Fan-heat exchanger (options)

 

The invention is intended for ventilation and air-conditioning, in which the fluids are not mixed with each other. In the first embodiment, the device includes a housing and mounted therein bilateral impeller in the form of a separating disc, one side of which is made of centrifugal fan blades and on the other centripetal, which provides a counter-current heat exchange occurring through the blades and disk. The design allows for the manufacture of blades of a given curvature, in particular, that provides constant width interscapular channel, and increase as the number of blades, and the density of the lattice of the impeller, which considerably increases the efficiency of heat transfer. According to the second variant the impeller is made in the form of a separating disc, one side of which is made of centrifugal fan blades and vanes centripetal turbine, which further allows you to organize two-stage scheme of heat transfer. Both stages are accurately aligned and face each other front turbine disks, and the discharge nozzles centrifugal fans one step executed connected with the current of one of the fluids in another turbine stage. In the opposite direction to migrate to another carrier. Dimensions and weight of the device can be reduced by performing the front drive turbines both steps in a single disk. 2 C. and 21 C.p. f-crystals, 8 ill.

The invention relates to heat exchange apparatus in which fluids are not mixed with each other, and can be used, for example, in ventilation systems and air conditioning for the heat exchange between the intake and exhaust air flows.

Famous fan-heat exchanger [1], comprising a housing and mounted in the housing on one shaft, two centrifugal fan, oriented in opposite directions to each other. In the housing formed by the two channels for the coolant (air flow) with different temperatures separated by a heat exchange element made in the form of corrugated radial partitions, installed at the edge of the impeller vanes and having a disk that separates the fans. During the rotation of the fans fluids through the respective suction nozzles come in the interscapular space fans and forth, washing both sides of the corrugated radial wall Teploobmennik through the corrugated septum during flushing the fluids of its faces. The disadvantages of this design should include large radial dimensions.

Also known fan-heat exchanger [2], comprising a housing and mounted in the housing on one shaft, two centrifugal fan, oriented in opposite directions to each other. In the housing formed by two channels for fluids with different temperatures separated by a separating wall, which separates both the fan. Heat exchange element made in the form of radial ribs that are installed on both surfaces of the walls behind the rim of the impeller fan. During the rotation of the fans fluids through the respective suction nozzles come in the interscapular space fans and forth, washing both sides of the radial ribs of the heat transfer element, removed from the casing through the respective injection nozzles. The heat exchange is carried out through the radial ribs and the wall. The disadvantages of this design should also include large radial dimensions.

Closest to the claimed invention is a fan-heat exchanger [3] , comprising a housing and installed in the casing impeller bilateral centrifugal fan, sypialnia blades. The housing has a partition wall adjacent to the outer rim of the impeller and dividing the housing into two isolated cavity (channel) for fluids with different temperatures. Thanks to a specified partition in the casing formed by two insulated centrifugal fan with single bilateral impeller. During the rotation of the impeller of the coolant through the respective suction nozzles in the housing are received in the interscapular space fans and then excreted from the body through the respective injection nozzles. Heat transfer in such a device is carried out through the radial face corrugated impeller.

In the famous fan-heat exchanger impeller, which simultaneously heat exchange surface formed radially corrugated surface. The performance of the impeller leads to low efficiency of the centrifugal fan and a heat exchanger.

The first is due to the fact that the function of the blades performs radially corrugated surface. In this case, the air flow at the outlet of the impeller has a gauge pressure exceeding the pressure required to overcome the PIO this feature, typical centrifugal fan with radial blades, the necessary blades of a different nature, namely backward curved blades. It is obvious that the manufacture of corrugated disc with curved blades is a complex technological problem. The curvature of these bumps will be determined acceptable by plastic deformation of the material from which is made the impeller. In addition, these material properties are in conflict with the desired rigidity of the impeller, which during operation are considerable centrifugal force. This contradiction leads to the fact that the manufacture corrugated disk with a large curvature of the blades is not possible. Therefore, it is not possible for the structure to eliminate excessive pressure and reduce input power.

The low efficiency of heat exchange of the known device is explained next. On the efficiency of heat transfer to some extent affects both the surface area of heat transfer and the rate of flow of this surface. In the case of radial vanes, first, the heat exchange area will be minimal as the radial vanes have a minimum length, and secondly, the rate of flow will be umeoka, increasing the sectional area of the interscapular space to the periphery. Another factor contributing to the low efficiency of heat transfer is implemented in the device uniflow circuit, when both of the heat carrier are unidirectional movement: in the known device, both of the fluid moving from the center to the periphery of the impeller. At the same time, it is known that the greater efficiency of heat exchange can be achieved if you use a counter-current scheme, when the fluids have a counter direction [4]. In relation to the known device, this means that one side of the impeller should work as centripetal. However, with radial vanes to achieve this impossible, and the manufacture of corrugated disc with curved blades, as already noted, is a fairly complex technological task, and given the fact that the shape of the blades on both sides of the impeller will vary, to make the impeller in the form of a corrugated disk fails.

Technical problem on which the invention is directed, is to increase the efficiency of heat transfer and lower power consumption. Claimed two options to solve the problem.

Replacement corrugated disk impeller solid disk on both sides which made blades, allows to make the latter any given shape, since such construction is not already associated with the technology of manufacturing corrugated surface. In particular, on one side of the impeller are centripetal blades, which makes it work as a centripetal fan the blades, you can change the area normal to the blades section interscapular space, achieving a constant speed of flow of the air stream surface of the blades. The specified execution blades in contrast to the known allows you to significantly increase as the number of blades, and the density of the lattice of the impeller, i.e. the ratio of the length of the scapula to the distance between the blades at the average radius, which significantly increases the efficiency of heat transfer. Despite the fact that in the inventive fan heat exchange between two fluids is advanced through the introduction of the separating disk, flow diagram of the heat transfer and the possibility of modifying the blades of the impeller, due to a new construction of the latter, not only compensate for the lower efficiency of heat transfer associated with additionally introduced a dividing disk, but increase in General this parameter.

To reduce the excess pressure at the outlet of the centrifugal fan and the inlet radial fan blades should be performed recurved.

To increase the area of heat exchange in the inventive device, the blades of the fan, it is advisable to make with fromhis area of heat exchange between the fan blades on the periphery of the separating disc can be made of the intermediate blades.

Additionally, the blades of the fans can be performed with a constant width interscapular channel that provides a uniform speed of movement of the coolant in the interscapular channel and, consequently, increases the efficiency of heat exchange.

Additionally, impeller centrifugal fan can be connected with the blades solid front disc and dividing the disk axial hole around which made outlet centrifugal fan which is connected with the interscapular space centripetal impeller of the fan. These outlet centripetal fan is placed inside the suction of the centrifugal fan. This arrangement enables the passage of fluids from one to the opposite side of the device that simplifies installation, e.g. in ventilation and air conditioning, as corresponds to the direction of intake (or exhaust) air flow.

Additionally, the impeller of the centrifugal fan may contain bonded with the blades of the cutting disk having an axial hole for passage of the intake talonite the creation, thereby reducing ventilation losses and increasing the efficiency of heat exchange.

In addition, to reduce losses at the entrance around the axial bore of the front disk of the impeller of the centrifugal fan can be executed inlet pipe which is connected with the interscapular space of the impeller of the centrifugal fan, in fact the inlet pipe is placed in the suction pipe of a centrifugal fan, with a minimum gap. In this case, the centripetal impeller of the fan can be connected with the blades solid front disc and dividing the disk axial hole around which made outlet centrifugal fan which is connected with the interscapular space centripetal impeller of the fan, these outlet centripetal fan is placed inside the input pipe of the centrifugal fan. As was shown above, this arrangement enables the passage of fluids from one to the opposite side of the device.

The essence of the invention according to the second variant is that in a well-known fan-those who cerned performed centrifugal fan blades, the housing is divided into two isolated cavities, which together with the impeller to form two separate sections, one of which is a centrifugal fan according to the invention the impeller is made in the form of the separating disk, and the said centrifugal fan blades on one side of the separating disk, and on its other side is made of the turbine blades, which together form the impeller, one side of which is impeller mentioned centrifugal fan, and the other centripetal turbine.

As in the first embodiment, replacement of the corrugated disk impeller on a solid drive on both sides which made blades, allows to make the latter any given shape, since such construction is not already associated with the technology of manufacturing corrugated surface. On one side of the impeller are of the centrifugal blades, which makes it work as a centrifugal fan, and on the other vanes centripetal turbine. In this case, provides the most effective scheme of counterflow heat exchange. As in the first embodiment, by changing the curvature of the blades, Moi flow air flow the surface of the blades, as well as significantly increase as the number of blades, and the density of the lattice of the impeller".

In addition, on one side of the impeller blades allows the use of the inventive device in systems with external blower, in addition it is possible to reduce power consumption due to the fact that flowing under pressure through the inlet of the turbine coolant begins to rotate the impeller. At a certain pressure that may be enough to ensure the rotation of the impeller without an additional drive.

To improve the performance of the device in the input pipe of the turbine can be installed supercharger. In one of the private execution of the inlet of the turbine has the form of circular holes, aligned to the impeller and the compressor is made in the form of an axial fan, the blades of which overlap mentioned circular hole in the input pipe of the turbine. In another case, the inlet of the turbine is made in the form of holes in its peripheral part, and the supercharger is made in the form of a centrifugal fan installed in this hole.

As in the first embodiment, reduced Auda recurved.

As in the first embodiment, to increase the area of heat transfer centrifugal fan blades and/or centripetal turbines are made in relation to their length to interscapular the distance at an average radius of not less than 10.

As in the first embodiment, to increase the area of heat exchange between the blades of the centrifugal fan and/or vanes on the periphery of the separating disc are intermediate blades.

As in the first embodiment, the centrifugal fan blades and/or vanes of the turbine can be performed with a constant width interscapular channel that provides a uniform speed of movement of the coolant in the interscapular channel and, consequently, increases the efficiency of heat exchange.

As in the first embodiment, it is possible to layout, ensuring the passage of fluids from one to the opposite side of the device. For this turbine wheel is connected with the blades solid front disc and dividing the disk has an axial hole, around which made the outlet of the turbine which is connected with the interscapular space of the impeller of the turbine, these outlet Turba reduce ventilation losses and increase the efficiency of heat exchange of the impeller of the centrifugal fan may contain bonded with front disc blades, having an axial hole for passage of fluid intake in the interscapular space of the centrifugal fan.

As in the first embodiment, to reduce losses at the entrance, around the axial bore of the front disk of the impeller of the centrifugal fan can be executed inlet pipe which is connected with the interscapular space of the impeller of the centrifugal fan, in fact the inlet pipe is placed in the suction pipe of a centrifugal fan, with a minimum gap. In this case, the turbine wheel may be connected with the blades solid front disc and dividing the disk axial hole around which made the outlet of the turbine which is connected with the interscapular space of the impeller of the turbine, while the mentioned outlet of the turbine is placed inside the input pipe of the centrifugal fan.

The presence of a centripetal turbine allows in the latter case, the composition of the suction and discharge nozzles of the centrifugal fan and the inlet and outlet fittings of the turbine to organize a two-stage scheme of heat transfer. In this case, the described device averescu each other front turbine disks, and the discharge nozzles centrifugal fans one step performed communicating with the inlet pipe turbines stairs. In this case the suction nozzle of the first stage and the outlet of the second stage are respectively the input and output for a single carrier, and the suction nozzle of the second stage and the outlet of the first stage are respectively the input and output for another carrier. If the specified connection of two identical devices of the centrifugal fan of one of them (one step) increases the flow of one of the fluids into the turbine of the other device. In the opposite direction to migrate to another carrier. The heat exchange between the fluids is as stated above - backflow.

The last special case of execution of the invention according to the second variant, on the one hand, can significantly increase the heat transfer, because the fluids are two heat exchange stages, and on the other hand, allows you to optimize the dimensions of the two-stage device, as in this case, the impellers can be mounted on the same shaft, and to rotate the turbines do not need an additional nagn both stages as a whole, that is, in the form of a single disk.

The essence of the invention is illustrated graphics, which depict: Fig. 1 - fan-heat exchanger according to the first embodiment with one-sided location of suction and discharge nozzles of both centrifugal and centripetal fan; Fig. 2 - fan-heat exchanger according to the first embodiment in the opposite location of suction and discharge nozzles of both centrifugal and centripetal fan; Fig. 3 is an example implementation of the blades of the impeller with a constant width interscapular channel; Fig. 4 illustrates the correlations for the calculation of the profile of the blades with a constant width interscapular channel; Fig. 5 - fan-heat exchanger according to the second variant, with axial fan as a blower in the input pipe of the turbine; Fig.6 - fan-heat exchanger according to the second variant with a centrifugal fan as a blower in the input pipe of the turbine; Fig. 7 - two-stage fan-heat exchanger according to the second variant with twin impellers; Fig. 8 is a two - stage fan-heat exchanger according to the second variant with a common front drive turbines for both stages.

Sawlani two cavities, forming section 3 of the centrifugal fan and section 4 centripetal fan. The housing 1 has 5 suction and discharge 6 nozzles centrifugal fan, and the input 7 and output 8 nozzles centripetal fan for the passage of fluids of different temperatures, the direction which is shown by arrows. In the housing 1 on a shaft 9 mounted impeller consisting of a separating disc 10 with the normally fixed on both sides of the blades 11 of the centrifugal fan and the blades 12 centripetal fan made backward-curved (relative to the direction of rotation). In the peripheral part of the blade 12 centripetal fan deployed across a direction of rotation and form a discharge blades 13, which provides the suction of fluid through the inlet 7 centripetal fan. Both centrifugal and centripetal fans to increase the area of heat transfer may further have an intermediate vanes are mounted in the periphery of the separating disc 10 between the blades 11 and 12, respectively. In Fig.1 as an example of the intermediate blade 14 for Centralny element 15, made for example of rubber or felt, thanks to which section 3 of the centrifugal fan and section 4 centripetal fan is isolated from each other.

In Fig. 1 shows an example of performing fan-heat exchanger with single-sided location of the nozzles 5 and 6 of the centrifugal fan and nozzles 7 and 8 centripetal fan, and Fig.2 is an example implementation of the fan-heat exchanger with the location of these nozzles on opposite sides of the device. In the latter case, the discharge pipe 6 of the centrifugal fan is expanded in the axial direction opposite from the suction pipe 5 side. The device includes (see Fig.2) is bonded with the blades 11 of the centrifugal fan front disc 16 having a hole 17 for the passage of fluid intake in the interscapular space of the centrifugal fan. Around the opening 17 of the front disk 16 is made of inlet pipe 18 which is connected with the interscapular space of the centrifugal fan and placed in the suction pipe 5 with a minimum clearance. To the blades 12 centripetal fan is attached to a solid front disc 19 and the separator disc 10 has an axial oilpatch space of the fan, and the pipe 21 is placed inside the inlet pipe 18 of the centrifugal fan. Due to these design features of the device shown in Fig.2, the output streams of fluids spaced on opposite sides of the fan-heat exchanger relative to the respective input streams.

Example execution of the blades 11 of the centrifugal fan with a constant width interscapular channel shown in Fig.3. In Fig.4 shows two adjacent blade (arc AB and arc CD) and the corresponding geometric constructions to calculate the specified profile blades. For an arbitrary point E of the arc AB, lying at a distance r from the center Of the impeller, and the corresponding point F of the arc CD, the distance between which t(r) is the width of the interscapular channel is determined by the G point of the arc CD, also lying at a distance r from the center Of the impeller. The distance(r) between points E and G for large number of blades Z is approximately equal to the length of the arc EG, or a(r)2r/Z. Under these same conditions, the value of t(r) can be defined as t(r)a(r)sin(r). Using numerical methods, it is possible for t(r)=T, where T=IG.3 and 4 presents an example with the number of blades Z=22 and the ratio of the minimum distances r0blades from the center (point a) and the maximum rto(point b): r0= 0,4 rto. In this case defined values(r) that lie within:(r0)=34,22oand(rto)=13,0o. One way to perform the blades of the specified profile can be milling disk, the original thickness of which is determined by the required depth of interscapular channel. In this case, the diameter cutter T, and software control milling machine uses the calculated values of(r).

The inventive device in the first embodiment (see Fig.1) works as follows. During the rotation of the shaft 9 with a fixed duplex impeller air flow (heat transfer) having different temperatures, with both sides coming through the pipes 5 and 7 and into the space between the blades 11 and 12, respectively. In centrifugal fan air flow flows in the interscapular space to the periphery of the impeller comes in lithopane cavity centrifugal partition 3 and then through the discharge pipe 6 is discharged from the housing 1. In the centripetal fan another through the outlet 8. As air flow through the impeller between them is the process of counter-current heat exchange through the blades 11, 12 and dividing the disk 10. In the construction shown in Fig.1, the heat exchange process involves intermediate blade 14.

In the device shown in Fig.2, the heat exchange process occurs in the same way. This device differs from the device shown in Fig.1, only the passage of the air flow after the impeller. The air flow after the centrifugal fan out through the discharge pipe 6, is expanded in the axial direction in the opposite direction relative to the suction pipe 5, and the air stream after centripetal fan out through the opening 20 separating disc 10, enters the outlet 21 of the centripetal fan, oriented in the axial direction in the opposite direction relative to the inlet pipe 7 of the fan.

The inventive single-stage fan-heat exchanger according to the second variant (Fig. 5) consists of a casing 1 divided by a partition 2 into two cavity forming section 3 of the centrifugal fan and section 22 of the turbine. Case 1 is CI turbine for the passage of fluids of different temperatures, direction which is shown by arrows. The inlet 23 of the turbine is made in the form of an annular opening in the case 1. Also in the housing 1 is installed impeller consisting of a separating disc 10 with the normally fixed on both sides of the blades 11 of the centrifugal fan and the blades 25 of the turbine, made backward-curved (relative to the direction of rotation). Its Central part of the partition wall 2 adjacent to the outer edge of the disk 10 through the sealing element 15, made for example of rubber or felt, thanks to which section 3 of the centrifugal fan and section 22 of the turbine is isolated from each other. Also the device has bonded with the blades 11 of the centrifugal fan front disc 16 having a hole 17 for the passage of fluid intake in the interscapular space of the centrifugal fan. Around the opening 17 of the front disk 16 is made of inlet pipe 18 which is connected with the interscapular space of the centrifugal fan and placed in the suction pipe 5 with a minimum clearance. To the blades 25 of the turbine is attached to a solid front disc 26, and the separator disc 10 has an axial hole 20, around which executed the above o the underwater pipe 18 of the centrifugal fan. In this case the impeller is installed in the housing 1 on the shaft 9 through the front disk 26 of the turbine.

The device also has a supercharger, made in the form of an axial fan 27, the blades 28 which is installed opposite the annular orifice inlet pipe 23 of the turbine. Axial fan 27 may be mounted on the shaft 9, as shown in Fig.5, or may have its own shaft rotation is not associated with the shaft 9 and driven in rotation by an independent actuator. In the latter case, the fan motor 27 can be driven the entire device, since the turbine will provide rotation of the impeller and, accordingly, the centrifugal section 3.

Another example implementation of the invention according to the second variant shown in Fig. 6. Unlike the previous example (Fig.5) in this arrangement, the inlet 29 of the turbine is made in the form of holes in its peripheral part, and the supercharger is made in the form of the centrifugal fan 30 installed in front of the hole.

The inventive device according to the second variant (see Fig.5 and 6) works as follows. The impeller is driven by a drive connected to the shaft 9, as well as through one of the air flow (calanog.6). When sufficient pressure impeller can rotate only at the expense injected into the turbine section 22 of the flow. Air flows having different temperatures, with both sides coming through the pipes 5 and 22 and into the space between the blades 11 and 25, respectively. In centrifugal fan air flow flows in the interscapular space to the periphery of the impeller comes in lithopane cavity centrifugal partition 3 and then through the discharge pipe 6 is discharged from the housing 1. In the turbine the air flow flows in the interscapular space to the center of the impeller through the hole 20 separating disc 10 enters the outlet 21 and is discharged from the housing 1. As air flow through the impeller between them is the process of counter-current heat exchange through the blades 11, 25 and dividing the disk 10.

Two-stage fan-heat exchanger according to the second variant (see Fig.7 and 8) consists of two identical stages - the first 31 and second 32, each of which, respectively, contain a section 33 and 34 of the centrifugal fan, and section 35 and 36 of the turbine. Both stages 31 and 32 are made as described single-stage fan-talabi installed on the same shaft 9, driven in rotation from an external drive (Fig.7 and 8 are not shown). The divider 37 divides the stages 31 and 32.

The discharge nozzle 38 section 33 of the centrifugal fan of the first stage 31 is connected to the inlet side 39 of the turbine section 36 of the second stage 32, and the discharge pipe 40 section 34 of the centrifugal fan of the second stage 32 is connected to the inlet side 41 of the turbine section 35 of the first stage 31. Suction nozzle 42 of the first stage 31 and the outlet 43 of the second stage 32 are respectively input and output for a single carrier, and the suction nozzle 44 of the second stage 32 and the outlet 45 of the first stage 31 are respectively the input and output for another carrier.

Preferred the second option is to perform a two-stage fan-heat exchanger shown in Fig. 8. In contrast to the example shown in Fig.7, in this device, the front disks turbine sections 35 and 36 both stages 32 and 31 made in the form of a uniform solid disk 46.

Two-stage fan-heat exchanger according to the second variant (see Fig.7 and 8) operates as follows. When the shaft 9 and, accordingly, the impellers of both stages 31 and 32 of the air 34, respectively. Output from centrifugal fan sections 33 and 36 of the air streams fall into the turbine section 34 and 35, respectively, and then through the corresponding output sockets 43 and 45 are removed from device. Thus, each air stream passes both stages 31 and 32. As air flow through the impellers between them is the above process counterflow heat exchange through the blades of the centrifugal fan, turbine blades and spacer disks. In the device shown in Fig.8, the heat addition occurs through a common front disc 46.

Sources of information 1. Japan's bid 60-75634, F 28 D 9/00, Appl. 10.04.85, publ. 06.07.94.

2. Japan's bid 60-75635, F 28 D 9/00, Appl. 10.04.85, publ. 06.07.94.

3. Japan's bid 61-86463, F 28 D 11/02, Appl. 15.04.86, publ. 01.06.94 prototype.

4. Kutateladze S. S. fundamentals of theory of heat transfer. - Novosibirsk: Nauka, 1970, S. 628.


Claims

1. Fan-heat exchanger, comprising a housing and installed in the case of bilateral impeller, one side of which is made of centrifugal fan blades, the housing is divided into two isolated cavities, which together with the impeller to form two izolirovana in the form of a separating disc, moreover, the above-mentioned centrifugal fan blades on one side of the separating disk, and on its other side is made blades centrifugal fan, which together forms mentioned bilateral impeller, one side of which is impeller mentioned centrifugal fan, and the other centripetal fan.

2. Fan-heat exchanger under item 1, characterized in that the centrifugal fan blades and/or centripetal fan made recurved.

3. Fan-heat exchanger according to p. 2, characterized in that the ratio of the length of the blades of the centrifugal fan and/or blades of the centrifugal fan to the distance between the blades at an average radius of not less than 10.

4. Fan-heat exchanger according to p. 2, characterized in that between the blades of the centrifugal fan and/or centripetal blades of the fan on the periphery of the separating disc is made intermediate the blades.

5. Fan-heat exchanger according to p. 2, characterized in that the centrifugal fan blades and/or blade centrifugal fan is made with a constant width interscapular Kahn the Torah has bonded with blades solid front disc while dividing the disk has an axial hole, around which made outlet centrifugal fan which is connected with the interscapular space centripetal impeller of the fan, these outlet centripetal fan is placed inside the suction of the centrifugal fan.

7. Fan-heat exchanger under item 1, characterized in that the impeller of the centrifugal fan has bonded with the blades of the cutting disk having an axial hole for passage of fluid intake in the interscapular space of the centrifugal fan.

8. Fan-heat exchanger according to p. 7, characterized in that around the axial bore of the front disk of the impeller of the centrifugal fan is made inlet pipe which is connected with the interscapular space of the impeller of the centrifugal fan, in fact the inlet pipe is placed in the suction pipe of a centrifugal fan, with a minimum gap.

9. Fan-heat exchanger according to p. 8, characterized in that the centripetal impeller of the fan is connected with the blades solid front disc and R is the hole, around which made outlet centrifugal fan which is connected with the interscapular space centripetal impeller of the fan, these outlet centripetal fan is placed inside the input pipe of the centrifugal fan.

10. Fan-heat exchanger, comprising a housing and installed in the case of bilateral impeller, one side of which is made of centrifugal fan blades, the housing is divided into two isolated cavities, which together with the impeller to form two separate sections, one of which is a centrifugal fan, wherein the impeller is made in the form of the separating disk, and the said centrifugal fan blades on one side of the separating disk, and on its other side is made of the turbine blades, which together form the impeller, one side of which is impeller mentioned centrifugal fan, and the other centripetal turbine.

11. Fan-heat exchanger according to p. 10, characterized in that it further in the input pipe of the turbine installed Agneta is avago holes, coaxially with the impeller and the compressor is made in the form of an axial fan, the blades of which overlap mentioned circular hole in the input pipe of the turbine.

13. Fan-heat exchanger according to p. 11, characterized in that the inlet of the turbine is made in the form of holes in its peripheral part, and the supercharger is made in the form of a centrifugal fan installed in this hole.

14. Fan-heat exchanger according to p. 10, characterized in that the blade of the centrifugal fan and/or turbines are made recurved.

15. Fan-heat exchanger according to p. 14, characterized in that the ratio of the length of the blades of the centrifugal fan and/or turbine blades to the distance between the blades at an average radius of not less than 10.

16. Fan-heat exchanger according to p. 14, characterized in that between the blades of the centrifugal fan and/or vanes on the periphery of the separating disc is made intermediate the blades.

17. Fan-heat exchanger according to p. 14, wherein the centrifugal fan blades and/or the turbine blades are made with a constant width interscapular channel.

18. Fan-heat exchanger according to p. 10, characterized in that the turbine wheel have the disk, while dividing the disk has an axial hole, around which made the outlet of the turbine which is connected with the interscapular space of the impeller of the turbine, while the mentioned outlet of the turbine is placed inside the suction of the centrifugal fan.

19. Fan-heat exchanger according to p. 10, characterized in that the impeller of the centrifugal fan has bonded with the blades of the cutting disk having an axial hole for passage of fluid intake in the interscapular space of the centrifugal fan.

20. Fan-heat exchanger according to p. 19, characterized in that around the axial bore of the front disk of the impeller of the centrifugal fan is made inlet pipe which is connected with the interscapular space of the impeller of the centrifugal fan, in fact the inlet pipe is placed in the suction pipe of a centrifugal fan, with a minimum gap.

21. Fan-heat exchanger according to p. 20, characterized in that the turbine wheel is connected with the blades solid front disc and dividing the disk has an axial hole, around which made the outlet of the turbine, suomalaisen inside the input pipe of the centrifugal fan.

22. Fan-heat exchanger according to p. 18 or 21, characterized in that it is the first step, and further comprises a second stage, identical to the first, with both stages are accurately aligned and face each other front turbine disks, and the discharge nozzles centrifugal fans one step performed communicating with the inlet pipe turbines stairs, while the suction nozzle of the first stage and the outlet of the second stage are respectively the input and output for a single carrier, and the suction nozzle of the second stage and the outlet of the first stage are respectively the input and output for another carrier.

23. Fan-heat exchanger according to p. 22, characterized in that the front turbine disks both stages is an integral whole.

 

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Diametrically fan // 2196924

FIELD: ventilation, heating or cooling systems.

SUBSTANCE: proposed ventilation device contains at least two impellers passing along one axle or revolution, each being made for suction of ambient air in cross direction over considerable part of length of impeller. It has also motor connected with impellers to provided rotation around said axle, at least one bolding member at each end of each impeller, cover covering holding members and impellers provided with holes to let in and let out of air from impellers. Cover is furnished also with connector to connected cover with holding members. Holding members are made for interaction with connector of cover to connect cover and holding members. Ventilation device can be installed together with heating or cooling pipe. Impellers are made for directing considerable part of air flow from impellers is cross direction along outer surface of pipe and back into ambient atmosphere. Building can contain at least two rooms and at least one of ventilation devices described above. Method of operation of ventilation device includes counteraction to heat transfer owing to natural convection by operating impellers to create convection opposite to natural convection. Holding member which holds at least one pipe in fixed position, pipe being laid in longitudinal direction, is adapted for fixing pipe is cross direction relative to holding member and fixing the pipe relative to holding member with possibility of disconnection. Holding member has open surface through which pipe can be fitted in holding member in cross direction by relative movement of holding member and pipe. System to change temperature in at least two rooms of building contains heating or cooling pipe passing between said rooms. System contains great number of ventilation devices, each being adapted for mounting in each room near said pipe. Ventilation device is adapted to create air flow across pipe and it contains control system to operate each ventilation device to change intensity of heat transfer from pipe into ambient medium by changing air flow rate. Method to regulated intensity of heat transfer from cooling or heating pipe in building having at least tow rooms, heating or cooling pipe passing from first room into second one and ventilation device arranged in each room near pipe includes the following operation: control of ventilation device to create air flow across pipe, control of ventilation device to change air flow rate and thus change intensity of heat transfer from pipe.

EFFECT: improved ventilation of building.

85 cl, 17 dwg

FIELD: production of rotation wheels of ventilating fans.

SUBSTANCE: the invention is dealt with the field of production of ventilating fans, in particular with production of rotation wheels of diametric ventilating fans. The diametric ventilating fan contains a body with an inlet and a force branch-pipes, a rotation wheel with bent forwards blades fixed on the lateral discs mounted on a through shaft. The diameter of the shaft inside the wheel does not exceed0.1D2 of diameter of the wheel and due to this the invention ensures an increase of developed pressures, productivity and efficiency of the ventilating fan.

EFFECT: the invention ensures an increase of developed pressures, productivity and efficiency of the ventilating fan.

3 dwg

FIELD: mechanical engineering; fan building.

SUBSTANCE: proposed fan can be used in industry and agriculture. Novelty is that in cross-flow fan which has housing with inlet port and outlet connection and flat wall separating them and equipped with louver grid, impeller installed in housing and straight - line wall mating with fan housing higher than inlet port, said straight-line wall, installed parallel to separating flat wall, forms channel. Fan housing behind inlet edge is provided with window in which curvilinear planes are installed by their outlet sections to form contraction channels connected through inlet section, located higher than inlet edge, with inlet channel.

EFFECT: increased pressure and air flow rate developed by fan, reduced noise level.

1 dwg

Cross-flow fan // 2254497

FIELD: agriculture and industry.

SUBSTANCE: invention can be used in agriculture and industry to provide higher operating capabilities of fan within the range of energy-saving control of mode of operation. According to invention proposed cross-flow fan contains housing with intake and outlet holes and flat wall separating the holes and equipped with louvers, and impeller installed in housing. Louvers of flat wall are made curvilinear forming contraction-recirculation channels pointed by outlet section to impeller of fan. Louvers mating with flat wall are installed on hinge joints and adjoin by other end over contraction-recirculation channels and impeller.

EFFECT: improved operating capabilities of fan.

1 dwg

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