WO1988004756A1

WO1988004756A1 - Turbomachine for propelling two media with heat transfer between the latter

Info

Publication number: WO1988004756A1
Application number: PCT/EP1987/000737
Authority: WO
Inventors: Wolfgang Reichel
Original assignee: Ingenieurbüro Timmer Gmbh
Priority date: 1986-12-19
Filing date: 1987-11-27
Publication date: 1988-06-30
Also published as: DE3643496C2; DE3643496A1

Abstract

Turbomachine for conveying two media by means of two separate flow paths, in particular to convey two media of the same type having different calorific capacities and for transferring thermal energy from the hotter medium to the colder medium. Said machine comprises a housing with two inlet apertures and two outlet apertures for the media, circulation means arranged inside the housing for drawing and compressing or discharging the media, as well as channels which are made adjacent by separation walls and through which the media flow in such a way that the separation walls form thermal exchange surfaces which enable heat transfer between the media. These circulation means are formed by a radial vane-type impeller (11) with suction on both sides, and the channels (12, 13) extend on the periphery of the impeller (11) in an essentially axial direction and the separation walls (14) arranged between the channels (12, 13) are in the form of radially mobile blades of the impeller (11, 11a). This configuration enables a compact turbomachine of simple design to be produced.

Description

Fluid machine for conveying two media with heat transfer between the. media

The present invention relates to a turbomachine for conveying two media via two separate flow paths, in particular for conveying two media of the same type with different heat contents and for transferring thermal energy from the respectively warmer to the respectively colder medium, with a housing with two inlets and two outlets for the media, within the housing arranged fluids for sucking in and compressing or displacing the media, and with channels adjacent to and through which the media flow so that the partition walls form heat exchange surfaces for heat transfer between the media .

Such a turbomachine is known from DE-GM 82 36 459. This is a device for heat exchange between two gaseous media, in particular fresh air and exhaust air in rooms. With the known For fluid-flow machines, the fluids consist of two separate radial fans which are arranged on the same shaft within the housing and which convey the two media through the channels of a separate countercurrent heat exchange unit. The heat exchange between the media takes place via the partitions separating the channels, which thus form heat exchange surfaces. Because of the two separate fans and the separate counterflow heat exchange unit, this known turbomachine is structurally complex and consequently also relatively expensive. In addition, the heat exchange unit at least partially surrounds the fans, which results in the further disadvantage of large dimensions. A further disadvantage is that the efficiency of the heat transfer is dependent on the length of the heat exchange unit through which a reduction in the size of the machine would lead to a deterioration in the efficiency or an improvement in the efficiency would lead to a further increase in the size of the machine.

Another system is described in DE-PS 24 20 733, which also has two fan wheels arranged on a common shaft. Heat exchangers connected by a pipe system are arranged on these impeller wheels. The heat exchangers consist of tubes through which liquid flows, which are designed as circular tube rings. A pump for circulating the liquid heat carrier is located in the hub area between the two fans. This system thus consists of numerous movable components with large masses to be moved. Due to the rotation of the fan wheels, complex sealing measures for the liquid heat transfer medium are required. Furthermore, the temperature-dependent change in volume of the heat carrier causes an expansion vessel which is designed as a bellows. In the reference "Hönmann, Sprenger, paperback for heating and air-conditioning technology, R. Oldenbourg Verlag, Munich, Vienna, 63rd edition, page 1141" a so-called capillary fan is described, a rotor made of porous mass serving simultaneously as a fan and storage . The interior of the rotor is divided into two chambers by a partition. The rotating porous storage mass of the rotor compresses or displaces the gaseous medium flowing into the chamber and transfers the energy content including the moisture content of one gaseous substance to the other. The disadvantage here is the inexact separation of the two gaseous media, which causes mixing effects. In addition, the porous mass filters out dirt particles, which requires frequent cleaning of the rotor.

The present invention is based on the object, based on the prior art described at the outset, of specifying a structurally simple and compact turbomachine in which the outlay for conveying the media and for the heat transfer between the media is reduced and the efficiency of the heat transfer is increased.

According to the invention, this is achieved in that the fluid is formed by a double-sided suction radial impeller, and in that the channels on the circumference of the impeller run in an essentially axial direction and the partition walls arranged between the channels as radial blades of the impeller are formed. Due to this advantageous embodiment, the two separate wheels previously required d -

and the additional heat exchanger unit combined in one component, namely the impeller according to the invention. As a result, the turbomachine according to the invention is extremely compact. The heat transfer between the media takes place via the partition walls or moving blades, which thus form the heat exchange surfaces.

In a particularly advantageous development of the invention, intermediate walls are arranged within the channels of the impeller in such a way that the axial direction of flow of the media within the channels reverses at least once by 180 °. As a result, a further, considerable increase in the efficiency of the heat transfer is achieved while the dimensions remain the same. In addition, this advantageous embodiment also makes it possible to further reduce the dimensions of the turbomachine according to the invention, in particular by axially shortening the impeller, while maintaining the efficiency.

Further advantageous design features are contained in the subclaims and the following description.

The invention is to be explained in more detail in the following using the drawings. Show:

1 shows a longitudinal section through a first embodiment of a turbomachine according to the invention along the section line I-I in FIG. 2,

2 shows a cross section of the turbomachine along the line II-II according to FIG. 1,

3 shows a longitudinal section through a further embodiment of a turbomachine according to the invention, Fig. 4 is a cross section along the line IV-IV of FIG. 3 and

Fig. 5 shows an alternative embodiment of an impeller of a turbomachine according to the invention.

Two embodiments of a turbomachine according to the invention are shown in FIGS. 1 to 4. A housing 1 has an inlet 2 and an outlet 3 for a first medium I and an inlet 4 and an outlet 5 for a second medium II. To convey the two media I, II, according to the invention, a single radial impeller 11 is arranged within the housing 1, rotatably mounted about an axis 7 and driven in the arrow direction 8 (FIG. 2) by a motor 9. For heat exchange between the media I, II, channels 12, 13 extending in the axial direction are formed on the circumference of the impeller 11 such that two channels 12, 13 adjacent in the circumferential direction via an essentially radially arranged partition 14 each one of the Guide both media I, II in axial flow directions and displace them radially. In the drawing, the medium I flows through the channels 12 and the medium II flows through the channels 13 between the channels 12, the partitions 14, which act as radial blades, form heat exchange surfaces for heat transfer between the media I, II.

In the exemplary embodiments according to FIGS. 1 to 4, the impeller 11 consists of an inner hollow cylinder 16 and an outer hollow cylinder 17 which is concentric with this. These two hollow cylinders 16, 17 are connected to one another via the partition walls 14 to form the channels 12, 13. This results in an annular opening between the two hollow cylinders 16, 17 on each end face, which, however, is closed, for example, by a disk ring. At the entry of the Media I, II into the channels 12, 13 has the inner hollow cylinder 16 in its two areas adjoining its end faces with slot-shaped inlet openings 19 opening radially into the channels 12, 13. These inlet openings 19 open into the channels 12 for the medium I on the side arranged in the region of the inlet 2 and into the channels 13 for the medium II on the side arranged in the region of the inlet 4.

In a particularly advantageous development of the invention, intermediate walls 21 are arranged within the channels 12, 13 in such a way that the axial flow direction of the media I, II within the channels 12, 13 reverses at least once by 180 °. This results in an extension of the effective flow path and thus an improvement in the efficiency of the heat exchange. In the example shown, an intermediate wall 21 is arranged in each channel 12, 13. The intermediate walls 21 lie on a cylindrical surface which is concentric with the axis of rotation 7, so that the channels 12 _r 13 are each divided into inner partial channels 12a, 13a and outer partial channels 12b, 13b. The intermediate walls 21 of the channels 12 for the medium I each extend axially through the channel 12 from the closed end of the channel 12 facing the inlet 2, but end at a distance in front of the opposite end, so that flow reversal openings between the Subchannels 12a, 12b are formed. In an analogous manner, the intermediate walls 21 of the channels 13 for the medium II extend axially through the closed end face of the channels 13 facing the inlet 4 and end at a distance in front of the opposite end face, so that flow reversal openings between the partial channels 13 a , 13b are formed. In order to separate the flow paths of the two media I, II from one another in the inlet area, at least one partition wall 23, which is preferably perpendicular to the impeller axis, is arranged in the inner hollow cylinder 16 in the axial direction between the inlet openings 19, which prevents that the axially sucked media I, II mix within the inner hollow cylinder 16. Preferably, in the illustrated embodiment of the invention, two partition walls 23 are arranged within the inner hollow cylinder 16 directly adjoining the inlet openings 19. The media I, II are thereby axially sucked in and subsequently flow radially through the inlet openings 19 into the channels 12, 13, ie into the inner subchannels 12a, 13a. For the axial entry of the media I, II into the inner hollow cylinder 16, an annular inlet nozzle 25, 26 advantageously opens into each of the two end faces. According to the invention, the outer hollow cylinder 17 has slot-shaped outlet openings 27 in its two regions adjacent to its end faces , which are arranged at the end (as seen in the direction of flow of the media I, II) of the channels 12, 13 and the sub-channels 12b, 13b. In its axially between the outlet openings 27 liegen¬ the area is the ^"outer hollow cylinder 17 sealingly surrounded by at least one radial housing wall 29, which ensures the separation of the radially from the outlet openings 27 discharged media I, II. It is particularly advantageous when as shown - the outer hollow cylinder 17 27 area lying is tightly surrounded by an annular sleeve 31 over the entire, between the outlet openings, which is mounted on two radial housing walls 29 on the housing 1. the ^• discharge openings 27 open into the pressure chambers 32, 33. merge into outlets 3 and 5.

The flow paths of the two media I, II are to be described below. Medium I: inlet 2, inlet nozzle 25, inlet openings 19, subchannels 12a, flow reversal opening (reversal through 180 °), subchannels 12b, outlet openings 27, pressure chamber 32, outlet 3.

Medium II: inlet 4, inlet nozzle 26, inlet openings 19, subchannels 13a, flow reversal opening (reversal through 180 °), subchannels 13b, outlet openings 27, pressure chamber 33, outlet 5.

It should be noted that the intermediate walls 21 are provided. are to increase the flow path and thus the effective heat exchange area. The intermediate walls 21 can, however, also be omitted, the flow paths then resulting as follows without reversing the flow:

Medium I: inlet 2, inlet nozzle 25, inlet openings 19, channels 12, outlet openings 27, pressure chamber 33, outlet 5.

Medium II: inlet 4, inlet nozzle 26, inlet openings 19, channels 13, outlet openings 27, pressure chamber 32, outlet 3.

In addition, it is of course also within the scope of the invention to arrange a plurality of intermediate walls in each channel 12, 13 in order to further increase the flow path and thus the heat exchange area by repeated flow reversal.

It is clear from the description of the flow paths that the media I, II each flow through two circumferentially adjacent channels 12, 13 or 12a, 13a and 12b, 13b in opposite directions, that is to say in the countercurrent principle, with heat being exchanged via the partition walls 14 . In the embodiment shown in Fig. 1 and 2, he equipped ^¬ invention modern turbo-machine for the otherwise exiting from the outlet 3 Medium I with an auxiliary heat exchanger 34 to cover the heat demand or the cooling load. In the latter case, a sweat or water tank 34a is provided. This design is of particular importance if the turbomachine according to the invention is used, for example, as a balustrade device for the ventilation of rooms. Here, the heat exchange achieved in the flow machine ^according to the invention is often not sufficient to sufficiently heat or cool the supply air (medium I) flowing into the room. The required residual heat is supplied or extracted from the supply air by the additional heat exchanger 34. The additional heat exchanger 34 is preferably integrated into the housing 1 in the region of one of the outlets 3, 5, which ensures a compact design of the turbomachine. The corresponding outlet 3 or 5 is then omitted.

The flow machine shown in FIGS. 3 and 4 is shown exclusively as a compressor / heat exchanger unit without an additional heat exchanger.

3, a shaft 35, which is rotatably mounted in the housing 1 about the impeller axis 7 and can be driven by the motor 9, extends axially centrally through the dividing walls 23 and projects beyond the impeller 11 on both end faces in the axial direction.

As an alternative to this, according to FIG. 1, a central shaft piece 36, which extends axially beyond the impeller 11 on the end face and which is rotatably mounted in the housing 1 about the impeller axis 7 and can be driven by the motor 9, can also be attached to each partition 23. The region of the hollow cylinder 16 arranged between the partition walls 23 assumes the supporting functions of a shaft. The essentially radial partitions 14 - as already stated - act as radial blades. According to FIG. 2, the partition walls 14 can be designed as forwardly curved blades or, as shown in FIG. 4, as rearwardly curved blades. In addition, however, it is also within the scope of the invention to design the partition walls 14 as straight-running blades.

5 shows an alternative embodiment of an impeller 11a according to the invention. This impeller 11a consists of a shaft 41 and a hollow cylinder 42 concentrically enclosing the shaft 41. Between the shaft 41 and the hollow cylinder 42, the partitions extend in an essentially radial direction to form the channels, which means that radial rotor blades also in this case are formed. In addition to the radial rotor blades, however, in this embodiment, axial rotor blades 44 are provided on the end face, which rotate together with the impeller 11a and thus axially displace the media I, II into the channels. If intermediate walls 21 are arranged within the channels, the axial rotor blades 44 are arranged in the area of the inner partial channels, so that the media ^" flow into the inner partial channels and exit the outlet openings 27 of the outer partial channels after the flow has been reversed. The advantage This design lies in particular in the enlarged heat exchanger area, which results from the fact that the partition walls between the channels extend from the hollow cylinder 42 to the shaft 41, that is to say are made wider in the radial direction.

The present invention is not limited to the exemplary embodiments shown and described, but also encompasses all features having the same effect in the sense of the invention. In particular, it is also Examples according to FIGS. 1 to 4 conceivable to provide additional axial impellers which are arranged in front of the end faces of the impeller 11 and rotate together therewith, which axially convey the media I, II into the region of the inner hollow cylinder 16.

Claims

claims

1. Fluid machine for conveying two media via two separate flow paths, in particular for conveying two media of the same type with different heat contents and for transferring thermal energy from the respectively warmer to the respectively colder medium, with a housing with two inlets and two outlets for the media, fluid within the housing for sucking in and compressing or displacing the media, as well as with channels adjacent to and through which the media flow so that the partition walls form heat exchange surfaces for heat transfer between the media, characterized in that the fluids

. are formed by a double-sided suction radial impeller (11,11a), and that the channels (12, 13) on the circumference of the impeller (11, 11a) extend in a substantially axial direction and that between the channels (12, 13) arranged partition walls (14) are designed as radial blades of the impeller (11, 11a). -li-

Turbomachine according to claim 1, characterized in that intermediate walls (21) are arranged within the channels (12, 13) such that the axial flow direction of the media (I, II) within the channels (12, 13) each at least once by 180 ° reverses.

Turbomachine according to claim 1 or 2, since ¬ characterized in that the impeller (11) has an inner hollow cylinder (16) and an outer hollow cylinder (17) which is concentric with the latter and which form the channels (12, 13) the partitions (14) are connected to one another, with annular openings, for example at the front, between the hollow cylinders (16, 17) are closed by washers.

Turbomachine according to claim 3, characterized in that the inner hollow cylinder (16) has slot-shaped inlet openings (19) opening in its two regions adjoining its end faces and opening radially into the channels (12, 13), the one end face Area in the channels (12) for the first medium (I) and in the other end area in the channels (13) for the second medium (II) open. ;

^'I-flow machine according to claim 4, dadrchgekennzeichnet that inside the inner hollow cylinder (16) in the axial direction between the inlet openings (19) preferably two anschlies- directly to the inlet openings (19) send, to the impeller axis vertical partitions (7) (23) are arranged.

-A-

6. flow machine according to one or more of claims 1 to 4, characterized in that a motor (9) than to the impeller axis (7) vertical separation is ^¬ is arranged within the inner hollow cylinder (16) in the axial direction between the inlet openings (19).

7. turbomachine according to claim 5, characterized in that in the housing (!) Around the Laufradach.se (7) rotatably mounted and driven by a motor (9) shaft (35) extends centrally axially through the partition walls (23) and axially projects beyond the impeller (11) on both end faces.

8. Turbomachine according to claim 5, characterized in that on each partition (23) a central, axially on the end of the impeller (11) extending shaft piece (36) .Fastened, the shaft pieces (36) in the housing (1) the impeller axle (7) is rotatably mounted and can be driven by a motor (9).

9. Turbomachine according to one or more of claims 3 to 8, d a d u r c h g e k e n n z e i c h n e t that in the inner hollow cylinder (16) on both faces one with one of the two inlets (2,

4) connected, annular inlet nozzle (25, 26) opens.

10. Turbomachine according to one or more of claims 2 to 9, characterized in that within the channels (12, 13) in each case an intermediate wall (21) is arranged which lie on a cylindrical surface concentric with the impeller axis (7), whereby each form radially inner subchannels (12a, 13a) and outer subchannels (12b, 13b). If-

11. Fluid machine according to claim 10, which also means that the intermediate walls (21) of the channels (12) are for the first medium

(I) or the channels (13) for the second medium (II) each extend axially through the closed end face of the channel (12, 13) facing the inlet (2, 4) and so at a distance from the opposite end end that flow reversal openings form between the sub-channels (12a, 12b or 13a, 13b).

12. Turbomachine according to one or more of claims 3 to 11, characterized in that the outer hollow cylinder (17) in its two areas adjoining its end faces has slot-shaped outlet openings (27) which flow in the direction of flow of the media (I, II) seen at the end of the channels (12, 13) or the partial channels (12b, 13b) are arranged and open into pressure chambers (32, .33) connected to the outlets (3, 5) of the housing (1).

13. Fluid machine according to one or more of claims 3 to 12, d a d u r c h g e, k e n n z e i c h n e t, that the outer hollow cylinder (17) for separating the media emerging from the outlet openings (27) (I,

II) is sealed in its wall area lying in the axial direction between the outlet openings (27) by at least one radial housing wall (29).

14. Turbomachine according to claim 1, characterized in that the impeller (11a) from a rotatable in the housing (1) about the impeller axis (7) and driven by a motor (9) / o -

Shaft (41) and a hollow cylinder (42) concentrically enclosing the shaft (41), the essentially radial partition walls forming the channels extending between the shaft (41) and the hollow cylinder (42).

15. Turbomachine according to claim 14, characterized in that the channels are each designed to be open on one end face, with additional axial media blades (44) displacing the media (I, II) axially into the channels in both areas lying in front of the channels. are arranged.

16. Turbomachine according to one or more of claims 1 to 15, d a d u r c h g e k e n n z e i c h n e t that the channels (12, 13) separating partitions (14) are designed as forward curved, backward curved or straight running blades.

1 . Fluid machine according to one or more of claims 1 to 16, g e k e n n z e i c h n e t d. u r c h at least one, preferably in the area of one of the outlets (3, 5) integrated in the housing (1) additional heat exchanger (34) for supplying or withdrawing thermal energy for or from the outlets

(3, 5) emerging media (I, II).