RU2539668C2 - Supply and exhaust plant with exhaust heat recovery and indirect adiabatic cooling of supply air - Google Patents

Abstract

FIELD: ventilation.SUBSTANCE: supply and exhaust plant with exhaust heat recovery and indirect adiabatic cooling of supply air includes supply and exhaust chambers, plate-type cross-flow recuperator mounted in diagonal, controlled recirculation air valve, the supply chamber includes inlet pipe, controlled and heated inlet air valve, air filter, bypass valve, mixing chamber with controlled air valve at the inlet, air heater unit, ventilation unit and discharge pipe, exhaust chamber includes air filter, ventilation unit, controlled air valve mounted at recuperator inlet, inlet and discharge pipes, supply air cooler. Supply chamber features additional inlet pipe with air filter, exhaust chamber features additional controlled air valve, additional inlet pipe with controlled and heated discharge valve and additional inlet pipe positioned between controlled and additional controlled air valves, controlled and heated inlet valve and air filter, recuperator consists of a case with walls, bottom, pan for condensate collection with drain choke and siphon, and four-stage heat exchanger made of plate-type heat exchangers connected in sequence by ridges and placed inside recuperator case in two rows separated by vertical partition connected to side ridges of heat exchangers. External ridges of heat exchanger rows are connected tightly to side walls of recuperator case, lower heat exchangers are connected by master link. In addition, floor panel of supply and exhaust plant features access hole in intermediate horizontal partition, top half of upper heat exchangers is protruding beyond recuperator case flanges and integrated through the access hole in the floor panel of supply and exhaust plant into supply chamber with tight connection of recuperator case flanges to the floor panel and of loose ends of upper heat exchangers to side walls of supply air chamber, recuperator is integrated by top ridges of upper heat exchangers into the main hole of intermediate horizontal partition, supply and exhaust plant features transverse partition in the main hole of intermediate horizontal partition, mounted on vertical partition of recuperator and connected to top panel of supply and exhaust plant thus forming air ducts connecting upper heat exchangers of recuperator with chambers of supply and exhaust plant, supply air cooler is made in the form of adiabatic damper of exhaust air with feeding water pipeline that are positioned in the exhaust chamber between controlled air valve and recuperator, bypass valve is installed in additional inlet pipe of supply chamber at the inlet before air filter, discharge pipe of exhaust chamber is positioned above inlet pipe of supply chamber, and side walls and bottom of recuperator feature maintenance hatches.EFFECT: improved energy efficiency of plant during cold and warm seasons, extended functional capabilities.9 cl, 17 dwg, 3 tbl

Description

The claimed solution relates to the field of supply and exhaust ventilation of industrial premises of data processing centers and hot shops, providing in the cold season recovery of the heat of the exhaust air, heating and humidification of the supply air to the specified temperature and relative humidity, and in the warm season, indirect adiabatic cooling supply air.

The claimed solution can be used in the metallurgical, flour, textile, chemical and other industries located in climatic regions with both low and low outside temperatures during the cold season, and with a long warm period typical of hot countries.

From the sources of scientific, technical and patent information, a large number of modifications of the supply and exhaust systems are known. Among them, those are selected that have a heat recovery unit for exhaust air and a supply air cooler with low energy efficiency and limited functionality, which makes it possible to improve them in the direction indicated in the claims of the claimed solution.

Known air handling unit with heat and moisture recovery modification "STANDART" (classic) model A-1400H2 company AirLASKA (Lithuania, Vilnius), described in the catalog of equipment July 2012 AirLASKA "Air handling units with heat and moisture recovery" on p.16-17. The catalog is published on the website:

http://www.airlaska.ru/images/dokumentacija/katalog_AirLaska_2012_www.pdf-Opera

The installation includes a supply and exhaust chamber. The supply chamber contains an inlet pipe, an air purifier, a two-stage recuperator, a fan, an air heater, and an exhaust pipe. The exhaust chamber contains an inlet pipe, an air purifier, a two-stage recuperator, a fan and an exhaust pipe. The air heater in the supply chamber is installed after the fan along the supply air. Each two-stage recuperator is made of two diagonally mounted and connected in series plate heat exchangers having vapor-permeable partitions. Both recuperators are connected to the inlet and outlet nozzles of the supply and exhaust chambers in a parallel circuit, which provides the simultaneous entry of external and exhaust air into two recuperators and the simultaneous exit of supply and exhaust air from two recuperators and the flow of these air flows into the corresponding fans.

The flow pattern of exhaust and supply air through two two-stage recuperators was obtained from LLC Airkon Group (Minsk) (www.prohlada.mfo), from Vitaliy Krasutsky <prohladainfo@gmail.com> November 20, 2012

In accordance with the attached diagram, the partitions in the installation casing are placed with the provision of:

- direct inlet of 50% of the volume of outdoor air entering the unit into the lower recuperator and direct inlet of 50% of the volume of exhaust air into the upper recuperator;

- receipts in a circular pattern of 50% of the volume of outdoor air into the upper recuperator and further to the supply air fan;

- receipts in a circular pattern of 50% of the exhaust air volume to the lower recuperator and further to the exhaust chamber fan.

Exhaust air flows coming in a circular pattern inlet pipe of the exhaust chamber - lower recuperator - exhaust fan are mixed in the side compartments of the unit with fresh air flows coming in in a circular pattern inlet pipe of the inlet chamber - upper recuperator - supply chamber fan, since have dividing channels.

AirLASKA air handling unit A-1400H2 has the following disadvantages:

1. The installation has low energy efficiency in the cold season F _x ,%, because Two-stage plate heat exchangers of the unit, connected to the supply and exhaust chambers in a parallel circuit, do not use all the energy efficiency possibilities of four plate heat exchangers located in the housing, which can be connected into one four-stage more efficient heat exchanger.

(в долях единицы 0,5) составит:2. In the manufacture of recuperators from aluminum plates, the total energy efficiency of four plate heat exchangers with the energy efficiency of one heat exchanger $$F_{Ri}^c=\mathrm{fifty}\%$$

(in units of 0.5) will be:

- for two two-stage, in parallel connected recuperators

; $${\Phi }_{R\Sigma }^c=\left[\mathrm{one}-{(\mathrm{one}-{\Phi }_{Ri}^c)}^2\right]\cdot \mathrm{one\; hundred}=\left[\mathrm{one}-{(\mathrm{one}-0,5)}^2\right]\cdot \mathrm{one\; hundred}=75\%$$

;

- for a four-stage recuperator

. $${\Phi }_{R\Sigma }^c=\left[\mathrm{one}-{(\mathrm{one}-{\Phi }_{Ri}^c)}^{\mathrm{four}}\right]\cdot \mathrm{one\; hundred}=\left[\mathrm{one}-{(\mathrm{one}-0,5)}^{\mathrm{four}}\right]\cdot \mathrm{one\; hundred}=93,75\%$$

.

Thus, the unused opportunity in the field of energy efficiency of four plate heat exchangers, made in the form of two two-stage unit heat exchangers connected in parallel, is

. $$\Delta {\Phi }_R=\left(\frac{{\Phi }_{Rc\mathrm{four}}-{\Phi }_{R\mathrm{<figure-callout\; id="2"\; label="c"\; filenames="00000108.png,00000110.png"\; state="\{\{state\}\}">c</figure-callout>}2}}{{\Phi }_{Rc2}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{93,75-75}{75}\right)\cdot \mathrm{one\; hundred}=25\%$$

.

3. Installation has limited functionality:

a) cannot be used for industrial premises, as plate heat exchangers of two-stage heat exchangers have vapor-permeable baffle plates through which harmful gases will flow from exhaust air to the supply air together with water vapor;

b) does not allow efficient cooling of the supply air in the warm season, because there is no supply air cooler in the installation;

c) does not allow for recirculation ventilation without mix and with mix in the recirculated air of various amounts of fresh outdoor air, because there is no air mixing chamber with a recirculation valve and a third fan in the installation;

g) does not provide a given volumetric flow of heated air into the room, because the air heater in the supply chamber is located after the fan, which causes an imbalance in the air exchange;

e) it is not possible to replace heat exchange cassettes with vapor-permeable plates in heat exchangers of the installation with heat-exchange cassettes with metal plates, because recuperators are made without a bypass air valve, the absence of which does not allow the installation to defrost on the plates of the recuperator, which is formed in the air exhaust line from freezing of condensate at low negative outside temperatures;

f) does not provide cooling of the supply air with equal temperatures at the inlets of the installation (t _beats = t ₁ ). With a temperature difference at the inlet of the recuperator Δt _bx = t _beats -t ₁ = 0, the temperature at the outlet of the recuperator t _R1 in the supply line will not decrease during the warm season and will remain equal to the outdoor temperature t ₁ , i.e. t _R1 = t ₁ , which confirms the calculation according to the formula at t _beats = t ₁ = 26 ° C and Ф _{RΣ (2)} = 75%.

t _R1 = t ₁ + Ф _{RΣ (2)} 10 ^-2 (t _beats -t ₁ ) = 26 + 75 · 10 ^-2 (26-26) = 26 ° C.

g) does not provide a direct emission of air removed from the room, bypassing the recuperator; This mode is necessary to eliminate the consequences of a fire in the production room.

The presence of the listed functional limitations of the A-1400H2 installation of AirLASKA does not allow the use of this installation for the organization of supply and exhaust ventilation in industrial premises.

The known Adia Vent® recirculation unit for cooling enclosed spaces of the company Hoval (Liechtenstein), described by United Elements in the article "Hoval Adia Vent®. Recirculation unit for cooling enclosed spaces ", published in the journal" Plumbing. Heating. Air conditioning ”7/2007, p.89. The article is attached.

The unit consists of a closed chamber in which a two-stage recuperator is installed, made of two vertically mounted plate heat exchangers, a water tank, a pump, an adiabatic humidifier for outdoor air spraying water to a highly dispersed aerosol, two fans for supplying exhaust and external air to the heat exchanger, and also two air filters for cleaning exhaust and outdoor air. Through the walls of the chamber, two air supply circuits (exhaust from the room and outdoor) are connected to the recuperator. The exhaust air circuit is connected to the upper plate heat exchanger of the recuperator and is made according to the recirculation circuit, being closed, since the air ducts are hermetically connected to the heat exchanger at the inlet and outlet of it. The external air circuit is connected to the lower plate heat exchanger of the recuperator and is open relative to the upper heat exchanger. In this case, the external air supply duct is not connected to the inlet of the upper heat exchanger, providing external air supply to the humidifier zone, and the external air exhaust duct is hermetically connected to the outlet of the lower heat exchanger. The upper and lower heat exchangers of the recuperator are hermetically interconnected. An air filter and a fan are installed in front of the upper heat exchanger in the exhaust line, which returns the air cooled in the recuperator to the room. The exhaust line fan is connected to the chamber, which can mix fresh air (up to 20%) into the recirculation loop.

Outside air is first cooled when passing through the lower heat exchanger, and then, with adiabatic humidification of ≈6 ° C, the cooled air enters the upper heat exchanger, cooling its plates. The exhaust air from the room warm air passes through the cooled upper heat exchanger, removes the accumulated cold from its plates and returns to the room in a cooled form.

Outside air that has passed through the recuperator is removed at the outlet of the lower heat exchanger by a fan in the suction mode and is discharged into the atmosphere.

The Adia Vent recirculation unit has the following disadvantages:

при охлаждении воздуха, так как пластинчатый рекуператор выполнен двухкаскадным.1. Has low dry energy efficiency $$F_{R\Sigma }^c$$

when cooling the air, since the plate heat exchanger is made in two stages.

2. Has limited functionality:

a) can not be used in the cold season, because it does not have an air heater;

b) does not provide cooling of the outdoor air in the lower heat exchanger with equal temperatures at the inlet to the recuperator (t _beats = t ₁ ), because An adiabatic humidifier that cools outside air by 6 ° C is installed between the lower and upper plate heat exchangers.

When the temperature difference at the inlet of the installation Δt _I = t _beats -t ₁ = 0, the temperature at the outlet of the lower heat exchanger t _R1 in the supply line will not decrease and will remain equal to the outdoor temperature t ₁ , i.e. t _R1 = t ₁ , which confirms the calculation according to the formula at t _beats = t ₁ = 26 ° C

. $$t_{R\mathrm{one}}=t_{\mathrm{one}}+{\Phi }_R^c\cdot {10}^{-2}(t_{\mathrm{at}d}-t_{\mathrm{one}})=26+\mathrm{fifty}\cdot {10}^{-2}(26-26)={26}^{\mathrm{about}}\mathrm{FROM}$$

.

Known supply and exhaust installation with heat recovery of exhaust air and cooling the supply air in a heat exchanger with forced circulating refrigerant, shown in Fig.6.9, p.38 of the training manual: Voskresensky V.E. Pneumatic conveying, dust collection and ventilation systems at woodworking enterprises. Theory and practice: in 2 vol. - vol. 2, part 2: Ventilation systems: a training manual. St. Petersburg: ABOK North-West, 2012. - 704 pp., Ill., Fig. 6.9.

The installation contains a supply and exhaust chambers separated by a horizontal intermediate partition with the main and additional windows, the main of which is equipped with a recuperator made of a single-section cross-flow and diagonally installed plate heat exchanger with a bypass valve, and a controllable recirculating air valve is integrated in the additional window, a supply the chamber contains an inlet pipe, a controlled inlet insulated air valve, an air purifier, a mixing chamber in the spirit with a controlled air valve at the inlet, a heater block with a bypass valve, an air cooler made in the form of a heat exchanger with forced recirculating refrigerant, a fan block and an exhaust pipe, an exhaust chamber contains an inlet pipe, an air cleaner, a fan block, a controlled air valve at the inlet to the recuperator and exhaust pipe. As a refrigerant (working medium) can be: chilled water, a mixture of water and glycol, freon (for example, R-22).

Despite the large number of coinciding features of the prototype and the claimed solution, the lack of distinctive features of the latter in the prototype does not provide a technical result consisting in increasing the energy efficiency of the installation in the cold and warm period of the year and expanding its functionality for the following reasons:

, %.1. The installation has a single-stage plate heat exchanger built into the main window of the horizontal intermediate partition, which has low energy efficiency $${\Phi }_{R\Sigma }^c$$

,%.

. (Рекуператоры пластинчатые REC Компания «Вентикон» ventx.ru/rekuperatory…plastikchatue.ru).The dry energy efficiency of a single-stage (single-section) plate cross-flow recuperator REC at an air velocity through the recuperator ν = 3.75 m / s is $${\Phi }_{R\Sigma }^c=\mathrm{fifty}\%$$

. (Lamellar recuperators REC Company "Venton" ventx.ru/rekuperatory...plastikchatue.ru).

, кВт·ч/м³.2. The air cooler in the installation is made in the form of a heat exchanger with forced circulation refrigerant, which can be: chilled water, a mixture of water and glycol, freon, and has high specific energy consumption for air cooling $$N_{\mathrm{about}xl}^{\mathrm{at}d}$$

, kW · h / m ³ .

3. Installation has limited functionality.

a) it does not allow to carry out recirculation regimes during the cold season with a mixture of different percent of fresh air (30%, 70%) and preheating of the air mixture in the air heater to the required temperature, because there is no third fan with an engine having a frequency converter; recirculation modes mixed with a different percentage of fresh outdoor air are needed to replace heavily polluted industrial premises with fresh air at night and to prepare the indoor air for a day shift;

b) it does not allow frost defrosting on the plates of the recuperator without a bypass valve in the recuperator, which increases the dimensions and cost of the recuperator, and also increases the pressure loss in the recuperator when external air passes through the bypass of the recuperator ΔP, Pa, which affects the increase in pressure in the fan H _c , Pa, inlet chamber and increase in energy consumption for defrosting.

c) it does not allow to carry out cooling of the supply air in the warm season at t ₁ <t _beats using cooler atmospheric air as a removable one that provides cooling of the recuperator and by exhausting the room exhaust air into the atmosphere, bypassing the recuperator, because in the exhaust chamber before entering the recuperator there are no additional inlet and outlet pipes with insulated air valves;

d) when the temperatures at the inlet of the unit are equal, t _beats = t ₁ and Δt _bx = t _beats -t ₁ = 0, the recuperator in the warm season does not cool the outside air (t _R1 = t ₁ ), which causes increased energy consumption for cooling the air in forced-circulation heat exchanger.

Q (N) = G _c · C _s.s. (t ₁ -t _cool ) / 3600

instead of reduced energy consumption at t _beats ≠ t ₁

Q (N) = G _s · C _s.s (t _R1 -t _okhl ) / 3600,

where indicated:

Q (N) - the necessary cooling capacity of the air cooler, kW;

G _c - mass flow of the dry part of the cooled air, kg / h;

C _r.s - specific mass heat capacity of dry air, C _r.s. = 1.005 kJ / (kg · K);

3600 is the conversion factor of kilojoules to kilowatts (1 kWh = 3600 kJ);

t ₁ - outdoor temperature in the warm season, ° C;

t _cool - the required temperature at the outlet of the cooler, ° C;

t _R1 - air temperature at the outlet of the recuperator in the supply line, ° C.

e) it does not allow due to the absence of a humidifier in the supply chamber to moisten the supply air heated in the heat exchanger and the air heater during the cold season, which dries out very much due to heating, which does not provide normative preparation of the air environment of the production room by humidity parameters and, as a result, leads to deterioration of sanitary -hygienic working conditions in the production room, causing respiratory diseases of workers.

So, in the coldest five-day period of St. Petersburg (t ₁ = -26 ° C, φ ₁ = 83%) when the outside air is heated from t ₁ = -26 ° C to t ₂ = 21 ° C, the relative humidity drops from φ ₁ = 83% to φ ₂ = 1.9%. In the absence of a humidifier in the supply chamber, the supply air with a relative humidity of φ ₂ = 1.9% is supplied by the air distributor to the working area of the room. The optimal relative humidity of the industrial premises, providing a microclimate in the working area, is in the range φ _opt = 40-60%.

f) does not allow the regime of exhaust air exhaust into the atmosphere and direct supply of external air to the supply chamber without the passage of air flows past the recuperator, because in the exhaust chamber there is no additional exhaust pipe with a controlled shut-off air valve at the entrance to the main ventilation unit of the chamber; and in the supply chamber there is no additional inlet pipe: the mode is necessary in case of fire in the production room and liquidation of the consequences of the fire.

g) in the installation, the inlet pipe of the supply chamber is located above the exhaust pipe of the exhaust chamber, which requires to ensure the intake of clean external air into the supply chamber and to disperse polluted emissions away from the clean air intake point by connecting long air ducts to the inlet pipe inlet and the exhaust pipe outlet pipe, directed in different directions.

The task of reducing energy consumption for heating and cooling the supply air in the installation and improving the sanitary and hygienic conditions of work in the production room, the implementation of which the claimed solution is aimed at, consisted in further improving the known design of the supply and exhaust system, which includes a heat recovery unit for the removed air and a cooler supply air, and obtaining a technical result - increasing the energy efficiency of the installation in cold and warm periods of the year and expanding its functionality.

The achievement of the above technical results is ensured by the fact that the supply and exhaust unit with heat recovery of the extract air and indirect adiabatic cooling of the supply air, comprising floor and ceiling panels, supply and exhaust chambers separated by a horizontal intermediate partition with the main and additional windows, into the main of which a diagonally mounted cross-flow plate heat exchanger is built-in, having inflow and exhaust lines, and an additional window Roen is a controlled recirculation air valve, the supply chamber contains an inlet pipe, a controlled inlet insulated air valve, an air cleaner, a bypass valve, a mixing chamber with a controlled air valve at the inlet, an air heater unit, a fan unit and an outlet pipe, an exhaust chamber contains an air cleaner, a fan unit controlled air valve installed at the inlet to the recuperator, inlet and outlet pipes, supply air cooler, characterized in that the supply chamber equipped with an additional inlet pipe with an air purifier located on one of the side panels of the air mixing chamber, the exhaust chamber is equipped with an additional controlled air valve installed at the outlet of the main fan unit, an additional exhaust pipe with a controlled outlet insulated air valve mounted on one of the side panels of the fan block, and an additional inlet pipe located between the controlled and additional controlled air valves on one of the side panels of the exhaust chamber controlled by an inlet insulated air valve and an air purifier located in the said additional inlet port of the exhaust chamber, the recuperator is made of a housing with side and end walls, a bottom, a condensate collecting pan with a drain fitting and a siphon, and at least four-stage of plate heat exchangers connected in series by the ribs, which are placed in the heat exchanger housing in two vertical rows separated by a vertical partition which is hermetically connected to the side ribs of the heat exchangers, while the outer side ribs of the vertical rows of heat exchangers are hermetically connected to the side walls of the heat exchanger housing, the ends of the heat exchangers are connected to the end walls of the heat exchanger housing with the formation of internal and external air channels between the heat exchangers of each vertical row, the lower heat exchangers are connected by a closing link, which together with the bottom forms air channels connecting the rows of heat exchangers in the exhaust lines and of the flow, in addition, the floor panel of the supply and exhaust unit is equipped with an assembly window placed coaxially with the main window in the horizontal intermediate partition, the upper half of the upper heat exchangers is protruding beyond the flanges of the heat exchanger housing and is integrated through the installation window in the floor panel of the supply and exhaust unit into the supply chamber with tight connection of the flanges of the heat exchanger housing to the floor panel and the free ends of the upper heat exchangers to the side walls of the supply air chamber ha, the recuperator is integrated by the upper fins of the upper heat exchangers into the main window of the horizontal intermediate partition, the supply and exhaust unit is equipped with a vertical transverse partition, which is located in the main window of the horizontal intermediate partition, is rigidly mounted on the vertical partition of the recuperator and hermetically connected to the ceiling panel of the supply and exhaust unit with the formation of air channels communicating the upper heat exchangers of the recuperator with the chambers of the supply and exhaust unit, oh the supply air cooler is made in the form of an adiabatic extract air humidifier with an inlet water supply, which are located in the exhaust chamber between the controlled air valve and the recuperator, the bypass valve is installed in the additional inlet pipe of the supply chamber at the inlet in front of the air purifier and is made insulated, the exhaust pipe of the exhaust chamber is located above the inlet a supply pipe, and the side walls and the bottom of the heat exchanger housing are equipped with service hatches.

Preferably, in the manufacture of the four-stage heat exchanger, the closing link is made in the form of a closing plate, which is rigidly connected to the lower ribs of the lower heat exchangers, and its ends are hermetically connected to the end walls of the heat exchanger housing, under the closing link of the lower heat exchangers there is a bottom of the heat exchanger housing.

Preferably, in the manufacture of the four-stage recuperator, the closing link of the lower heat exchangers is made with a window in which a condensate collection tray is integrated, rigidly connected to the service hatch of the bottom of the recuperator housing by racks, and a drain fitting is mounted on the condensate collection tray and is made with a transit passage through the service hatch of the bottom heat exchanger housing, under which a siphon is installed.

Preferably, in the manufacture of the five-stage heat exchanger, the closing link is made in the form of a closing diagonally mounted plate heat exchanger, which is hermetically connected to the lower heat exchangers of the heat exchanger and the lower edge is rigidly mounted on the bottom of the heat exchanger housing, the condensate collection tray is placed in the air channel connecting the rows of heat exchangers in the air exhaust line .

Preferably, in the manufacture of a six-stage recuperator, the closing link is made in the form of a closing plate, which is rigidly connected to the lower ribs of the lower heat exchangers, and its ends are hermetically connected to the end walls of the heat exchanger housing, under the closing link of the lower heat exchangers there is a bottom of the heat exchanger housing.

Preferably, in the manufacture of the heat exchanger with a six-stage condensate drain pan in the heat exchanger, it is integrated in the service hatch located in the bottom of the heat exchanger housing.

Preferably, in the humid treatment of the supply air, the supply chamber is provided with an adiabatic supply air humidifier with a supply pipe located behind the air heater.

Preferably, when mixing outdoor air with exhaust air in the proportions of 30% and 70%, respectively, the exhaust chamber is equipped with an additional fan unit with a frequency converter located at the outlet of the recuperator.

Preferably, in the forced cooling mode of the supply air, the supply and exhaust unit is equipped with an additional adiabatic air humidifier located in the recuperator on a condensate collecting tray with a water supply to it.

The evidence of the materiality of the differences and the relationship of the distinguishing features with the achieved technical results are disclosed sequentially in the following order:

1. Improving the energy efficiency of the installation in the cold season _{f x} ,%.

2. Improving energy efficiency in the warm season, f _t ,%.

3. Extension of installation functionality.

The technical result, which consists in increasing the energy efficiency of the installation in the cold period of the year Ф _x ,%, is ensured by the creation of a highly efficient recuperator with a different number of cascades (four-stage, five-stage, six-stage) having the same dimensions along the length, and embedding a multi-stage recuperator in the claimed installation.

Below is a comparison of the total dry energy efficiency of multi-stage plate heat exchangers with dry energy efficiency of a single-stage plate heat exchanger installation of the prototype.

The total dry energy efficiency of multi-stage heat exchangers made of diagonally mounted cross-flow plate heat exchangers with metal plates with a series connection of heat exchangers and countercurrent flow of exhaust and supply air in the heat exchanger is calculated by the formula

, $${\Phi }_{R\Sigma }^c=\left[\mathrm{one}-{(\mathrm{one}-{\Phi }_{Ri}^c)}^n\right]\cdot \mathrm{one\; hundred},\%$$

,

- сухая энергетическая эффективность одного пластинчатого теплообменника в долях единицы, n - число теплообменников в рекуператоре.Where $${\Phi }_{Ri}^c$$

- dry energy efficiency of one plate heat exchanger in fractions of a unit, n is the number of heat exchangers in the recuperator.

зависит от скорости прохождения воздушного потока через теплообменник V=(1÷5) м/с и достигает при использовании алюминиевых пластин максимального значения $${\Phi }_{Ri}^c=59\%$$

при V=1 м/с. Но при этом растут габариты теплообменника и рекуператора и их стоимость. Поэтому с целью уменьшения габаритов и стоимости пластинчатые теплообменники проектируют со скоростью, не превышающей V=3,7 м/с, которой соответствует энергетическая эффективность теплообменника $${\Phi }_{Ri}^c=50\%$$

(в долях единицы 0,5).Value $${\Phi }_{Ri}^c$$

depends on the speed of air flow through the heat exchanger V = (1 ÷ 5) m / s and reaches the maximum value when using aluminum plates $${\Phi }_{Ri}^c=59\%$$

at V = 1 m / s. But at the same time, the dimensions of the heat exchanger and recuperator and their cost are growing. Therefore, in order to reduce the size and cost, plate heat exchangers are designed at a speed not exceeding V = 3.7 m / s, which corresponds to the energy efficiency of the heat exchanger $${\Phi }_{Ri}^c=\mathrm{fifty}\%$$

(in fractions of a unit of 0.5).

The dry energy efficiency of a single-stage recuperator of the prototype plant is

. $${\Phi }_{R\Sigma (\mathrm{one})}^c={\Phi }_{Ri}^c=\mathrm{fifty}\%$$

.

составит:The total dry energy efficiency of the inventive multi-stage recuperators with $${\Phi }_{Ri}^c=0,5$$

will be:

- for a four-stage recuperator

; $${\Phi }_{R\Sigma (\mathrm{four})}^c=\left[\mathrm{one}-{(\mathrm{one}-0,5)}^{\mathrm{four}}\right]\cdot \mathrm{one\; hundred}=93,75\%$$

;

- for a five-stage recuperator

; $${\Phi }_{R\Sigma (5)}^c=\left[\mathrm{one}-(\mathrm{one}-0,5)5\right]\cdot \mathrm{one\; hundred}=96,8\%$$

;

- for a six-stage recuperator

. $${\Phi }_{R\Sigma (6)}^c=\left[\mathrm{one}-{(\mathrm{one}-0,5)}^6\right]\cdot \mathrm{one\; hundred}=98,\mathrm{four}\%$$

.

Moreover, the increase in dry energy efficiency of multi-stage recuperators ΔF,%, embedded in the inventive installation, compared with the energy efficiency of a single-stage recuperator of the prototype installation is

- for a four-stage recuperator

; $$\Delta {\Phi }_{\mathrm{four}}=\left(\frac{{\Phi }_{R\Sigma (\mathrm{four})}^c-{\Phi }_{R\Sigma (\mathrm{one})}^c}{{\Phi }_{R\Sigma (\mathrm{one})}^c}\right)\cdot \mathrm{one\; hundred}=\left(\frac{93,75-\mathrm{fifty}}{\mathrm{fifty}}\right)\cdot \mathrm{one\; hundred}=87,5\%$$

;

- for a five-stage recuperator

; $$\mathrm{<figure-callout\; id="5"\; label="\Delta \; \Phi "\; filenames="00000114.png,00000117.png"\; state="\{\{state\}\}">\Delta \; </figure-callout>}{\Phi }_{}{}_5=\left(\frac{{\Phi }_{R\Sigma (5)}^c-{\Phi }_{R\Sigma (\mathrm{one})}^c}{{\Phi }_{R\Sigma (\mathrm{one})}^c}\right)\cdot \mathrm{one\; hundred}=\left(\frac{96,8-\mathrm{fifty}}{\mathrm{fifty}}\right)\cdot \mathrm{one\; hundred}=93,6\%$$

;

- for a six-stage recuperator

. $$\mathrm{<figure-callout\; id="6"\; label="\Delta \; \Phi "\; filenames="00000113.png,00000114.png"\; state="\{\{state\}\}">\Delta \; </figure-callout>}{\Phi }_{}{}_6=\left(\frac{{\Phi }_{R\Sigma (6)}^c-{\Phi }_{R\Sigma (\mathrm{one})}^c}{{\Phi }_{R\Sigma (\mathrm{one})}^c}\right)\cdot \mathrm{one\; hundred}=\left(\frac{98,\mathrm{four}-\mathrm{fifty}}{\mathrm{fifty}}\right)\cdot \mathrm{one\; hundred}=96,8\%$$

.

The increase in the energy efficiency of the installation in the cold season F _x ,% when using multi-stage recuperators compared to single-stage recuperators is determined in the following sequence.

1. The temperature of the air flow at the outlet of the recuperator in the supply line t _{R1 is} determined by the formula

$$t_R{}_{\mathrm{one}}=t_{\mathrm{one}}+{\Phi }_{R\Sigma }^c\cdot {10}^{-2}(t_{\mathrm{at}d}-t_{\mathrm{one}})$$

where t _beats is the temperature of the air removed from the room (exhaust), ° C; t ₁ - outdoor temperature for the coldest five-day period of the region in which the claimed installation will operate, ° C.

The calculation of t _R1 values is given for the climatic conditions of St. Petersburg (t ₁ = -26 ° C and t _beats = 18 ° C). For these conditions, the air temperature at the outlet of the recuperator t _R1 will be:

- for a single-stage recuperator of a prototype installation having Ф _{R∑ (1)} = 50%

t _R1 = -26 + 50 · 10 ^-2 (18 + 26) = - 4 ° C;

- for a four-stage recuperator having $${\Phi }_{R\Sigma (\mathrm{four})}^c=93,75\%$$

t _R1 = -26 + 93.75 · 10 ^-2 (18 + 26) = 15.25 ° C;

- for a five-stage recuperator having $${\Phi }_{R\Sigma (5)}^c=96,8\%$$

t _R1 = -26 + 96.8 · 10 ^-2 (18 + 26) = 16.6 ° C;

- for a six-stage recuperator having $${\Phi }_{R\Sigma (6)}^c=98,\mathrm{four}\%$$

t _R1 = -26 + 98.4 · 10 ^-2 (18 + 26) = 17.3 ° C;

2. The consumed thermal power is determined by the air heater Q _N , kW, in the coldest five-day period by the formula

Q _N = G _c · C _s.s. (t ₂ -t _R1 ) / 3600,

where G _c is the mass flow of dry air, kg / h; C _r.s. - specific mass heat capacity of dry air, kJ / (kg · K), C _r.s. = 1,005; 3600 - conversion factor kJ in kW, 1 kWh = 3600 kJ; t ₂ - air temperature at the outlet of the heater, ° C, t _R1 - air temperature after the recuperator in the line of air flow, ° C.

For the inventive installation, followed by humidification of the heated air in the supply chamber

, $${\mathrm{<figure-callout\; id="2"\; label="t"\; filenames="00000108.png,00000110.png"\; state="\{\{state\}\}">t</figure-callout>}}_2={\left[t_{R.s}^{\min }\right]}_{x\mathrm{about}l}+\Delta t_{\mathrm{about}xl}=\mathrm{fifteen}+6={21}^{\mathrm{about}}C$$

,

- минимально допустимая температура в производственном помещении для работ средней тяжести 116 в холодный период года, °C; Δt_охл - понижение температуры воздуха при его адиабатическом увлажнении, °C.Where $${\left[t_{R.s}^{\min }\right]}_{x\mathrm{about}l}$$

- the minimum allowable temperature in the production room for moderate work 116 in the cold season, ° C; Δt _okhl - lowering of air temperature at its adiabatic moistening, ° C.

For the installation of the prototype, followed by humidification of the heated air in the supply chamber

. $${\mathrm{<figure-callout\; id="2"\; label="t"\; filenames="00000108.png,00000110.png"\; state="\{\{state\}\}">t</figure-callout>}}_2={\left[t_{R.s}^{\min }\right]}_{x\mathrm{about}l}+\Delta t_{\mathrm{about}xl}=\mathrm{fifteen}+6={21}^{\mathrm{about}}C$$

.

For conditions (G _c = 10,000 kg / h, t ₂ = 21 ° C, C _r.s. = 1,005), the consumed heat output by the air heater of the installation Q _N , kW, in the coldest five-day period will be:

- when using a single-stage recuperator (t _R1 = -4 ° C) of the prototype installation

Q _N (1) = 10000 · 1.005 (21 + 4) / 3600 = 69.8 kW;

- when using a four-stage recuperator (t _R1 = 15.25 ° C)

Q _N (4) = 10000 · 1.005 (21-15.25) / 3600 = 16 kW;

- when using a five-stage recuperator (t _R1 = 16.6 ° C)

Q _N (5) = 10000 · 1.005 (21-16.6) / 3600 = 12.3 kW;

- when using a six-stage recuperator (t _R1 = 17.3 ° C)

Q _N (6) = 10000 · 1.005 (21-17.3) / 3600 = 10.3 kW.

3. The total expendable power is determined in the prototype installation in the coldest five-year period N _{Σ (1)} , kW

N _{Σ (1)} = Q _{N (1)} + N _s.pr. + N _s.out = 69.8 + 4.0 + 4.0 = 77.8 kW,

where N _u.pr , N _u.vt is the installed power of the fan motor in the _intake and exhaust lines, kW

N _u.pr -N _u.out = 4 kW.

4. The increase in the consumed power by the fan motors in the supply and exhaust lines of the inventive installation is determined, which takes place due to an increase in the number of heat exchangers in the recuperator

, $$\Delta N_i=\frac{L_B\Delta {\mathrm{<figure-callout\; id="3"\; label="H\; B\; i"\; filenames="00000111.png,00000117.png"\; state="\{\{state\}\}"><figure-callout\; id="6"\; label="H\; B\; i"\; filenames="00000113.png,00000114.png"\; state="\{\{state\}\}">H\; </figure-callout></figure-callout>}}_{Bi}}{3,6\cdot {10}^6\cdot {\eta }_B}$$

,

where L _B - supply air fan capacity, m ³ / h.

Defined from expression

L _B = G _c (1 + d _pr · 10 ^-3 ) / ρ _pr ,

where G _c is the mass flow of dry air, kg / h, G _s = 10000 kg / h; d _CR - moisture content of the supply air, g / kg dry. air With a relative humidity of the supply air φ _pr = 55% and t _pr = 15 ° C, d _pr = 5.83 g / kg dry. air ρ _CR - the density of the supply air, kg / m ³ is determined from the expression:

, $${\rho }_{PR}={\rho }_0\frac{P_{b\mathrm{but}R}\cdot T_0}{P_{b\mathrm{but}\mathrm{<figure-callout\; id="0"\; label="R"\; filenames="00000116.png"\; state="\{\{state\}\}">R</figure-callout>}0}\cdot T_{PR}}$$

,

where P _bar = 101000 Pa - barometric pressure in St. Petersburg; T _ol - supply air temperature, K;

T _pr = 273,15 + t _ave = 273.15 + 15 = 288,15 K,

T ₀ , P _bar0 - temperature (K), barometric pressure at standard air parameters (t ₀ = 20 ° C, (φ ₀ = 50%), T ₀ = 293.15 K, P _bar0 = 101345 Pa.

. $${\rho }_{PR}=\mathrm{one},2\frac{101000\cdot 293,\mathrm{fifteen}}{101345\cdot 288,\mathrm{fifteen}}=\mathrm{one},216{\text{kg / <figure-callout id="3" label="m" filenames="00000111.png,00000117.png" state="{{state}}">m</figure-callout>}}^{\text{3}}$$

.

Wherein

L _B = 10000 (1 + 5.83 · 10 ^-3 ) / 1.216 = 8270 m ³ / h.

ΔH _B is the increase in pressure developed by the fan due to the increase in the number of heat exchangers in the recuperator, Pa; η _B - fan efficiency, 775 = 0.82.

The values of ΔH _B (Pa) are determined by the formula

ΔH _B = ΔP _pt (n _pt -1),

where ΔP _pt is the hydraulic resistance of one plate heat exchanger at an air flow velocity in it of ν = 3.7 m / s, Pa; ΔP _pt = 150 Pa; n _PTO - the number of plate heat exchangers in a multi-stage heat exchanger; (n _pt -1) - the number of additionally installed plate heat exchangers in the recuperator of the inventive installation.

The values of ΔH _B (Pa) for the electric motors of the fans of the supply and exhaust lines of the inventive installation will be:

- when using a four-stage recuperator

ΔH _{B (4)} = 150 (4-1) = 450 Pa;

- when using a five-stage recuperator

ΔH _{B (5)} = 150 (5-1) = 600 Pa;

- when using a six-stage recuperator

ΔH _{B (6)} = 150 (6-1) = 750 Pa.

The increase in power consumption by the electric motors of the fans of the supply and exhaust lines of the inventive installation will be ΔN _i (kW):

- when using a four-stage recuperator

; $$\Delta N_{(\mathrm{four})}=\frac{8270\cdot 450}{3,6\cdot {10}^6\cdot 0,82}=\mathrm{one},3\text{kw}$$

;

- when using a five-stage recuperator

; $$\Delta N_{(5)}=\frac{8270\cdot 600}{3,6\cdot {10}^6\cdot 0,82}=\mathrm{one},7\text{kw}$$

;

- when using a six-stage recuperator

. $$\Delta N_{(6)}=\frac{8270\cdot 750}{3,6\cdot {10}^6\cdot 0,82}=2,\mathrm{one}\text{kw}$$

.

5. The value of the consumed power by the electric motors of the fans of the supply lines N _pri and the hood N _{extracts of the} inventive installation is _determined :

- when using a four-stage recuperator

N _{ol (4)} = N _u.pr + ΔN ₍₄₎ = 4 + 1.3 = 5.3 kW;

N out ₍₄₎ = N _{U. out} + ΔN ₍₄₎ = 4 + 1.3 = 5.3 kW.

- when using a five-stage recuperator

N _{ol (5)} = N _ypr + ΔN ₍₅₎ = 4 + 1.7 = 5.7 kW;

N out ₍₄₎ = N _out + ΔN ₍₄₎ = 4 + 1.7 = 5.7 kW.

- when using a six-stage recuperator

N _{ol (4)} = N _Upr + ΔN ₍₄₎ = 4 + 2.1 = 6.1 kW;

_{Nout (4)} = N _in.out + ΔN ₍₄₎ = 4 + 2.1 = 6.1 kW.

6. The total consumed power is determined by the air heater and electric motors of the fans of the claimed installation in the coldest five-day period:

- when using a four-stage recuperator

N _{Σ (4)} = Q _{N (4)} + N _{ol (4)} + N out ₍₄₎ = 16 + 5.3 + 5.3 = 26.6 kW;

- when using a five-stage recuperator

N _{Σ (5)} = Q _{N (5)} + N _{ol (5)} + N out ₍₅₎ = 12.3 + 5.7 + 5.7 = 23.7 kW;

- when using a six-stage recuperator

N _{Σ (6)} = Q _{N (6)} + N _{ol (6)} + N out ₍₆₎ = 103 + 6.1 + 6.1 = 22.5 kW.

7. Determines the increase in energy efficiency of the inventive installation in the cold season when replacing a single-stage recuperator of a prototype installation with a multi-stage:

- when using a four-stage recuperator

. $${\Phi }_{x(\mathrm{four})}=\left(\frac{\Delta N_{\mathrm{one}-\mathrm{four}}}{N_{\Sigma (\mathrm{one})}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{N_{\Sigma (\mathrm{one})}-N_{\Sigma (\mathrm{four})}}{N_{\Sigma (\mathrm{one})}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{77,8-26,6}{77,8}\right)\cdot \mathrm{one\; hundred}=65,8\%$$

.

- when using a five-stage recuperator

. $${\Phi }_{x(5)}=\left(\frac{\Delta N_{\mathrm{one}-5}}{N_{\Sigma (\mathrm{one})}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{N_{\Sigma (\mathrm{one})}-N_{\Sigma (5)}}{N_{\Sigma (\mathrm{one})}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{77,8-23,7}{77,8}\right)\cdot \mathrm{one\; hundred}=69,5\%$$

.

- when using a six-stage recuperator

. $${\Phi }_{x(6)}=\left(\frac{\Delta N_{\mathrm{one}-6}}{N_{\Sigma (\mathrm{one})}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{N_{\Sigma (\mathrm{one})}-N_{\Sigma (6)}}{N_{\Sigma (\mathrm{one})}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{77,8-22,5}{77,8}\right)\cdot \mathrm{one\; hundred}=71,\mathrm{one}\%$$

.

The resulting advantage in increasing the energy efficiency of the inventive installation _{f x} ,%, in the cold season is provided by the hallmark 1.

Distinctive feature 1

The supply chamber is equipped with an additional inlet pipe with an air purifier located on one of the side panels of the air mixing chamber, the recuperator is made of a housing with side and end walls, a bottom, a condensate collection tray with a drain fitting and a siphon and at least four stages in series fins of plate heat exchangers, which are placed in the heat exchanger housing in two vertical rows separated by a vertical partition, which is hermetically connected to the side p heat exchanger ribs, while the outer side ribs of the vertical rows of heat exchangers are hermetically connected to the side walls of the heat exchanger housing, the ends of the heat exchangers are connected to the end walls of the heat exchanger housing with the formation of internal and external air channels between the heat exchangers of each vertical row, the lower heat exchangers are connected by a closing link, which together with the bottom forms air ducts connecting the rows of heat exchangers in the exhaust and supply lines, in addition, the floor panel the exhaust system is equipped with a mounting window coaxially with the main window in the horizontal intermediate partition, the upper half of the upper heat exchangers is protruding beyond the flanges of the heat exchanger housing and is integrated through the installation window in the floor panel of the air handling unit into the air supply chamber with a tight connection of the heat exchanger flanges to the floor panel and the free ends of the upper heat exchangers to the side walls of the supply air chamber, the recuperator is integrated with upper ribs external heat exchangers in the main window of the horizontal intermediate partition, the supply and exhaust unit is equipped with a vertical transverse partition, which is located in the main window of the horizontal intermediate partition, is rigidly mounted on the vertical partition of the recuperator and hermetically connected to the ceiling panel of the supply and exhaust unit with the formation of air channels communicating the upper heat exchanger heat exchangers with chambers of the supply and exhaust installation, a bypass valve is installed in an additional the inlet pipe of the supply chamber at the inlet in front of the air purifier is made insulated, and the side walls and the bottom of the recuperator case are equipped with service hatches.

Preferably, in the manufacture of the four-stage heat exchanger, the closing link is made in the form of a closing plate, which is rigidly connected to the lower ribs of the lower heat exchangers, and its ends are hermetically connected to the end walls of the heat exchanger housing, under the closing link of the lower heat exchangers there is a bottom of the heat exchanger housing.

Preferably, in the manufacture of the four-stage recuperator, the closing link of the lower heat exchangers is made with a window in which a condensate collection tray is integrated, rigidly connected to the service hatch of the bottom of the recuperator housing by racks, and a drain fitting is mounted on the condensate collection tray and is made with a transit passage through the service hatch of the bottom heat exchanger housing, under which a siphon is installed.

Preferably, in the manufacture of the five-stage heat exchanger, the closing link is made in the form of a closing diagonally mounted plate heat exchanger, which is hermetically connected to the lower heat exchangers of the heat exchanger and the lower edge is rigidly mounted on the bottom of the heat exchanger housing, the condensate collection tray is placed in the air channel connecting the rows of heat exchangers in the exhaust line air.

Preferably, in the manufacture of a six-stage recuperator, the closing link is made in the form of a closing plate, which is rigidly connected to the lower ribs of the lower heat exchangers, and its ends are hermetically connected to the end walls of the heat exchanger housing, under the closing link of the lower heat exchangers there is a bottom of the heat exchanger body.

Preferably, in the manufacture of a six-stage recuperator, the condensate collecting pan in the recuperator is integrated in the service hatch located in the bottom of the recuperator body.

Distinctive feature 1 provides the creation of energy-saving multi-stage recuperators (four-stage, five-stage and six-stage) and their integration into the inventive installation without a significant increase in its length compared to the prototype installation, as well as their normal operation in the cold season and ease of service.

The technical result, which consists in increasing the energy efficiency of the inventive installation in the warm period of the year Ф _t ,%, is ensured by replacing the heat exchanger for cooling the supply air of the heat exchanger with forced circulating refrigerant (for example, freon) of the prototype installation with an energy-saving indirect adiabatic cooling system of the supply air, including multi-stage recuperator. Moreover, the supply air cooler in the inventive installation is made in the form of an adiabatic humidifier to be removed (exhaust air from the room). As an adiabatic humidifier in the inventive installation, a humidifier with water spraying through nozzles by a high-pressure pump (humiFog) is adopted, which has the smallest of all series of humidifiers specific energy consumption for spraying water into a highly dispersed aerosol equal to $$N_{RF}^{\mathrm{at}d}=0,004\text{kw}\cdot \text{h / kg}\text{.}$$

The energy consumption for cooling the air in the installation of the prototype and the inventive installation was calculated with the following initial data (outdoor temperature t ₁ = 26 ° C, temperature of air removed from the production room (exhaust) t _beats = 23 ° C, G _c - mass flow of dry air G _c = 10000 kg / h, the relative humidity of the removed air φ _beats = 55%.

Prototype Installation

The air flow temperature at the outlet of the single-stage recuperator in the supply line having Ф _{RΣ (1)} = 50% is determined by the formula

t _R1 = t ₁ + Ф _{RΣ (1)} · 10 ^-2 (t _beats -t ₁ ) = 26 + 50 · 10 ^-2 (23-26) = 24.5 ° C.

Power consumption by the refrigeration unit of the prototype installation with a single-stage recuperator, N ₍₂₎ , kW, is determined by the formula

. $$N_{(\mathrm{one})}^{\mathrm{about}xl}=G_{\mathrm{from}}\cdot C_{R\mathrm{from}}(t_{R\mathrm{one}}-t_{\mathrm{about}xl})/3600=\mathrm{10,000}\cdot \mathrm{one},005(24,5-17,5)/3600=19,5\text{kw}$$

.

where G _with - mass flow of dry air, kg / h; C _r.s. - specific mass heat capacity of dry air, kJ / (kg · K), C _r.s. = 1,005; _OHL t - temperature of the chilled air at the outlet of the refrigerant circuit, ° C, t _OHL = 17,5 ° C; 3600 is the conversion factor kJ in kW.

The inventive installation

The air flow temperature at the outlet of the multi-stage recuperator in the supply line during operation of one adiabatic humidifier is determined by the formula

, $$t_{R\mathrm{one}}=t_{\mathrm{one}}+{\Phi }_{R\Sigma i}\cdot {10}^{-2}\left(t_{\mathrm{at}d}^{\mathrm{at}\mathrm{at}}-t_{\mathrm{one}}\right)$$

,

- температура удаляемого воздуха на выходе из адиабатического увлажнителя, °C;Where $$t_{\mathrm{at}d}^{\mathrm{at}\mathrm{at}}$$

- temperature of the removed air at the outlet of the adiabatic humidifier, ° C;

, $$t_{\mathrm{at}d}^{\mathrm{at}\mathrm{at}}=t_{\mathrm{at}d}-\Delta t_{\mathrm{about}xl}=23-6={17}^{\mathrm{about}}C$$

,

where Δt _okhl - decrease in air temperature during its adiabatic moistening, ° C, Δt _okhl = 6 ° C.

The temperature at the outlet of the recuperator in the supply line of the inventive installation will be:

- when using a four- _stage recuperator having Ф _{RΣ (4)} = 93.75%

t _R1 = 26 + 93.75 · 10 ^-2 (17-26) = 17.6 ° C;

- when using a five-stage recuperator having Ф _{RΣ (5)} = 96.8%,

t _R1 = 26 + 96.8 · 10 ^-2 (17-26) = 17.3 ° C;

- when using a six-stage recuperator having _{f RΣ (6)} = 98.4%,

t _R1 = 26 + 98.4 · 10 ^-2 (17-26) = 17.1 ° C;

To determine the energy consumption for cooling the supply air in the inventive installation, it is necessary to determine the performance of the adiabatic humidifier according to the formula

G _SW = G _c (d ₃ -d ₂ ) 10 ^-3 ,

where G _c is the mass flow of dry air, kg / h; d ₂ - moisture content of the air removed from the room, g / kg dry. air (see table 1); d ₃ - moisture content of the air removed from the room at the outlet of the adiabatic humidifier, g / kg dry. air (see table 1).

Table 1

, φ, P_н, P_п для удаляемого и увлажненного воздуха для г. Санкт-Петербурга при P_бар=101000 ПаThe values of t _beats , $$t_{\mathrm{at}d}^{\mathrm{at}\mathrm{at}}$$

, φ, P _n , P _p for removed and humidified air for the city of St. Petersburg at P _bar = 101000 Pa Air temperature ° C Relative humidity (in fractions of a unit) Partial pressure of water vapor, Pa Moisture content d, g / kg dry. air $$d_i=622\frac{P_{Pi}}{P_{b\mathrm{but}R}-P_P{}_i}$$

Saturated P _ni Unsaturated P _pi = P _нi φ _i t _beats = 23 φ _i = 0.55 2810.4 1545.7 d ₂ = 9.66 After moisturizing $$t_{\mathrm{at}d}^{\mathrm{at}\mathrm{at}}=17$$

φ _i = 1,0 1937.9 1937.9 d ₃ = 12.17

With the obtained values of d ₂ = 9.66 g / kg dry. air and d ₃ = 12.17 g / kg dry. air humidifier capacity will be, kg / h

G _SW = 10,000 (12.17-9.66) 10 ^-3 = 25 kg / h.

The energy consumption for humidification of the exhaust air will be, kW · h

$$N_{\mathrm{at}\mathrm{at}}=G_{\mathrm{at}\mathrm{at}}{N}_{\mathrm{at}\mathrm{at}}^{\mathrm{at}d}=25\cdot 0,004=0,\mathrm{one}\text{kw}\cdot \text{h}$$

- удельные энергозатраты на увлажнение, кВт·ч/кг, $$N_{ув}^{уд}=0,004$$

.Where $$N_{\mathrm{at}\mathrm{at}}^{\mathrm{at}d}$$

- specific energy consumption for humidification, kW · h / kg, $$N_{\mathrm{at}\mathrm{at}}^{\mathrm{at}d}=0,004$$

.

The energy consumption for demineralization of the water sprayed in the nozzles in a reverse osmosis plant will be, kW · h.

$$N_{dm}=G_{\mathrm{at}\mathrm{at}}{N}_{dm}^{\mathrm{at}d}=25\cdot 0,004=0,\mathrm{one}\text{kw}\cdot \text{h}$$

- удельные энергозатраты на деминерализацию воды, $$N_{дм}^{уд}=0,004\text{ кВт}\cdot \text{ч/кг}$$

.Where $$N_{dm}^{\mathrm{at}d}$$

- specific energy consumption for demineralization of water, $$N_{dm}^{\mathrm{at}d}=0,004\text{kw}\cdot \text{h / kg}$$

.

The energy costs for indirect adiabatic cooling of the supply air in the inventive installation will be:

- when using one adiabatic humidifier

$$N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(\mathrm{one})}=N_{\mathrm{at}\mathrm{at}}+N_{dm}+N_{d.\mathrm{uh}.s.}=0,\mathrm{one}+0,\mathrm{one}+0,157=0,357\text{kw}\cdot \text{h}\text{.}$$

- during the work of two adiabatic humidifiers

$$N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(2)}=2N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(\mathrm{one})}=2\cdot 0,357=0,714\text{kw}\cdot \text{h}\text{.}$$

where N _doe - additional equivalent energy costs for the production of drinking water spent on air humidification, kW · h. Defined from expression

N _DEE = S _B / S _N ,

where S _B - the cost of water spent on humidification with one humidifier, rub .; S _N - the cost of electricity in St. Petersburg in 2012, rubles / kWh, S _N = 4.0.

Costs of drinking water in a reverse osmosis unit

G = 1,5G _{o.osm uv} = 1.5 × 25 = 37.5 = 0.037 kg m ³ water / h,

where 1.5 is a coefficient that takes into account the increase in drinking water consumption by a reverse osmosis unit compared to a humidifier.

The cost of drinking water for humidification with one humidifier

. $$S_B=G_{\mathrm{about}.\mathrm{about}\mathrm{from}m}\cdot S_{\mathrm{at}}^{\mathrm{at}d}=0,037\cdot 17=0,63\text{rub}\text{./h}$$

.

- стоимость питьевой воды, руб./м³; $$S_{в}^{уд}=17\text{ руб}{\text{./м}}^{\text{3}}$$

.Where $$S_{\mathrm{at}}^{\mathrm{at}d}$$

- the cost of drinking water, rubles / m ³ ; $$S_{\mathrm{at}}^{\mathrm{at}d}=17\text{rub}{\text{./<figure-callout id="3" label="m" filenames="00000111.png,00000117.png" state="{{state}}">m</figure-callout>}}^{\text{3}}$$

.

Additional equivalent energy costs for the production of drinking water spent on humidification with one humidifier

N _DEE = S _B / S _N = 0.63 / 4 = 0.157 kWh.

Improving the energy efficiency of the indirect adiabatic supply air cooler of the inventive installation compared to the freon cooler of the prototype installation N (1) = 19.5 kW in the warm season is:

- when using one adiabatic humidifier installed at the inlet to the recuperator

. $${\Phi }_{t(\mathrm{one})}=\left(\frac{N_{(\mathrm{one})}-N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(\mathrm{one})}}{N_{(\mathrm{one})}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{19,5-0,357}{19,5}\right)\cdot \mathrm{one\; hundred}=98,\mathrm{one}\%$$

.

- when using two adiabatic humidifiers (primary and secondary)

. $${\Phi }_{t(2)}=\left(\frac{N_{(\mathrm{one})}-N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(2)}}{N_{(\mathrm{one})}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{27,9-0,714}{27,9}\right)\cdot \mathrm{one\; hundred}=97,\mathrm{four}\%$$

.

The energy consumption for cooling the air in the warm season when using the inventive installation compared with the installation of the prototype are reduced:

- when using one adiabatic humidifier at Δt _cool = 7 ° C in

. $$n=\frac{N_{(\mathrm{one})}^{\mathrm{about}xl}}{N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(\mathrm{one})}}=\frac{19,5}{0,357}=54,6R\mathrm{but}s\mathrm{but}$$

.

- when using two adiabatic humidifiers Δt _okhl = 10 ° C in

, $$n=\frac{N_{(\mathrm{one})}^{\mathrm{about}xl}}{N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(2)}}=\frac{27,9}{0,714}=39R\mathrm{but}s$$

,

Where

, $$N_{(\mathrm{one})}^{\mathrm{about}xl}=G_c\cdot C_{p.c}\cdot \Delta t_{\mathrm{about}xl}/3600=\mathrm{10,000}\cdot \mathrm{one},005\cdot 10/3600=27,9\mathrm{to}\mathrm{AT}t$$

,

_OHL Δt = (t _R1 -t _OHL) 24,5-14,5 = 10 ° C.

The advantages obtained are provided by the distinctive features of 2.1 and 3.

Hallmark 2

The exhaust chamber is equipped with an additional controlled air valve installed at the outlet of the main fan unit, an additional exhaust pipe with a controlled output insulated air valve installed on one of the side panels of the fan unit, and an additional inlet pipe located between the controlled and additional controlled air valves on one from the side panels of the exhaust chamber controlled by an inlet insulated air valve and an air purifier located in the mentioned additional inlet branch pipe of the exhaust chamber, and the supply air cooler is made in the form of an adiabatic extract air humidifier with a supply pipe, which are placed in the exhaust chamber between the controlled air valve and the recuperator.

Hallmark 3

In the forced cooling mode of the supply air, the supply and exhaust unit is equipped with an additional adiabatic air humidifier located in the recuperator on the condensate collecting tray, with a water supply leading to it.

The increase in energy efficiency of the claimed installation in the warm season compared to the installation of the prototype is determined in the following sequence.

1. The consumed power is determined by the supply air cooler and the electric motors of the fans of the supply and exhaust lines of the prototype installation.

$$N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}=N_{(\mathrm{one})}\cdot N_{\mathrm{at}.PR}\cdot N_{\mathrm{at}.\mathrm{at}\mathrm{at}st}=19,5+\mathrm{four},0+\mathrm{four},0=27,5\mathrm{to}\mathrm{AT}t$$

2. The consumed power is determined by the supply air cooler and electric motors of the fans of the supply and exhaust lines of the inventive installation when using one adiabatic humidifier:

- when using a four-stage recuperator:

; $$N_{\Sigma (\mathrm{four})}^{\mathrm{about}xl}=N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(\mathrm{one})}\cdot N_{PR(\mathrm{four})}\cdot N_{\mathrm{at}st(\mathrm{four})}=0,357+5,3+5,3=\mathrm{eleven},0\mathrm{to}\mathrm{AT}t$$

;

- when using a five-stage recuperator:

; $$N_{\Sigma (5)}^{\mathrm{about}xl}=N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(\mathrm{one})}\cdot N_{PR(5)}\cdot N_{\mathrm{at}st(5)}=0,357+5,7+5,7=\mathrm{eleven},6\mathrm{to}\mathrm{AT}t$$

;

- when using a six-stage recuperator:

. $$N_{\Sigma (6)}^{\mathrm{about}xl}=N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(\mathrm{one})}\cdot N_{PR(6)}\cdot N_{\mathrm{at}st(6)}=0,357+6,\mathrm{one}+6,\mathrm{one}=12,6\mathrm{to}\mathrm{AT}t$$

.

3. Determines the increase in energy efficiency of the inventive installation in the warm season in comparison with the installation of the prototype:

- when using a four-stage recuperator:

$$F_{t(\mathrm{four})}=\left(\frac{\Delta N_{\Sigma (\mathrm{one}-\mathrm{four})}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}-N_{\Sigma (\mathrm{four})}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{27,5-\mathrm{eleven},0}{27,5}\right)\cdot \mathrm{one\; hundred}=60\%;$$

- when using a five-stage recuperator:

$$F_{t(5)}=\left(\frac{\Delta N_{\Sigma (\mathrm{one}-5)}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}-N_{\Sigma (5)}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{27,5-\mathrm{eleven},6}{27,5}\right)\cdot \mathrm{one\; hundred}=57,8\%;$$

- when using a six-stage recuperator:

$$F_{t(6)}=\left(\frac{\Delta N_{\Sigma (\mathrm{one}-6)}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}-N_{\Sigma (6)}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{27,5-12,6}{27,5}\right)\cdot \mathrm{one\; hundred}=54,2\%;$$

The technical result, which consists in expanding the functionality of the claimed installation compared to the installation of the prototype, is provided due to the following advantages:

1. Due to the multi-stage (four-stage, five-stage and six-stage) heat recovery unit, the installation can operate in the cold season in an extended range of negative outside temperatures, up to (-40 ° C). This advantage is provided by the hallmark 1.

в приточном воздухе и, как следствие, в рабочей зоне при изменении температуры наружного воздуха в холодный период года обеспечивает решение трех дополнительных проблем:2. In the cold season, the unit provides normative preparation of supply air with respect to relative humidity φ,%, which allows supplying fresh air directly to the working area of the production room with a microclimate and eliminating diseases of the upper respiratory tract in workers due to the low relative humidity of the supply air that occurred when using the installation of the prototype. Automatic maintenance of average optimum moisture content $${\varphi }_{\mathrm{about}Pt}^{\mathrm{from}R}=55\%$$

in the supply air and, as a result, in the working area when the temperature of the outside air changes during the cold season provides three additional problems:

- eliminates the formation of static electricity, the discharges of which can lead to explosions in premises of category B for fire and explosion safety, for example, in workshops for grinding plywood and white grinding;

- eliminates the formation of cracks, delamination and deformation of dried lumber and finished wood products;

- the spread of dust in the air of the working area is reduced, its precipitation is improved. These advantages are provided by the hallmark 4.

3. In the cold season, the installation provides two recirculation modes with a mixture of different amounts of fresh outside air (30%, 70%) in the recirculated air with additional heating of the air mixture in the air heater to the required temperature. This advantage is provided by the hallmark 5.

4. The unit provides options for supplying external air to the supply chamber in the cold season (defrosting mode of icy plates of heat exchanger cartridges) and in the warm season (direct feeding mode), bypassing the multi-stage recuperator, which allows multi-stage recuperators without bypass line and without bypass valves . This provides a reduction in the size and cost of recuperators, and, as a result, of the inventive installation.

The defrosting mode of the icy plates of the heat exchanger cassettes is provided by a distinctive feature 6 and the removal of exhaust warm air through the recuperator 8. The installation provides a direct supply of external air to the supply chamber and direct exhaust of exhaust air from the production room into the atmosphere, bypassing the recuperator.

The mode is applied:

- when extinguishing a fire in a production building and eliminating its consequences at any time of the year;

- provided t ₁ <t _beats in the summer season for effective cooling of the air environment of the room.

The mode is provided by the hallmarks 6 and 7.

6. The unit provides a forced supply air cooling mode used to cool the air of the data center premises (data centers) and hot shops. The mode is provided by distinctive features 3 and 7.

In forced air cooling mode:

- two adiabatic humidifiers are installed in the exhaust line of the recuperator;

- external, colder than the air removed from the room (at t ₁ <t _beats ), is supplied through an additional inlet pipe of the exhaust chamber with an additional fan to the exhaust line of the recuperator;

- exhaust air from the room is emitted into the atmosphere by the main fan of the exhaust chamber through an additional exhaust pipe of the exhaust chamber with the closed additional air valve located at the outlet of the main fan unit;

- the outside air is supplied by the fan of the supply chamber through a cooled recuperator and in a cooled form through the supply line enters the room.

, % (где t_уд - температура удаляемого из помещения воздуха, °C; t₁ - температура наружного воздуха, °C). Преимущество обеспечивается отличительным признаком 8, т.е. размещением основного адиабатического увлажнителя в вытяжной камере между управляемым воздушным клапаном и рекуператором, в отличие от агрегата Hoval Adia Vent®, в котором увлажнитель размещен между пластинчатыми теплообменниками.7. The installation allows you to effectively cool the exhaust and supply air, even if t _beats = t ₁ , using the full energy efficiency of the recuperator $${\Phi }_{R\Sigma }^{\mathrm{from}}$$

,% (where t _beats is the temperature of the air removed from the room, ° C; t ₁ is the outdoor temperature, ° C). The advantage is provided by the hallmark 8, i.e. by placing the main adiabatic humidifier in the exhaust chamber between the controlled air valve and the recuperator, in contrast to the Hoval Adia Vent® unit, in which the humidifier is placed between the plate heat exchangers.

Example: t ₁ = 26 ° C, t _beats = 26 ° C, Ф _{RΣ (6)} = 98.4%. The temperature at the outlet of the recuperator of the supply line at $$t_{\mathrm{at}d}^{\mathrm{at}\mathrm{at}}=t_{\mathrm{at}d}-\Delta t=26-6={\mathrm{twenty}}^{\mathrm{about}}C$$

. $$t_{R\mathrm{one}}=t_{\mathrm{one}}+{\Phi }_{R\Sigma (6)}\cdot {10}^{-2}\left(t_{\mathrm{at}d}^{\mathrm{at}\mathrm{at}}-t_{\mathrm{one}}\right)=26+98,\mathrm{four}\cdot {10}^{-2}(\mathrm{twenty}-26)=\mathrm{twenty},{\mathrm{one}}^{o}C$$

.

The placement of the adiabatic humidifier at the inlet to the recuperator ensured at Δt _bx = t _beats -t ₁ = 0 that the temperature at the outlet of the recuperator t _R1 decreased compared to the outdoor temperature at

Δt _ochl = (t ₁ -t _R1 ) = (26-20, l) = 5.9 ° C.

8. The installation allows the discharge of contaminated air from the exhaust chamber and the intake of clean external air into the supply chamber without connecting long ducts to the inlet of the exhaust chamber of the exhaust chamber, which divert the suction and exhaust ports in different directions. The resulting advantage is provided by the hallmark 8.

The following are the distinguishing features that provide the five listed advantages of the installation in the section for expanding the functionality of the installation.

Distinctive feature 4.

During humid treatment of the supply air, the supply chamber is equipped with an adiabatic supply air humidifier with a supply pipe located behind the air heater.

Distinctive feature 5.

When mixing outdoor air with exhaust air in the proportions of 30% and 70%, respectively, the exhaust chamber is equipped with an additional fan unit with a frequency converter located at the outlet of the recuperator.

Hallmark 6

The supply chamber is equipped with an additional inlet pipe with an air purifier located on one of the side panels of the air mixing chamber, and the bypass valve is installed in the additional inlet pipe of the supply chamber at the inlet in front of the air cleaner and is made insulated.

Hallmark 7

The exhaust chamber is equipped with an additional controlled air valve installed at the outlet of the main fan unit, an additional exhaust pipe with a controlled output insulated air valve installed on one of the side panels of the fan unit, and an additional inlet pipe located between the controlled and additional controlled air valves on one from the side panels of the exhaust chamber controlled by an inlet insulated air valve and an air purifier located in the mentioned additional inlet pipe of the exhaust chamber.

Hallmark 8

The exhaust pipe of the exhaust chamber is located above the inlet pipe of the supply chamber.

The effectiveness of using the indirect adiabatic cooling of the supply air with the intake of atmospheric air as a removable one and the operation of two adiabatic humidifiers can be seen in the following example t ₁ = 26 ° C, hot shop, t _beats = 35 ° C, four-stage recuperator. The temperature at the outlet of the four-stage recuperator in the supply line with two adiabatic humidifiers is calculated by the formula

, $$t_{R\mathrm{one}}=t_{\mathrm{one}}+({\Phi }_{R\Sigma (\mathrm{four})}+{\Phi }_{R\Sigma (2)})\cdot {10}^{-2}\left(t_{\mathrm{one}}^{\mathrm{at}\mathrm{at}}-t_{\mathrm{one}}\right)$$

,

- температура увлажненного наружного воздуха, °Cwhere Ф _{RΣ (4)} is the total energy efficiency of the four- _stage recuperator,%; Ф _{RΣ (4)} = 93.75%; Ф _{RΣ (2)} - total energy efficiency of a two-stage recuperator located after an additional adiabatic humidifier,%, Ф _{RΣ (2)} = 75%; $$t_{\mathrm{one}}^{\mathrm{at}\mathrm{at}}$$

- humidified outdoor temperature, ° C

, $$t_{\mathrm{one}}^{\mathrm{at}\mathrm{at}}=t_{\mathrm{one}}-\Delta t_{\mathrm{about}xl}=26-6={\mathrm{twenty}}^{\mathrm{about}}C$$

,

where Δt _okhl = 6 - lowering of air temperature at its adiabatic moistening, ° C.

With these data, the air temperature at the outlet of the four-stage recuperator in the supply line will be

t _R1 = 26 + (93.75 + 75) · 10 ^-2 (20-26) = 15.9 ° C

Outdoor air cooling in multi-stage recuperators with two adiabatic humidifiers will be:

- for a four-stage recuperator

Δt _{cooling Σ} = (93.75 + 75) · 10 ^-2 Δt = 1,687 · 6 = 10.1 ° C,

- for a five-stage recuperator

Δt _coolΣ = (96.8 + 75) · 10 ^-2 Δt = 1.718 · 6 = 10.3 ° C,

- for a six-stage recuperator

Δt _coolΣ = (98.4 + 75) · 10 ^-2 Δt = 1.86 · 6 = 11.1 ° C.

Increasing the energy efficiency of the inventive setup in the warm season when the forced mode cooling supply air (Δt _OHL = 10 ° C) was determined as follows.

1. Determine the power consumed in the forced cooling of the supply air at _OHL Δt = 10 ° C in the prototype installation the formula

. $$\Delta N_{(\mathrm{one})}^{\mathrm{about}xl}=G_{\mathrm{from}}{C}_{R.\mathrm{from}}\Delta t_{\mathrm{about}xl}/3600=\mathrm{10,000}\cdot \mathrm{one},005\cdot 10/3600=27,9\text{kw}$$

.

2. The total consumed power in the installation of the prototype for cooling the supply air and electric motors of the fans of the supply and exhaust lines of the installation of the prototype is determined

. $$N_{(\mathrm{one})}^{\mathrm{about}xl}=N_{(\mathrm{one})}^{\mathrm{about}xl}+N_{\mathrm{at}PR}+N_{\mathrm{at}\mathrm{at}st}=27,9+\mathrm{four},0+\mathrm{four},0=35,9\text{kw}$$

.

3. The total expendable power in the inventive installation for cooling the supply air and fan motors is determined:

- when using a four-stage recuperator:

; $$N_{(\mathrm{four})}^{\mathrm{about}xl}=N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(2)}+N_{\mathrm{at}PR(\mathrm{four})}+N_{\mathrm{at}\mathrm{at}st(\mathrm{four})}=0,714+5,3+5,3=\mathrm{eleven},3\text{kw}$$

;

- when using a five-stage recuperator:

; $$N_{(5)}^{\mathrm{about}xl}=N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(2)}+N_{\mathrm{at}PR(5)}+N_{\mathrm{at}\mathrm{at}st(5)}=0,714+5,7+5,7=12,\mathrm{one}\text{kw}$$

;

- when using a six-stage recuperator:

. $$N_{(6)}^{\mathrm{about}xl}=N_{s\mathrm{but}\mathrm{I\; am}\mathrm{at}l}^{\mathrm{about}xl(2)}+N_{\mathrm{at}PR(6)}+N_{\mathrm{at}\mathrm{at}st(6)}=0,714+6,\mathrm{one}+6,\mathrm{one}=12,9\text{kw}$$

.

4. Determines the increase in energy efficiency of the claimed installation compared with the installation of the prototype in the forced cooling mode of the supply air:

- when using a four-stage recuperator:

; $${\Phi }_{t(\mathrm{four})}^{\mathrm{about}xl}=\left(\frac{\Delta N_{\Sigma (\mathrm{one}-\mathrm{four})}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}-N_{\Sigma (\mathrm{four})}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{35,9-\mathrm{eleven},3}{35,9}\right)\cdot \mathrm{one\; hundred}=68,5\%$$

;

- when using a five-stage recuperator:

; $${\Phi }_{t(5)}^{\mathrm{about}xl}=\left(\frac{\Delta N_{\Sigma (\mathrm{one}-5)}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}-N_{\Sigma (5)}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{35,9-12,\mathrm{one}}{35,9}\right)\cdot \mathrm{one\; hundred}=66,3\%$$

;

- when using a six-stage recuperator:

. $${\Phi }_{t(6)}^{\mathrm{about}xl}=\left(\frac{\Delta N_{\Sigma (\mathrm{one}-6)}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}-N_{\Sigma (6)}^{\mathrm{about}xl}}{N_{\Sigma (\mathrm{one})}^{\mathrm{about}xl}}\right)\cdot \mathrm{one\; hundred}=\left(\frac{35,9-12,9}{35,9}\right)\cdot \mathrm{one\; hundred}=64\%$$

.

The design of the inventive air handling unit with the recovery of the heat of the removed air and indirect adiabatic cooling of the supply air is illustrated in the drawings in figures 1-17.

Figure 1 presents a vertical projection of a supply and exhaust unit with a four-stage recuperator; figure 2 is a view of figure 1; figure 3 is a vertical projection of a supply and exhaust installation with a five-stage recuperator; figure 4 is a view In figure 3; figure 5 is a vertical projection of the supply and exhaust unit with a six-stage recuperator; in Fig.6 is a view C in Fig.5: in Fig.7 is a vertical projection of a supply and exhaust installation without a recuperator controlled by a recirculating air valve and a vertical transverse partition; on Fig - section DD DD six-stage recuperator (Fig.9); Fig.9 is a view of D in Fig.8; figure 10 is a section aa in figure 2; figure 11 is a section bb in figure 4; on Fig - section CC in Fig.6; in Fig.13 is a General view of a plate heat exchanger with a removable heat exchanger cartridge; in Fig.14 is a section GG (in Fig.2, 6); on Fig-section ZZ (figure 4); in Fig.16 - section FZ (Fig.2, 6); in Fig.17 - section II (in Fig.4).

Service hatches on the supply and exhaust installation in Figs. 1-7, 10-12 are conditionally not shown and not indicated.

In figure 10, 11, 12, the arrows indicate

The installation contains floor 1 and ceiling 2 panels, inlet 3 and exhaust 4 cameras, separated by a horizontal intermediate partition 5 with the main 6 and additional 7 windows (Fig.7). In the main window 6 of the horizontal intermediate partition 5, a multi-stage recuperator 8 (Fig. 10, 11, 12), consisting of diagonally mounted cross-flow plate heat exchangers 9, is integrated, and a controllable recirculation air valve 10 is built into the additional window 7. Inlet chamber 3 (Fig. 10 , 11, 12) contains an inlet pipe 11, a controllable inlet insulated air valve 12, an air purifier 13, an air mixing chamber 14 with a controllable air valve 15 at the inlet, a heater block 16 with a controllable bypass valve ohm 17, the fan unit 18 and the exhaust pipe 19.

The exhaust chamber 4 (FIGS. 10, 11, 12) comprises an inlet pipe 20, an air cleaner 21, a fan unit 22, a controllable air valve 23 installed at the inlet to the recuperator 8, an exhaust pipe 24.

The recuperator 8 (Figs. 8-12) contains a housing 37, including side 38 and end walls 39, a bottom 40, a condensate collecting pan 41, a drain fitting 42 and a siphon 43. The recuperator 8 can be made in four stages (Fig. 10), five stages (Fig. 11) and six-stage (Fig. 12) and consisting of plate heat exchangers 9 connected in series by ribs, which are located in the housing 37 of the recuperator 8 by two vertical rows 44, separated by a vertical partition 45, which is hermetically connected to the side ribs 46 of the heat exchangers 9, placed on both hundred the rods from the vertical partition 45. The outer side ribs 46 of the vertical rows 44 of the heat exchangers are hermetically connected to the side walls 38 of the heat exchanger housing 37, the ends 47 (Fig. 13) of the heat exchangers 9 are connected to the end walls 39 (Fig. 9) of the heat exchanger housing 37 to form internal 48 and external 49 air channels between the heat exchangers 9 of each vertical row 44 (figure 10, 11, 12).

The lower heat exchangers are connected by a closing link 50, which, depending on the number of stages of the recuperator, is made:

- in the form of a closing plate (in four and six-stage recuperators) (Fig.10, 12);

- in the form of a closing diagonally mounted plate heat exchanger (in five-stage recuperators) (Fig. 11).

The closing link (the closing plate and the closing plate heat exchanger) together with the bottom of the heat exchanger body form air channels 51 and 52 (FIGS. 10, 11, 12) connecting the rows of 4 heat exchangers 9 in the exhaust and air supply lines.

In addition, the floor panel 1 of the supply and exhaust installation is equipped with a mounting window 53 (Fig. 7), placed coaxially with the main window 6 in the horizontal intermediate partition 5. The upper half 54 of the upper heat exchangers (Fig. 9) is made protruding beyond the flanges 55 of the housing 37 of the recuperator and is integrated through the mounting window 53 (Fig. 7) in the floor panel 1 (Fig. 7) of the air handling unit into the air supply chamber 3 with a tight connection of the flanges 55 (Fig. 8, 9) of the heat exchanger housing 37 to the floor panel 1 (Fig. 7) .7) and free ends 56 of the upper heat transfer nnikov (Fig.8, 9) to the side walls 57 of the supply chamber 3 (Fig.7). The recuperator 8 is integrated by the upper fins 58 of the upper heat exchangers (Fig. 8) into the main window 6 in the horizontal intermediate partition 5 (Fig. 7). The exhaust chamber 4 is provided with a vertical transverse partition 59 (Fig. 10, 11, 12), which is located in the main window 6 of the horizontal intermediate partition 5, is rigidly mounted on the vertical partition 45 of the housing 37 of the recuperator and is hermetically connected to the ceiling panel 2 of the supply and exhaust unit with the formation of individual air channels 60 and 61 connecting the upper heat exchangers with chambers 3 and 4 of the supply and exhaust system. The air channel 60, depending on the number of stages in the recuperator 8, has the following purpose:

- when using four and six-stage recuperators (Fig.10, 12) is the exhaust air inlet to the recuperator 8:

- when using five-stage recuperators (11) is the supply air outlet from the recuperator 8. The air channel 61, regardless of the number of stages of the recuperator 8, is the exhaust duct for exhaust air from the recuperator 8 (FIGS. 10, 11, 12).

The supply air cooler is made in the form of an adiabatic extract air humidifier 62 with a supply pipe 63 (FIGS. 10, 11, 12), which are located in the exhaust chamber 4 between the controlled air valve 23 and the recuperator 8, and the exhaust pipe 24 of the exhaust chamber 4 is located above the inlet the pipe 11 of the supply chamber 3 (figure 10, 11, 12).

The plate heat exchangers 9 of the recuperator 8 (Fig. 13) are made of a housing 64 and a removable heat-exchange cartridge 65, the plates 66 of which are made of aluminum. The vertical partition 45 of the housing 37 of the recuperator 8 and the vertical transverse partition 59 of the exhaust chamber 4 (FIGS. 10, 11, 12) are heat insulated with a double wall, and the side walls 38 and the bottom of the housing 37 of the recuperator are equipped with service hatches 68, 69.

When performing the recuperator four-stage (figure 10) and six-stage (figure 12), the closing link 50 is made in the form of a plate that is rigidly connected to the lower ribs 70 of the lower heat exchangers, and its ends are hermetically connected to the end walls 39 (Fig. 9) of the housing 37 recuperator. Under the closing link 50 (locking plate) of the lower heat exchangers (FIGS. 10, 12), a bottom 40 of the heat exchanger housing 37 is located (FIGS. 10, 12) with the formation of air channels 51 and 52 connecting the vertical rows 44 of the heat exchangers 9 in lines hoods and inflows.

When the recuperator 8 is made in four stages (Fig. 10), the closing link 50 of the lower heat exchangers is made with a window 71, in which a removable condensate collecting pan 41 is mounted, rigidly connected to the service hatch 69 of the bottom 40 of the racks 72, and a drain fitting 42 mounted on the pallet for condensate collection 41 is made with a transit passage through the service hatch 69 of the bottom 40 of the housing 37 of the recuperator 8, under which a siphon 43 is installed.

In the manufacture of the five-stage recuperator (Fig. 11), the closing link is made in the form of a closing diagonally mounted plate heat exchanger 50, which is hermetically connected through the transit air channels 73 to the lower heat exchangers of the recuperator 8 with a rigid installation of its lower rib 74 on the bottom 40 of the recuperator body, and the tray for condensate collection 41 is located in the air channel 51 connecting the vertical rows 44 of the heat exchangers of the air exhaust line.

In the manufacture of the recuperator in five-stage and six-stage (11, 12) condensate drain pan 41 in the recuperator 8 is built into the service hatch 69 located in the bottom 40 of the recuperator housing 37.

When humid supply air treatment, which is necessary to supply fresh air directly to the working area of the production room, the supply chamber 3 is equipped with an adiabatic fresh air humidifier 76 with a supply pipe 63 located behind the air heater 16 (Fig. 10, 11, 12).

The adiabatic humidifier 76 increases the relative humidity of the heated air from φ ₂ to a standardized value for the supply air φ _pr In order to maintain a normalized value of the relative humidity of the supply air φ _pr when the outdoor temperature changes t ₁ , ° C, the supply chamber 4 is equipped with an automatic control system (ACS) for the performance of the humidifier with an air humidity sensor, which is not indicated in figures 1-17.

When mixing outdoor air with exhaust air in various proportions, which is necessary when providing recirculation modes, the exhaust chamber 4 is equipped with an additional fan unit 25 with a frequency converter located at the outlet of the recuperator 8.

To ensure the defrosting of the icy plates 66 of the heat exchanger cassettes 65 of the recuperator 8 during the cold season, the supply chamber 3 is equipped with an additional inlet pipe 33 located on one of the side panels 36 of the air mixing chamber 14, controlled by a bypass warmed air valve 34 and an air cleaner 35, located in the said additional inlet pipe 33 of the supply chamber 3.

The bypass valve 34 is interlocked with a differential pressure sensor installed in the exhaust line of the recuperator 8 (not shown in FIGS. 1-17), which has two contacts (upper and lower). The upper contact of the differential pressure sensor is configured for a critical differential pressure in the exhaust line of the recuperator, when closed, bypass valve 34 opens. When the lower contact closes in the differential pressure sensor, the bypass valve 34 closes.

To ensure direct discharge of the air removed from the room, bypassing the multi-stage recuperator 8, the exhaust chamber 4 is equipped with an additional controlled air valve 26 installed at the outlet of the main fan unit 22, and an additional exhaust pipe 31 with a controlled outlet warmed air valve 32.

To ensure forced cooling of the supply air, the supply and exhaust unit is equipped with an additional adiabatic extract air humidifier 75 located in the recuperator 8 on the condensate collecting tray 41 and the water supply 63 leading thereto, and the exhaust chamber 4 is provided with an additional inlet pipe 27 located between the controlled 23 and additional controlled by 26 air valves on one of the side panels 28 of the exhaust chamber 4, controlled by an inlet warmed air valve 29 and an air cleaner 30, times placed in the mentioned additional inlet pipe 27 of the exhaust chamber 4. The additional inlet pipe 27 of the exhaust chamber 4 allows to supply cooler external air than the air removed from the room into the exhaust line of the recuperator 8 provided that t ₁ <t _beats , which ensures cooling of the recuperator 8.

The line of air flow in the installation can be formed:

- through the inlet pipe 11 of the supply chamber 3 and a multi-stage recuperator 8;

- bypassing the multi-stage recuperator 8, through an additional inlet pipe 33 of the supply chamber 3.

The exhaust line of the air removed from the room in the installation can be formed:

- through the inlet pipe 20 of the exhaust chamber 4 and the multi-stage recuperator 8;

- bypassing the multi-stage recuperator 8 through the inlet pipe 20 of the exhaust chamber 4 and an additional exhaust pipe 31 of the exhaust chamber 4.

In the installation, with the closed additional controlled air valve 26 closed, two exhaust lines can be formed simultaneously;

- air removed from the room through the inlet pipe 20 of the exhaust chamber 4 and an additional exhaust pipe 31 of the exhaust chamber 4;

- external air through an additional inlet pipe 27 of the exhaust chamber and a multi-stage recuperator 8.

The inventive air handling unit has 9 operating modes and a standby mode that are displayed on a push-button control panel (not indicated by positions).

The condition of the equipment (on, off) included in the supply and exhaust unit (fans, air valves, air heater and adiabatic humidifiers for exhaust and supply air) for the applicable installation modes is shown in Table 2.

The regimes of the cold season

Mode 1. The main ventilation mode with 100% exhaust and 100% outside air passing through the recuperator 8 with additional heating of the supply air in the air heater 16 to the desired temperature.

Mode 2. Recirculation mode with 100% recirculation of the exhaust air heated in the air heater 16 to the production room.

Mode 3. Recirculation mode with a mixture of 30% of fresh outdoor air into recirculated air with preheating of the air mixture in the air heater 16 to the desired temperature.

Mode 4. Recirculation mode with a mixture of 70% of fresh outdoor air in recirculated air with preheating of the air mixture in the air heater 16 to the desired temperature.

Mode 5. The mode of defrosting ice on the plates 66 of the heat exchange cassettes 65.

Modes of the warm season

Mode 6. The mode of indirect adiabatic cooling of the supply air with the intake of exhaust air from the production room (t _beats <t ₁ ) and the operation of two adiabatic humidifiers.

Mode 7. The mode of indirect adiabatic cooling of the supply air with the intake of external air as a discharge (t _beats <t ₁ ) and the operation of one adiabatic humidifier.

Mode 8. The mode of indirect adiabatic cooling of the supply air with the intake of external air as a discharge (t _beats <t ₁ ) and the operation of two adiabatic humidifiers.

Mode 9. The mode of direct supply of outdoor air to the production room and the direct emission of exhaust air into the atmosphere without passing the exhaust and outdoor air through the recuperator 8 when eliminating the effects of a fire in the production room.

Mode 10. Standby.

Modes 1-10 are carried out during round-the-clock operation of the inventive straight-exhaust system.

The control modes 1-10 is carried out from the microprocessor, which is not indicated in Fig.1-17.

Installation in mode 1 works as follows. The air removed from the production unit by the fan unit 22 of the exhaust chamber 4 enters through the inlet pipe 20, the air cleaner 21, the open air valves 26, 23 and the inlet air channel 60 into the recuperator 8, which recudes the heat of the removed air by the plates 66 of the heat exchangers 9 and gives it to the cold outside air . Exhaust air after exiting the recuperator 8 passes through the exhaust air channel 61 and is discharged into the atmosphere through the exhaust pipe 24 of the exhaust chamber 4. Outside air enters the supply chamber 3 through the inlet 11, the open insulated inlet air valve 12, the air purifier 13 and then into the recuperator 8. After exiting the recuperator 8, the supply air passes through the open air valve 15, the mixing chamber 14 to the air heater 16, in which heats up to the required temperature t ₂ , ° C using a temperature sensor (not indicated in FIG.) installed behind the air heater 16. Then, in the adiabatic humidifier 76, the heated air is humidified with a relative humidity φ ₂ (after the heater) up to φ _pr for the supply air equal to the relative humidity of the air in the room φ _pom using an air humidity sensor (not indicated in Fig.) installed behind the adiabatic humidifier 76. After that, the supply air is supplied by the supply fan unit 18 chamber 3 is fed through the exhaust pipe 19 of the supply chamber 3 into the air distributor (not shown in FIG.) installed in the production room.

The route of exhaust and external air in the exhaust and supply lines in mode 1 is indicated by the positions of the equipment of the supply and exhaust system

Extraction Line (Mode 1)

G = 100% _stretch

Inflow Line (Mode 1)

G _ol = 100%

Mode 1 can be used in the claimed supply and exhaust unit regardless of the number of stages of the recuperator.

The temperature of the air heating t ₂ in the air heater is determined from the condition

, $${\mathrm{<figure-callout\; id="2"\; label="t"\; filenames="00000108.png,00000110.png"\; state="\{\{state\}\}">t</figure-callout>}}_2={\left[t_{R.s}^{x\mathrm{about}l}\right]}_{\min }+\Delta t_{\mathrm{about}xl}$$

,

- минимально допускаемая температура в рабочей зоне производственного помещения для работ соответствующей категории тяжести, определяемой по СНиП Отопление. Вентиляция. Кондиционирование воздуха. 2003 г.; Δt_охл=6°C.Where $${\left[t_{R.s}^{x\mathrm{about}l}\right]}_{\min }$$

- the minimum allowable temperature in the working area of the production room for work of the corresponding severity category, determined by SNiP Heating. Ventilation. Air conditioning. 2003; Δt _ochl = 6 ° C.

Installation in mode 2 works as follows. One fan unit 22 of the exhaust chamber 4 is turned on at 100% capacity. With the closed air valves 15 and 23 and the open air valve 26 and the recirculation air valve 10, the exhaust air from the production room is supplied by the fan block 22 through the inlet pipe 20 of the exhaust chamber 4, the air cleaner 21 and the mixing chamber 14 to the air heater 16 of the supply chamber 3, after which, in the heated state, through the outlet pipe 19 of the supply chamber 3 enters the production room. Mode 2 is used at night during a non-working shift at low negative outside temperatures to prepare room air for a day shift. After heating the room air to a temperature equal to the upper limit of the temperature setting, the fan unit 22 is turned off at the temperature sensor (not indicated by positions), and the recirculating air valve 10 is closed and the supply and exhaust unit goes into standby mode (mode 10). After the room temperature drops to the lower limit of the temperature setting of the temperature sensor, mode 2 automatically resumes. In mode 2, the recirculated air after heating is not humidified, since the cold air infiltrated into the room through the cooling structures has a higher relative humidity than the required one, and recirculation with heating is periodic.

The exhaust air route in the exhaust-recirculation line in mode 2 is indicated by the positions of the equipment of the supply and exhaust system.

Extract-recirculation line (mode 2)

G = 100% _stretch

Installation in mode 3 works as follows. Three fan units 18, 22 with 100% capacity and block 25 with 30% capacity are included. The air that is removed by the fan unit 22 of the exhaust chamber 4 comes from the production room through the inlet pipe 20, the air cleaner 21 into the exhaust chamber 4, in which it is distributed into 2 flows. One stream in the amount of 30% of the capacity of the fan unit 22 is directed in the suction mode by the fan unit 25 of the exhaust chamber 4 through the open air valves 26, 23 and the inlet air duct 60 to the recuperator 8 and then through the outlet air duct 61 and the exhaust pipe 24 of the exhaust chamber 4 emitted into the atmosphere. A second extract air stream in the amount of 70% of the capacity of the fan unit 22 is directed in the injection mode by the fan unit 22 of the supply chamber 3 through the open air valve 26 and the recirculation air valve 10 for recirculation to the mixing chamber 14. At the same time, a third air stream is generated in the line of outdoor air supply . The fan block 18 of the supply chamber 3 in the intake mode supplies 30% of the outdoor air from the unit through the inlet pipe 11 of the supply chamber 3, an open inlet insulated valve 12, an air purifier 13, a recuperator 8 and an open air valve 15 into the air mixing chamber 14. The air mixture ( 30% of the external and 70% of the removed) is supplied by the fan unit 18 of the supply chamber 3 to the air heater 16, and then to the air humidifier 78, after which it enters the air distributor through the outlet pipe 19 of the supply chamber 3 (on It was not indicated), located in the production area. Mode 3 is used for increased air pollution in the production room. The air flow route (exhaust 100%, recycled 70%, external 30% and supply 100%) in mode 3 is indicated by the positions of the equipment of the supply and exhaust unit.

Extract-recirculation-inflow line (Mode 3)

Installation in mode 4 works as follows. Three fan units 18, 22 with 100% capacity and block 25 with 70% capacity are included.

The air that is removed by the fan unit 22 of the exhaust chamber 4 comes from the production room through the inlet pipe 20, the air cleaner 21 into the exhaust chamber 4, in which it is distributed into 2 flows. One stream in the amount of 70% of the capacity of the fan unit 22 is directed in the suction mode by the fan unit 25 of the exhaust chamber 4 through the open air valves 26, 23 and the inlet air duct 60 to the recuperator 8 and then through the outlet air valve 61 and the exhaust pipe 24 of the exhaust chamber 4 emitted into the atmosphere. The second stream of exhaust air in the amount of 30% of the capacity of the fan unit 22 is directed in the discharge mode by the fan unit 22 of the supply chamber 3 through the open air valve 26 and the recirculation air valve 10 for recirculation to the mixing chamber 14. At the same time, a third air stream is generated in the line of outdoor air supply . The fan unit 18 of the supply chamber 3 in the suction mode supplies 70% of the outdoor air from the capacity of the fan unit through the inlet pipe 11 of the supply chamber 3, an open inlet insulated valve 12, an air purifier 13, a recuperator 8 and an open air valve 15 into the air mixing chamber 14. The air mixture (70% of the outer and 30% of the removed) is supplied by the fan unit 18 of the supply chamber 3 to the air heater 16, and then to the air humidifier 76, after which it enters the air outlet through the exhaust pipe 19 of the supply chamber 3 a divider (Fig. not indicated), located in the production area. Mode 4 is used for severe air pollution in the production room. The air flow route (exhaust 100%, recirculated 30%, external 70% and supply 100%) in mode 4 is indicated by the positions of the equipment of the supply and exhaust unit.

Extract-recirculation-inflow line (Mode 4)

Installation in mode 5 works as follows. Mode 5 is activated automatically from the operation of the differential pressure sensor (Fig. 10, 11, 12 is not shown and is not indicated by the position) installed on the recuperator 8. When icing the plates 66 of any heat exchange cartridge 65 to the critical state, the air passage cross section decreases channels 67, heat exchange cassettes 65, the air flow velocity V, m / s increases, the dynamic pressure P _din , Pa increases, and, as a result, the hydraulic resistance of the heat exchanger ΔP _R , Pa increases. When reaching the ΔР _R value of the upper limit of the hydraulic resistance, Pa, installed on the differential pressure sensor, a signal appears to turn on mode 5. At the same time, all equipment (fans, air valves, air heater, recirculation and bypass valves) is brought into the state corresponding to mode 5, described in table 1.

The outside air is supplied by the fan unit 18 of the supply chamber 4 through the open insulated inlet air valve 34 and the air purifier 35 of the additional inlet pipe 33 of the supply chamber 3, and also through the air mixing chamber 14 in transit to the air heater 16, which is switched on for forced heating of air with increased power, and then to a humidifier 76, after which it is supplied to the production room in a humidified state. Warm air removed from the room is supplied by the fan unit 22 through the inlet pipe 20 of the exhaust chamber 4, the air cleaner 21, the open air valves 26 and 23 and the inlet air channel 60 to the recuperator 8 and then through the outlet channel 61 and the exhaust pipe 24 of the exhaust chamber 4 is released into the atmosphere . The line of influx of external cold air into the recuperator 8 through the inlet pipe 11 of the supply chamber 3 does not work, because the insulated air inlet valve 12 is closed. After the ice has thawed on the plates 66 of the heat exchanger cassette 65, the flow area of the air ducts 67 increases, the exhaust air velocity V, m / s and the hydraulic resistance of the heat exchanger ΔP _R decrease to normalized values, which causes the differential pressure sensor to trigger and formation of a signal to terminate mode 5. All equipment of the installation is brought into the state in which it was before mode 5.

Additional inlet 27 and outlet 31 nozzles of the exhaust chamber 4 in the cold season are not used. Therefore, the air purifier 30 installed in the additional inlet pipe 27 can be dismantled in cold weather.

When ordering a supply and exhaust system for two additional inlet pipes 27 and 33, one air purifier is ordered.

The air flow path (exhaust and cold external supply air) in mode 5 is indicated by the positions of the equipment of the supply and exhaust unit

Extraction Line (Mode 5)

Inflow Line (Mode 5)

Installation in mode 6 works as follows. Two adiabatic extract air humidifiers 62 and 75 operate, each of which cools the exhaust air ≈ by 6 ° C. The air removed from the production unit by the fan unit 22 of the exhaust chamber 4 enters through the inlet pipe 20, the air cleaner 21, the open air valves 26, 23, the adiabatic humidifier 62, which provides cooling of the exhaust air, and the air inlet channel 60 to the recuperator 8, in which it is humidified by an additional adiabatic Humidifier 75 with cooling. Once adiabatically cooled by adiabatic humidification, the exhaust air after leaving the recuperator 8 passes through the outlet air channel 61 and is discharged into the atmosphere through the outlet pipe 24 of the exhaust chamber 4.

External warm air enters the supply chamber 3 through the inlet pipe 11, the open insulated inlet air valve 12, the air purifier 13 and then into the recuperator 8 cooled by the exhaust air, in which it is cooled. After exiting the recuperator 8, the fresh fresh air enters through the open air valve 15, the mixing chamber 14 in transit and in parallel through the open bypass valve 17 and the air ducts of the turned-off air heater 16, after which the fan block 18 of the supply chamber 3 is fed through the exhaust pipe 19 of the supply chamber 3 and an air distributor (not indicated in FIGS. 1-17) installed in the production room.

The route of exhaust and outdoor air in the exhaust and supply lines in mode 6 is indicated by the positions of the equipment of the supply and exhaust system.

Extraction Line (Mode 6)

Inflow Line (Mode 6)

Installation in mode 7 works as follows. Two exhaust lines (air from the production room and outdoor air) work, as well as one adiabatic humidifier 62, which adiabatically humidifies the exhaust air by adiabatic humidification ≈ 6 ° C. The air removed from the production unit by the fan unit 22 of the exhaust chamber 4 enters the exhaust chamber 4 through the inlet pipe 20 and the air purifier 21 and, when the air valve 26 is closed, is immediately discharged into the atmosphere through an open outlet insulated air valve 32 and an additional exhaust pipe 31. Removed by an additional fan block 25 of the exhaust chamber 4, external air enters through an additional inlet pipe 27 of the exhaust chamber 4, an open inlet insulated air valve 29, and air purification Tel 30 exhaust chamber 4. Then, exhaust air is moved through the open air valve 23, an adiabatic humidifier 62 and the air inlet passage 60 in the recuperator 8 which recovers the cold outdoor air exhaust. Adiabatically cooled by adiabatic humidification, the exhaust external air after leaving the recuperator 8 passes through the outlet air channel 61 and is discharged into the atmosphere through the exhaust pipe 24 of the exhaust chamber 4.

External warm air enters the supply chamber 3 through the inlet pipe 11, the open insulated inlet air valve 12, the air purifier 13 and then into the recuperator 8 cooled by the exhaust air, in which it is cooled. After exiting the recuperator 8, the fresh fresh air enters through the open air valve 15, the mixing chamber 14 in transit, the open bypass valve 17 and the air ducts of the turned-off air heater 16, after which the fan block 18 of the supply chamber 3 is fed through the exhaust pipe 19 of the supply chamber 3 and an air distributor (in FIGS. 1-17 is not installed) installed in the production room.

The route of the exhaust and outdoor air in two exhaust lines and the supply line in mode 7 is indicated by the positions of the equipment of the supply and exhaust system.

Room air exhaust line (Mode 7)

Outdoor Air Extraction Line (Mode 7)

Inflow Line (Mode 7)

Installation in mode 8 works as follows. Two exhaust lines (air from the production room and outdoor air), as well as two adiabatic humidifiers 62, 75, each of which adiabatically cools the air taken from the atmosphere by ≈ 6 ° C, work. The air removed from the production unit by the fan unit 22 of the exhaust chamber 4 enters the exhaust chamber 4 through the inlet pipe 20 and the air cleaner 21 and, when the air valve 26 is closed, is immediately discharged into the atmosphere through the open, heated air inlet valve 32 and the additional exhaust pipe 31. To be removed by the additional fan block 25 of the exhaust chamber 4, the external air enters through an additional inlet pipe 27 of the exhaust chamber 4, the open inlet of the insulated air valve 29, will clean the air l 30, outdoor air valve 23, an adiabatic humidifier 64 and the air inlet passage 60 in the recuperator 8, wherein the humidified additional adiabatic humidifier 75 with cooling. Once adiabatically cooled by adiabatic humidification, the exhaust air after leaving the recuperator 8 passes through the outlet air channel 61 and is discharged into the atmosphere through the outlet pipe 24 of the exhaust chamber 4. External warm air enters the supply chamber 3 through the inlet pipe 11, the open insulated inlet air valve 12, the air purifier 13 and then into the recuperator 8 cooled by the exhaust air, in which it is cooled. After exiting the recuperator 8, the fresh fresh air enters through the open air valve 15, the air mixing chamber 14 in transit, the open bypass valve 17 and the air ducts of the switched off air heater 16, after which the fan block 18 of the supply chamber 3 is fed through the exhaust pipe 19 of the supply chamber 3 into the air distributor (in FIGS. 1-17 is absent) installed in the production room. The route of the exhaust (atmospheric) outside air in the exhaust and supply lines in mode 8 is indicated by the positions of the equipment of the supply and exhaust system.

Room air exhaust line (Mode 8)

Outdoor Air Extraction Line (Mode 8)

Inflow Line (Mode 8)

Installation in mode 9 works as follows. The exhaust and inflow lines pass bypassing the recuperator 8. The air of the production room removed by the fan unit 22 enters through the inlet pipe 20 of the exhaust chamber 4, the air cleaner 21 and is discharged through the open outlet insulated air valve 32 and an additional exhaust pipe 31 into the atmosphere. The external cold air supplied by the fan unit 18 of the supply chamber 3, enters through an additional inlet pipe 33, an open inlet insulated air valve 34, and an air purifier 35 into the mixing chamber 14, from which it is simultaneously fed into the open bypass valve 17 and the air ducts are turned off the air heater 16 and then through the exhaust pipe 19 to the air distributor (Fig.1-17 is absent) located in the production room.

The route of exhaust and outdoor air in the exhaust and supply lines in mode 9 is indicated by the positions of the equipment of the supply and exhaust system.

Extraction Line (Mode 9)

Inflow Line (Mode 9)

In mode 10 (standby mode), the air valves 12, 29, 32, 34 are closed, as well as the recirculation 10 and bypass 17 air valves, and the remaining air valves (23, 26, 15) are open, the fan blocks 18, 22, 25 are turned off as well as adiabatic humidifiers 62, 75, 76 and the heater block 16.

Comparative indicators of the claimed installation and installation of the prototype at G _with = 10000 kg / h and climatic conditions of St. Petersburg in the cold season (t ₁ = -26 ° C, φ ₁ = 83%) and t _beats = 18 ° C, φ _beats = 55% and in the warm season (t ₁ = 26 ° C, t _beats = 23 ° C) are given in Tables 3, 4 and 5.

All of the above, including a description of the operation of the forced-air and exhaust installation, confirms the possibility of its use in industry with obtaining high technical indicators in comparison with the known designs of the forced-air and exhaust installations. In addition, both in the sources of patent and scientific and technical information, and in industry, such a design did not occur, which indicates that the proposed solution meets the criteria of the invention.

Table 3 Comparative performance of the inventive installation with the installation of the prototype in the cold season (Mode 1) Indicators Recuperators Prototype The inventive installation Single stage Four-stage Five cascade Six-stage The total energy efficiency of recuperators Ф _RΣ ,% at Ф _Ri = 50% fifty 93.75 96.8 98.4 Air temperature after the recuperator in the supply line, t _R1 , ° C -four 15.25 16.6 17.3 Air temperature after air heater, t ₂ , ° C 21 21 21 21 Estimated temperature difference for heating air, Δt = t ₂ -t ₁ , ° C 25 5.75 4.4 3,7 Power Consumption, kW: - air heater 69.8 16 12.3 10.3 - fan motor for the air intake line 4.0 5.3 5.7 6.1 - fan motor for the air exhaust line 4.0 5.3 5.7 6.1 - total installation power 77.8 26.6 23.7 22.5 Improving the energy efficiency of the inventive installation in the cold season, _{f x} ,% - 65.8 69.5 71.1

Table 4 Comparative performance of the inventive installation with the installation of the prototype in the warm season during the operation of one humidifier Indicators Recuperators Prototype The inventive installation Single stage Four-stage Five cascade Six-stage The total energy efficiency of recuperators Ф _RΣ ,% at Ф _Ri = 50% fifty 93.75 96.8 98.4 Air temperature after the recuperator in the supply line, t _R1 , ° C 24.5 17.6 17.3 17.1 Air recuperator cooling, * 1,5 8.4 8.7 8.9 Calculated temperature differential for the cooling air, Δt _OHL, ° C 7.0 - - - Exhaust air humidifier capacity, Gw, kg / h - 25 25 25 Power Consumption, kW: - air heater 19.5 0.357 0.357 0.357 - fan motor for the air intake line 4.0 5.3 5.7 6.1 - fan motor for the air exhaust line 4.0 5.3 5.7 6.1 - total installation power 27.5 11.0 11.6 12.6 Improving the energy efficiency of the inventive installation in the warm season, f _t ,% - 60 57.8 54,2

Table 5 Comparative performance of the inventive installation with the installation of the prototype in the warm season with forced cooling mode (Mode 6) Indicators Recuperators Prototype The inventive installation Single stage Four-stage Five cascade Six-stage The total energy efficiency of recuperators Ф _RΣ ,% at Ф _Ri = 50% fifty 93.75 96.8 98.4 Air temperature after the recuperator in the supply line, t _R1 , ° C 24.5 15.9 15.7 14.9

Recuperator air cooling, $$\Delta t_{\mathrm{about}xl}^R=t_{\mathrm{one}}-t{R}_{\mathrm{one}}$$

1,5 10.1 10.3 11.1 Calculated temperature differential for the cooling air, Δt _OHL, ° C 10 - - - Power Consumption, kW: - air cooler 27.9 0.714 0.714 0.714 - fan motor for the air intake line 4.0 5.3 5.7 6.1 - fan motor for the air exhaust line 4.0 5.3 5.7 6.1 - total installation power 35.9 11.3 12.1 12.9 Improving the energy efficiency of the inventive installation in the warm season with forced cooling mode, $${\Phi }_t^f$$

% - 68.5 66.3 64.0

Sequence listing

(Figs. 1-17)

1. The floor panel of the supply and exhaust installation (Fig. 1, 3, 5, 7, 10, 11, 12)

2. The ceiling panel of the supply and exhaust installation (Fig. 1, 3, 5, 7, 10, 11, 12)

3. The supply chamber (figure 10, 11, 12)

4. The exhaust chamber (figure 10, 11, 12)

5. The horizontal intermediate partition of the supply and exhaust installation (Fig.7)

6. The main window in the horizontal intermediate installation (Fig.7)

7. An additional window in the horizontal intermediate installation (Fig.7)

8. The recuperator (Fig.1, 3, 5, 10, 11, 12)

9. Diagonally installed cross-flow plate heat exchanger (Fig. 8, 10, 11,12)

10. The controlled recirculating air valve of the supply chamber (figure 10, 11, 12)

11. The inlet pipe of the supply chamber (figure 10, 11, 12)

12. The controlled input warmed air valve of the supply chamber (Fig. 10, 11, 12)

13. The air cleaner of the supply chamber (figure 10, 11, 12)

14. The chamber of mixing the air in the supply chamber (figure 10, 11, 12)

15. The controlled air valve at the inlet to the mixing chamber (figure 10, 11, 12)

16. The block of the air heater of the supply chamber (figure 10, 11, 12)

17. The controlled bypass valve in the heater block (Fig.10, 11, 12)

18. The fan unit of the supply chamber (figure 10, 11, 12)

19. The exhaust pipe of the supply chamber (figure 10, 11, 12)

20. The inlet pipe of the exhaust chamber (figure 10, 11, 12)

21. The air cleaner of the exhaust chamber (figure 10, 11, 12)

22. The fan unit of the exhaust chamber (figure 10, 11, 12)

23. The controlled air valve of the exhaust chamber at the inlet to the recuperator (figure 10, 11, 12)

24. The exhaust pipe of the exhaust chamber (figure 10, 11, 12)

25. Additional Fan block exhaust chamber (Fig.10, 11, 12)

26. An additional controlled air valve installed at the outlet of the main fan unit (Fig. 10, 11, 12)

27. An additional inlet pipe of the exhaust chamber (Fig.14, 15)

28. The outer panel of the exhaust chamber (Fig.14, 15)

29. Controlled insulated air valve in the additional inlet pipe (Fig.14, 15)

30. The air cleaner installed in the additional inlet pipe (Fig.14, 15)

31. Additional exhaust pipe of the exhaust chamber (Fig.15, 17)

32. Controlled insulated air valve in an additional air pipe (Fig.16, 17)

33. An additional inlet pipe of the supply chamber (Fig.14, 15)

34. A controlled bypass insulated air valve located in the additional inlet pipe of the supply chamber (Fig.14, 15)

35. An air cleaner located in the additional inlet pipe of the supply chamber (Fig.14, 15)

36. The outer panel of the chamber mixing air (Fig.14, 15)

37. The housing of the recuperator (Fig.10, 11, 12)

38. The side walls of the housing of the recuperator (figure 10, 11, 12)

39. The end walls of the housing of the recuperator (Fig.9)

40. The bottom of the housing of the recuperator (figure 10, 11, 12)

41. A tray for collecting condensate (figure 3, 5, 8, 10, 11,12)

42. Drain fitting (Fig. 1, 3, 5, 8, 10, 11, 12)

43. Siphon (figures 1, 3, 5, 8, 10, 11, 12)

44. The vertical row of series-connected plate heat exchangers (figure 10, 11, 12)

45. The vertical partition of the heat exchanger housing (Fig. 8, 10, 11, 12)

46. Side ribs of heat exchangers (Fig.10, 11, 12)

47. The ends of the heat exchangers (Fig.13)

48. Internal air channels between the heat exchangers of each vertical row (Fig. 8, 10, 11, 12)

49. External air channels between the heat exchangers of each vertical row (Fig. 8, 10, 11, 12)

50. The closing link (Fig.8, 10, 11, 12)

51. The air channel between the rows of heat exchangers in the air exhaust line (figure 10, 11, 12)

52. The air channel between the rows of heat exchangers in the line of air flow (figure 10, 11, 12)

53. Mounting window in the floor panel of the supply and exhaust system (Fig. 7)

54. The upper half of the upper heat exchangers (Fig.9)

55. Flange housing recuperator (Fig.9)

56. The free ends of the upper heat exchangers (Fig.9)

57. The side walls of the supply air chamber (Fig.7)

58. The upper ribs of the upper heat exchangers (Fig)

59. The vertical transverse partition of the supply and exhaust installation (figure 10, 11, 12)

60. Individual air channel, the purpose of which depends on the number of stages in the recuperator:

- when using four- and six-stage recuperators, it is the exhaust air channel inlet to the recuperator;

- when using five-stage recuperators, it is the outlet for the supply air from the recuperator (Fig. 10, 11, 12)

61. Individual outlet from the recuperator air duct for exhaust air (Fig.10, 11, 12)

62. Adiabatic humidifier exhaust air installed in the exhaust chamber at the inlet to the recuperator (Fig.10, 11, 12)

63. Water supply

64. The body of the plate heat exchanger (Fig.13)

65. Removable heat transfer cartridge (Fig.13)

66. Plate heat transfer cassettes (Fig.13)

67. Air channels between the plates 66 of the heat exchange cartridge (Fig.13)

68. Service hatches in the side walls of the heat exchanger housing (Fig. 10, 11, 12)

69. Service hatch in the bottom of the heat exchanger housing (figure 10)

70. The lower ribs of the lower heat exchangers (figure 10, 12)

71. The window in the closing link of the four-stage recuperator (figure 10)

72. Racks connecting the condensate collection tray to the service hatch 66 of the recuperator bottom (Fig. 10)

73. Transit air channel in a five-stage recuperator (11)

74. The lower edge of the closing link of the five-stage recuperator (11)

75. An additional adiabatic humidifier installed in the recuperator on a condensate drain pan (FIGS. 10, 11, 12)

76. Adiabatic supply air humidifier located behind the air heater

Claims (9)

1. A supply and exhaust unit with heat recovery of the exhaust air and indirect adiabatic cooling of the supply air, comprising floor and ceiling panels, supply and exhaust chambers separated by a horizontal intermediate partition with main and additional windows, the main of which is a diagonal mounted cross-flow plate a recuperator having intake and exhaust lines, and a controllable recirculating air valve, an inlet chamber with holds an inlet pipe, a controlled inlet insulated air valve, an air purifier, a bypass valve, a mixing chamber with a controlled air valve at the inlet, an air heater unit, a fan unit and an outlet pipe, an exhaust chamber contains an air purifier, a fan unit, a controlled air valve installed at the inlet to the recuperator , inlet and outlet pipes, supply air cooler, characterized in that the supply chamber is equipped with an additional inlet pipe with an air cleaner, size mounted on one of the side panels of the air mixing chamber, the exhaust chamber is equipped with an additional controlled air valve installed at the outlet of the main fan unit, an additional outlet pipe with a controlled outlet warmed air valve installed on one of the side panels of the fan unit, and an additional inlet pipe, placed between the controlled and additional controlled air valves on one of the side panels of the exhaust chamber, the controlled inlet is insulated With the help of an air valve and an air purifier located in the aforementioned additional inlet branch pipe of the exhaust chamber, the recuperator is made of a housing with side and end walls, a bottom, a condensate collecting pan with a drain fitting and a siphon, and at least four stages of plate heat exchangers connected in series with the fins, which are placed in the heat exchanger housing in two vertical rows separated by a vertical partition, which is hermetically connected to the side fins of the heat exchangers, when the outer side ribs of the vertical rows of heat exchangers are hermetically connected to the side walls of the heat exchanger housing, the ends of the heat exchangers are connected to the end walls of the heat exchanger housing with the formation of internal and external air channels between the heat exchangers of each vertical row, the lower heat exchangers are connected by a closing link, which together with the bottom forms air channels, connecting the rows of heat exchangers in the exhaust and inflow lines, in addition, the floor panel of the supply and exhaust unit is equipped with It is equipped with a mounting window coaxially with the main window in the horizontal intermediate partition, the upper half of the upper heat exchangers is protruding beyond the flanges of the heat exchanger housing and is integrated through the mounting window in the floor panel of the air handling unit into the air supply chamber with a tight connection of the heat exchanger flanges to the floor panel and free ends of the upper heat exchangers to the side walls of the supply air chamber, the recuperator is integrated with the upper fins of the upper heat exchangers in the main The oval window of the horizontal intermediate partition, the supply and exhaust unit is equipped with a vertical transverse partition, which is located in the main window of the horizontal intermediate partition, is rigidly mounted on the vertical partition of the recuperator and hermetically connected to the ceiling panel of the supply and exhaust unit with the formation of air channels communicating the upper heat exchangers of the recuperator with supply and exhaust installation chambers, the supply air cooler is made in the form of adiabatic humidify For exhaust air with an inlet water supply, which are located in the exhaust chamber between the controlled air valve and the recuperator, the bypass valve is installed in the additional inlet port of the inlet chamber at the inlet in front of the air cleaner and is insulated, the outlet nozzle of the exhaust chamber is located above the inlet port of the supply chamber, and the side walls and the bottom of the heat exchanger housing is equipped with service hatches. 2. The supply and exhaust installation with heat recovery of the exhaust air and indirect adiabatic cooling of the supply air according to claim 1, characterized in that in the manufacture of the four-stage recuperator, the closing link is made in the form of a closing plate that is rigidly connected to the lower ribs of the lower heat exchangers, and its ends hermetically connected to the end walls of the heat exchanger housing; under the closing link of the lower heat exchangers, the bottom of the heat exchanger housing is located with an interval from it. 3. The supply and exhaust unit with the recovery of heat of the exhaust air and indirect adiabatic cooling of the supply air according to claim 2, characterized in that the closing link of the lower heat exchangers is made with a window in which a condensate collection tray is integrated, rigidly connected to the service hatch of the bottom of the heat exchanger racks, and the drain fitting is mounted on a condensate drain pan and is made with a transit passage through the service hatch of the bottom of the heat exchanger housing, under which a siphon is installed. 4. The supply and exhaust unit with the recovery of heat of the exhaust air and indirect adiabatic cooling of the supply air according to claim 1, characterized in that in the manufacture of the five-stage recuperator, the closing link is made in the form of a closing diagonally mounted plate heat exchanger, which is hermetically connected to the lower heat exchangers of the heat exchanger and the lower rib is rigidly mounted on the bottom of the heat exchanger housing, the condensate collection tray is placed in the air channel connecting the rows of heat exchangers in nii air exhaust. 5. The supply and exhaust unit with the recovery of heat of the exhaust air and indirect adiabatic cooling of the supply air according to claim 1, characterized in that in the manufacture of a six-stage recuperator, the closing link is made in the form of a closing plate, which is rigidly connected to the lower ribs of the lower heat exchangers, and its the ends are hermetically connected to the end walls of the heat exchanger housing; under the closing link of the lower heat exchangers, the bottom of the heat exchanger housing is located with an interval from it. 6. The supply and exhaust unit with heat recovery of the exhaust air and indirect adiabatic cooling of the supply air according to claim 5, characterized in that the condensate collecting pan in the recuperator is integrated in the service hatch located in the bottom of the recuperator body. 7. The supply and exhaust unit with the recovery of the heat of the exhaust air and indirect adiabatic cooling of the supply air according to claim 1, characterized in that during the humid treatment of the supply air, the supply chamber is equipped with an adiabatic supply air humidifier with an inlet water supply located behind the air heater. 8. The supply and exhaust unit with heat recovery of the exhaust air and indirect adiabatic cooling of the supply air according to claim 1, characterized in that when mixing the outdoor air with the exhaust in the proportions of 30% and 70%, respectively, the exhaust chamber is equipped with an additional fan unit with a frequency a converter located at the outlet of the recuperator. 9. The supply and exhaust unit with the recovery of the heat of the exhaust air and indirect adiabatic cooling of the supply air according to any one of claims 1, 2, 4, 5, characterized in that in the forced cooling mode of the supply air, the supply and exhaust unit is equipped with an additional adiabatic air humidifier, placed in the recuperator on a condensate drain pan, with a water supply leading to it.

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