation risk is judged by the impact factor that condenses and forms preliminary feedback, packet
Include: fresh air system moisture condensation impact factor, dry-type fan coil moisture condensation impact factor and metal radiant panel moisture condensation impact factor pass through
The setting of room end system is adjusted, reduction system integrally condenses risk.It i.e. can be with by moisture condensation impact factor in the design phase
Judge the risk height of each room moisture condensation, such as: the moisture condensation impact factor of office 1 is 1 > 0, illustrate room moisture condensation risk compared with
Height pays particular attention to anti-condensation control；The moisture condensation factor of office 2 be -8 < 0, illustrate the room moisture condensation risk it is lower, at
In the case that this is preferential, the anti-condensation monitoring device in the room be can be omitted；Meanwhile it can be in the design phase by adjusting system
The roomed moisture condensation factor of institute is adjusted to respectively less than 0, reduces whole moisture condensation risk by configuration.(2) in the operation phase, according to
The calculated result of design phase room moisture condensation impact factor, only in higher impact factor, the biggish room of weight or the end of condensing
Additional temperature and humidity probe is set, and each room temperature and humidity parameter, fresh air air-supply temperature and humidity parameter, radiant panel surface temperature are joined
Number, dry-type fan coil air-supply temperature and humidity parameter feedback to moisture condensation impact factor judge terminal, respectively condense with the design phase first
Impact factor is compared, and judges whether the room or end-equipment need to carry out anti-condensation control.If condensing impact factor
Greater than 0, then anti-condensation control is carried out, by anti-condensation control equipment specific implementation.
2, the present invention also has great innovation in the determination of dew point limit offset point.Based on dry-type fan coil+metal
Radiant panel+dedicated outdoor air system determines indoor design condition dew-point temperature (NLJX) limit highest point that is likely to be breached, it is possible thereby to really
Fixed reasonable supply water temperature, the risk of moisture condensation is reduced in the design phase.The dew point limit offset point is virtual state point, is only used for
Determine that independent temperature-humidity control system water supply temperature, i.e., indoor limiting condition dew-point temperature are not higher than NLJXWhen, dry-type fan coil
+ metal radiant panel+dedicated outdoor air system is able to satisfy use demand.General anti-condensation control is to compare supply water temperature and interior
Relationship between dew point, the relationship are generally dynamic, need to detect and formed in time when system is run feedback, and then adjust system
System operating parameter, has certain hysteresis quality.Indoor design condition dew point limit offset point is related to system composition, and system should after determining
Offset point determines immediately, without being fed back, can simplify control logic in control, reduces the quantity of monitoring point.
Detailed description of the invention
Below by clearly understandable mode, preferred embodiment is described with reference to the drawings, to above-mentioned characteristic, the skill of the application
Art feature, advantage and its implementation are further described.
Fig. 1 is a kind of signal that the independent temperature-humidity control system of indoor anti-condensation risk of the invention is arranged in each room
Figure；
Fig. 2 is a kind of whole control structure schematic diagram of the whole control method of indoor anti-condensation risk of the invention；
Fig. 3 is a kind of schematic diagram of embodiment of the control logic of indoor anti-condensation risk of the invention；
Dew point limit deviates the psychrometric chart of the method for determination when Fig. 4 is indoor design state of the present invention.
Drawing reference numeral explanation:
Sx- fresh air ventilation state point；F- dry-type fan coil state point；O- fresh air and fan coil admixture point；N-
Indoor design condition point；N '-dry-type fan coil outlet air state point；The moisture removal of W1- fresh air system.
Specific embodiment
In order to more clearly explain the embodiment of the invention or the technical proposal in the existing technology, Detailed description of the invention will be compareed below
A specific embodiment of the invention.It should be evident that drawings in the following description are only some embodiments of the invention, for
For those of ordinary skill in the art, without creative efforts, it can also be obtained according to these attached drawings other
Attached drawing, and obtain other embodiments.
To make simplified form, part related to the present invention is only schematically shown in each figure, their not generations
Its practical structures as product of table.
The whole control method of indoor anti-condensation risk of the invention include two stages: the control method of design phase and
The control method of operation phase.
In the embodiment one of design control method of the present invention comprising:
(1) fresh air system moisture condensation impact factor is determined according to the weighing factor of fresh air system moisture condensation risk and fresh air system；
(2) determine that dry-type fan coil condenses according to dry-type fan coil moisture condensation risk and dry-type fan coil weighing factor
Impact factor；
(3) according to metal radiant panel condense risk and metal radiant panel weighing factor determine metal radiant panel moisture condensation influence because
Son；
(4) fresh air system moisture condensation impact factor, dry-type fan coil moisture condensation impact factor, metal radiant panel moisture condensation influence because
Son, the sum of three are room moisture condensation impact factor.
In the present embodiment one, room moisture condensation impact factor is the sum of the moisture condensation impact factor of each end.The knot of each end
Dew impact factor includes: fresh air system moisture condensation impact factor, dry-type fan coil moisture condensation impact factor, metal radiant panel moisture condensation shadow
Ring the factor.Each moisture condensation impact factor is determined according to respective moisture condensation risk and weighing factor.
Specifically, when determining fresh air system moisture condensation impact factor, fresh air system moisture condensation risk and fresh air system are calculated first
System weighing factor.Fresh air system moisture condensation risk is determined by following algorithm:
I-th of room fresh air system moisture condensation risk RiX:
RiX=(TiX-TiL)/[min(TC1X、TC2X……TCNX)-max(TC1X、TC2X……TCNX)]；
Wherein: TCiX=TiX-TiL；Fresh air air-supply dry-bulb temperature TiX；Indoor design condition limit offset point dew-point temperature TiL；
Fresh air system weighing factor is determined by following algorithm:
I-th of room fresh air system weighing factor WiX:
WiX=Qix/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that each room of fresh air system can undertakeiXFor in the case where setting fresh air air output, newly
Wind from air-supply dry-bulb temperature TiXIt is changed to room temperature TNAfforded sensible heat amount, QiX=CMiX(TN-TiX), i=1,
2,……N；Wherein, MiXFor New atmosphere quality flow, C is air specific heat；Total sensible heat load Q in each roomZ1、QZ2……QZNIt is each
Room must heat, including according to preset condition obtain heat, preset condition include building enclosure must heat, equipment
What fever was formed must heat, personnel's heat dissipation capacity etc..
Specifically, when determining dry-type fan coil moisture condensation impact factor, dry-type fan coil moisture condensation risk is calculated first
With dry-type fan coil weighing factor.Dry-type fan coil moisture condensation risk is determined by following algorithm:
I-th of room dry-type fan coil moisture condensation risk RiP:
RiP=(TiP-TiL)/[min(TC1P、TC2P……TCNP)-max(TC1P、TC2P……TCNP)]；
Wherein: TCiP=TiP-TiL；Dry-type fan coil air-supply dry-bulb temperature TiP；Indoor design condition limit offset point dew point temperature
Spend TiL；
Dry-type fan coil weighing factor is determined by following algorithm:
I-th of room dry-type fan coil weighing factor WiP:
WiP=QiP/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that dry-type fan coil can undertake1P、Q2P……QNPFor in the case where setting air output,
Dry-type fan coil is from supply air temperature TiPIt is changed to room temperature TNAfforded sensible heat amount, QiP=CMiP(TN-TiP), i=
1,2,……N；Wherein, MiPFor dry-type fan coil air-supply mass flow, C is air specific heat；Total sensible heat load in each room
QZ1、QZ2……QZNFor each room must heat, including according to preset condition obtain heat, preset condition include go along with sb. to guard him knot
Structure must heat, equipment heating formed must heat, personnel's heat dissipation capacity etc..
Specifically, when determining metal radiant panel moisture condensation impact factor, metal radiant panel moisture condensation risk and gold are calculated first
Belong to radiant panel weighing factor.Metal radiant panel moisture condensation risk is determined by following algorithm:
I-th of room metal radiant panel moisture condensation risk RiF:
RiF=(TiF-TiL)/[min(TC1F、TC2F……TCNF)-max(TC1F、TC2F……TCNF)]；
Wherein: TCiF=TiF-TiL；Metal radiant panel surface temperature TiF；Indoor design condition limit offset point dew-point temperature TiL；
Metal radiant panel weighing factor is determined by following algorithm:
I-th of room metal radiant panel weighing factor WiF:
WiF=QiF/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that metal radiant panel can undertakeiF=5 × 10-8×[(TiF+273)4-(AUST+273)4]×
A, i=1,2 ... N；Wherein, AUST is the weighted mean of the remaining surface in addition to metal radiant panel, and A is metal spoke
Penetrate plate suqare；Total sensible heat load Q in each roomZ1、QZ2……QZNFor each room must heat, including obtained according to preset condition
Heat, preset condition include building enclosure must heat, equipment heating formed must heat, personnel's heat dissipation capacity etc..
I-th of room fresh air system moisture condensation impact factor: κX=RiX·WiX×100；
I-th of room dry-type fan coil moisture condensation impact factor: κP=RiP·WiP×100；
I-th of room metal radiant panel moisture condensation impact factor: κF=RiF·WiF×100；
I-th of room moisture condensation impact factor: κ=κX+κP+κF。
The determinating reference value of room moisture condensation impact factor κ is 0, as κ < 0, illustrates that room moisture condensation risk is small, and negative value
Smaller, risk is lower.
Fresh air system moisture condensation impact factor κXDeterminating reference value be 0, work as κXWhen < 0, illustrate that the room fresh air system condenses
Risk is small, and negative value is smaller, and risk is lower；
Dry-type fan coil moisture condensation impact factor κPDeterminating reference value be 0, work as κPWhen < 0, illustrate the room dry type blower
Coil pipe moisture condensation risk is small, and negative value is smaller, and risk is lower；
Metal radiant panel moisture condensation impact factor κFDeterminating reference value be 0, work as κFWhen < 0, illustrate the room metal radiant panel
The risk that condenses is small, and negative value is smaller, and risk is lower.
According to the calculated value κ of each room moisture condensation factorX、κP、κF, κ, can be with the height of each room of quantitative reaction moisture condensation risk
The height for the risk that condenses with each end system, to can be carried out for the end system in the higher room of risk in the design phase
Adjustment, reduces the room or the moisture condensation risk of the end, for example, if fresh air system moisture condensation risk is higher, then can be sent by adjusting
Air quantity is adjusted；If dry-type fan coil moisture condensation risk is higher, then can be adjusted by adjusting its chilled water supply water temperature；
If metal radiant panel moisture condensation risk is higher, then can be adjusted by adjusting the position of metal radiant panel and area to realize.Pass through tune
Section makes the moisture condensation risk of all rooms and end be respectively less than zero as far as possible.
On the basis of above-mentioned design control method, the whole control method of indoor anti-condensation risk further includes operation control
Method.
Indoors in the embodiment one of the whole control method of anti-condensation risk comprising design control method above-mentioned and
Progress control method, wherein progress control method include:
It filters out in design control method, the room of room moisture condensation impact factor >=0, and in the first temperature of room setting
Moisture probe；
Room moisture condensation impact factor instantly is calculated according to the temperature and humidity parameter of the first temperature and humidity probe detection.
Indoors in the embodiment one of the whole control method of anti-condensation risk, room moisture condensation impact factor passes through with lower section
Method obtains, and following methods are consistent with the design phase calculated room moisture condensation method of impact factor:
(1) fresh air system moisture condensation risk is determined by following algorithm:
I-th of room fresh air system moisture condensation risk RiX:
RiX=(TiX-TiL)/[min(TC1X、TC2X……TCNX)-max(TC1X、TC2X……TCNX)]；
Wherein: TCiX=TiX-TiL；Fresh air air-supply dry-bulb temperature TiX；Indoor design condition limit offset point dew-point temperature TiL；
Fresh air system weighing factor is determined by following algorithm:
I-th of room fresh air system weighing factor WiX:
WiX=Qix/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that each room of fresh air system can undertakeiXFor in the case where setting fresh air air output, newly
Wind from air-supply dry-bulb temperature TiXIt is changed to room temperature TNAfforded sensible heat amount, QiX=CMiX(TN-TiX), i=1,
2,……N；Wherein, MiXFor New atmosphere quality flow, C is air specific heat；Total sensible heat load Q in each roomZ1、QZ2……QZNIt is each
Room must heat, including according to preset condition obtain heat；
(2) dry-type fan coil moisture condensation risk is determined by following algorithm:
I-th of room dry-type fan coil moisture condensation risk RiP:
RiP=(TiP-TiL)/[min(TC1P、TC2P……TCNP)-max(TC1P、TC2P……TCNP)]；
Wherein: TCiP=TiP-TiL；Dry-type fan coil air-supply dry-bulb temperature TiP；Indoor design condition limit offset point dew point temperature
Spend TiL；
Dry-type fan coil weighing factor is determined by following algorithm:
I-th of room dry-type fan coil weighing factor WiP:
WiP=QiP/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that dry-type fan coil can undertake1P、Q2P……QNPFor in the case where setting air output,
Dry-type fan coil is from supply air temperature TiPIt is changed to room temperature TNAfforded sensible heat amount, QiP=CMiP(TN-TiP), i=
1,2,……N；Wherein, MiPFor dry-type fan coil air-supply mass flow, C is air specific heat；Total sensible heat load in each room
QZ1、QZ2……QZNFor each room must heat, including according to preset condition obtain heat；
(3) metal radiant panel moisture condensation risk is determined by following algorithm:
I-th of room metal radiant panel moisture condensation risk RiF:
RiF=(TiF-TiL)/[min(TC1F、TC2F……TCNF)-max(TC1F、TC2F……TCNF)]；
Wherein: TCiF=TiF-TiL；Metal radiant panel surface temperature TiF；Indoor design condition limit offset point dew-point temperature TiL；
Metal radiant panel weighing factor is determined by following algorithm:
I-th of room metal radiant panel weighing factor WiF:
WiF=QiF/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that metal radiant panel can undertakeiF=5 × 10-8×[(TiF+273)4-(AUST+273)4]×
A, i=1,2 ... N；Wherein, AUST is the weighted mean of the remaining surface in addition to metal radiant panel, and A is metal spoke
Penetrate plate suqare；Total sensible heat load Q in each roomZ1、QZ2……QZNFor each room must heat, including obtained according to preset condition
Heat；
I-th of room fresh air system moisture condensation impact factor: κX=RiX·WiX×100；
I-th of room dry-type fan coil moisture condensation impact factor: κP=RiP·WiP×100；
I-th of room metal radiant panel moisture condensation impact factor: κF=RiF·WiF×100；
I-th of room moisture condensation impact factor: κ=κX+κP+κF。
Indoors in the embodiment two of the whole control method of anti-condensation risk, in the implementation of aforementioned whole control method
It is improved in example one, wherein progress control method further comprises:
It filters out in design control method, the room of fresh air system moisture condensation impact factor >=0, and the fresh air in the room
System is arranged the second temperature and humidity and pops one's head in；
Room fresh air system moisture condensation impact factor instantly is calculated according to the temperature and humidity parameter of the second temperature and humidity probe detection.
Fresh air system moisture condensation impact factor in room obtains by the following method, and following methods and design phase calculated room are new
The method of wind system moisture condensation impact factor is consistent:
I-th of room fresh air system moisture condensation risk RiX:
RiX=(TiX-TiL)/[min(TC1X、TC2X……TCNX)-max(TC1X、TC2X……TCNX)]；
Wherein: TCiX=TiX-TiL；Fresh air air-supply dry-bulb temperature TiX；Indoor design condition limit offset point dew-point temperature TiL；
Fresh air system weighing factor is determined by following algorithm:
I-th of room fresh air system weighing factor WiX:
WiX=Qix/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that each room of fresh air system can undertakeiXFor in the case where setting fresh air air output, newly
Wind from air-supply dry-bulb temperature TiXIt is changed to room temperature TNAfforded sensible heat amount, QiX=CMiX(TN-TiX), i=1,
2,……N；Wherein, MiXFor New atmosphere quality flow, C is air specific heat；Total sensible heat load Q in each roomZ1、QZ2……QZNIt is each
Room must heat, including according to preset condition obtain heat；
I-th of room fresh air system moisture condensation impact factor: κX=RiX·WiX×100。
Can also condense shadow on the basis of room fresh air system moisture condensation impact factor is calculated further according to aforementioned room
The calculation for ringing the factor further calculates integral room moisture condensation impact factor.
Indoors in the embodiment three of the whole control method of anti-condensation risk, in the implementation of aforementioned whole control method
It is improved in example one, wherein progress control method further comprises:
It filters out in design control method, the room of dry-type fan coil moisture condensation impact factor >=0, and in the room
Dry-type fan coil is arranged third temperature and humidity and pops one's head in；
Room dry-type fan coil moisture condensation shadow instantly is calculated according to the temperature and humidity parameter of third temperature and humidity probe detection
Ring the factor.
Dry-type fan coil moisture condensation impact factor in room obtains by the following method, and following methods and design phase calculate room
Between dry-type fan coil moisture condensation impact factor method it is consistent:
I-th of room dry-type fan coil moisture condensation risk RiP:
RiP=(TiP-TiL)/[min(TC1P、TC2P……TCNP)-max(TC1P、TC2P……TCNP)]；
Wherein: TCiP=TiP-TiL；Dry-type fan coil air-supply dry-bulb temperature TiP；Indoor design condition limit offset point dew point temperature
Spend TiL；
Dry-type fan coil weighing factor is determined by following algorithm:
I-th of room dry-type fan coil weighing factor WiP:
WiP=QiP/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that dry-type fan coil can undertake1P、Q2P……QNPFor in the case where setting air output,
Dry-type fan coil is from supply air temperature TiPIt is changed to room temperature TNAfforded sensible heat amount, QiP=CMiP(TN-TiP), i=
1,2,……N；Wherein, MiPFor dry-type fan coil air-supply mass flow, C is air specific heat；Total sensible heat load in each room
QZ1、QZ2……QZNFor each room must heat, including according to preset condition obtain heat
I-th of room dry-type fan coil moisture condensation impact factor: κP=RiP·WiP×100。
It can also be further according to aforementioned room knot on the basis of room dry-type fan coil moisture condensation impact factor is calculated
The calculation of dew impact factor further calculates integral room moisture condensation impact factor.
Indoors in the example IV of the whole control method of anti-condensation risk, in the implementation of aforementioned whole control method
It is improved in example one, wherein progress control method further comprises:
It filters out in design control method, the room of metal radiant panel moisture condensation impact factor >=0, and the gold in the room
Belong to radiant panel and the 4th temperature and humidity probe is set；
Calculating room metal radiant panel moisture condensation instantly according to the temperature and humidity parameter of the 4th temperature and humidity probe detection influences
The factor.
Metal radiant panel moisture condensation impact factor in room obtains by the following method, following methods and design phase calculated room
The method of metal radiant panel moisture condensation impact factor is consistent:
I-th of room metal radiant panel moisture condensation risk RiF:
RiF=(TiF-TiL)/[min(TC1F、TC2F……TCNF)-max(TC1F、TC2F……TCNF)]；
Wherein: TCiF=TiF-TiL；Metal radiant panel surface temperature TiF；Indoor design condition limit offset point dew-point temperature TiL；
Metal radiant panel weighing factor is determined by following algorithm:
I-th of room metal radiant panel weighing factor WiF:
WiF=QiF/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that metal radiant panel can undertakeiF=5 × 10-8×[(TiF+273)4-(AUST+273)4]×
A, i=1,2 ... N；Wherein, AUST is the weighted mean of the remaining surface in addition to metal radiant panel, and A is metal spoke
Penetrate plate suqare；Total sensible heat load Q in each roomZ1、QZ2……QZNFor each room must heat, including obtained according to preset condition
Heat；
I-th of room metal radiant panel moisture condensation impact factor: κF=RiF·WiF×100。
It can also condense further according to aforementioned room on the basis of room metal radiant panel moisture condensation impact factor is calculated
The calculation of impact factor further calculates integral room moisture condensation impact factor.
Embodiment two, embodiment three, the example IV of the whole control method of aforementioned interior anti-condensation risk can also be free
Combination.The fresh air system moisture condensation impact factor and dry-type fan coil moisture condensation impact factor obtained such as a room in the design phase
It is all larger than and is equal to 0, then all need to adjust.Other combinations are similar.
Indoors in a kind of specific embodiment of the whole control method of anti-condensation risk, it is based on dry-type fan coil+gold
Belong to radiant panel+dedicated outdoor air system design, but is not limited to dry-type fan coil+metal radiant panel+dedicated fresh air in application
System.
Each room schematic diagram shown in referring to Fig.1:
(1) room 1 to room n, total sensible heat load in each room are QZ1、QZ2……QZN；Indoor design condition limit offset point dew
Point temperature T1L、T2L……TNL；
Total sensible heat load Q in each roomZ1、QZ2……QZNFor each room must heat, including by building enclosure must
What heat, equipment heating were formed must heat, personnel's heat dissipation capacity etc.；
(2) sensible heat load that each room of fresh air system can undertake is Q1X、Q2X……QNX；Fresh air air-supply dry-bulb temperature T1X、
T2X……TNX；
The sensible heat load Q that fresh air system can undertake1X、Q2X……QNXFor in the case where setting fresh air air output, fresh air from
Blow dry-bulb temperature TiXIt is changed to room temperature TNAfforded sensible heat amount, QiX=CMiX(TN-TiX), i=1,2 ... N；
Wherein, MiXFor New atmosphere quality flow, C is air specific heat；
(3) sensible heat load that each room of dry-type fan coil can undertake is Q1P、Q2P……QNP；Dry-type fan coil is sent
Wind dry-bulb temperature T1P、T2P……TNP；
The sensible heat load Q that dry-type fan coil can undertake1P、Q2P……QNPFor in the case where setting air output, dry type wind
Machine coil pipe is from supply air temperature TiPIt is changed to room temperature TNAfforded sensible heat amount, QiP=CMiP(TN-TiP), i=1,
2,……N；Wherein, MiPFor dry-type fan coil air-supply mass flow, C is air specific heat；
(4) sensible heat load that each room of metal radiant panel can undertake is Q1F、Q2F……QNF；Metal radiation plate surface temperature
Spend T1F、T2F……TNF；
The sensible heat load Q that metal radiant panel can undertakeiF=5 × 10-8×[(TiF+273)4-(AUST+273)4] × A, i=
1,2,……N；Wherein, AUST is the weighted mean of the remaining surface in addition to radiant panel, and A is radiation plate suqare.
(5) i-th of room fresh air system moisture condensation risk RiXAnd fresh air system weighing factor WiX:
RiX=(TiX-TiL)/[min(TC1X、TC2X……TCNX)-max(TC1X、TC2X……TCNX)]
WiX=Qix/ ∑ (QZ1、QZ2……QZN)
Wherein: TCiX=TiX-TiL
(6) i-th of room dry-type fan coils moisture condensation risk RiPAnd dry-type fan coil weighing factor WiP:
RiP=(TiP-TiL)/[min(TC1P、TC2P……TCNP)-max(TC1P、TC2P……TCNP)]
WiP=QiP/∑(QZ1、QZ2……QZN)
Wherein: TCiP=TiP-TiL
(7) i-th of room metal radiation ceilings moisture condensation risk RiFAnd metal radiation ceiling weighing factor WiF:
RiF=(TiF-TiL)/[min(TC1F、TC2F……TCNF)-max(TC1F、TC2F……TCNF)]
WiF=QiF/∑(QZ1、QZ2……QZN)
Wherein: TCiF=TiF-TiL
(8) condense impact factor
I-th of room fresh air moisture condensation impact factor: κX=RiX·WiX×100；
I-th of room fan coil moisture condensation impact factor: κP=RiP·WiP×100；
I-th of room metal radiation ceiling moisture condensation impact factor: κF=RiF·WiF×100；
I-th of room moisture condensation impact factor: κ=κX+κP+κF。
The impact factor κ decision content that condenses is 0, as κ < 0, illustrates that room moisture condensation risk is small, and negative value is smaller, risk
It is lower.
(9) design phase moisture condensation impact factor application
According to the calculated value κ of each room moisture condensation factorX、κP、κF, κ, can be with the height of each room of quantitative reaction moisture condensation risk
It with the height of each end system moisture condensation risk, is adjusted so as to the end system for the higher room of risk, reducing should
The moisture condensation risk in room or the end makes the moisture condensation risk of all rooms and end be respectively less than zero as far as possible.
(10) operation phase moisture condensation impact factor application
Design phase, the in general more difficult moisture condensation risk for accomplishing all rooms and end was respectively less than zero, therefore, in conjunction with Fig. 2
And Fig. 3, additional temperature and humidity probe is set in the room of design moisture condensation impact factor >=0 and end, and test value is anti-in real time
It is fed to moisture condensation impact factor and judges terminal, calculation and the calculation of design phase are consistent, by each to measured value
The anti-condensation control system that information feeds back to room setting is carried out moisture condensation control by the calculating in room and each Condensation impact factor
System.
Moisture condensation impact factor κ, which is based on indoor design condition limit offset point dew-point temperature T1L, T2L ... TNL, κ value itself, to be had
Certain risk surplus.If κ >=0, it will appear moisture condensation immediately not representing the room, but represent the moisture condensation wind in the room
Danger has reached one and the point to arouse attention is needed therefore the indoor design condition point of κ=0 can be set as pre-alarm state, room
Interior dew-point temperature state is set as alarm condition.It avoids condensing to realize by monitoring moisture condensation impact factor κ.When room moisture condensation shadow
When ringing factor κ=0, pre-alarm is carried out.When indoor dew-point temperature is higher than supply water temperature, alarm.
The present invention is also based on dry-type fan coil+metal radiant panel+dedicated outdoor air system, determines indoor design condition dew-point temperature
(NLJX) limit highest point that is likely to be breached it is possible thereby to determine reasonable supply water temperature reduces the wind of moisture condensation in the design phase
Danger.The dew point limit offset point is virtual state point, is only used for determining independent temperature-humidity control system water supply temperature, i.e., indoor pole
Limit state dew-point temperature is not higher than NLJXWhen, dry-type fan coil+metal radiant panel+dedicated outdoor air system is able to satisfy to use and need
It asks.
Fig. 4 is the psychrometric chart that indoor design state dew point limit of the present invention deviates the method for determination, describes indoor design shape
How state admixture point levels off to limiting condition in fresh air air-supply and under the action of dry-type fan coil.In conjunction with Fig. 4 to this hair
Bright determination method is specifically described.
(1) in independent temperature-humidity control system, fresh air air-supply is wanted according to indoor dehumidification load, personnel's health demand and positive pressure
It asks and determines three fresh air volume G1、G2And G3, the big value of three is taken to determine fresh air air output Gx=max (G1、G2、G3), the matter of fresh air
Amount flow is Mx；It is possible thereby to determine the dehumidifying effect W of fresh air supply system according to known calculations mode1, heat-removal capability Q1.It is logical
The calculating process for crossing this section can determine the dehumidifying effect W of fresh air supply system1, and then determine fresh air supply system remove thermal energy
Power Q1, to prepare for subsequent calculating.
Determine fresh air volume G1 according to indoor dehumidification carry calculation: indoor various wet sources, such as the water surface, human body etc. pass through steaming
The modes such as hair distribute moisture to interior, form humidity load W；Water capacity corresponding to indoor design state point is w1, and fresh air is sent
The corresponding water capacity of wind state point is wx；G1 × (w1-wx)=W, it is possible thereby to determine G1；
Personnel's health demand fresh air volume G2: everyone i.e. indoor required fresh air volume is Gr, total number of persons n, G2=Gr × n；
Maintain indoor positive pressure fresh air volume G3: room is since the formation such as door and window gap leak, outdoor untreated sky in order to prevent
Gas is entered the room by behaviors such as door and window gap, enablings, needs to remain indoor in slight positive pressure state, wherein maintain door and window seam
The air quantity of gap positive pressure is g1, and the air quantity for maintenance positive pressure of opening the door is g2 and other need leakage, therefore deduces that G3=g1+
g2+……
(2) heat-removal capability of dry-type fan coil is Q2=Mp × Δ t, in which:
The air-supply mass flow of Mp --- dry-type fan coil；
The supply air temperature difference of Δ t --- dry-type fan coil.Dry-type fan coil can be determined by the calculating process of this section
Heat-removal capability Q2。
(3) heat-removal capability of metal radiant panel is Q3, which is determined by lectotype selection and radiation-curable area, in this method
It is considered as definite value in calculating.
(4) schematic diagram referring to Fig.1, N are indoor design condition point；N ' is dry-type fan coil outlet air state point.NN ' is corresponding
Refrigerating capacity be Q3；Refrigerating capacity corresponding to N ' F is Q2；W1For moisture removal corresponding to fresh air.O point is fresh air and fan coil
Admixture point, admixture point temperature, water capacity To, Wo；
Enable Δ Wxo=(Wo-WSx), Δ Wof=(WF- Wo), in which:
WF--- fan coil ventilation state water capacity；
Wo --- admixture point water capacity；
WSx--- fresh air ventilation state point water capacity；
Enable Δ Txo=(To-TSx), Δ Tof=(TF- Wo), in which:
TF--- fan coil ventilation state temperature；
To --- admixture point temperature；
TSx--- fresh air ventilation state point temperature；
It can thus be concluded that:
Mx Δ Txo=Mp Δ Tof,
Mx Δ Wxo=Mp Δ Wof；
Mx Δ Txo, Mx Δ Wxo is definite value in the case where fresh air air output is constant.Assuming that Mp infinitely increases, then Δ
Wof, Δ Tof are infinitely close to 0, and admixture point O point is infinitely close to F point, and N ' O is infinitely close to vertically, in limiting condition
It is lower to be overlapped with NF.But the dehumidifying effect W of fresh air1When fresh air air output is constant, W1Constant, i.e. N ' O considers fresh air dehumidification ability
It is position shown in dotted line in schematic diagram after offset.
(5) indoor design condition limit offset point N is determinedLJX
First according to fresh air air-supply can undertake indoor humidity load Wx (for pre-set value), fresh air mass flow be Mx,
The water capacity W of indoor design condition point NNTo calculate indoor state limit offset point NLJXWater capacity, calculation formula herein are existing public affairs
Formula.
Assuming that indoor design condition limit offset point NLJXDry-bulb temperature be equal to indoor design condition point N dry-bulb temperature, be TLJX, should
Value is known definite value；
Indoor design condition limit offset point NLJXWater capacity be dLJX=dN+ Δ d (formula is the variation of state parameter,
With 5 DEG C of room air, heating 8 DEG C for 13 DEG C similarly)；Wherein, dNFor the water capacity of indoor design condition point N, Δ d is fresh air air-supply
The variation of water capacity caused by indoor humidity load Wx；
By TLJX、dLJXN can be determined by psychrometric chartLJXDew-point temperature.
It should be noted that above-described embodiment can be freely combined as needed.The above is only of the invention preferred
Embodiment, it is noted that for those skilled in the art, in the premise for not departing from the principle of the invention
Under, several improvements and modifications can also be made, these modifications and embellishments should also be considered as the scope of protection of the present invention.
Claims (18)
1. a kind of design control method of interior anti-condensation risk characterized by comprising
Fresh air system moisture condensation impact factor is determined according to the weighing factor of fresh air system moisture condensation risk and fresh air system；
According to dry-type fan coil condense risk and dry-type fan coil weighing factor determine dry-type fan coil moisture condensation influence because
Son；
Metal radiant panel moisture condensation impact factor is determined according to metal radiant panel moisture condensation risk and metal radiant panel weighing factor；
The fresh air system moisture condensation impact factor, dry-type fan coil moisture condensation impact factor, metal radiant panel moisture condensation
Impact factor, the sum of three are room moisture condensation impact factor.
2. the design control method of anti-condensation risk in interior according to claim 1, it is characterised in that:
Fresh air system moisture condensation risk is determined by following algorithm:
I-th of room fresh air system moisture condensation risk RiX:
RiX=(TiX-TiL)/[min(TC1X、TC2X……TCNX)-max(TC1X、TC2X……TCNX)]；
Wherein: TCiX=TiX-TiL；Fresh air air-supply dry-bulb temperature TiX；Indoor design condition limit offset point dew-point temperature TiL；
Fresh air system weighing factor is determined by following algorithm:
I-th of room fresh air system weighing factor WiX:
WiX=Qix/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that each room of fresh air system can undertakeiXFor in the case where setting fresh air air output, fresh air from
Blow dry-bulb temperature TiXIt is changed to room temperature TNAfforded sensible heat amount, QiX=CMiX(TN-TiX), i=1,2 ... N；
Wherein, MiXFor New atmosphere quality flow, C is air specific heat；Total sensible heat load Q in each roomZ1、QZ2……QZNFor the total of each room
Must be hot, heat is obtained including what is obtained according to preset condition.
3. the design control method of anti-condensation risk in interior according to claim 2, it is characterised in that:
Dry-type fan coil moisture condensation risk is determined by following algorithm:
I-th of room dry-type fan coil moisture condensation risk RiP:
RiP=(TiP-TiL)/[min(TC1P、TC2P……TCNP)-max(TC1P、TC2P……TCNP)]；
Wherein: TCiP=TiP-TiL；Dry-type fan coil air-supply dry-bulb temperature TiP；Indoor design condition limit offset point dew-point temperature TiL；
Dry-type fan coil weighing factor is determined by following algorithm:
I-th of room dry-type fan coil weighing factor WiP:
WiP=QiP/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that dry-type fan coil can undertake1P、Q2P……QNPFor in the case where setting air output, dry type
Fan coil is from supply air temperature TiPIt is changed to room temperature TNAfforded sensible heat amount, QiP=CMiP(TN-TiP), i=1,
2,……N；Wherein, MiPFor dry-type fan coil air-supply mass flow, C is air specific heat；Total sensible heat load Q in each roomZ1、
QZ2……QZNFor each room must heat, including according to preset condition obtain heat.
4. the design control method of anti-condensation risk in interior according to claim 3, it is characterised in that:
Metal radiant panel moisture condensation risk is determined by following algorithm:
I-th of room metal radiant panel moisture condensation risk RiF:
RiF=(TiF-TiL)/[min(TC1F、TC2F……TCNF)-max(TC1F、TC2F……TCNF)]；
Wherein: TCiF=TiF-TiL；Metal radiant panel surface temperature TiF；Indoor design condition limit offset point dew-point temperature TiL；
Metal radiant panel weighing factor is determined by following algorithm:
I-th of room metal radiant panel weighing factor WiF:
WiF=QiF/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that metal radiant panel can undertakeiF=5 × 10-8×[(TiF+273)4-(AUST+273)4] × A, i=
1,2,……N；Wherein, AUST is the weighted mean of the remaining surface in addition to metal radiant panel, and A is metal radiation plate face
Product；Total sensible heat load Q in each roomZ1、QZ2……QZNFor each room must heat, including according to preset condition obtain it is hot
Amount.
5. the design control method of anti-condensation risk in interior according to claim 4, it is characterised in that:
I-th of room fresh air system moisture condensation impact factor: κX=RiX·WiX×100；
I-th of room dry-type fan coil moisture condensation impact factor: κP=RiP·WiP×100；
I-th of room metal radiant panel moisture condensation impact factor: κF=RiF·WiF×100；
I-th of room moisture condensation impact factor: κ=κX+κP+κF。
6. the design control method of anti-condensation risk in interior according to claim 5, it is characterised in that:
The determinating reference value of room moisture condensation impact factor κ is 0, as κ < 0, illustrates that room moisture condensation risk is small, and negative value is got over
Small, risk is lower.
7. the design control method of anti-condensation risk in interior according to claim 5, it is characterised in that:
Fresh air system moisture condensation impact factor κXDeterminating reference value be 0, work as κXWhen < 0, illustrate room fresh air system moisture condensation risk
It is small, and negative value is smaller, risk is lower；
And/or
Dry-type fan coil moisture condensation impact factor κPDeterminating reference value be 0, work as κPWhen < 0, illustrate the room dry-type fan coil
The risk that condenses is small, and negative value is smaller, and risk is lower；
And/or
Metal radiant panel moisture condensation impact factor κFDeterminating reference value be 0, work as κFWhen < 0, illustrate that the room metal radiant panel condenses
Risk is small, and negative value is smaller, and risk is lower.
8. the design control method of anti-condensation risk in interior according to claim 6, it is characterised in that:
Indoor design condition limit offset point dew-point temperature TiLIt obtains by the following method:
Under the action of fresh air system and dry-type fan coil, the admixture point of indoor fresh air and dry-type fan coil is to the limit
State is close；The limiting condition is the dry-type fan coil state point for not considering fresh air system and influencing；
Due to the influence of fresh air system, the admixture point of indoor fresh air and fan coil, which infinitely leans on, described is bordering on the limit shape
State will not be overlapped with the limiting condition.
9. the design control method of anti-condensation risk in interior according to claim 8, it is characterised in that:
Indoor design condition limit offset point dew-point temperature TiLFurther obtain by the following method:
Three fresh air air output G are determined according to preset condition1、G2And G3, the maximum value of three is taken to determine fresh air air output Gx=
max(G1、G2、G3), the mass flow of fresh air is Mx；It is possible thereby to determine the dehumidifying effect W of fresh air system1, heat-removal capability Q1；
The heat-removal capability for determining dry-type fan coil is Q2=Mp × Δ t, in which:
The air-supply mass flow of Mp --- dry-type fan coil；
The supply air temperature difference of Δ t --- dry-type fan coil；
The admixture point of indoor fresh air and fan coil is set as O point, admixture point temperature, water capacity To, Wo；
Enable Δ Wxo=(Wo-WSx), Δ Wof=(WF- Wo), in which:
WF--- fan coil ventilation state water capacity；
Wo --- admixture point water capacity；
WSx--- fresh air ventilation state point water capacity；
Enable Δ Txo=(To-TSx), Δ Tof=(TF- Wo), in which:
TF--- fan coil ventilation state temperature；
To --- admixture point temperature；
TSx--- fresh air ventilation state point temperature；
It can thus be concluded that:
Mx Δ Txo=Mp Δ Tof,
Mx Δ Wxo=Mp Δ Wof；
Mx Δ Txo, Mx Δ Wxo in the case where fresh air air output is constant be definite value, it is assumed that Mp infinitely increases, then Δ Wof,
Δ Tof is infinitely close to 0, then admixture point is infinitely close to dry-type fan coil state point；
The water capacity of the indoor humidity load Wx, the flow mass M x that fresh air is blown, indoor design condition point N that can be undertaken according to fresh air air-supply
WNThe interior of calculating is related to state limit offset point NLJXWater capacity；
Indoor design condition limit offset point NLJXWater capacity be dLJX=dN+Δd；Wherein, dNFor the water capacity of indoor design condition point N, Δ
D is that water capacity caused by the indoor humidity load Wx of fresh air air-supply changes；
Indoor design condition limit offset point NLJXDry-bulb temperature TLJXFor pre-set value；
By TLJX、dLJXIt can determine NLJXDew-point temperature TiL。
10. a kind of whole control method of interior anti-condensation risk characterized by comprising
The described in any item design control methods of claim 1-9；
It further include progress control method, the progress control method includes:
It filters out in design control method, the room of room moisture condensation impact factor >=0, and the first temperature and humidity is set in the room
Probe；
Room moisture condensation impact factor instantly is calculated according to the temperature and humidity parameter of first temperature and humidity probe detection.
11. the whole control method of anti-condensation risk in interior according to claim 10, it is characterised in that:
It filters out in design control method, the room of fresh air system moisture condensation impact factor >=0, and the fresh air system in the room
Second temperature and humidity probe is set；
Room fresh air system moisture condensation impact factor instantly is calculated according to the temperature and humidity parameter of second temperature and humidity probe detection.
12. the whole control method of anti-condensation risk in interior according to claim 10, it is characterised in that:
It filters out in design control method, the room of dry-type fan coil moisture condensation impact factor >=0, and the dry type in the room
Fan coil is arranged third temperature and humidity and pops one's head in；
According to the third temperature and humidity probe detection temperature and humidity parameter calculate instantly room dry-type fan coil moisture condensation influence because
Son.
13. the whole control method of anti-condensation risk in interior according to claim 10, it is characterised in that:
It filters out in design control method, the room of metal radiant panel moisture condensation impact factor >=0, and the metal spoke in the room
It penetrates plate and the 4th temperature and humidity probe is set；
Room metal radiant panel moisture condensation impact factor instantly is calculated according to the temperature and humidity parameter of the 4th temperature and humidity probe detection.
14. the whole control method of anti-condensation risk in interior according to claim 10, it is characterised in that: room moisture condensation shadow
The factor is rung to obtain by the following method:
(1) fresh air system moisture condensation risk is determined by following algorithm:
I-th of room fresh air system moisture condensation risk RiX:
RiX=(TiX-TiL)/[min(TC1X、TC2X……TCNX)-max(TC1X、TC2X……TCNX)]；
Wherein: TCiX=TiX-TiL；Fresh air air-supply dry-bulb temperature TiX；Indoor design condition limit offset point dew-point temperature TiL；
Fresh air system weighing factor is determined by following algorithm:
I-th of room fresh air system weighing factor WiX:
WiX=Qix/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that each room of fresh air system can undertakeiXFor in the case where setting fresh air air output, fresh air from
Blow dry-bulb temperature TiXIt is changed to room temperature TNAfforded sensible heat amount, QiX=CMiX(TN-TiX), i=1,2 ... N；
Wherein, MiXFor New atmosphere quality flow, C is air specific heat；Total sensible heat load Q in each roomZ1、QZ2……QZNFor the total of each room
Must be hot, heat is obtained including what is obtained according to preset condition；
(2) dry-type fan coil moisture condensation risk is determined by following algorithm:
I-th of room dry-type fan coil moisture condensation risk RiP:
RiP=(TiP-TiL)/[min(TC1P、TC2P……TCNP)-max(TC1P、TC2P……TCNP)]；
Wherein: TCiP=TiP-TiL；Dry-type fan coil air-supply dry-bulb temperature TiP；Indoor design condition limit offset point dew-point temperature TiL；
Dry-type fan coil weighing factor is determined by following algorithm:
I-th of room dry-type fan coil weighing factor WiP:
WiP=QiP/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that dry-type fan coil can undertake1P、Q2P……QNPFor in the case where setting air output, dry type
Fan coil is from supply air temperature TiPIt is changed to room temperature TNAfforded sensible heat amount, QiP=CMiP(TN-TiP), i=1,
2,……N；Wherein, MiPFor dry-type fan coil air-supply mass flow, C is air specific heat；Total sensible heat load Q in each roomZ1、
QZ2……QZNFor each room must heat, including according to preset condition obtain heat；
(3) metal radiant panel moisture condensation risk is determined by following algorithm:
I-th of room metal radiant panel moisture condensation risk RiF:
RiF=(TiF-TiL)/[min(TC1F、TC2F……TCNF)-max(TC1F、TC2F……TCNF)]；
Wherein: TCiF=TiF-TiL；Metal radiant panel surface temperature TiF；Indoor design condition limit offset point dew-point temperature TiL；
Metal radiant panel weighing factor is determined by following algorithm:
I-th of room metal radiant panel weighing factor WiF:
WiF=QiF/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that metal radiant panel can undertakeiF=5 × 10-8×[(TiF+273)4-(AUST+273)4] × A, i=
1,2,……N；Wherein, AUST is the weighted mean of the remaining surface in addition to metal radiant panel, and A is metal radiation plate face
Product；Total sensible heat load Q in each roomZ1、QZ2……QZNFor each room must heat, including according to preset condition obtain it is hot
Amount；
I-th of room fresh air system moisture condensation impact factor: κX=RiX·WiX×100；
I-th of room dry-type fan coil moisture condensation impact factor: κP=RiP·WiP×100；
I-th of room metal radiant panel moisture condensation impact factor: κF=RiF·WiF×100；
I-th of room moisture condensation impact factor: κ=κX+κP+κF。
15. the whole control method of anti-condensation risk in interior according to claim 11, it is characterised in that:
Fresh air system moisture condensation risk is determined by following algorithm:
I-th of room fresh air system moisture condensation risk RiX:
RiX=(TiX-TiL)/[min(TC1X、TC2X……TCNX)-max(TC1X、TC2X……TCNX)]；
Wherein: TCiX=TiX-TiL；Fresh air air-supply dry-bulb temperature TiX；Indoor design condition limit offset point dew-point temperature TiL；
Fresh air system weighing factor is determined by following algorithm:
I-th of room fresh air system weighing factor WiX:
WiX=Qix/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that each room of fresh air system can undertakeiXFor in the case where setting fresh air air output, fresh air from
Blow dry-bulb temperature TiXIt is changed to room temperature TNAfforded sensible heat amount, QiX=CMiX(TN-TiX), i=1,2 ... N；
Wherein, MiXFor New atmosphere quality flow, C is air specific heat；Total sensible heat load Q in each roomZ1、QZ2……QZNFor the total of each room
Must be hot, heat is obtained including what is obtained according to preset condition；
I-th of room fresh air system moisture condensation impact factor: κX=RiX·WiX×100。
16. the whole control method of anti-condensation risk in interior according to claim 12, it is characterised in that:
Dry-type fan coil moisture condensation risk is determined by following algorithm:
I-th of room dry-type fan coil moisture condensation risk RiP:
RiP=(TiP-TiL)/[min(TC1P、TC2P……TCNP)-max(TC1P、TC2P……TCNP)]；
Wherein: TCiP=TiP-TiL；Dry-type fan coil air-supply dry-bulb temperature TiP；Indoor design condition limit offset point dew-point temperature TiL；
Dry-type fan coil weighing factor is determined by following algorithm:
I-th of room dry-type fan coil weighing factor WiP:
WiP=QiP/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that dry-type fan coil can undertake1P、Q2P……QNPFor in the case where setting air output, dry type
Fan coil is from supply air temperature TiPIt is changed to room temperature TNAfforded sensible heat amount, QiP=CMiP(TN-TiP), i=1,
2,……N；Wherein, MiPFor dry-type fan coil air-supply mass flow, C is air specific heat；Total sensible heat load Q in each roomZ1、
QZ2……QZNFor each room must heat, including according to preset condition obtain heat
I-th of room dry-type fan coil moisture condensation impact factor: κP=RiP·WiP×100。
17. the whole control method of anti-condensation risk in interior according to claim 13, it is characterised in that:
Metal radiant panel moisture condensation risk is determined by following algorithm:
I-th of room metal radiant panel moisture condensation risk RiF:
RiF=(TiF-TiL)/[min(TC1F、TC2F……TCNF)-max(TC1F、TC2F……TCNF)]；
Wherein: TCiF=TiF-TiL；Metal radiant panel surface temperature TiF；Indoor design condition limit offset point dew-point temperature TiL；
Metal radiant panel weighing factor is determined by following algorithm:
I-th of room metal radiant panel weighing factor WiF:
WiF=QiF/∑(QZ1、QZ2……QZN)；
Wherein, the sensible heat load Q that metal radiant panel can undertakeiF=5 × 10-8×[(TiF+273)4-(AUST+273)4] × A, i=
1,2,……N；Wherein, AUST is the weighted mean of the remaining surface in addition to metal radiant panel, and A is metal radiation plate face
Product；Total sensible heat load Q in each roomZ1、QZ2……QZNFor each room must heat, including according to preset condition obtain it is hot
Amount；
I-th of room metal radiant panel moisture condensation impact factor: κF=RiF·WiF×100。
18. the whole control method of the described in any item indoor anti-condensation risks of 0-17 according to claim 1, it is characterised in that:
When room condenses impact factor κ=0, pre-alarm is carried out；
When indoor dew-point temperature is higher than supply water temperature, alarm.
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