FI124779B - Supply air device and method in supply air device - Google Patents

Description

Supply air device and method in supply air device Tilluftanordning och förfarande vid en tilluftanordning

ENGINEERING

The invention relates to an supply air device according to the preamble of claim 1.

The invention also relates to a method in the supply air device according to the preamble of claim 8.

BACKGROUND OF THE INVENTION

FI patent 113891 discloses an inlet air device comprising an inlet air chamber, nozzles arranged in the inlet air chamber, through which the inlet air from the supply air chamber is blown from the wheel to the mixing chambers below the supply air chamber. The supply air device further comprises a heat exchanger located below the supply air chamber, through which the room air is circulated to the mixing chambers by inducing supply air blown from the nozzles. Each mixing chamber is formed by a duct formed by an oblique-down side plate mounted on the side wall of the supply air chamber and mounted below the heat exchanger and inclined downwardly. The guide member can be swiveled aside on the hinge device or completely detached, providing access to serviceable and cleanable objects within the structure, such as a heat exchanger.

GB-A-2 391 613 discloses an inlet air device comprising an inlet chamber, nozzles arranged in the inlet chamber through which the inlet air from the inlet chamber is blown into the mixing chamber on either side of the inlet chamber. The supply air device further comprises at least one heat exchanger through which side air is circulated into the mixing chamber by fresh supply air blown from the nozzles. The upper surface of the heat exchanger forms the lower surface of the mixing chamber. The lower part of the supply air unit is closed on the plate. The room air thus passes through the side surface of the heat exchanger through the heat exchanger, after which it changes its direction of travel by 180 degrees and returns from the supply air unit with the fresh supply air stream from the mixing chamber in a substantially horizontal direction.

U.S. Patent Publication No. 2007/0164124 discloses an inlet air device comprising an inlet air chamber, nozzles fitted in an inlet chamber, through which wheeled inlet air from the inlet air chamber to the mixing chambers is blown. The supply air device further comprises a heat exchanger through which the room air is circulated to the mixing chambers by the induction of fresh supply air from the nozzles. The supply air device further comprises a controller through which a by-pass from the supply air chamber can be conducted to the room to be ventilated. By-pass is used to direct fresh supply air from the supply air chamber to the room to be ventilated past the nozzles. By-pass can provide additional flow of fresh supply air to the air-conditioned room. This allows a wider operating range for the supply air unit, where the amount of fresh supply air can be changed without changing the supply air unit nozzles.

In addition, there is known a so-called passive beam, which uses liquid, in principle water, to cool or heat the beam heat exchanger. The heat exchanger in turn cools or heats the air in the room. The room air in connection with the heat exchanger thus becomes colder or warmer than the rest of the air in the room, thereby providing a flow of room air through the heat exchanger. Heavier cold air tends to lower due to gravity and lighter warm air tends to rise up due to gravity. The passive beam does not contain any supply air part at all, ie no passive supply air is supplied to the air-conditioned room through the passive beam. The passive beam is thus used solely to cool or heat the air in the room by circulating the room air through the heat exchanger of the passive beam.

Induction-based supply air devices have a combined flow of air from the mixing chamber to the room to be ventilated in the heating situation from overheated to the room air temperature and in the cooling situation to the underheated room to air temperature respectively.

In a heating situation, the overheated combined airflow tends to be deposited in the upper part of the air-conditioned room, whereby a vertical temperature difference is created in the air-conditioned room and the air flow to the lower part of the air-conditioned room. This results in low ventilation efficiency as well as unsatisfactory temperature conditions in the air-conditioned room.

In a cooling situation, the sub-heated combined airflow tends to be directed to the lower part of the air-conditioned room, the living area, where it can create a sense of draft.

Raising or lowering the temperature, especially in high-volume rooms, is a slow process. On the other hand, the time needed for ventilation does not depend on the mass of the room. In the air-conditioned room, the temperature should be adjusted to the desired level before the room is used, and the air in the room should be changed. According to the instructions, it is sufficient for fresh air to be supplied to the air-conditioned room approximately twice the volume of the room before use. The time required for this is typically about one hour. Bringing the room to the desired temperature normally takes much longer compared to the time needed to change the room air. Induction-based supply air devices thus need to change the air in the air-conditioned room much longer than would be necessary for ventilation in order to bring the air-conditioned room to the desired temperature before use.

SUMMARY OF THE INVENTION

The supply air device according to the invention is characterized in what is stated in the characterizing part of claim 1.

The method of the invention in the supply air device is characterized by what is disclosed in the characterizing part of claim 8.

The supply air device according to the invention comprises a frame structure, and at least one heat exchanger supported on the frame structure. The air in the room to be air-conditioned is recirculated by gravity through said at least one heat exchanger, where the recirculated air stream is cooled or heated, after which the cooled or heated recirculated air flow is returned to the room to be air-conditioned. The supply air device is characterized in that it further comprises at least one supply air portion supported on the frame structure, said at least one supply air portion comprising an adjusting means for adjusting the amount of fresh air flow supplied from said at least one supply air portion to a ventilated room.

In the solution according to the invention, the recirculated air circulates through the heat exchanger solely due to gravity, whereby the cooling and heating operation of the supply air device is independent of the ventilation of the room to be ventilated. Thus, the temperature of the room to be ventilated can be controlled independently of the operating hours of the fresh air supply unit. The supply of fresh air from the supply air section has little effect on the cooling or heating output achieved. In the prior art supply air device, the fresh air flow discharged from the nozzles of the supply belt chamber induces the recirculation belt flow to circulate through the heat exchanger, whereby the amount of fresh air flow directly affects the recirculation air flow rate and thereby the cooling and heating of the supply air device.

The control of the amount of fresh air flow to be supplied to the air-conditioned room can be based on e.g. the number of people in the air-conditioned room, the temperature of the air-conditioned room or the air quality of the air-conditioned room.

The supply air device according to the invention does not cause unnecessary movement of air in a room to be ventilated in a situation where there is no need for cooling or heating in the room to be ventilated. The supply of fresh supply air to the room to be ventilated from the supply air portion of the louvre device can then be closed by a regulating member of the supply air portion.

The supply air device according to the invention can supply fresh supply air, which is isothermal or, if necessary, underheated, in the heating situation, whereby the supply air flow to the room to be ventilated causes the air to be mixed. Ventilation efficiency is also maintained at a good level.

The supply air device according to the invention can supply fresh supply air, which is isothermal or, if necessary, overheated, when cooling, so that the supply air flow to the room to be ventilated can be traveled the desired route outside the residence area of the room to be ventilated. This way you can prevent the feeling of draft in the living area of the air-conditioned room.

With the supply air device according to the invention, the heating or cooling of the room to be ventilated can be started earlier and the ventilation of the room to be ventilated only later, The supply air section and the heat exchanger are independent of each other. This results in significant savings when you do not have to keep the ventilation unnecessarily on.

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

Fig. 1 is a perspective view of the first embodiment of the supply air device.

Figure 2 is a plan view of the supply air device shown in Figure 1.

Figure 3 is a bottom view of the supply air device shown in Figure 1.

Figure 4 is a longitudinal sectional view A-A of Figure 2.

Figure 5 is a transverse sectional view B-B of Figure 2.

Figure 6 is a perspective view of another embodiment of the supply air device.

Fig. 7 is a plan view of the supply air device of Fig. 6.

Figure 8 is a bottom view of the supply air device shown in Figure 6.

Figure 9 is a longitudinal sectional view A-A of Figure 7.

Figure 10 is a bottom view of the supply air device shown in Figure 6.

Figure 11 is a transverse sectional view B-B of Figure 7 corresponding to the situation shown in Figure 10.

Figure 12 shows a variation of the supply belt device shown in Figure 6, viewed from below.

Figure 13 is a transverse sectional view B-B of Figure 7 corresponding to the situation shown in Figure 12.

Fig. 14 is a transverse sectional view C-C of Fig. 7 in a first mode of operation.

Figure 15 is a transverse sectional view C-C of Figure 7 in another mode of operation.

Fig. 16 is a transverse sectional view C-C of Fig. 7 in a third mode of operation.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

Figure 1 is a perspective view of a first embodiment of the supply air device and Figure 2 is a plan view of the supply air device of Figure 1. The supply air device 100 comprises a frame structure 40 fitted with an supply air duct 10, an supply air section 20, a first heat exchanger 30a and a second heat exchanger 30b. The fresh air flow L1 is led through the supply air duct 10 to the supply air section 20 and from there to the room to be ventilated. The frame structure 40 here consists of a rectangular sheet metal frame 41. Here the lower surface of the sheet metal frame 41 is closed by a hole plate 42 and the upper surface of the sheet metal frame is open. The supply air duct 10 and the supply air section 20 are located in the middle of the damper frame 41 and the heat exchangers 30a, 30b are located on both sides of the supply air section 20. The supply air duct 10, the supply air section 20 and the heat exchangers 30a, 30b are supported on the damper frame 41 by transverse Y-Y supports 43. The heat exchangers 30a, 30b extend over the entire longitudinal direction X-X of the damper frame 41.

Figure 3 is a bottom view of the supply air device shown in Figure 1. The figure shows the air supply passage 10, the diffuser 20, the heat exchangers 30a, 30b, a frame structure 40 and the apertured base plate 42. The figure shows in addition to the air supply part 20 of the lower surface of the damper 21, which can be moved in the direction of arrow SI direction of the actuator 50. The supply air portion 20 bottom surface of the first openings and the damper 21 has a second openings 21a. In the situation shown in the figure, the second openings 21a of the damper 21 overlap the first openings of the lower surface of the supply air section 20, whereby the maximum flow area, i.e. the maximum air flow from the supply air section 20, discharges into the room to be ventilated. By moving the damper 21 of the arrow SI in the direction indicated by an actuator 50 can change the flow area, wherein the TU-20 loilmaosasta conditioned room space amount of the fresh air flow emitted can be controlled. The damper 21 thus functions as an air volume control in the supply air section 20. The room to be ventilated may further comprise a sensor 71 which is coupled to the control circuit 70 which in turn controls the actuator 50, which in this case is an electric motor. The sensor 71 may be e.g. a temperature sensor or a CO2 sensor. Thus, the amount of fresh supply air supplied to the air-conditioned room can be adjusted based on the temperature of the air-conditioned room or the CO 2 content of the air-conditioned room.

Figure 4 is a longitudinal sectional view A-A of Figure 2. The figure shows the supply air duct 10, the supply air section 20, the second heat exchanger 30a, the frame structure 40 and the apertured bottom plate 42.

Figure 5 shows a transverse section B-B of Figure 2. From the Figure shows the diffuser 20, the heat exchangers 30a, 30b, below the frame structure 40 and the apertured base plate 42. The supply air portion 20 is adapted to Sector shielding 60, which may be adjustable in the direction of arrow S2 direction, i.e. in the vertical plane. The fresh air flow L1 is led through the other openings 22 of the lower surface of the supply air section 20 into the room to be ventilated downwards. The baffle plate 60 directs the downward flow of fresh air L1 from the supply air section 20 to the side and thus to a wider area into the room to be ventilated. The guide surface 61 of the baffle plate 60 forms an angle α with the horizontal. The angle α and the length of the guide surface 61 of the baffle plate influence the distribution of the fresh airflow L1 to the room to be ventilated. The recirculated airflow L2 is directed from the room to be ventilated from above the supply air device through the heat exchanger flanges 30a, 30b back to the room to be ventilated. The circulation of recycled air L2 through the heat exchanger nozzles 30a, 30b is based on the difference in density of air layers at different temperatures, whereby the colder or heavier air tends to descend and the warmer or lighter air tends to rise up. The fresh airflow L1 discharged from the supply air section 20 does not inducibly influence the recirculated airflow L2. When discharged into the air-conditioned room, the fresh airflow L1 mixes the air in the room and thereby improves the circulation of recirculated air L2 through heat exchangers 30a, 30b.

Figure 6 is a perspective view of another embodiment of the supply air device. In this embodiment, the body structure 40 comprises a rectangular sheet metal frame 41, the upper surface of which is enclosed by a cover plate 44 and having a perforated plate 42 at its lower surface. The supply air duct 10 and the supply air section 20a, 20b extend over the transverse direction Y-Y. The heat exchangers 30a, 30b are located on either side of the supply air section 20a, 20b and extend longitudinally X-X from the supply air section 20a, 20b to the ends of the frame structure 40. The supply air section 20a, 20b consists of two separate supply air chambers 20a, 20b fed with fresh air L1 through a common supply air duct 10. Below the supply air chambers 20a, 20b are control portions 60a, 60b that direct fresh air from the supply air chambers 20a, 20b.

Figure 7 is a top view of the supply belt device of Figure 6. The figure shows the supply air duct 10, the frame structure 40 and the cover plate 44, which closes the frame structure 40 from above.

Figure 8 is a bottom view of the supply air device shown in Figure 6. The figure shows the supply air duct 10, the supply air section 20a, 20b consisting of two separate supply air chambers 20a, 20b, the heat exchangers 30a, 30b, the frame structure 40 and the opening bottom plate 42. Each supply air chamber 20a, 20b has a damper , 20b has corresponding first openings. Each damper 21a, 21b is controlled by an actuator 50a, 50b. The control dampers 21a, 21b can be adjusted independently of each other to achieve a wider control range compared to the embodiment with one supply air chamber and one control damper.

Figure 9 is a longitudinal sectional view A-A of Figure 7. The figure shows an inlet air duct 10, an inlet air portion 20a, 20b, two air supply chambers 20a, 20b, heat exchangers 30a, 30b, a frame structure 40 and associated roof plate 44 and an apertured bottom plate 42.

Figure 10 is a bottom view of the supply air device of Figure 6 and Figure 11 is a transverse sectional view B-B of Figure 7, which corresponds to the situation shown in Figure 10. Figure 11 shows only the first supply air chamber 20a, but the parasitic input air chamber 20b is identical to the first supply air chamber 20a. In this embodiment, the base plate 42 of the frame structure 40 consists of two separate apertured base plates. A first apertured bottom plate covers a portion below the first heat exchangers 30a and a second apertured bottom plate covers a portion below the second heat exchanger 30b. The base plate 62a, 62b of the guide portions 60a, 60b comprises slots 62a1, 62a2 at the ends, the remainder of the base plate 62a, 62b of the guide portion 60a, 60b being closed. The fresh air flow L1 is thus discharged from the slots 42a, 42b on the edge to the side of the room to be ventilated substantially parallel to the ceiling surface.

Fig. 12 shows a variation of the supply air device shown in Fig. 6, viewed from below, and Fig. 13 shows a transverse section B-B of Fig. 7, which corresponds to the situation shown in Fig. 12. Figure 13 shows only the first supply air chamber 20a, but the second supply air chamber 20b is identical to the first supply air chamber 20a. In this embodiment, the base plate 42 of the frame structure 40 consists of two separate apertured base plates. A first apertured bottom plate covers a portion below the first heat exchangers 30a and a second apertured bottom plate covers a portion below the second heat exchanger 30b. Below each supply air chamber 20a, 20b is a guide portion 60a, 60b with a bottom plate 62a, 62b The base plate 62a, 62b of the guide portions 60a, 60b comprises a slot 62a3, 62b3 in the middle, the remainder of the base plate 62a, 62b of the guide portion 60a, 60b being closed. The fresh air flow L1 is thus discharged from the central slit 62a3, 62b3 downwardly into the room to be ventilated substantially vertically.

Fig. 14 is a transverse sectional view C-C of Fig. 7 in a first mode of operation. The recirculated airflow L2 circulates from the sides of the heat exchanger 30b above the heat exchanger 30b and thence through the heat exchanger 30b to the room to be ventilated.

Figure 15 is a transverse sectional view C-C of Figure 7 in another mode of operation. In this mode of operation, the bead beads 31 on the sides of the heat exchanger 30b are moved to the lower position, whereby they enhance the circulation of the recirculating line L2 in the heat exchanger 30b by virtue of the chimney effect.

Fig. 16 is a transverse sectional view C-C of Fig. 7 in a third mode of operation. In this mode, the bead strips 31 on the sides of the heat exchanger 30b are moved to an up position, thereby reducing the circulation of recirculated air L2 in the heat exchanger 30b.

In the solution according to the invention, the amount of fresh air discharged from the supply air part 20, 20a, 20b of the supply air device 100 into the air-conditioned room can be controlled, for example, by the number of people in the air-conditioned room. The adjustment of the damper 21, 21a, 21b may be manual, whereby the damper 21, 21a, 21b is manually adjusted. In automatic control, the control damper 21, 21a, 21b is controlled by an actuator 50, 50a, 50b, which can be e.g. an electric motor or a so-called thermal actuator based on the thermal expansion of the substance.

The embodiment shown in Figure 1 is better suited to the situation in which the recirculated air flow is also heated in the heat exchangers 30a, 30b compared to the embodiment shown in Figure 3. The top open design of the embodiment of Figure 1 allows the heated recirculated air flow to rise upwardly into the space above the supply air device from which the heated recirculated air flow is directed to the room to be ventilated.

The embodiment shown in Fig. 1 may also be implemented with the outlet air of the supply air portion 20 on the upper surface of the supply air portion 20, wherein the damper 21 is on the upper surface of the supply air portion 20. The fresh air flow L1 is then blown up obliquely to the sides above the supply air device. This arrangement is well suited to the situation where the recirculated air flow is also heated in the heat exchangers 30a, 30b, because the fresh air flow L1 in this arrangement improves the circulation of the warm recirculated air L2

The embodiment shown in Figs. 1 may be installed inside a suspended ceiling so that the lower edge of the sheet metal frame 41 of the frame structure 40 remains at or below the ceiling height of the room to be ventilated. The supply air device according to this embodiment may also be mounted below the solid ceiling at a distance from the ceiling.

The embodiment shown in Figs. 6 can likewise be installed inside a suspended ceiling so that the lower edge of the sheet metal frame 41 of the frame structure 40 remains at or below the ceiling height of the room to be ventilated. The supply air device according to this embodiment can also be mounted below the solid ceiling, at a distance from the ceiling or directly mounted from the ceiling panel to the ceiling.

The supply air portion 20, 20a, 20b in the embodiments shown in the figures is located in the center of the supply air device. This is an advantageous arrangement, but the supply air section 20, 20a, 20b may also be positioned on either side of the supply air device longitudinally or transversely inside the damper frame 41. The supply air section 20, 20a, 20b may also be disposed adjacent the outer surface of the sheet metal frame.

In the embodiments shown in the figures, two heat exchangers 30a, 30b are used, but there can also be only one or more than two heat exchangers. The inlet air portions 20, 20a, 20b may likewise be one or more, the 3 "outside air portions 20, 20a, 20b may also be located at different locations in the supply air device.

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

Claims (10)

An supply air device (100) comprising: - a frame structure (40), - at least one heat exchanger (30a, 30b) supported on the frame structure (40), wherein the air (L2) in the room to be ventilated is recirculated by said at least one heat exchanger 30a, 30b), wherein the recirculated air stream (L2) is cooled or heated, after which the cooled or heated recirculated air stream (L2) is returned to the room to be ventilated, characterized in that the supply air device further comprises: at least one supply air section (20, 20a, 20b) supported by a frame structure (40), said at least one supply air section (20, 20a, 20b) comprising a control means (21, 21a, 21b) for adjusting said at least one supply air section (20, 20a, 20b) to be supplied to a the amount of fresh air flow (LI), wherein said at least one heat exchanger (30a, 30b) and said at least one the stomach (20, 20a, 20b) function independently of one another. Supply air device (100) according to Claim 1, characterized in that: - the frame structure (40) comprises a rectangular, closed frame (41) with an open top and a lower surface closed by an apertured bottom plate (42), - at least one heat exchanger (30a, 30b) consists of two heat exchangers (30a, 30b) extending over the longitudinal direction (XX) of the frame (41), - the supply air section (20) is located in the middle of the frame (41) between the heat exchangers (30a, 30b). The supply air device (100) according to claim 2, characterized in that: - the underside of the supply air section (20) comprises first openings, - the underside of the supply air section (20) has a adjusting plate (21) with second openings (22) ) the free surface area of the first openings in the underside and thereby the amount of fresh air flow (LI) discharged into the room to be ventilated. Supply air device (100) according to Claim 3, characterized in that the adjusting plate (21) further comprises an actuator (50) for controlling the position of the adjusting plate (21) on the lower surface of the supply air part (20). Supply air device (100) according to claim 1, characterized in that: - the frame structure (40) comprises a rectangular solid frame (41), the upper surface of which is closed by a roof plate (44) and the lower surface is closed by at least one apertured base plate (42). , - the supply air section (20, 20a, 20b) is located in the middle of the frame (41) in the transverse direction (YY) of the frame (41), - said at least one heat exchanger (30a, 30b) consists of two heat exchangers (30a, 30b) on both sides of the supply air portion (20, 20a, 20b) and extending between the longitudinal (XX) end of the frame (41) and the supply air portion. Supply air device (100) according to claim 5, characterized in that - the supply air section (20, 20a, 20b) consists of two separate supply air chambers (20a, 20b), - the lower surface of each supply air chamber (20a, 20b) comprises first openings, The lower surface (20a, 20b) has a baffle plate (21a, 21b) with second openings (22a, 22b) for adjusting the free surface area of the first openings of the lower surface of each supply air chamber (20a, 20b) and thereby the amount of fresh air (LI) . Supply air device (100) according to claim 6, characterized in that each adjusting plate (21a, 21b) is further provided with an actuator (50a, 50b) for controlling the position of each adjusting plate (21a, 21b) on the underside of the supply air chamber (20a, 20b). A method in the supply air device (100) comprising: - forming a frame structure (40), - supporting at least one heat exchanger (30a, 30b) to the frame structure (40), - gravitationally circulating air (L2) in the room to be ventilated; 30b) through which the recirculated air stream (L2) is cooled or heated, after which the cooled or heated recirculated air stream (L2) is returned to the room to be ventilated, characterized in that: - at least one supply air part (20, 20a, 20b) is supported in the frame structure (40); regulating the flow rate of fresh air flow (L1) to be supplied to the air-conditioned room from said at least one supply air portion (20, 20a, 20b) by a regulating means (21) provided to the supply air portion (20, 20a, 20b), wherein said at least one heat exchanger (30a, 30b) said at least one supply air portion (20, 20a, 20b) operating independently. Method according to Claim 8, characterized in that: - arranging first openings on the underside of the supply air section (20), - arranging an adjusting plate (21) with second openings (22) on the underside of the supply air section (20), the free surface area of the first apertures and thereby the flow rate of fresh air flow (LI) discharged into the room to be ventilated by the control plate (21). A method according to claim 9, characterized in that an actuator (50) is provided in connection with the baffle plate (21) for controlling the position of the baffle plate (21) on the underside of the supply air section (20).