Fan-heat exchanger

 

The invention is intended for ventilation and air-conditioning, in which the fluids are not mixed with each other. The device includes a housing and mounted therein the impeller bilateral centrifugal fan, the housing is divided into two isolated cavity (canal), which together with the impeller to form two isolated centrifugal fan. The impeller is made in the form of a continuous separation of the drive on both sides which is normal to its plane made blades, with backward-curved blades are made. This simplifies the mounting of the fan-heat exchanger in ventilation and air conditioning, as corresponds to the direction of inlet and exhaust flows. 5 C.p. f-crystals, 5 Il.

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, intended the data flows with different temperatures, split 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 of the heat exchange element, removed from the casing through the respective injection nozzles. Heat transfer takes place through the corrugated wall during flow coolant her face.

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 Talon the alley, 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, made in the form of a radially corrugated disc with the outer rim, while the faces of the corrugations function of radial 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 the coolant (air flow) 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. Teplocom the 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 fan has a gauge pressure exceeding the pressure required to overcome the hydraulic resistance of the fan. This requires an increase in input power. To resolve this particular characteristic of the 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 of privaie for such designs 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 equally 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 decrease as it approaches the periphery of the impeller, driven, taking into account the continuity of the air flow, increasing the sectional area of the interscapular space to the periphery. Thus, despite the relatively large heat transfer surface, its effectiveness will be low.

The technical challenge which seeks the invention is to reduce power consumption and increase the efficiency of heat exchange.

The essence of the invention lies in the fact that in a well-known fan-heat exchanger, comprising a housing and installed in the casing impeller bilateral centrifugal fan, the housing is divided into two isolated cavities, which together with the impeller to form two isolated centrifugal valve is x which is normal to its plane made blades, with backward-curved blades are made.

Replacement corrugated disk impeller on a solid drive on both sides which is normal to its surface is made of blades, allows to make the latter any given curvature, since such construction is not already associated with the technology of manufacturing corrugated surface. Performing backward-curved blades can significantly reduce excess pressure at the outlet of the centrifugal fan and, thereby, to reduce power consumption. Changing the curvature of the blades, you can change the area normal to the blades section interscapular space, ensuring the constancy of the velocity of the flushing air flow the surface of the blades. The specified performance of the blades, in contrast to the known, allows to increase significantly 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 the two air streams is advanced through the introduction of the separating disk, modifying the blades of the impeller, education and training the efficiency of heat exchange, associated with additionally introduced a dividing disk.

For significantly increasing the efficiency of heat transfer in the inventive device the blades, it is advisable to make with respect to their length to the distance between the blades at an average radius of not less than 10.

To increase the area of heat exchange between the blades of the impeller at the periphery of the separating disc may be optionally performed intermediate blades.

Additionally, the impeller blades 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, fans can contain bonded with the blades of the cutting disk having an axial hole for passage of a coolant in the interscapular space. Front disc closes the interscapular space, thereby reducing ventilation losses and increasing the efficiency of heat exchange.

The discharge nozzles of both fans can be made and deployed asymmetrically in the axial direction in the opposite direction relative to the corresponding suction nozzle. This chanelno simplifies the installation of the proposed fan-heat exchanger in ventilation and air conditioning, since corresponds to the direction of supply and exhaust air streams.

The essence of the invention is illustrated graphics, which depict: Fig. 1 - fan-heat exchanger with unidirectional symmetric location of injection nozzles; Fig. 2 - fan-heat exchanger with divergent axisymmetric arrangement of the injection nozzles; Fig. 3 - fan-heat exchanger with divergent axisymmetric arrangement of discharge nozzles that are deployed in the axial direction in the opposite direction relative the respective suction nozzles; Fig. 4 is an example implementation of the blades of the impeller with a constant width interscapular channel; Fig.5 illustrates the relation for the calculation of the profile of the blades with a constant width interscapular channel.

The inventive fan-heat exchanger (Fig.1-3) consists of a body 1 lithobates shape with axial suction nozzles 2 and 3, is made on its opposite end faces, and relevant tangentially arranged discharge pipes 4 and 5. In the housing 1 on a shaft 6 mounted impeller consisting of a separating disc 7 with normal sakuradani). The inner space of the housing 1 is divided by a partition 10 into two cavities 11 and 12, forming snails two centrifugal fans. Its Central part of the partition wall 10 adjacent to the outer edge of the disk 7 through the sealing element 13, made for example of rubber or felt. Also in Fig.1-3 arrows show the direction of air flow of fluids.

In Fig.1 shows an example of performing fan-heat exchanger with unidirectional symmetrical arrangement of the injection nozzles 4 and 5, and Fig.2 is an example implementation of the fan-heat exchanger with divergent axisymmetric arrangement of the injection nozzles 4 and 5.

It is preferable to perform fan-heat exchanger shown in Fig.3. In this case, the impeller has on each side of the front discs 14 and 15, having an axial hole for passage of intake air in the interscapular space. Front discs 14 and 15 in the area mentioned axial holes have a conical portions 16 and 17 respectively, which are placed in the respective suction nozzles 2 and 3, with a minimum gap. Additionally, on both sides of the disk 7 on its periphery is made intermediate the positive feature of this design is the implementation of the injection nozzles 4 and 5, are mixed and deployed asymmetrically in the axial direction in the opposite direction relative the respective suction nozzles 2 and 3.

Example execution of the blades 8 (or 9) of the centrifugal fan with a constant width interscapular channel shown in Fig.4. In Fig.5 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=const, calculate the value of angle(r), thereby defining the profile of the blade. In particular, in Fig.4 and Fig.5 presents Pikalyovo rto(point b): r0=0,4 rto. In this case defined values(r) that lie within:(r0) = 34,22and(rto) = 13,0. 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 operates as follows. When the shaft 6 with a fixed impeller air flow (heat transfer) having different temperatures, with both sides coming through suction pipes 2 and 3 and into the space between the blades 8 and 9 respectively. The centrifugal force of the air streams flowing in the interscapular space to the outer circumference of the impeller, proceed to the appropriate lithopane cavities 11, 12 and further through the discharge pipes 4, 5 are removed from the housing 1. As the air potulny disk 7. In the construction shown in Fig. 3, the heat exchange process involves intermediate vanes 18.

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.

Claims

1. Fan-heat exchanger, comprising a housing and installed in the casing impeller bilateral centrifugal fan, the housing is divided into two isolated cavities, which together with the impeller to form two isolated centrifugal fan, wherein the impeller is made in the form of a continuous separation of the drive on both sides which is normal to its plane made blades, with backward-curved blades are made.

2. Fan-heat exchanger under item 1, characterized in that the ratio of the length of the blades, at least one of the fans to the distance between the blades at an average radius of not less than 10.

3. Fan-heat exchanger under item 1, characterized in that between the shoulder blades, at least one of the fans on the periphery of the separating disc made split timing is of tilateral performed with a constant width interscapular channel.

5. Fan-heat exchanger under item 1, characterized in that at least one of the fan further comprises bonded with the blades of the cutting disk having an axial hole for passage of a coolant in the interscapular space.

6. Fan-heat exchanger according to p. 1, wherein the injection nozzles are both fans are implemented and deployed asymmetrically in the axial direction in the opposite direction relative the corresponding suction nozzle.

 

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