NL1009754C2 - Method for manufacturing a blade or sheet metal plate. - Google Patents

Description

METHOD FOR MANUFACTURING A SHAFT OR SHAPE OF SHEET METAL

The invention relates to a rotation * device, comprising: (a) a housing having a central, substantially axial first medium throughput and at least one substantially axial second medium throughput; (b) a rotor shaft extending in that housing and beyond that housing, which is rotatably mounted relative to that housing and carries a rotor accommodated in that housing, said rotor having a central third medium throughput at said first medium throughput which third medium throughput branches into an r number of angularly equidistant rotor channels, each of which extends in a respective at least more or less radially main plane from the third medium throughput to a respective fourth medium throughput, the end zone of the third medium throughflow and the end zone of the fourth medium passage each extend substantially axially and each rotor channel has a curved shape, for example a general U-shape or a general S-shape, has a center part that extends in a direction with at least a substantial radial component, and each rotor channel a flow tube cross-sectional area, that is, a cross-section to any local -

main direction, which increases in the direction from the third medium throughput to the fourth medium throughput

from a relative value of 1 to a relative of at least 4. - (c) a stator accommodated in that housing, comprising: '30 (c.1) a first central body which has a substantially rotationally symmetrical, for example at least n min or more cylindrical, at least more or less conical, curved or hybrid shaped outer surface with a smooth

1. 5 4 I

2 has a shape which, together with an inner surface of the housing, defines a generally substantially rotationally symmetrical, for example cylindrical, medium passage space with a radial dimension of at most 0.4x the radius of said outer surface, in which medium passage space a number of angularly equidistant pairwise stator channels bounding stator vanes are accommodated, which stator vanes each have a substantial, in particular at least 60 °, direction deviating from the axial direction at their end zone facing the rotor, forming a fifth medium throughput, and at their other, forming a sixth medium throughput end zone have a direction which deviates slightly from the axial direction, in particular at most 15 °; which fifth media passages for medium flow connect in substantially axial direction to the fourth medium passages, and are placed in substantially the same radial positions, and which sixth medium passages are in communication with the at least one second medium passage; (c.2) a second central body, wherein between the sixth medium throughput and the at least one second medium throughflow, a number extending in the direction from the sixth medium throughes to the at least one second medium throughthrough the outer surface of the second central body and the cylindrical inner surface of the housing extend bound manifold channels; wherein a general medium flow path is defined between the first medium pass and the at least one second medium pass through the first medium pass, the third medium passages, the rotor channels, the fourth medium passages, the stator channels, the sixth medium passages, the manifold channels, the second medium passages, and vice versa, with substantially smooth and continuous transitions between said parts during operation; and wherein the construction is such that during operation there is a mutual force coupling between the! i f-n ~.

T 3 j rotation of the rotor, and thus the rotation of the shaft, on the one hand, and the pressure in the medium flowing through said medium flow path.

To explain the new manufacturing method for a rotary device of the new type to which the invention relates, an introduction to this follows below.

Rotary devices are known in many embodiments.

It is known, for example, a centrifugal pump with an axial inlet and a liquid to be pumped radially under the influence of centrifugal forces with a rotor swinging outwards and one or more, for example, substantially tangential outlets.

Furthermore, an axial compressor with cascaded groups of rotor and stator blades is known. "

The structure contains many thousands of extremely complex: molded parts, which also have to meet high requirements of: dimensional accuracy and mechanical strength.

An example of this is a gas turbine, in which in this case gaseous medium is released under pressure from a designated source and is directed at the blades of a rotor, such that this rotor is driven with force for, for example, rotating a machine such as an electric generator.

These known devices exhibit flow instabilities, especially at low flow rates.

These often cause an imbalance in the rotor load, which gives rise to heavy vibrations, uncontrollable speed variations and very heavy mechanical loads on bearings, shafts and blades.

All known rotary devices have further technical shortcomings.

For example, the efficiency is often relatively low and strongly dependent on the speed. - 1 Π Π 0 ~ £ 4 i U \ j ν 'ί: - 4

In addition, the known devices are usually bulky, heavy and expensive.

When using casting techniques to produce a rotor, the blades must have a certain minimum wall thickness, which gives rise to undesired decreases in the effective flow volume and losses due to loosening and wake formation. In addition, the blade wall thickness and the necessary blade shape limits the number of blades to be accommodated. Furthermore, the casting technique inevitably leads to undesired surface roughness and unbalance due to unintended and uncontrollable density differences, for example due to inclusions.

Furthermore, the tensile strength of cast metals and 15 alloys is limited.

Known centrifugal pumps further suffer from so-called slip, the phenomenon that the flow is poorly attached to the suction side of the flow channel, which is bounded by neighboring vanes. Due to the expansion angle ~ 20 between the blades, there is a slip area or an area of "dead water", in which there is a large-scale stationary vortex, whereby the flow in that area is zero. As a result, the output pressure of the centrifugal pump is highly pulsating.

Known devices are furthermore constructed in such a way that they produce a lot of noise during operation.

All known devices operating as, for example, a water pump, have a limited pressure capacity. For example, for applications such as a fire brigade pump, pumps are often cascaded with one another to realize the required pressure, also expressed as the head of the water to be pumped.

In the known rotary devices it is furthermore sometimes experienced as a drawback that medium inlet and medium outlet do not show the same direction, but are for instance perpendicular to each other. Under certain circumstances it may be desirable, at least the! r ·; . . ; ,] ï V u u i j 4 5 possibility to give the input and output the same direction.

Known devices are furthermore unable to work with media with widely varying viscosities.

In known devices, the flow rates of the flow-through media during the flow-through of a device vary very widely. As a result of the accelerations occurring, noise production and loss of efficiency occur. In this connection, it would be desirable to keep the flow rate of flow-through medium through a rotary device the same, for example, within a range of 0.2-5 times a guideline value under all conditions.

The invention focuses specifically on the manufacture of the stator blades and the rotor baffles, which are preferably used for a rotary device of the type described.

It is essential that the modeling of the 20 blades or the baffles be done with high precision

takes place to obtain a substantially medium-tight connection to the surfaces, with which the blades and I

the bulkheads must cooperate in a sealing manner. ï

A stator vane must meet high requirements of accuracy, which is technically very difficult to realize in connection with the spatially extremely complicated form of such a vane. "

A rotor baffle should be manufactured with high precision and preferably welded to two rotor discs. The welding spots in question are inaccessible with normal welding techniques, so that one would tend to resort to other connection methods such as soldering, gluing, screw connections, lip-hole connections and the like.

It is essential for the method according to the invention that the shape accuracy of the blades and partitions must meet very high requirements.

1000754 7 6

The method of claim 1 generally permits manufacture with high dimensional accuracy.

The method according to claim 2 relates to a special method which is intended for manufacturing a stator blade. Such blades have a more or less partly helical structure, while their radially inward and outwardly directed edges should have an exact partly cylindrical shape. Spatially, such a structure is extremely complicated. The method of claim 2 nevertheless allows the manufacture of stator blades with a very high degree of shape accuracy.

It is noted that the perpendicularly bent longitudinal edge zones are very suitable for joining, for instance by gluing, to a corresponding cylindrical contact surface.

Claim 3 relates to a preferred embodiment of the method according to claim 2, 20 according to which the forming of the converted longitudinal edge zones takes place simultaneously with the modeling of a stator vane as described above.

Claim 4 relates to a method which is particularly, but not exclusively, suitable for forming the stator blades.

Claim 5 relates to a method which is particularly, but not exclusively, suitable for manufacturing a rotor bulkhead.

Claim 6 concerns a preferred method for manufacturing a rotor. The method can be carried out very quickly and with high accuracy.

In order to define the flow paths between the flow-through protrusions as sharply as possible, the method according to claim 6 is preferred. This avoids thermal differences between the different welding positions which could adversely affect the quality of a rotor to be manufactured.

<r; Γ *. C C ·· *? i, f * 'r! 5 · 7

Claim 8 concerns a mold for performing the method according to claim 2.

Claim 9 concerns a rotor baffle or stator vane, which is manufactured by the method according to any one of the preceding claims, while claim 10 concerns a rotor, which is manufactured using the method according to claim 6 or 7.

The invention will now be elucidated with reference to the annexed drawings. In the drawings: figure 1 shows partly in cross-section, partly in cut-away side view, a first exemplary embodiment of a rotary device; figure 2 shows a partly broken away perspective view of the device according to figure 15, which is schematized for the representation of the spatial structure; figure 3 shows a variant of a manifold; figure 4 is a partly broken away perspective view of a second embodiment of a rotation device; figure 5A is an exploded view of a part of a stator with stator blades delimiting stator channels; Figure 5B is an exploded view of a stator vane; figure 5C shows a view corresponding with figure 5A of two stator blades for explaining the geometric proportions; figure 5D shows a rectilinearized view of the stator channel according to figure 5C; figure 5E is a graph of the channel width as a function of the channel distance; figure 5F shows the included angle as a function of the channel distance; Figure 6A shows a schematic cross section of a third embodiment of a rotary device; 9 1009754 8 ƒ \ figure 6B a view of a variant corresponding to figure 6A.

figure 7 shows a perspective exploded view from below of the internal structure with rotor and stator of a fourth embodiment of a rotary device, with the housing and the lower rotor plate omitted; Figure 8 from the top of the stator of Figure 7, with the housing and rotor omitted; Figure 9 shows a perspective exploded view from below, corresponding to figure 7, of the rotor; figure 10A shows a perspective view corresponding with figure 8 of the stator part of a fifth exemplary embodiment, wherein the manifold is designed differently; figure 10B shows a view corresponding with figure 10A of a variant; figure IOC shows a view corresponding with figure 10B of a variant; Figure 10D is a graphical representation of the relationship between the tangential distance between two blades and the axial position; Figure 10E shows the channel width as a function of the channel position; Figure 10F is a graphical representation of the included angle as a function of the channel position; figure 11 shows a partly broken away perspective view of a part of a sixth embodiment of a rotary device; Figure 12A is a partial schematic perspective view of a die for forming rotor blades; figure 12B shows a cross-section along the line 35 B-B in figure 12A; Figure 12C is a schematic exploded view of a device for manufacturing a stator vane; "5 f" Γ. i "; - 1 · I J U U t f O '{.

Figure 12D shows a perspective view of the device according to figure 12C; figure 13A shows a highly schematic exploded view of a device for assembling a rotor according to figure 9; Figure 13B is a schematic partial perspective view of an arrangement of a number of guide blocks in the manufacturing phase of a stator; Figure 13C shows a partly broken away perspective view drawn under figure 13B of the stator manufactured according to figure 13B; figure 13D shows an assembly of heat and electricity conducting blocks according to figure 13B;

Figure 14 shows a schematic graph i

comparison of the efficiency as a function of the relative flow rate of a known rotary device and a device according to the present patent application; figure 15 shows the pressure to be generated by a device according to the invention as a function of the flow rate at different speeds in comparison with a known pump; Figure 16 is a graphic representation corresponding to Figure 15 of another embodiment; Figure 17 shows a perspective view of a further embodiment of the rotation device according to the invention; figure 18 shows a cut-away perspective view of the device according to figure 17; Figure 19 shows an exploded view of the device according to figure 17; figure 20 shows a perspective view of the motor; figure 21 shows a perspective view of the flow channel unit, which extend between the sixth medium passage and the second medium passage; and - figure 22 a top view of the unit according to figure 21 .

1000754: 10

Figure 1 shows a rotation device 1. It comprises a housing 2 with a central, axial first medium feed-through 3 and three axial second medium feed-throughs 4, 5, 6. Furthermore, the device 1 comprises a housing 2 mentioned above and outside that housing 2 extending shaft 7, which is rotatably mounted with respect to the housing 2 and carries a rotor 8 accommodated in the housing 2, which will be specified hereinafter. The rotor 8 connects to the first medium passage 3 with a central third medium passage 9. The third medium passage 9 branches into a number of angularly equidistant rotor channels 10, each of which extends in a respective, at least more or less radially major plane from the third medium passage 9 to a respective fourth medium passage 11. The end zone of the third medium passage 9 and the end zone of the fourth medium passage 11 each extend substantially in axial direction. As shown in Figure 1, each rotor channel 10 has a generally faint S shape, about 20 corresponds to a half cosine function, and has a center portion 12 extending in one direction with at least a significant radial component. Each rotor channel has a cross-sectional area that extends from the third medium throughput to the fourth medium throughput.

The rotation device 1 further comprises a stator 13 accommodated in the housing 2. This stator 13 comprises a first central body 14 and a second central body 23.

The first central body 14 has on its zone adjoining the rotor 8 a cylindrical outer surface 15, which together with a cylindrical inner surface 16 of the housing 2 has a generally cylindrical medium passage space 17 with a radial dimension of at most 0.2x the radius of the cylindrical outer surface 15, in which medium passage space 17 is accommodated a number of angularly equidistant pairwise stator channels 18 stator blades 19, which src '-' '. : '·; 11 stator vanes 19 each at their end zone 20 one at their end zone 20, which faces a rotor 8, forming a fifth medium feed-through 24; substantially, in particular at least 60 °, direction deviating from the axial direction 21, and at their other end zone 22, forming a sixth medium feed-through 25, have a direction deviating slightly, in particular at most 15 °, from the axial direction 21 , which fifth medium passages 24 connect to the fourth medium passages 11, and which sixth medium passages 10 communicate with the three second medium passages 4, 5, 6.

The second central body is configured such that between the sixth medium throughput 25 and the second medium throughflows 4, 5, 6 three, extending in the direction 15 from the sixth medium throughflows 25 to the second medium throughflows 4, 5, 6, manifold channels. 26 1

stretch out. These manifold channels are also bounded by the outer surface 29 of the second central body 23 and the cylindrical inner surface 16 of the L

20 house 2.

In Figure 1, a general medium flow path 27 is indicated by arrows. This path 27 is defined between the first medium throughput 3 and the second medium throughputs 4, 5, 6 through 25, respectively: the first medium throughput 3, the third medium throughputs 9, the rotor channels 10, the fourth medium throughputs 11, the stator channels 18, the sixth ”medium passages 25, the manifold channels 26, the second; medium throughputs 4, 5, 6, with essentially smooth ~

30 transitions between said parts. It is noted that I

in figure 1 the flow of the medium according to arrows 26 is shown in accordance with a pumping action of Ξ

the device 1, for which the shaft 7 is rotatably driven by motor means (not shown). Through 35 the medium passages 4, 5, 6 would pressurize medium with force L.

are allowed in the second medium passages 4, 5, 6, "

then the medium flow would have been reversed and the rotor • f η Π Γ A

1 U \ j · -> i o 4 12 8 are driven in rotation, also under rotary drive of shaft 7.

The construction of the device is such that during operation there is a mutual force coupling between the rotation of the rotor 8, and thus the rotation of the shaft, on the one hand, and the speed and pressure in the medium flowing through the said medium flow path 27.

In general, therefore, the device can operate as a pump, in which case the shaft 7 is driven 10 and the medium is pumped according to the arrows 27, or as a turbine / motor, in which case the medium flow is reversed and the medium provides the driving force .

Figure 2 shows in a highly schematic exploded perspective the device 1. It is clear that the manifold channels 26 are formed by a second central body 23, which can be regarded as an insert located above the first central body 14 and three recesses 30 forming manifold channels 26. These recesses have rounded shapes and adjoin the underside of the sixth medium passages 25 for guiding the medium according to arrows 27 to the second medium passages 4, 5, 6.

Figure 3 shows the insert 23 in partly broken away perspective view. In this arbitrary embodiment, the insert 23 is formed from sheet metal. However, it can also consist of other suitable materials, such as solid, optionally reinforced plastic and the like.

Figure 4 shows a device 31, which corresponds functionally to device 1. Device 31 comprises a drive motor 28.

As can be seen more clearly in figure 4 than in figure 1, an input propeller 32 with a number of propeller blades 33 is arranged in the third medium feed-through 9 serving as medium inlet.

In anticipation of the discussion of the rotor according to figure 9, which corresponds to the rotor 8 according to figure 1, it is already noted that the rotor 34 in the device 31 according to figure 4 has a number of additional stiffening braces 35 which are missing in the rotor 8.

As shown in Figure 9, rotor 8 comprises a number of separate parts, which are integrated with each other in a manner to be described below. The rotor 8 comprises a lower saucer 36, an upper saucer 37, twelve relatively long partitions 38 and twelve relatively short partitions 39 interposed therewith which form equidistant boundaries of respective rotor channels 10 in the manner shown. The partitions 38, 39 each have a curved shape and perpendicularly bent edges 40, 41 for medium-tight coupling with the dishes 36, 37. The partitions 38, 39 are preferably connected to the dishes by welding and thus form an integrated rotor. The input propeller 32 is placed in the central third medium passage 9. It has twelve sheets, without a rheologically significant transition; 20 connect to the long rotor baffles 38. In the center 1 of the input propeller 32 a downwardly tapering fairing element 42 is placed.

In particular figure 4 clearly shows the operation of the device 31 acting as, for example, a liquid pump. By driving shaft 7 with carrier "

the rotor channels 10 of rotor 34 are pressed in by the action of propeller 32 liquid. Partly as a result of the occurring centrifugal acceleration, an I.

strong pumping effect, comparable with that of centrifugal pumps. Centrifugal pumps, however!: Work with fundamentally differently shaped rotor channels. The fluid flowing out of the rotor channels 10 exhibits a z strong rotation and is in the form of an annular flow with both a tangential or rotational directional component and an axial directional component. The stator vanes 19 remove the rotational component and return the initially axially introduced flow in axial z towards the manifold channels 26, where the partial flows are collected and fed respective medium discharges 4, 5, 6. If desired, the medium can be further pumped via one pipe in the manner shown in figure 2 by means of a union of the three outlets 4, 5, 6 into one pipe 43.

Referring to Figure 10, it is noted that other embodiments are also possible, wherein the discharge also extends in an almost exactly axial direction.

Figure 5A shows that the stator blades 19 have a bent edge 44 on their input side. This edge has a rheological function. It provides a smooth, streamlined transition from the strongly rotating medium flow delivered by the fast-rotating rotor 34 to the stator channels 18.

The rotors described in this embodiment consist of stainless steel parts, with reference to figure 9 the dishes 36, 37, the partitions 38, 39, the propeller 32.

Figure 5A shows in expanded form the outer surface 15 of the first central body and the stator blades 19.

Figure 5B shows a view of a partition 19 along the broken line B-B in Figure 5a.

Figure 5C shows a set of stator blades 19 bounding stator channel 18 together.

Figure 5D shows a deflection of the channel 18 with the determination of the mutual angles in accordance with the successive lines 46, which, as Figure 5D shows, have all mutual distances along the axis of approximately 5 mm, at least in this embodiment. The run-out width of each stator channel, as shown in Figure 5C, is approximately 15mm. Figure 5D shows the different positions with the associated half angles between the blades 19 at the indicated positions.

Figure 5E shows the channel width as a function of the positions according to Figures 5C and 5D.

Figure 5F shows the included angle in accordance with the representation in Figure 5D. It is important to note, j * 1 '' Λ Γ /; · .I! t ·· ..: · / o 4-a 15 that this angle never exceeds the rheologically important value of approximately 15 ° and even remains below the value of 14 °.

In Figure 1 and Figure 4, it can be clearly seen that the respective rotors 8, 34 in the region of the third medium throughput and the fourth medium throughput with respect to the housing 2 are sealed by respective labyrinth seals 45, 46. The shaft is mounted with respect to the housing by means of at least two bearings, 10 of which only one is shown in Figures 1 and 4.

This bearing is indicated by reference number 47.

Figure 6A shows a rotation device with a slightly different structure. In this structure, there is a continuous unit of manifold channels, since there is a space 49 bounded by a second central body 50 together with the wall 51 of the housing 52.

Thus there is only one medium discharge 4.

Figure 6B shows a rotation device 48 ', the construction of which corresponds almost entirely to the structure of the device 48 according to Figure 6A. Unlike in device 48, device 48 'includes an electric motor. It comprises a number of stator windings denoted by reference numeral 90, which 7

are stationary, and a rotor armature 91, which is fixedly connected to the top plate 37 of rotor 8. I

The lead wires of the stator windings are not shown r. They may very suitably extend upwardly through the unused space within the stator vanes 19 and exit the device 48 'at a desired suitable position. ~

Figure 7 shows the internal structure of rotor 8, leaving out the lower saucer 36. Reference is made in this connection to figure 9. Of interest in this figure 7 is the construction of the second central body 53 in particular. a comparison with figure ^ 2 makes clear, in which this embodiment differs from the construction of device 1. The second central body 53 is provided with three inserts 54 delimiting recesses ~ 1009754 16 55, which connect the outflow openings of the stator channels 18 to medium drains. 4, 5, 6. The recesses 55 are provided with current-conducting partitions, which, although have different shapes, are all conveniently indicated by reference number 56 for convenience. Due to this construction, a very calm swirl-free flow is also realized.

Figure 8 shows the stator 57 of Figure 7 from the other side.

Figure 10A shows part of a fifth exemplary embodiment. The stator 61 has a highly regular and symmetrical construction and differs in that from the embodiments which are particularly clearly drawn in Figures 2 and 7. In the embodiment according to Figure 10A, manifold channels 62 are formed in an analogous manner to the stator channels 18. The manifold channels 62 are delimited on the one hand by a surface 63 20 of a second central body 64 which tapers in the direction of discharge 4 and on the other hand by the inner surface of a housing (not shown). The channels 62 are separated from each other by separators 65. As shown, on average about 2.7 stator channels unite into one manifold-channel 62.

Figure 10B shows a variant of Figure 10A. The stator 61 'of Figure 10B differs from the embodiment of Figure 10A in that the channels 62' are separated from each other by a plane 63 'and partitions 30' of different shapes than the respective parts in the stator 61. The As a result, the medium throughput 93 'of Figure 10B has a larger passage than the medium throughput 93 of Figure 10A. The speed difference across channels 62 'is therefore smaller than the speed difference across channels 62. Under circumstances this may be desirable.

Figure 10C shows a further variant, in which the stator 61 '' comprises not only the relatively long partitions 19, 10, but also shorter partitions 19 'placed intertwined therewith. The effect of this will be explained with reference to Figures 10D, 10E and 10F below. Otherwise, the stator 61 '' substantially corresponds to the stator 61 '. It is pointed out that the lower end zones of the partitions 19 and 19 'are folded over.

This ensures a good streamline shape with increased stiffness, strength and erosion resistance.

Figure 10D shows the tangential distance between the adjacent partitions 19 and 19 'of Figure 10C and the partitions 19 of Figures 10A and 10B. The tangential distance is shown as a function of the axial position.

Curves I and II correspond to neighboring bulkheads.

Figure 10E relates to the embodiment 15 according to Figure IOC. The graph shows the channel width as'

function of the channel position. The influence of the interwoven placement of relatively long and relatively I is clear

short shots. This influence is recognizable by the jump in the graph. If this jump were not present, then; 20, the part indicated by II would flow smoothly to the part indicated by I, as a result of which the channel width in the region II would become substantially larger. This would greatly compromise the elongated nature of the stator channels and thereby affect the performance of the device 25 in question.

Figure 10F shows the included angle as a function of the channel position. A comparison with Figure 5F shows that, due to the choice of the interwoven arrangement of short and long partitions, the included angle which is 30 according to Figure 5F is almost 14 °, in the structure r according to Figure 10C is always smaller than 10 °.

Figure 11 shows a sixth embodiment.

The rotation device 66 comprises a rotor 67 with a number of rotor channels 68 bounded by sheet metal walls 35. This rotor may be formed by explosive deformation, by internal medium pressure, by a rubber press or other suitable known techniques. Manifold channels 69 are bounded by 1 µm O O A-18 by baffles 70 extending approximately helically in the drawn region.

Figure 12 shows how the spatially very complicated shaped stator blades 19 can be manufactured from respective strips of stainless steel.

Figure 12A shows very diagrammatically a mold 71 for forming a stator vane 19 from a flat strip of steel of a given length. The mold comprises two mold parts 72, 73 which are rotatable relative to each other and which, in a closed rotation position, face two towards each other. have interfaces, the shapes of which are substantially identical, which shapes correspond to the shape of a blade 19. The interface in question is located at the position indicated by 74, where in accordance with reality when forming a blade 19 such a blade is shown with the adjacent parts of the mold parts 72, 73 broken away. On the underside, the respective interface 75 is visible, which continues in accordance with the shape of the blade 19. Arrows 76 show the relative rotatability of mold parts 72, 73. Guide blocks 76, 77 serve as guidance of the mold parts 72, 73 during rotation. The said means for rotary driving of the mold parts 72, 73 are not shown.

In the open position of the die, not shown in Figure 12A, a straight stainless steel strip is inserted. This strip is completely flat and straight.

The mold parts are then rotated mutually, such that the molding surfaces approach each other. As a result, the strip engages while simultaneously deforming it. In this regard, reference is made to Figure 12B, where the co-operating mold parts 35, 72, 73 are shown. As will be apparent, mold part 73 has a recess 78 on its underside adjacent to support cylinder 77 corresponding to the flanged bottom edge 79 of strip 19, while at the top a '1000754' 1 19 similar recess 80 remains between the top surface of mold part 72 and mold part 73 when closing the mold cavity. The final closure of the mold cavity is determined solely by the thickness of the metal of blade 19. The recess 80 corresponds to the top flanged edge 81.

Figures 12C and 12D show an alternative device or die 871 for forming a stator vane 819 from a flat strip of steel 801 with the curved shape of certain length shown in Figure 12D. The die 871 includes two rotatable with respect to each other mold parts 872, 873, which in a closed rotational position have two mutually facing interfaces, the shapes of which are substantially identical, which shapes correspond to the shape of a blade 819.

The mutual rotation of said mold parts 872, 873 can take place by rotation of mold part 873 by means of handle 802, mold part 872 remaining stationary, because it is formed in one piece with a frame 803, which is attached to a worktop.

A second handle 804 is attached to a generally cylindrical element 805 which has a more or less triangular opening 806 which serves to place strip 801 and take out a shaped blade 819. By means of a keyway 807 matching key 808, the respective parts 805 and 814 are coupled together for rotation.

Said interfaces 810, 811 serve to impart to strip 801 the double-curved main shape, but without the flanged edges 812, 813 which serve to connect a blade deformation of a stator to respective cylindrical bodies. After this shape has been obtained by rotation by means of handle 802, the flanged edges 812, 813, 1 may be formed by a follow-up rotation by handle 804. During this follow-up rotation, the intended conversion of said edges takes place by rotation of central part 814, such as stated for rotation, 1009754 is coupled to element 805 and is provided with a turnover edge 815. A second turnover edge 816 is provided on the inside of element 805.

Thus, by a very simple operation 5 with the device 871, a blade 819 can be produced from the preformed metal strip 801.

It is noted that strip 801 is made by laser cutting. This provides a very accurate and chip and burr-free sheet metal element, 10 which is free from internal stresses. The narrowed end zone 820 can be bent in accordance with arrow 823 to the position indicated with 820 '. Thus, blade 819 is ready to serve as part of a stator. Such a stator is shown, for example, in Figure 13C.

Figure 13A shows a possible and very practical manufacturing method of rotor 8. It is assumed that saucer 36, upper saucer 37 and the rotor baffles 38, 39 to be fixed therebetween are to be placed therebetween (see also figure 9).

The exploded view according to Figure 13A also shows that the three-dimensionally formed partitions 38, 39 can accommodate chains of correspondingly shaped electricity and heat conducting blocks 82. These blocks are joined by wires 83 to 25, respectively, chains and can serve to conduct the current, which can be passed through a top electrode 84 and a bottom electrode 85 through tray 37, blocks 82, baffles 38, 39, bottom tray 36 and bottom electrode 85, respectively. guided by an electrical supply 86. By means of pressing means (not shown), the dish-shaped electrodes 84, 85, the respective shapes of which correspond to top dish 37 and bottom dish 36, respectively, are forcefully pressed together under corresponding pressure of said and in Figure 3A spaced apart parts. Profiled, like! areas 86 serving pressure points are disposed in top electrode 84. Corresponding zones 87 are in the: 1 0 ü ^ ..

21 bottom electrode fitted. During the passage of a sufficiently large current, a large current will be passed through the relevant flow path via the pressure zones 86, 87, which are registered with the partitions 38, 39.

As a result, effective spot welding of the partitions 38, 39 to dishes 36, 37 takes place. The copper blocks 82, for example, are essential for good current conduction without detrimental thermal effects on the partitions 38, 39. After a spot welding operation has thus been completed, the respective chains of blocks can be removed by pulling on the wires 83. After this operation, the rotor is in principle ready. As Fig. 1 shows, a mounting disc 90 can be welded to top plate 37. With cap 91 it forms the fastening of the rotor to shaft 7. The rotor according to figure 4 is provided with braces 35 after the spot welding operation as described above with reference to figure 13, after which shaft 37 is attached.

Figure 13B shows greatly simplified and with 1

Omitting a number of parts, an arrangement 830 for manufacturing a stator 831 as shown in Figure 13C. For an understanding of the arrangement of Figure 13B, reference is first made to Figure 13C. The stator 831 includes a cylindrical inner wall 832 and a cylindrical outer wall 833. This I.

walls in this exemplary embodiment are made of stainless steel. The outer wall 833 is relatively thick, while the inner wall 832 is relatively thin. The stator vanes 819 (see Figure 12) of relatively great length and the interlaced interposed vanes 819 'Τ'

of shorter length are placed in the desired position I

and with the flanged edges 812 and 813 are welded to inner wall 832 and

outer wall 833. It will be clear that the I

35 shapes of these flanged edges 812 and 813 must accurately match the respective cylindrical surfaces. The devices shown in Figure 12 are specially designed thereon.

22

Figure 13B, with the omission of cylinders 832, 833, shows an arrangement of equidistantly arranged chains of copper blocks, all of which are conveniently designated 834 and which have the shape shown in Figure 13D 5, corresponding to the shape of blades 819 and 819 ', respectively. . The blocks are mechanically connected to each other and electrically separated from each other by means of a lace 835. A rubber pad 836 has such a shape that the overall structure 1037, consisting of blocks 834, lace 835 and pad 836, fits snugly between the blades 819, 819 'of a stator 831. The blocks 834 have a general U shape . This allows the edges 812, 813 to be electrically conductive and thermally conductive connected to each other without the electrical conduction taking place through the center plate of a blade 819. Comparison of Figures 13B and 13C shows the relative placement of blocks 834 and blades 819, 819 '.

Figure 13B is shown simplified in that only the front group of chains 837 is shown, while, moreover, the cylindrical jackets 832, 833 are omitted for clarity. An outer electrode 838 is placed outside the outer jacket 833, while an inner electrode 832 is placed inside the inner jacket 832. These electrodes are adapted to simultaneously pass currents through spot welding zones, all of which are conveniently designated 840. For this purpose, the electrodes 838, 839 are connected to a current source 841. After arranging the blades 819, 819 'with intermediate placement of the chains 837 over the entire circumference with placement of both inner cylinder 832 and outer cylinder 833, the inner electrodes 839 and outer electrodes 838 are placed, after which the current passage is effected, which results in that at the 35 flow passage locations the flanged edges 812, 813 are spot welded to inner cylinder 832 and outer cylinder 833. Then, the respective - i! i. ^ V. t v_. ^ 23 chains 837 at the top with laces 835 pulled out of the structure, after which the stator 831 is ready.

Figure 14 shows a graphical representation of the efficiency "EFF" expressed as a percentage as a function of the relative flow rate Q of a prior art device, respectively (Graph I), as measured on a device of the type described above according to FIG. 1 (graph II) and finally according to figures 7, 8, 9, 10. It will be clear that the yield curve of the structure according to the invention is substantially higher than that according to the prior art and shows a considerably flatter course. In particular, the improvement at lower speeds is spectacular. This improvement 'T

15 states that one device can be used for many very diverse applications. In the prior art, different devices are often required for different applications.

Figure 15 also shows the performance of a = 20 device according to the invention operating as a pump. The graphs drawn in figure 15 refer to the pump pressure “

as a function of the flow rate of a device according to the invention, compared to an eight-stage standard I.

centrifugal pump with a dimensioning comparable to the dimensioning of the device according to the invention. The graph I indicated with circular measuring points concerns the measurement on a known pump NOVA PS i] 1874. The other graphs concern measurements on a pump according to the invention with the following speeds, respectively: 1500, 3000, 4000, 5000, 5500, 6000 revolutions a minute.

Figure 16 shows measurement results in a comparison between two types of pumps according to the invention and two types of pumps according to the prior art. Graphs I and II relate to a conventional type eight-stage centrifugal pump at 3000 rpm. Graph I concerns an inlet of ü 58mm while graph II concerns an inlet of 80mm.

1 00 37 5 4 24

The drawn graphs with the indications 1500, 3000, 4000, 5000, 6000 revolutions per minute, respectively, relate to a one-stage device according to the invention with a housing of 170mm diameter, a rotor diameter of 152mm and an inlet diameter of 38mm. The graphs drawn with broken lines also relate to a one-stage device according to the invention with a housing with a diameter of 170mm, a rotor diameter of 155mm, and an inlet diameter of 60mm.

The lines III and IV respectively indicate the respective cavitation limits of the first type of pump according to the invention as described and the second type of pump according to the invention as described.

From the foregoing it can be seen that the described new structure of a rotating device produces substantially better results than comparable known devices. With particular reference to Figures 15 and 16, it is again pointed out that the comparisons relate to a one-stage device according to the invention and an eight-stage device according to the prior art, i.e. eight in cascade-switched known rotary devices.

Figure 17 shows a unit 901 comprising a rotation device 902 and a motor 903. The unit is designed to operate as a pump. At the bottom there is a first medium feed 904 serving as an inlet and on the side there is the second medium feed 905 serving as a drain.

Figure 18 schematically shows the construction of the unit 901. Contrary to the embodiment according to, for example, figure 4, in which the unit consists of a | motor and an inseparably connected pump, unit 901 is composed of two separate 35 components. To this end, the motor shaft 906 has an outwardly tapering end with a conical thread 907 at the end, while rotor shaft 908 has a corresponding complementary shape. In this way, motor 903 and pump 902 are releasably coupled and transmitting forces, while nevertheless very easy releasability is assured. In particular the structure of a part of pump 902 5 will be further discussed below with reference to Figures 21 and 22.

Figure 19 shows, in exploded view, how the main constituent components are interconnected and interrelated. It is important to note that the top component 909 of pump 902, in which the stator is located, is constructed differently from the respective parts in the above-described and shown embodiments. Rotor 910 and input component 911 correspond to the previously described embodiments.

Figure 20 shows motor 903 with a coupling piece 912 at the bottom for coupling with a corresponding coupling sleeve 913 to output component 909.

Figures 21 and 22 show part 914 of I.

Output component 909. Part 914 includes a sheet metal funnel 915 with a central opening 916.

Current conductors are arranged in the funnel 915 against the wall, which are arranged in the manner shown in FIGS. 21 and although they have different shapes, but for convenience all are designated with reference numeral 917. The bulkheads 917 are members of one parametric family.

Inside the funnel 915 there is an inner funnel 918, also of sheet metal, such that the current conductivity partitions 917 are bounded by the respective funnels 915 and 918 and thus form current conducting channels 919. These current conduction channels 919 all end in outlet 905 _

and ensure a controlled flow pattern with very I.

35 low friction losses. The flow conductor baffles 917 may be constructed in a manner related to the manner in which the stator blades and / or the rotor baffles can be manufactured. With regard to 1009754 26 f κ to possible manufacturing methods, reference is made in this respect to Figures 12 and 13.

The structure of the unit 901 need not be discussed further. On the basis of discussion 5 of the preceding embodiments, both construction and operation will be clear.

Functionally, the current conduction channels 919 correspond to the manifold channels 62 and 62 'of Figures 10A and 10B, respectively. Contrary to FIG. 10, the structure of unit 903 is such that drain 905 extends to the side of unit 903. This simplifies the construction of the critical coupling between motor 903 and pump 902. It should be noted, however, that the design according to, for example, figures 1, 2 and 4 could also be used in this connection.

j 1009754

Claims (10)

1. U ƒ b 4 < 1 Lius i o? (curved or hybrid shaped outer surface (15) with a smooth shape, which together with an inner surface (16) of the housing (2) has a generally substantially rotationally symmetrical, for example cylindrical, medium passage space (17) with a radial dimension of at most 0 , 4x defines the radius of said outer surface (15), in which medium passage space (17) a number of angularly equidistant stator vanes (19) bounding pairwise stator channels (19) are accommodated, which stator vanes (19) are each attached to the rotor (8) directed end zone (20) forming a fifth medium throughput (24) have a direction substantially different, in particular at least 60 °, from the axial direction (21), and on their other one, a sixth) medium throughput (25 forming end zone (22) have a direction slightly deviating, in particular at most 15 °, from the axial direction (21); which fifth: medium flow medium passages (24) connect in substantially axial direction to the fourth medium passages 20 (11), and are arranged in substantially the same radial positions, and which sixth medium passages (25) communicate with the at least one second medium throughput (4) (5) (6); (c.2) a second central body, a number extending between the sixth medium passage (26) and the at least one second medium passage (4) (5) (6) in the direction from the sixth medium passages (26) to the at least one second medium passage (4) (5) (6) tapering, defined by the outer face (29) of the second central body 30 (23) and the cylindrical inner face (16) of the housing (2) ( 26) stretching; wherein a general medium flow path (27) is defined between the first medium throughput (3) and the at least one second medium throughput (4) (5) (6) through respectively the first medium throughput (3), the third medium throughputs (9), the rotor channels (10), the fourth media passages (11), the stator channels (18), the sixth media passages (25), the manifold channels (26), 1009754 the second media passages (4) (5) (6), and vice versa, with substantially smooth and continuous transitions between said parts during operation; and wherein the structure is such that during operation there is a mutual force coupling between the rotation of the rotor (8), and thus the rotation of the shaft (7), on the one hand, and the pressure in the said medium flow path (27). flowing medium. the method comprising the following steps to be performed in an appropriate order: i (a) providing a strip of sheet metal, for example of stainless steel; (b) bending the two longitudinal edge zones of a strip under plastic deformation such that the strip is provided with longitudinal edge zones extending at an angle, for instance at right angles, to the local main plane, which longitudinal edge zones correspond to the shapes of the respective surfaces to which the stator vane or rotor baffle 20 is to be substantially sealingly bonded. A method of manufacturing a stator vane or a rotor bulkhead for a rotary device (1), comprising: (a) a housing (2) with a central, substantially axial, first fluid passage (3) and at least one in: substantially axial second fluid passage (4) (5) (6); (b) one located in that house (2) and beyond that! housing shaft (2), which shaft is rotatably mounted with respect to that housing (2) and which carries a rotor (8), which is accommodated in that housing (2): which rotor (8) has a; central third medium throughput (9) connects to said first medium throughput (3), which third medium throughput: (9) branches into a number of angularly equidistant rotor channels (10), each of which extends in a respective at least ~ 15 radial major plane extending from the third medium pass (9) to a respective fourth medium pass (11), the end zone of the third medium pass (9) and the end zone of the fourth medium pass (11) each extending substantially axially and each rotor channel (10) has a curved shape, for example a general U shape or a general S shape, has a center part (12) extending in a direction with at least a significant radial component, and each rotor channel (10) 25 shows flow tube cross-sectional area, ie, a cross-section transverse to each local main direction, which increases in the direction from the third medium throughput to the fourth medium throughput from a relative value T 1 to a relative of at least 4.30 (c) a stator Ü (13) accommodated in that housing (2), comprising: (c.1) a first central body (14) which is a = substantially rotationally symmetrical, for example at least L more or less cylindrical, at least more or less conical, O Π Γι O fs / 1 2. Method as claimed in claim 1 for the manufacture of a stator vane, comprising step · ^ (c) spatially modeling shapes corresponding to the nominal shape of a stator vane by means of a mold with mutually rotatable molding surfaces of mutually rotatable one - strip into a blade. The method of claim 2, comprising - step 30 (d) performing steps (b) and (c) simultaneously. The method of claim 1, comprising - step (e) performing step (b) such that the two longitudinal edge zones extend in mutually opposite directions. Λ rs resume Λ "7 Γ * A Method according to claim 1, in particular for manufacturing a rotor bulkhead, comprising (f) performing step (b) such that the two longitudinal edge zones extend in equal directions. A method according to claim 5, performing the manufacture of a rotor, comprising the following steps to be performed in an appropriate order: (g) manufacturing the number of rotor blades required for a rotor according to step (f); (h) providing chains of wire interconnected blocks of heat and electric current conducting blocks that fit between the longitudinal edge zones without significant gaps; (i) placing such a chain in each blade; :: (j) positioning the vanes obtained in step (i) between a saucer and a top saucer; (k) providing a spot welding apparatus having a (k.1) top electrode having a plurality of blade impulse feed protrusions registered with the blades, which can be pressed against the top tray for flow through pressure means; (k.2) bottom electrode having a plurality of vane registered underflow feedout protrusions which can be pressed against the tray for current flow through the pressure means; (k.3) a power supply device for applying an electrical voltage between the upper electrode and the lower electrode during operation of the pressure means; (1) placing the mutually positioned parts i 'in step (j) in the welding device following step (j) and switching on and switching off the welding device after a selected time, such that by 100 0 7 -: flow through the flow through protrusions the upper longitudinal edge zone of a bulkhead with the top dish is connected by spot welding and the lower longitudinal edge zone with the lower dish is connected by spot welding; and (m) removing the finished rotor from the welder and removing the chains. A method according to claim 6, comprising step 10 (n) of performing the welding device such that the upstream feed-through protrusions and the underflow feed-through protrusions are mutually registered substantially axially. 8. Mold for manufacturing a stator vane by the method according to claim 2, comprising two mutually rotatable molding surfaces with equal shapes, corresponding to the nominal shape of a stator vane, for rotating the molding planes towards each other under enclosure 20 of a strip of sheet metal, for example of stainless steel, spatial modeling of a strip into: a blade. i 9. Stator vane or rotor baffle, manufactured by applying the method according to any one of claims 1, 2, 3, 4 or 5. 10. Rotor obtained by applying the I method according to any one of claims 6 or 7. ***** 1009754 I