FI122965B - Supply air device and method for ventilation - Google Patents

Description

Supply air device and method of ventilation Tilluftanordning och förfarande vid ventilation

5 TECHNICAL FIELD

The invention also relates to a supply air device according to the preamble of claim 1. The invention also relates to a method of ventilation in accordance with the preamble of claim 3.

BACKGROUND OF THE INVENTION

15 The supply air devices or air-conditioning beams comprise an supply air chamber, a mixing chamber and a heat exchanger. The fresh air flow is brought from the supply air chamber to the mixing chamber, where the fresh air flow is mixed with the recirculated air, after which the combined air flow is led to the room. The recirculated air is led to the mixing chamber via a heat exchanger where the recirculated air can be heated or cooled. The same supply air unit can be used to cool room air during the summer and to heat the room during the winter. During the summer, the recirculated air in the room is cooled down and heated in the supply air heat exchanger during the winter. cm The fresh air flow induces the recirculated air flow from the room through the heat exchanger to the mixing chamber.

o 25 o The problem is the peripheral space of the room, such as a wall adjoining the open air, which includes a £ window. During the winter, strong cold draft occurs when cold window surface 00 causes cold air to flow downward in the room and during summer time the air heated by the window surface tends to rise strongly to the ceiling of the room.

2

The air-conditioning beam or air-beams are usually adjusted for the average cooling and heating needs of the room, which is unsatisfactory at the extremes of the room. In a situation where the room has several beams, the beams closest to the window wall can be dimensioned for higher cooling or heating power. Passive air-conditioning beams have also been used near the window wall, whereby the air-conditioning beam absorbs airflow from the sun-heated window up to the ceiling of the room.

The known solutions have not been able to solve this aforementioned peripheral room-related problem in a satisfactory manner.

SUMMARY OF THE INVENTION

With the supply air device according to the invention, the above mentioned air flows due to the temperature of the window surface can be better taken into account.

The main features of the ventilation device according to the invention are set forth in the characterizing part of claim 1.

The main features of the process according to the invention are set forth in the characterizing part of claim 3.

By means of the control system of the supply air device according to the invention, the combined ° airflow can be directed to the room to be ventilated from the mixing chambers of the supply air device o 25 either by directing the entire combined airflow downwardly to the room to be ventilated or by controlling the total combined airflow to the room. that part of the combined airflow is directed downwards and part of the combined airflow is directed sideways to the ceiling of the room to be ventilated.

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1 30 3

The supply air device according to the invention can be used to regulate the room conditions so as to take into account the seasonal heating and / or cooling demand and the convection flow from the window surface which is cold to the floor in winter and warm to the ceiling in summer.

In summer, the summer mode of the supply air unit is used, in which the first portion of the combined airflow is directed downwards along the window wall and the second portion of the combined airflow is directed sideways towards the ceiling of the room. 10 In winter, a winter mode is used in which the combined air flow is directed downwards in the direction of the window wall as a whole. In spring, the spring mode of the supply air unit is used, where the combined air flow is controlled entirely along the ceiling of the room.

The invention will now be described with reference to some preferred embodiments of the invention shown in the figures of the accompanying drawings, but which are not intended to be limited thereto.

BRIEF DESCRIPTION OF THE FIGURES

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Figure 1 shows the supply air device according to the invention in its various modes of operation. Fig. 2 is an axonometric view of the supply air device according to the invention.

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Fig. 3 is a cross-sectional view of Fig. 2 showing the principle of supply air control σ> 0.

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a> Figure 4 is a cross-sectional view of the supply air device shown in Figure 2.

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O 30 DESCRIPTION OF THE PREFERRED EMBODIMENTS

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Figure 1 shows the supply air device according to the invention in three different operating modes A1, A2 and A3. Each mode of operation A1, A2 and A3 shows a cross-section of a room H to be ventilated, in which the supply air device 10 according to the invention is shown. The supply air device 10 is suspended in the ceiling K of room H, at a distance 5 from ceiling K and a distance SI from the window wall W of room H. The supply air device 10 is parallel to the window wall W of room H.

Figure 1 is a top view of the summer mode AI of the air conditioner 10. During the summer, the window heats the window W1, whereby the warm airflow LL is directed upwards towards the ceiling K along the perimeter button W1 and the window wall W. Hereby, the first airflow LA cooling the room H is directed obliquely downwards towards the floor E through the air conditioner 10 and the second airflow LB cooling the room H in a direction parallel to the roof K sideways. By this arrangement, the upward warm airflow LL from window W1 is directed along with the recirculated air to the heat exchanger of the air conditioning unit 15, whereby this warm airflow LL is prevented from spreading into room H. By controlling a portion of the cooling airflow LB LA feels reasonable not to create a sense of bet.

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Figure 1 shows in the middle the winter mode A2 of the air conditioner 10. In winter, window W1 shines cold, which as cold air flows down the wall W down the wall E towards the floor E. The heating air flow LA is then directed through the air conditioner 10 only obliquely downwards towards the floor E.

00 o 25 In this way, the cold air flow LK downwards from the cold permeable window W1 can be cut off, thus avoiding the spread of cold air down the floor g E to the room H.

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c \ | co Figure 1 shows the A3 spring mode of the air conditioner at the bottom. Spring icon

o 30 since W1 is still cold, there is a cold air flow LK from window W1

down to the window wall W. The air flow LB is then directed through the air conditioner 10 only in the direction of the roof K sideways. In the spring, the sun heats up room H, but window W1 is still cold. The airflow LB exiting the air-conditioning beam 10, cooling the room H, is directed to the side only in the direction of the roof K, whereby it does not amplify the cold airflow LK from the cold sparkling window W1.

Fig. 2 is an axonometric view of the supply air device according to the invention. The supply air device 10 comprises a rectangular cross-sectional inlet to the air chamber 11, into which fresh air flow is led externally through a duct system and a fan 10. The sidewall of the supply air chamber 11 has a first flow opening 12a and a second 12b which are closed and opened in the direction of the sidewall by a horizontally movable control plate 13. The first flow opening 12a connects the first elongated manifold 14a to the supply air chamber 11 14a and the second distribution chamber 14b are parallel and rectangular in cross-section.

The baffle plate 13 in connection with the side wall of the supply air chamber 11 cooperates with the first flow openings 12a and 12b. Opening the first flow port 12a closes the second flow port 12b and vice versa. The total throttle in the fresh air flow from the supply air chamber 11 to the distribution chambers 14a, 14b thus remains constant, whereby the total track air flow to the air-conditioned room space c i H will also remain constant. The adjustment on the plate 13 thus adjusts the distribution of the total flow of the feed ridge from the supply air chamber 11 to the distribution chamber 14a, 14b among the distribution chambers 14a, 14b.

The bottom surface of the first distribution chamber 14a has a first row of nozzles 16a oo through which fresh air can be supplied from the first distribution chamber 14a S to the first mixing chamber 15a below it. Similarly, a second nozzle array 16b is provided on the underside of the second manifold chamber 14b, through which fresh air from the second manifold chamber 14b can be led to the second second manifold chamber 15b.

Between the first distribution chamber 14a and the second distribution chamber 14b there is provided an elongated rectangular cross-section heat exchanger 17. second control unit 20.

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The lower part of the first mixing chamber 15a has a first outlet 25a, from which the combined air flow formed in the first mixing chamber 15a is directed downwards towards the floor surface of the room to be ventilated. The lower part of the second mixing chamber 15b has a second outlet port 25b, from which the combined air flow formed in the other part 15b of the mixing chamber 15 is directed sideways in the direction of the ceiling of the room to be ventilated.

Figure 3 is a cross-sectional view of Figure 2 showing the principle of regulating the supply air. The window wall in this room is located to the right of the supply air unit.

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In the mode B1 of Fig. 3, the adjusting plate 13 in the side wall of the supply air chamber 11 is in its first extreme position, whereby the entire fresh air flow of the supply air chamber 11 is directed through the first flow opening 12a to the first distributor chamber 14a.

3) In operating mode B2 of Fig. 3, the adjustment plate g 13 in the side wall of the supply air chamber 11 is in its central position. Half of the fresh air flow from the supply air chamber 11 is directed through the first flow opening 12a to the first distribution chamber 14a and the other half of the fresh air flow from the supply air chamber 11 is directed through the second flow port 30b to the second distribution chamber 14b.

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In the mode of operation B3 of Figure 3, the adjusting plate 13 in the side wall of the supply air chamber 11 is close to one of its extreme positions. A small portion of the fresh air flow from the supply air chamber 11 is directed through the first flow opening 12a to the first distribution chamber 14a and the majority of the fresh air flow from the supply air chamber 11 is directed through the second flow opening 12b to the second distribution chamber 14b.

In operating mode B4 of Figure 3, the baffle plate 13 in the side wall of the supply air chamber 11 is at its second extreme position, whereby the entire fresh air flow of the supply air chamber 11 is directed through the second flow opening 12b to the second distribution chamber 14b.

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Figure 3 shows that the flow openings 12a, 12b in the sidewall of the supply air chamber 11 are shaped such that the total throttling of the fresh air flow from the supply air chamber 11 to the distribution chambers 14a, 14b is kept constant. In modes B1 and B4, the entire fresh air flow from the supply air chamber 15 11 is directed through the nozzles 16a, 16b of one of the distribution chambers 14a, 14b to the respective mixing chamber 15a, 15b. The fresh air flow flow path in these modes B1 and B4 is one-half of the total number of nozzles 16a, 16b if the number of nozzles 16a, 16b is equal in each distribution chamber 14a, 14b. In other modes, the fresh air flow flow path has the entire number of nozzles 16a, 16b. This must be taken into account in the design of the flow openings 12a, 12b.

Figure 4 is a cross-sectional view of the supply air device shown in Figure 2. c \ i The window wall of the room is thus to the left of the supply air device 10. The inlet on the left side of the Y-Y vertical axis of the machine 10

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cp 25, the first mixing chamber 15a is formed by the bottom of the first distribution chamber 14a, the left side wall of the heat exchanger 17, the left sloping guide surface F2 of the first control member 18 and the first distribution chamber 14a from the outer side wall downwards from the <o in the space defined by the wall 19a. The second mixing chamber 15b to the right of the vertical air axis 10-Y 30 of the supply air device 10 is formed by a boundary located below the bottom of the second manifold 14b, the right side wall of the heat exchanger 17, the right bevel guiding surface F2 of the first

Through a first row of nozzles 16a 5 at the bottom of the first distribution chamber 14a, fresh air flow L1 is blown downwardly into the first mixing chamber 15a adjacent to the left vertical side wall 19a to which the fresh air flow L1 is attached by the coanda effect. The recirculated air flow L2 entering through the heat exchanger 17 into the first mixing chamber 15a combines with the fresh air flow L1 in the first mixing chamber 15a and the combined airflow 10a is directed by the .

Through a second row of nozzles 16b at the bottom of the second distribution chamber 14b, a fresh air stream L1 is blown downwardly into a second mixing chamber 15b adjacent to the left vertical side wall, i.e. the right side wall of the heat exchanger 17, to which the fresh air flow adheres. The recirculated air flow L2 through the heat exchanger 17 to the first mixing chamber 15a and the combined airflow LB first flows downwardly to the right side wall of the heat exchanger 17, after which it is guided to the right side of the first guide piece 18 20 through the duct 25b of the second mixing chamber 15b, through the ceiling of the room to be ventilated horizontally to the side and connected to it by the coanda effect.

σ> o g The recirculated airflow L2 passes from the room H to be ventilated to the heat exchanger oo 17 and then to the first one to the left of the heat exchanger 17.

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g into the mixing chamber 15a and the second mixing chamber 15b on the right side of the heat exchanger 17. The recirculated air flow L2 can be either heated or cooled in a heat exchanger 17.

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In the supply air device 10 shown in Figures 2-4, the combined airflow LA from the first mixing chamber 15a is directed downwards only and the combined airflow LB from the second mixing chamber 15a is directed sideways only horizontally. The supply air device 10 is positioned on the ceiling K of the room H to be ventilated, so that the edge of the supply air device 10 having the first distribution chamber 14a and the first mixing chamber 15a below it faces the window wall W.

The supply air device 10 according to the invention can be located near the ceiling of the room, parallel to the window wall, at a distance from the window wall or in the suspended ceiling of the hotel room parallel to the door wall of the hotel room, at a distance from the door wall.

In the embodiment shown in Figures 2-4, the cross sections of the supply air chambers 11, the distribution chambers 14a, 14b and the heat exchangers 17 form a rectangle. This is a preferred cross-sectional shape for manufacturing purposes, but the cross-sectional shape of these devices may also be other, e.g. round, trapezoidal, or polygonal.

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In the embodiment shown in Figs. 2-4, one common adjusting plate 13 is used for both flow openings 12a, 12b in the supply air chamber 11. This is a preferred embodiment of cm, but a separate adjusting plate for each of the flow openings 12a, 12b could also be used here.

Only some preferred embodiments of the invention have been described above, and it will be apparent to one skilled in the art of g that numerous modifications may be made within the scope of the appended claims.

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Claims (3)

A supply air device (10) comprising: - a supply air chamber (11), 5. two flow openings (12a, 12b) located on a side wall of the supply air chamber (11), - two distribution chambers (14a, 14b), which were and one is connected to its own flow orifice (12a, 12b), which are located parallel to each other and formed by elongated bodies, the bottom of which has a row (16a, 16a) of nozzles, - a heat exchanger (17) which is located partially in part between the distribution chambers (14a, 14b) and formed by an elongate body, - a first mixing chamber (15a) located below the first distribution chamber (14a) and comprising a first outlet opening (25) from which a combined air flow is directed downwards toward the floor surface of the room space to be ventilated; - a second mixing chamber (15b) located below the second distribution chamber (14b) and comprising a second outlet opening (25b) from which a combination d air flow is directed to the side parallel to the ceiling of the room space 20 to be ventilated, characterized in that the supply air device (10) further comprises a control arrangement comprising: a control disc (13) which closes and opens the flow openings (12a). , 12b) in cm supply air chamber (11) so that when the first flow opening (12a) leading in 00 cp 25 to the first distribution chamber (14a) is closed, the second flow and opening (12b) leading to the second distribution chamber (14b) is opened ), and vice versa, ro - wherein the amount of combined air flow conducted from the outlet openings (25a, 25b) in each mixing chamber (15a, 15b) downstream (LA) and oo to the side (LB) in the room space to be ventilated can be regulated in such a way that the total throttling in the fresh air flow (LI) to be conducted from the supply air chamber (11) to the distribution chambers (14a, 14b) remains constant and the total the fresh air flow (LI) to be fed to the room space (H) to be ventilated remains constant. Supply air device (10) according to claim 1, characterized in that the supply air device (10) further comprises: - a first side wall (19a), which is directed vertically downward from an outer side wall of the first distribution chamber (14a), - a first guide body (18) located beneath the heat exchanger (17) and formed by an elongate, to the cross section, trapezoidal portion, the shorter parallel wall of the trapezoid being attached to the flat lower surface of the heat exchanger (17), second control body (20) located below the second distribution chamber (14b), wherein: - the first mixing chamber (15a) is formed in a space bounded by the first distribution chamber (14a), the first side wall (19a), the heat exchanger (17) and the first control body (18), - the second mixing chamber (15b) is formed in a space limited by the second distribution chamber (14b), the heat exchanger (17), the first control body (18) and the second control body pin (20). 20 A method of ventilation, wherein an supply air device (10) is arranged in a room space (H) in the vicinity of the roof (K), parallel to a window wall (W), at a distance from the window wall (W), which supply air device comprises: cv - one supply air chamber (11), 25. two flow openings (12a, 12b) located on a side wall of the supply air chamber (11), g - two distribution chambers (14a, 14b), which were and one is connected to its own g flow opening (12a, 12b) and which are located parallel to each other and C \ | <o is formed by elongate bodies, the bottom surface of which has a row (16a, 16a) of the mouth piece, - a heat exchanger (17) located parallel in part between the distribution chambers (14a, 14b) and formed by an elongated body a first mixing chamber (15a) located below the first distribution chamber (14a) and comprising a first outlet opening (25) from which a combined air flow is directed downwardly to the floor surface of the room space to be ventilated, - a second mixing chamber (15b), which is located below the second distribution chamber (14b) and comprises a second outlet opening (25b), from which a combined air flow is directed to the side parallel to the ceiling of the room space 10 to be ventilated, characterized in that: closes and opens the flow openings (12a, 12b) in the supply air chamber (11) with a control disc (13) so that the first flow opening (12a) leading to the first distribution chamber one (14a) is closed, the second flow opening (12b) leading to the second distribution chamber (14b) is opened, and vice versa - the amount of combined air flow conducted from the outlet openings (25a, 25b) into each mixing chamber (15a, 15b) downstream (LA) and to the side (LB) of the room space to be ventilated can be regulated in such a way that the total throttling in the fresh-air flow (LI) to be conducted from the supply air chamber (11) to the distribution chambers (14a, 14b ) remains constant and the total fresh air flow (LI) to be measured in the room space (H) to be ventilated remains constant. δ CVJ 00 o 25 CD O X cc CL 00 CD CM CO CD O O CM