EP0186268B1

EP0186268B1 - Air distribution terminals and air treatment systems

Info

Publication number: EP0186268B1
Application number: EP85307142A
Authority: EP
Inventors: James M. Giles
Original assignee: RADIALTEMP Ltd
Current assignee: RADIALTEMP Ltd
Priority date: 1984-10-11
Filing date: 1985-10-04
Publication date: 1990-06-13
Anticipated expiration: 2005-10-04
Also published as: EP0186268A2; EP0186268A3; DE3578204D1

Description

The present invention relates to air distribution terminals and air treatment systems incorporating such terminals.
Air treatment systems are known in which air is heated centrally and is distributed through ducts to points of utilisation distributed around the volume to be heated, typically in separate rooms of a building or in different parts of rooms of a building.
Commonly such air ducts are of large cross-sectional area so that adequate masses of air can be distributed through them and discharged into the space to be heated at an acceptably low velocity. It is also known to distribute the heated air through ducts of smaller cross-sectional area. It is then necessary to move the air at a higher linear velocity through these ducts in order to transfer air at a high mass rate to convey the quantity of heat involved at times of maximum demand.
In such a system, the delivery of heated air into the space to be heated can cause an unacceptable amount of turbulence and of noise in the heated space and it is known therefore to reduce these effects by causing the high velocity air to induce a secondary flow of air, air being drawn from the space to be heated and delivered back into the space mixed with the high velocity heated air, or primary air as it might be called from the heating source. An example of such a system is described in GB-A 1316887.
It is also known to produce a flow of ambient air from the space in which the air is to be treated into an air distribution terminal and back into the space by using an air blower in the terminal to produce said flow. Typically the air blower produces a constant rate of output. Treated air, or primary air, is supplied to the air distribution terminal and is mixed with the air drawn into the terminal by the blower. The mixture of treated air and ambient air is then blown out by the blower from the distribution terminal. Various methods have been proposed for controlling the flow of air from the air ducts into such distribution terminals. In US-A 3929285 of Daugherty Jr. the air duct for transport of heated air terminates in the distribution terminal in a reduced diameter portion described as a venturi restriction. A ball valve is mounted in the air duct adjacent the venturi restriction and is movable axially in the duct to approach and recede from the restriction under the control of an actuator linked to a thermostat. The ball is also spring loaded and is displacable in the axial direction to a limited extent by pressure in the duct.
Such a flow control system has a number of severe disadvantages. The range of movement of the ball serving to provide any significant alteration in the outflow of air from the duct is very small and the ball acts essentially to provide only open and closed states of the air duct rather than to provide genuine progressive alteration of the flow of air out of the duct. Moreover, as the ball approaches the venturi restriction, the progressively restricted flow of air will become turbulent and noisy due to the increasingly high velocity of the air passing over the ball and through the restriction. To attempt to cope with this Daugherty provides a noise absorbing baffle but this will not in practice prove an adequate solution to the problem.
Other systems suffering similar disadvantages have been proposed. Some use a control valve of the butterfly type, another uses a control valve having a ported cytinder at the outlet of the primary air conduit and a piston axially movable to open and close the ports.
When fully open such valves allow air to pass through at high velocity with little pressure drop. Until such control valves are almost shut, the pressure drop across them is considerably less than the pressure typically available in the primary air circuit for driving air through the valves. Therefore, little or no restriction of the flow occurs until such valves are close to closing and hence poor control is achieved.
US-A 3 669 349 is an example of many disclosures of air distribution terminals having inlets and/or outlets which are variable between closed and open positions by relative movement of overlying perforate plates so that the perforations in the one plate overly those in the other to a greater or lesser extent. In these systems however the control is too coarse for the purposes of the present applicant as the whole range from closed to open is covered by movement of one plate over a distance corresponding to the dimension of a simple perforation. Generally, in systems of this kind, the perforations or other apertures employed are too large for present purposes.
In GB-A 2 069 127 (Simmons) a system for treating environmental air is described in which treated air is conveyed between small diameter ducts to air distribution terminals where it is released into a buffer zone of enlarged diameter and passes from the buffer zone through a flow restricting perforated plate and is then mixed with air drawn into the distribution terminal by an air blower which expells the mixed air from the terminal. Such a system is quiet and efficient in use. In setting up a system of this kind with a number of terminals the effective open cross-sectional area of the perforate plate for each terminal needs to be selected with care in order that the system may be properly balanced. Once the system is balanced, it will operate efficiently but it is not easy to modify the system by adding further terminals because that is likely to upset the balance of the system and necessitate a recalculation of the effective open cross-sectional area required in each of the terminals.
It might be thought that a terminal design such as Daugherty teaches might solve this problem in that Daugherty professes to provide a continuous control of the effective cross-sectional area of the exit from the duct for treated air into the distribution terminal. However, in practice, as pointed out above, Daugherty's control mechanism will not provide a satisfactory variable control over the flow of treated air into the terminal as the ball and restriction mechanism taught by Daugherty acts to provide too sharp a cut off of air flow in response to linear movement of the ball.
However, Daugherty neither suggests or describes the use of the ball and venturi restriction appearing in the terminals he describes as a means of balancing an air treatment system.
GB-A 1 226 089 discloses a control valve for regulating the flow of air from a high pressure side receiving supplies of hot and cold air to a low pressure side of the valve. A piston is displaced by pressure in the air supply to partially obscure outlet holes in a cylinder in which the piston is mounted, so as to provide a constant volume output despite variations in inlet pressure. Such a valve would not be suitable for controlling air flow in an air distribution terminal to overcome the problems discussed above. It lacks any means for controlling the output of treated air to provide a variable output.
The systems described above are applicable not only to the distribution of heated air but also primary air treated in other ways, e.g. by cooling.
The present invention provides an air distribution terminal comprising a housing having at least one inlet for drawing in ambient air, an inlet for treated air, at least one terminal outlet for a mixture of said treated air and ambient air, and a control valve regulating the flow through said inlet for treated air, which control valve comprises means defining a flow path for air from the inlet for treated air to the interior of the housing, and a variable flow restrictor in said flow path characterised in that the flow restrictor comprises a wall member dividing an upstream part of said flow path from a downstream part of said flow path, and having flow passages therethrough, means acting as a shutter for at least substantially closing a proportion of the flow passages of said wall member against air flow therethrough, mechanical means for producing relative movement between said wall member and said closing means to vary the area of said wall member exposed for air flow therethrough, the cross-sectional area of each of the flow passages through said wall member being not greater than about 0.7 cm2.
By virtue of the structure of the valve, adjustment of the fluid flow is achieved by progressive unmasking of increasing numbers of flow passages as the adjustment is carried out rather than by simultaneous variation of the effective size of all the flow passages.
The control valve will be likely to experience inlet pressures from 62 Pa (0.25 inches water gauge) upwards, e.g. 1495 Pa (6 inches water gauge).
Generally, the larger the apertures, perforations or foraminae in the wall member, the higher the minimum pressure at which the valve will exhibit satisfactory control over the air flow.
We have found that for dealing with high pressure systems in which the static pressure in the primary air distribution circuit is above 1495 Pa, circular perforations in the wall member of a diameter of 0.95 cm (3/8 inches) are as large as will provide the desired result. Preferably, therefore, the apertures are in the range of 9.5 mm to 1.6 mm diameter. More preferably therefore the diameter of such circular perforations in the wall member is in the range of 0.44 to 0.51 cm.
If non-circular, the apertures preferably have a largest dimension in this range or an area equivalent to a circle with a diameter in that range.
The perforations in the wall member need not be circular. More generally therefore the flow passages through the wall member each have a cross sectional area not exceeding 0.7 sq.cm., e.g. from 0.02 to 0.7 sq.cm., more preferably not exceeding 0.2 sq.cm., e.g. from 0.15 to 0.2 sq.cm. For use in systems where the primary air static pressure is relatively low, flow passages at the lower ends of these ranges may be desired.
The form of the wall member and the manner in which it interacts with the means for closing a portion of the wall member against fluid flow may be of various kinds.
In one arrangement, the valve is as described above, and the wall member is a foraminous or perforate tube telescopically movable to extend from the downstream end of the said flow path defining means by a greater or lesser extent, the bore of said tube having a closure or flow restriction therein e.g. at the end of the tube. Preferably, the tube is uniformally foraminous or perforate along its length, so that the effective cross sectional area open for air flow from the valve into the interior of the housing is directly proportional to the length of the foraminous or perforate tube extending.
Preferably the valve further comprises actuator means adapted to move the tube telescopically in the outlet by a degree dependent on a signal provided to the actuator means. The means for generating a signal to cause the actuator to move the tube telescopically which is preferably provided may for instance be a manual control such as a manually operable switch or may be some means for monitoring some ambient condition and moving the tube in response to variations in that condition, for instance a thermostat.
Another alternative arrangement, the valve may be generally as described above and the wall member may have a first portion having said flow passages and a second portion without said flow passages, and the closure may be a shutter having one or more apertures therein and the wall member and the shutter may be mounted to be adjacent and rotatable with respect to one another so as to vary the amount of said first and second portions of the wall member aligned with the aperture in the shutter.
Preferably, the wall member and shutter are interfitting generally cylindrical members. Alternatively, they might for instance be overlying circular members.
Preferably, the wall member is disposed over the shutter. However, the shutter may lie over the wall member.
Preferably, the valve further comprises actuator means adapted to rotate the wall member and shutter with respect to one another. Preferably, the valve further comprises means for generating a signal to cause said actuator to rotate said wall member and actuator with respect to one another. In this type of embodiment also, the signal generating means may be a thermostat or a manually operable switch or other control.
Preferably the terminal includes an air blower for expelling air from the housing through the outlet or outlets.
Preferably the housing has a cross-sectional area substantially in excess of the cross-sectional area of the flow path of the valve.
The invention further provides an air treatment system comprising a plurality of terminals as described above, air treatment apparatus including means for drawing in and treating air, and means for delivering treated air from said air treatment apparatus to the flow path of the flow control valve of each said terminal. The means for treating air may suitably be means for heating or cooling or humidifying the air or a mixture of two or more of these functions.
Preferably the means for delivering treated air is a system of conduits of a cross-sectional area substantially less than the cross-sectional area of the housing of each terminal, preferably similar to the cross-sectional area of said flow path of the valve.
Preferably the system of conduits include flexible conduit portions connecting to the terminals.
The invention will be illustrated by the following description of a preferred embodiment with reference to the accompanying drawings in which:

Fig. 1 is a schematic view of an air treatment system according to the invention including an air flow control valve incorporated in an air distribution terminal;
Fig. 2 is an expanded view of the air flow control valve of the air distribution terminal of Fig. 1;
Fig. 3 is a schematic elevation of an air distribution terminal incorporating a second embodiment of a valve for use in the invention;
Fig. 4 is a exploded view of the components of the valve of Fig. 3;
Fig. 5 is a plan view of a distribution terminal incorporating a third embodiment of a valve for use in the invention; and
Fig. 6 is a plan view of the valve of Figure 5.

As shown in Fig. 1; an air treatment system comprises an air blower such as a centrifugal fan 2 for drawing air to be treated from outside a wall 1 demarcating the space within which the air is to be treated. Wall 1 is therefore typically an exterior wall of a building. Air is directed by the blower 2 through an air treatment means 3 such as an air heater or an air cooler. From the air treatment means 3 the air is directed through a duct 4 to a primary air duct 14 serving air distribution terminals. Each terminal is connected to the respective primary air duct 4 by a flexible duct 15. Each terminal comprises a housing 12 defining an air inlet 8 for drawing air from a room or other space in which the air is to be treated, an air blower 11 in the form of an axial fan in this instance within the housing 12 for drawing air into the inlet 8 and an outlet duct 13 having an outlet into the space in which the air is to be treated.
At the end of the housing remote from the outlet is an inlet for treated air connected to the flexible duct 15. The inlet for treated air is provided at one end of a conduit 16 having an opposite open outlet end in which is received a perforate tube 5 closed at its downstream end by an end plate 18. The perforate tube 5 is provided uniformly along its length with perforations 19 and therefore provides a wall member through which air passing through the conduit 16 may escape into the housing 12 upstream of the inlet 8.
An annular sleeve 20, for instance a nylon sleeve, seals the tube 5 to the interior of the conduit 16 in which it slides. A rod 21 connected to end plate 18 connected to a linear actuator 6. Alternatively, rod 21 is articulated to an actuator arm 7 which is in turn connected at one end to a rotary actuator 6a.
Downstream of the inlet 8 but upstream of the fan 11 is a mixing zone 10 demarcated by a perforate plate 9 at its upstream end. Plate 9 is particularly of use in terminals having a cross section which is very wide compared to its height and serves to ensure good mixing of air entering the mixing zone 10.
In use, the fan 11 draws air from the space or room in which the air is to be treated through inlet 8 and into the housing 12. At the same time, treated, e.g. heated, air passes at a relatively high velocity through the ducts 4, 14 and 15 and is released through the perforate tube 5 at a rate depending upon the amount of the tube 5 extending from the conduit 16. This treated air mixes with the air drawn in through inlet 8 in the mixing zone 10 and is expelled back into the space through outlet duct 13.
The extent to which the foraminous or perforate tube 5 extends from the outlet end of conduit 16 of the treated air duct depends on the setting of the actuator 6. This may be linked to one of a variety of means for controlling the setting of the position of the tube 5.
The actuator 6 may be linked to a manually operated control used to fix the position of the tube 5 so that the whole system, incorporating a number of terminal units 12, is in balance and provides the correct degree of heating or cooling from each terminal. Alternatively or additionally, the actuator 6 may be linked to a thermostat or other means for monitoring some condition of the air in the space to be treated to provide some degree of movement of the tube 5 to increase or decrease the amount of treated air allowed into the housing 12 in response to conditions in the space or room. The flow of air through the housing 12 as a whole will be substantially constant but depending on the position of the foraminous tube 5, more or less of this air will be constituted by air drawn from the treated air ducts 4, 14 and 15.
Whereas the position of the foraminous tube 5 may be completely under the control of a thermostat acting through actuator 6 or may be entirely dictated by a manual control acting through actuator 6, it is possible to mix these functions so that a manual control dictates a base position for the tube 5 which is modified by a thermostat or such that the position of the tube 5 is controlled by a thermostat within a range dictated by a manual control.
Advantages of the system described above are that the pressure which is inherent in the high velocity duct 14 is absorbed by the perforated tube. Likewise the velocity of the air escaping from the foraminous tube is greatly reduced. The air leaving the perforated tube has substantially no excess pressure or velocity. Accordingly, air noise and air turbulence is minimal. It will be appreciated that whatever the position of the tube 5, air escaping from the interior to the exterior passes through each perforation 19 with substantially the same pressure drop and accordingly substantially the same velocity. This is in contrast to the situation in the controller taught in the specification of Daugherty referred to above. There is accordingly no tendency to increased noise as the tube 5 is moved further into the conduit 16. The perforated tube 5 allows control over the air flow from the duct 14 from full air flow to zero air flow and the rate of flow of air from the duct 14 into the housing 12 is linearly proportional to the displacement of the tube 5 from the end of the conduit 16. The maximum rate of flow from the tube 5 into the housing 12 is easily selected by an appropriate choice of the specific free area provided by the perforations in the tube 5. All this provides a very accurate control over the flow of the high velocity air into the housing 12.
Setting up a high velocity air distribution system comprising a series of many outlets has in the past provided extremely difficult and adding subsequent outlets can prove to be impossible in some systems because of the imbalances created throughout the system by any modifications. By resetting the perforated tube described above to increase or reduce the free area, the starting point or base position of the tube or tubes can take account of the revised system pressures. If pressure changes to be made are drastic, then a perforated plate having a different total aperture are can be inserted into each terminal and the position of the tube may be varied as a fine control. By this means, the system according to the invention is capable of ready modification.
Fig. 3 shows a further embodiment of a distribution terminal according to the invention incorporating a further type of valve. As shown in Fig. 3, a distribution terminal 30 has an inlet for primary air 31 leading through a control valve 32 to the interior of the distribution terminal. Inlets 33 for air drawn from the room containing the terminal are provided on a front face of the terminal on either side of an outlet for air drawn into the terminal from the room mixed with air from the primary air inlet 31. This secondary air outlet may be formed by a grill 34 behind which is positioned a centrifugal blower 35 of a crossflow or tangential type driven by a motor 36. As best seen in Figure 4, the valve comprises an outer cylindrical sheet metal wall member 37 having a hemi-cylindrical surface portion 38 provided with a multitude of small circular perforations. Portion 38 is disposed between two ciruclar end bands 39 which are not perforated. Within the cylindrical wall member 37 is received a generally cylindrical shutter 40 having a cut away portion forming an aperture 41 generally corresponding in size to the portion 38 containing the perforations in the cylindrical wall members 37. Gaskets (not shown) form a seal between the wall member and the cylindrical member at each end. Radially directed arms 42 meet in the centre of each end face of the cylindrical member 40 at a bushing 43 in which is received a drive shaft 44 mounted to an end cap 45 which on its outer surface bears an electric motor 46 connected to the rod 44 for rotation thereof. Rotation of the rod 44 causes rotation of the cylindrical shutter 40 within the cylinder 37 causing the aperture 41 to coincide to a greater or lesser extent with the perforate portion 38 of the member 37. Electric motor 46 is connected to a thermostatic control which adjusts the position of the cylindrical shutter 40 in response to room temperature. In a modification of what is shown in Figs. 3 and 4, motor 46 may be replaced by a manually operable control to allow presetting of the position of the shutter 40 according to the expected heat demands for the particular terminal.
As in the case of the embodiment described with reference to Figs. 1 and 2, the static pressure in the primary air distribution ducts leading to the inlet 31 to the terminal produces a volume rate of flow through the apertures in the member 37 proportional to the exposed area of the portion 38 containing the perforations. In normal use, the pressure of the high velocity primary air is absorbed in passing the perforate barrier. The unit therefore operates in a quiet manner with accurate control of the flow of treated air through the primary air circuit.
The distribution terminal shown in Figs. 3 and 4 is of the kind likely to be suitable for residental systems. A distribution terminal more suited to larger installations, for instance, commercial installations, is shown in Figs. 5 and 6. As shown in Fig. 5, a distribution terminal 50 comprising an inlet 51 for primary treated air to a control valve 52. Air from the room enters the distribution terminal from below through an inlet 53 and mixes with primary air passing out of the control valve 52 in a mixing chamber 54 and is drawn from the mixing chamber 54 by a centrifugal blower 55 in an inline configuration and directed out of the terminal through exits 56. The control valve 52 comprises a generally T-shaped housing, the inlet 51 constituting the upright of the T. The cross member of the T is formed by a cylindrical closed- ended tubular member 57 having adjacent each closed end a cut away window covered by a perforated plate 58. Each window extends around approximately half of the circumference of the tube 57 and extends inwardly from adjacent the respective end of the tube 57 to a line continuing the base of the T formed by the inlet 51.
Within the tubular member 57 a rotatable shutter is provided mounted for rotation by a valve motor 59 provided on one end of the tube 57. The rotatable shutter 60 is divided into two parts, one received adjacent each of the perforated plates 58. Each part of the shutter 60 is linked by a central drive shaft (not shown) connected to the motor 59. Each of the two parts of the shutter 60 is formed as a cylindrical tube having a window therein corresponding in size and shape to the perforated plate 58 so that the shutter 60 is rotatable so that the perforated plate 58 is entirely closed by an underlying, non-windowed portion of the shutter 60 and is also rotatable, via intermediate positions, to a position in which the perforated plate 58 is fully open for air flow therethrough and is coincident with the aperture formed in the respective part of the shutter 60.
It can be seen that the terminal designs described with references to Figs. 3 to 6 share the advantages described above in connection with Figs. 1 and 2. They are however more compact and enable the use of a rotary rather than a linear form of actuator.

Claims

1. An air distribution terminal comprising a housing having at least one inlet (8) for drawing in ambient air, an inlet for treated air, at least one terminal outlet (13) for a mixture of said treated air and ambient air, and a control valve regulating the flow through said inlet for treated air, which control valve comprises means (16) defining a flow path for air from the inlet for treated air to the interior of the housing, and a variable flow restrictor in said flow path characterised in that the flow restrictor comprises a wall member (5) dividing an upstream part of said flow path from a downstream part of said flow path, and having flow passages (19) therethrough, means (20) acting as a shutter for at least substantially closing a proportion of the flow passages of said wall member against air flow therethrough, mechanical means (21) for producing relative movement between said wall member and said closing means to vary the area of said wall member exposed for air flow therethrough, the cross-sectional area of each of the flow passages through said wall member being not greater than about 0.7 cm2_.

2. A terminal as claimed in Claim 1, wherein the said flow passages each have a cross-sectional area not exceeding 0.2 cm2.

3. A terminal as claimed in Claim 1 or Claim 2, wherein said flow path defining means (10) is tubular and said wall member is a foraminous or perforate tube (5) telescopically movable to extend from the downstream end of said flow path defining means by a greater or lesser extent, the bore of said tube having a closure or substantial flow restriction therein.

4. A terminal as claimed in Claim 3, wherein said tube (5) is uniformly foraminous or perforate along its length.

5. A terminal as claimed in Claim 3 or Claim 4, further comprising actuator means (6) adapted to move said tube telescopically with respect to the downstream end of the flow path defining means by a degree dependent on a signal provided to said actuator means.

6. A terminal as claimed in Claim 5, further comprising means (6a) for generating a signal to cause said actuator (6) to move said tube telescopically with respect to the downstream end of said flow path defining means.

7. A terminal as claimed in Claim 1 or Claim 2, wherein the wall member has a first portion (38) having said flow passages and a second portion without said flow passages, the closure member is a shutter (41) having an aperture therein, and the wall member and the shutter are mounted to be adjacent and rotatable with respect to one another so as to vary the amount of said first and second portions of the wall member aligned with the aperture in the shutter.

8: A terminal as claimed in Claim 7, wherein said wall member and shutter are interfitting generally cylindrical members.

9. A terminal as claimed in Claim 7 or Claim 8,. further comprising actuator means adapted to rotate the wall member and shutter with respect to one another and means for generating a signal to cause said actuator to rotate said wall member and actuator with respect to one another.

10. A terminal as claimed in any preceding claim, wherein said flow passages each have a cross-sectional area in the range 0.02 to 0.7 cm².

11. A terminal as claimed in Claim 10, wherein said flow passages each have a cross-sectional area in the range 0.15 to 0.2 cm2.

12. An air treatment system comprising a plurality of terminals as claimed in any preceding claim, an air treatment apparatus including means (2, 3) for drawing in and treating air, and means (4) for delivering treated air from said air treatment apparatus to the flow path of the control valve of each said terminal.