EP1721078A1

EP1721078A1 - Rotary pump provided with an axially movable blade

Info

Publication number: EP1721078A1
Application number: EP04802973A
Authority: EP
Inventors: Manfred Sommer
Original assignee: Individual
Current assignee: Individual
Priority date: 2004-01-09
Filing date: 2004-12-21
Publication date: 2006-11-15
Also published as: WO2005066498A1; EP1714037A1; EP1714035A1; US7614863B2; DE112004002793A5; DE112004002792A5; US20070148027A1; WO2005066499A1; DE112004002789A5; WO2005066496A1; WO2005066497A1; EP1714036A1; EP1714038A1; WO2005066501A1; DE112004002794A5; DE112004002788A5; DE112004002786A5; EP1714036B1; WO2005066500A1

Abstract

The invention relates to a pump (10) comprising a rotor (70) whose collar (120) laterally describes a pump channel (124) provided with an input (152) and an output. An axially adjustable sealing disc (182) is tightly placed on two sides of the rotor collar (120) in an axial direction and divides the pump channel (124) into the input (152) and the output. A first bearing for a drive shaft (60) is axially arranged in the clear space occupied by the rotor (70) and makes it possible to axially support said drive shaft.

Description

ROTARY PISTON PUMP WITH AXIAL MOVABLE LEAF

TECHNICAL AREA

The invention relates to a pump designed as a positive displacement pump or a rotary lobe pump. The main areas of application for pumps of this type which are viscous and viscous are found in the chemical, pharmaceutical and food processing industries.

STATE OF THE ART

From DE 34 18 708 AI a pump of the type mentioned is known. This pump has a rotor which is rotatably mounted on a drive shaft which can be connected to a motor drive. The rotor has a radially protruding, rotating shaft collar. The pump inlet and outlet are separate. The inlet communicates with an intake space and the outlet with an outlet space. These two pump rooms are connected to each other via a pump channel. By means of a sealing slide which is adjustable in the axial direction and which bears sealingly on both sides of the rotor collar in the axial direction, it is ensured that the medium conveyed from the inlet to the outlet by the pump channel cannot flow back past the sealing slide back to the inlet. The sealing slide must therefore continuously bear tightly on both sides of the rotor collar during the rotary movement of the rotor. Adequate sealing must also be present between the rotor collar and the walls of the pump channel that delimit it in the axial direction if the pumping action and thus the efficiency of the pump are not to be impaired. In this pump, the drive shaft driving the rotor extends far into the pump chamber. Their bearing points are located on the one hand in the area of the rear housing wall and on the other outside the pump housing in a hollow cylindrical shaft carrier flanged to the rear wall of the pump housing. The rotor is thus seated on the collar end area of the drive shaft. Due to the inevitable deflections of the collar end area of the drive shaft, the higher the higher the working pressures with which the pump is operated, correspondingly large tolerances between the rotating parts, such as the rotor collar, and the non-rotating parts, such as the channel walls framing the pump channel laterally, are taken into account in order to avoid undesirably high wear of parts rubbing against one another.

PRESENTATION OF THE INVENTION

Based on this known prior art, the invention has for its object to provide a pump of the type mentioned, which can be operated economically, especially with high working pressures.

This invention is given by the features of the main claim. Useful further developments of the invention are the subject of further claims following the main claim.

The pump according to the invention is characterized in that a bearing point for the drive shaft is present within the clearance area occupied by the rotor in the axial direction. The drive shaft no longer projects freely into the pump chamber, but is supported in the radial direction within the clearance area occupied by the rotor in the axial direction or preferably in the clearance area occupied by the rotor collar in the axial direction. The extremely large deflections that have to be considered constructively in the prior art at correspondingly high working pressures no longer occur. This means that the bearing designs of the drive shaft and the design of the drive shaft itself no longer have to be dimensioned to such an extent that the deflections in the cantilever region of the drive shaft become correspondingly small. The bearing point for the drive shaft located within the pump housing has the further advantage that the overall length of the pump is considerably shorter compared to the previously known pump; the externally flanged-on hollow cylindrical shaft support according to the prior art, on the end of which is further away from the pump housing, a bearing point for the drive shaft can now be dispensed with. The drive shaft can be adequately supported in the area of the rear wall of the pump and within the clearance profile taken up by the rotor or its rotor collar in the axial direction. The bearing point for the drive shaft inside the pump housing can be realized according to the exemplary embodiments also shown in the drawing by a hollow cylindrical shaft support which projects freely into the interior of the pump from the rear region. The shaft support can be designed to be sufficiently rigid so that the unavoidable deflections at its collar end are of no importance for the practical operation of the pump. For the rotor and its rotor collar, which is arranged in a rotationally fixed manner on the collar end region of the shaft carrier, it is therefore possible constructively to assume a bearing which is practically fixed in the axial direction. Such a pump not only builds much shorter than the pump known above in the prior art, but can also be operated with comparatively higher working pressures.

As already mentioned, the rotor collar must lie as close as possible to the fixed wall areas delimiting the pump channel in the axial direction in order to enable a correspondingly high efficiency of the pumps. In order to prevent wear of the building walls and the rotor by stringing them together, it is known to line the pump channel with replaceable wear parts, so-called stators. Existing deflections of the drive shaft, as are present in the prior art, make it necessary to maintain tolerances between the rotor and the stator which must be so large that the rotor does not touch the stator when the pump is under maximum load. To a certain extent, one helps by using plastic material for the stator, so that when it is touched by the rotor made of steel, there is no material removal from steel to steel. This problem is all the greater, the greater the deflection of the drive shaft. With these tolerances to be observed, it must also be taken into account in this connection that the different plastics expand to different extents under the influence of heat. Now such pumps are usually cleaned at temperatures that are 100 degrees Celsius and above, so that corresponding expansion tolerances of the respective plastics must be taken into account when designing the pump, so that it is ensured that the rotors are free even at high temperatures Pump room can rotate. The problem within the tolerances to be observed is decisively influenced by the existing deflections of the drive shaft and thus the rotor sitting on it; if the tolerances are too large, the efficiency of the pump drops sharply. With the pump according to the invention, it is therefore no longer necessary to use more powerful pumps to avoid the above problems; Pumps that are not operated at full capacity have correspondingly smaller deflections, so that the tolerance problem is more favorable. Such larger pumps, which would not be required from the operational point of view, increase the operating costs of such a pump.

Due to the drive shaft forming a freely projecting structural part together with the shaft support, the rotor can encompass the drive shaft and also the shaft support at the end in the manner of an end cap. This then allows simple assembly and disassembly of the rotor, in that the rotor can be axially pushed onto the drive shaft in a rotationally fixed manner and can be held axially immovably on the drive shaft, for example by means of a retaining or locking nut.

The bearing point of the drive shaft can be formed on the inside of the shaft carrier. An additional bearing point for the rotor can be formed on the outside of the shaft carrier opposite thereto, provided that the cap wall of the rotor is not sufficiently rigid that the rotationally fixed bearing point of the rotor on the drive shaft is sufficient.

According to an embodiment shown in the drawing, it is also possible to arrange the bearing for the drive shaft on the outside of the shaft carrier. This bearing point can then be used simultaneously as a bearing point acting in the axial direction for the rotor or for its cap area. In this case, the drive shaft attaches to the shaft carrier from the outside via the rotor.

The respective bearing point for the drive shaft and for the rotor, which is provided in the collar end region of the shaft carrier, if the latter is provided in addition to the rotationally fixed bearing of the rotor, can be arranged in the same axial cross-sectional plane.

In order to make bearings as slim as possible, each bearing point can consist of several bearings lying side by side in the axial direction. In addition to this first bearing point described above, which is present within the pump housing, a second bearing point for the drive shaft can be present in the region of the rear wall of the pump adjacent to the motor drive. In the case of very light pump designs, this second bearing point could also be dispensed with and the drive shaft could only be mounted in the area of the motor drive.

It has proven to be advantageous to attach the pump housing to a bearing bracket in such a way that the pump housing can be attached to it in different rotational positions. In this way, the inlet and the outlet can be optimally spatially adapted to the corresponding local conditions even in the case of a circular cylindrical outer contour of the pump housing. Such a bearing chair can have a holding flange to which the pump housing can be screwed, for example, in the desired rotational position. The drive shaft then penetrates this holding flange and ends in the pump housing.

The second bearing point for the drive shaft, which is already available as an alternative, can then be provided in the holding flange.

As an alternative to this, this second bearing point could also be provided in the rear wall of the pump housing.

The shaft support projecting freely into the pump housing can be attached to the rear wall of the pump housing or also to the holding flange in a rigid manner. The shaft carrier, which in this case is not a part of the pump housing by weight, does not have to be taken into account by weight when the pump housing is removed from the holding flange.

In order to prevent the bearing oil of these bearings from leaking and contaminating the interior of the pump after the pump has been opened and the rotor has been axially withdrawn from its bearings, such as the radial bearings described above, these bearings can be coated with a bushing. Such a bush remains as an assembled structural part when dismantling the rotor on the bearing or bearings and reliably seals the same unchanged. By means of a ventilation groove molded into the sleeve wall or axially through the sleeve wall ventilation holes through it can facilitate the assembly and disassembly of the sleeve.

Further advantages and features of the invention can be found in the features further specified in the claims and in the exemplary embodiments below.

BRIEF DESCRIPTION OF THE DRAWING

The invention is described and explained in more detail below with reference to the exemplary embodiments shown in the drawing. Show it:

1 is a vertical longitudinal section through a first embodiment of a pump according to the invention,

2 shows a vertical longitudinal section through a second embodiment of a pump according to the invention,

3 shows a vertical longitudinal section through a third embodiment of a pump according to the invention,

Fig. 4 is a vertical longitudinal section through a fourth embodiment of an inventive pump, with axially pulled apart individual components of the pump.

WAYS OF CARRYING OUT THE INVENTION

The pump 10 shown in FIG. 1 is screwed to the rear flange 14 of its housing 12 by means of screws 16 on the holding flange 18 of a bearing block 20. The housing 12 is designed to be rotationally symmetrical about its axis 22, with the rear wall 14 which is circular in plan and a circular cylindrical jacket wall 24 which is integrally connected to the rear wall 14.

A cover 28, which closes the housing 12 in the axial direction, bears against the left end wall 26 of the casing wall 24 in FIG. 1. The cover 28 is attached to a plurality of studs distributed circumferentially on the cover 28, only two of which are shown in FIG. 1 with their stud screw axis 30 the rear wall 14 screwed. The studs lead through the interior of the housing 12. Of the stud bolts, the respective ring nut 34 screwed on the outside is shown in FIG. 1. Between the end face 26 of the jacket wall 24 and the cover 28, an O-ring 36 is inserted in an annular groove running around the cover 28, which ensures the required tightness.

The inner wall of the jacket wall 24 can be slightly conical in the shape of a circular cylinder or for the purpose of easier shaping when producing the one-piece piece consisting of the rear wall 14 and the jacket wall 24.

The thread sections present at the two ends of the stud screw are smaller in diameter than the diameter of the stud screw shaft present in the interior of the housing 12, so that each stud screw which screws the cover 28 and the rear wall 14 together fix the cover 28 and the rear wall 14 in a mutual manner Keeps distance from each other.

The bearing chair 20 has a footplate 38, which is connected to it at right angles in the present example and by means of which the housing 12 and thus the pump 10 can be set up on a base 40. This base 40 can also be a structural part that can be oriented as desired in space, because for example by means of a screw connection, of which two screw axes 42 are shown, the base plate 38 and thus the entire bearing bracket 20 can be releasably fixed to said base 40.

A hollow cylindrical shaft support 50, the cylinder axis of which coincides with the axis 22, protrudes through the rear wall 14 into the interior of the housing 12. The shaft support 50 is attached to the retaining flange by means of an end flange 52 by means of a plurality of screws 54, which are accessible from the outside and distributed over the circumference 18 attached. The shaft carrier 50 is constructed in terms of material and cross section such that its collar end region ending in the housing 12 has practically no deflection under load, at least one deflection which is negligible for the operation of the pump 10.

A drive shaft 60 protrudes centrally through the shaft support 50. The right end of the drive shaft 60 in FIG. 1 is rotationally fixed by means of a feather key 62 on the driven shaft of a motor, not shown in the drawing Drive can be connected so that the drive shaft 60 can be driven in both directions of rotation.

A rotor 70 is fixed in a rotationally fixed manner to the collar end 64 of the drive shaft 60 which ends in the rear space of the housing 12. The rotor 70 is - based on FIG. 1 - pushed from the left onto the collar end 64 of the drive shaft 60 and held in its fixed, rotationally fixed position by means of a lock nut 66 screwed onto the end of the drive shaft 60. The locking nut 66 lies sealed against the end wall 72 of the rotor 70 via an O-ring 68.

The rotor 70 has a rotor hub 74 which has a central recess pointing towards the rear wall 14, so that the rotor hub 74 in the form of a cap engages around the collar end region 76 of the drive shaft 60 from the outside at a distance. The collar end region 76 is adjoined in the direction of the projecting end of the drive shaft 60 by the collar end 64 and by this the screw region for the locking nut 66.

A tapered roller bearing 80 or inclined roller bearing is formed between the drive shaft 60 and the shaft carrier 50 in the collar end region 76. This tapered roller bearing 80 can absorb radial, in particular, also axial forces. Such forces acting on the rotor 70 can be transmitted or removed via its rotor hub 74 and via the drive shaft 60 to the shaft carrier 50 and ultimately to the bearing block 20. The tapered roller bearing 80 thus forms an existing bearing point in the interior of the housing 12 for the drive shaft 60, since the tapered roller bearing 80 is practically fixed in position in the housing 12 due to its support on the shaft support 50. The drive shaft 60 is thus supported in the region of the tapered roller bearing 80.

The tapered roller bearing 80 is held on the left in FIG. 1 by a shoulder widening 82 of the drive shaft 60 and on the opposite right side by an axially supported bearing inner ring 84 seated in a shaft groove. Radially on the outside, the tapered roller bearing 80 is held in a fixed position between a support ring 86 screwed onto the end of the shaft support 50 and a recess 88 formed in the shaft support 50. For the purpose of sealing, a shaft sealing ring 90 is arranged on the outside of the support ring 86, which sealingly rests on the shoulder widening 82.

On the outside of the shaft carrier 50 opposite the tapered roller bearing 80, a radial needle bearing 92 is arranged between the shaft carrier 50 and the rotor hub 74. The rotor hub 74 is also supported on the shaft carrier 50 via this needle bearing 92. This bearing 92 is - with reference to FIG. 1 - sealed on its left side by a shaft sealing ring 94, which is present between the rotor hub 74 and the shaft carrier 50. On its opposite side - based on FIG. 1 - on the right-hand side, a radial seal bearing 100 is connected to the radial needle bearing 92.

This sealing ring receptacle 100 lies against the inside of the rotor hub 74 in a rotationally fixed manner. The end face of the sealing ring receptacle 100, which has a rotationally symmetrical cross section, projects through the rear wall 14. In the event of a leak, a sharp edge 104 facing away from the wall end area 102 ensures that the medium escaping from the shaft support 50 emerges from the area of the sealing ring receptacle 100. This leakage medium enters an intermediate space 106 formed between the rear wall 14 and the holding flange 18, from which it can exit to the outside via openings formed in the holding flange 18 and not shown in the drawing.

A shaft sealing ring 110 is supported on a radially projecting shoulder 108 of the sealing ring receptacle 100 and rests sealingly on the outside of the shaft carrier 50. Together with the shaft sealing ring 94, it seals the radial needle bearing 92 on both sides in the axial direction.

In the area of the holding flange 18 there is another bearing between the drive shaft 60 and the shaft carrier 50 in the form of a ball bearing 114. This ball bearing 114 is sealed off from the outside of the holding flange 18 by means of a shaft sealing ring 116, which in turn is held by a screw ring 118 screwed onto the holding flange 18 from the outside.

In the configuration shown in FIG. 1, the tapered roller bearings 80 and the radial needle bearing 92 are arranged in the same cross-sectional plane 112. This cross-sectional plane 112 lies within the axial region of the rotor hub 74 and, moreover, also in the axial cross-sectional region of the rotor collar 120 integrally formed on the rotor hub 74.

This rotor collar 120 has a circumferential wave-like shape, as is described in detail in DE 34 18 708 A1 already mentioned above with respect to the prior art.

In the lower area of the housing 12 there is a pump channel 124 within which the rotor collar 120 moves back and forth in the axial direction when the drive shaft 60 rotates. The pump channel 124 is framed by a stator 130, which is composed of two stator halves 132, 134. In the present example, the two stator halves 132, 134 are identical in cross-section and lie closely together via a common contact surface 136. The two stator halves 132, 134 are kept pressed in between the cover 28 and the rear wall 14. The stud screws already mentioned above, which hold the cover 28 at a fixed position on the rear wall 14, also pass through the stator 130 or through its two stator halves 132, 134, outside the pump channel 124.

The cover 28 has a central, circularly projecting cover area 138. A rotationally symmetrical front sleeve 140 is partially seated in the inner arch formed thereby. This front sleeve 140 is held screwed to the cover 28 or to its central cover area 138 via screws 142 accessible from the outside. The front sleeve 140 surrounds the end of the rotor hub 74 at a distance and the locking nut 66 screwed onto the drive shaft 60. In the present case, its inner wall 144 is curved, without sharp edges, so that it can be cleaned easily. The front sleeve 140 is sealed off from the cover 28 or the rotor hub 74 and the left stator half 132 by means of O-rings 146, 148 fitted all round in the front sleeve 140.

The top side of the front sleeve 140, based on FIG. 1, forms the bottom of the intake space or the outlet space 150, via which the pump channel 124 is connected on the one hand to the inlet 152 and on the other hand to the outlet of the pumps 10. The longitudinal axes 154 of the inlet 152 and the outlet are at right angles to one another in the present example. Aligned to the top of the front sleeve 140 is on the

- With reference to Fig. 1 - right side of the rotor hub 74, a retaining ring 160 is positioned with its top. With its upper side, this retaining ring 160, like the front sleeve 140, forms the bottom of the intake space or the outlet space 150.

The retaining ring 160 represents the sealing bottom area of the suction space or the outlet space 150 between the rotor hub 74 and the rear wall 14 of the housing 12. In the present example, between the rotor hub 74 and the retaining ring 160 there are two axially and radially offset, co-rotating with the rotor hub 74 Fit sliding rings 164, 166. Stationary sliding rings 165 and 167, respectively, press against these sliding rings 164, 166. These latter slide rings 165, 167 are pressed against the slide ring 164 and 166 by spring rings 168 and 170, respectively, which are supported on the rear on radially projecting shoulders 172 and 174 of the retaining ring 160.

The retaining ring 160 is fastened to the rear wall 14 by means of screws 176 arranged around the circumference.

The slide rings 165, 167 can be made of any suitable material, such as, for example, in particular also of ceramic material. The rotating seal rings 164, 166 can in particular consist of metallic material.

The seals formed from the two sliding rings 164, 165 and 166, 167 can both be arranged in the axial direction in any mutual orientation.

The suction space and the outlet space 150 are separated from one another in terms of pressure by a slide guide 162, which represents a sealed shut-off plate between these two spaces. On the sliding guide 162, a sealing slide 182 bears back and forth in the axial direction. The sealing slide 182 is arranged in the outlet space 150, so that due to the pressure prevailing there, which is greater than the pressure prevailing in the suction space, it bears tightly against the slide guide 162 during its back and forth movement. In the sealing slide 182 there is a central opening 184 which is open at the bottom the rotor collar 120 is present. During its rotating movement, the rotor collar 120 lies with its two collar walls on the side in the axial direction, of which one side wall 186 is visible in FIG. 1. This design principle is also described in detail in the aforementioned DE 34 18 708 AI.

The sealing slide 182 is held on its opposite side to the slide guide 162 by structural parts, not shown in the drawing, which are fixedly connected to the housing 12, so that the sealing slide 182, even when fallen compared to the illustration in FIG. 1, on the retaining flange 18 screwed rotary positions maintains its tight position on the slide guide 162 and does not fall away from the slide guide 162, for example in the circumferential direction. The slide guide 162 can be fixed in position, for example, by one of the stud bolts shown with its axis 30 between the cover 28 and the rear wall 14.

A plurality of leak drains 190 protrude from the rear wall 14 into the intermediate space 106 distributed over the circumference. These hose- or tube-shaped leak drains 190 connect the individual bearing spaces to one another via longitudinal and transverse bores (not shown in the drawing) which are formed in the shaft support 50, so that they are to be used for lubricating these bearings.

The pump 10.2 shown in FIG. 2 is basically constructed like the pump 10 described above. Its tapered roller bearing 80 and radial needle bearing 92 also lie in the same axial cross-sectional plane 112, which lies within the clearance area occupied by the rotor collar 120 in the axial direction. The additional bearing in the area of the holding flange 18.2, which in the present example also represents an auxiliary bearing for the drive shaft 60.2 designed as a ball bearing 114, is now provided with a retaining ring 118.2 which holds the shaft seal 116 axially instead of the screw ring 118 of the pump 10 and which is held by means of screws 117 is held screwed to the shaft support 50.2.

As further differences from the pump 10, the cover 28.2 of the pump 10.2 is flat on the outside and its rear wall 14.2 is designed without the cross-sectional reinforcement present in the lower region of the rear wall 14. The retaining ring 160.2, which corresponds to the retaining ring 160, has a slightly different cross-sectional shape than the retaining ring 160 due to the different spatial conditions to the pump 10. Its function is the same as that of the retaining ring 160; Via two slide rings 165.2, 167.2, which are pushed away in the axial direction by spring rings, it bears sealingly against sealing rings 164.2 and 166.2, which are molded in the rotor hub 74.2.

The tapered roller bearing 80 is supported on its radial inside instead of the bearing inner ring 84 present in the pump 10 by a screw ring 84.2.

The intermediate space 106 is connected to the individual bearings via the leak drains 190 and transverse and longitudinal bores 196, 198, so that bearings can be provided with oil lubrication on the one hand, and corresponding media in the intermediate space 106 from leaks and from there not through in the drawing shown openings in the holding flange 18 or 18.2 can flow out of the pump 10 or 10.2.

In the pump 10.3 shown in FIG. 3, which is also basically functional like the pumps 10 and 10.2, there are two radial needle bearings 200, 202 in the axial collar end region 76.3 of the drive shaft 60.3, specifically on the outside of the shaft carrier 50.3. The cross-sectional planes 112.2, 112.3, which are centered on the respective bearing 200, 202, in turn lie within the clearance area occupied by the rotor collar 120.3 in the axial direction. In this construction, the rotor hub 74.3 is designed to be sufficiently rigid so that the loads acting on the rotor hub 74.3 during operation of the pump 10.3 and thus on the drive shaft 60.3 via the collar end region 64.3 can be introduced into the shaft carrier 50.3. The drive shaft 60.3 is, as it were, suspended from the shaft support 50.3 via the rigid rotor 74.3. With this construction, which should be preferred for high-performance pumps working at high pressures in particular, the height of the tapered roller bearing 80 (FIGS. 1 and 2) existing between the shaft carrier and the drive shaft would be gained. This height can be used due to the stronger design of the shaft support and the drive shaft in the stronger pump. In order to absorb axial forces acting on the drive shaft 60, the bearing present in the region of the flange 52.3 of the shaft carrier 50.3 is designed as a tapered roller bearing 210. This tapered roller bearing is sealed on its axial side facing the rotor by a shaft sealing ring 203 held axially in a radial recess. On its opposite axial side, the tapered roller bearing 210 is held immovably by a screw ring 204 on the drive shaft 60.3. On the outside of the screw ring 204, a retaining ring 206 is held screwed to the flange 52.3 of the shaft carrier 50.3 from the outside by means of screws 117. On the inside, in an annular recess provided there, a shaft sealing ring 208 is seated in the retaining ring 206, which together with the shaft sealing ring 203 seals the tapered roller bearing 210 on both sides in the axial direction.

The flange 52.3 of the shaft carrier 50.3 could be screwed to a bearing bracket or to the holding flange of a bearing bracket 20. However, it is also possible to use the flange 52.3 of the shaft support 50.3 as the holding flange 18 and - for example detachably - to fasten it to a footplate corresponding to the footplate 38 or to another structural part.

The pump 10.4 shown in FIG. 4 also basically works in the same way as the pumps 10, 10.2 and 10.3 mentioned above. Thus, the pump 10.4 has a pot-like housing 12.4, which can be closed by a cover 28.4 on its left side in FIG. 4, as has already been explained for the pumps described above. In its rear wall 14.4 axially opposite the cover 28.4 there is again a central opening through which a shaft support 50.4 with the drive shaft 60.4 mounted on it and with the retaining ring 160.4 fastened to it by means of screws 176 is pushed freely projecting into the interior of the housing 12.4 from the outside and can be screwed onto the rear wall 14.4 by means of screws 16.

The radial needle bearings 200 and 202 described in the above pumps are not present in the pump 10.4 between the shaft carrier 50.4 and the rotor 70.4, as is the case with the pump 10.3, for example, but these two radial needle bearings 200, 202 are covered with a sleeve 220. This bushing 220 has a central opening in its bottom region 222 on the left in FIG. 4 so that it can be pushed onto the drive shaft 60.4 from the right as far as the position shown in FIG. 4, based on FIG. 4. After the sleeve 220 has been pushed on, it is held by a nut 228 screwed onto the drive shaft 60.4. Then the shaft carrier 50.4 with the radial needle bearings 200, 202 is pushed onto the drive shaft 60.4 from the same direction. In the assembled state, the bottom region 222 of the sleeve 220 and thus the sleeve 220 are fixed in position with an annular recess 223 between the collar end 64.4 of the drive shaft 60.4 and the nut 228.

The right end of the bushing 220 in FIG. 4 has a flange 224, in which two slide rings 164.4, 166.4 are fitted radially one above the other. These two slide rings 164.4, 166.4 abut two slide rings 165.4 and 167.4, respectively, which are also embedded in the retaining ring 160.4. These slide rings correspond to the corresponding slide rings present between the retaining ring and the rotor in the above pumps. In the pump 10.4, these sliding rings are not present between the rotor 70.4 and the retaining ring 160.4, but between the bushing 220 present in the pump 10.4 and the retaining ring 160.4 in a comparable manner.

On the circular cylindrical outer surface 226 of the sleeve 220, the circular cylindrical inside of the rotor hub 74.4 of the rotor 70.4 - with the rotor 70.4 pushed onto the sleeve 220 - bears practically no play. The existing play between the rotor 70.4 and the sleeve 220 is only necessary in order to be able to push the rotor 70.4 onto the sleeve 220 or to be able to pull it off again.

In order to facilitate or facilitate this assembly or disassembly of the rotor 70.4, ventilation channels are provided in the rotor 70.4. In the embodiment variant shown in FIG. 4, there is both an air groove 230 which extends helically on the inside of the rotor hub 74.4 and air bores 232 which pass axially through the end wall 72.4 of the rotor hub 74.4. Only one embodiment of these two ventilation ducts (the air groove 230 and the air bores 232) needs to be provided. An O-ring 68.4 is countersunk in the end wall 72.4 of the rotor hub 74.4 in such a way that it circumferentially frames the air bores 232 radially from the outside. The locking nut 66 screwed onto the head 234 of the drive shaft 60.4 in the assembled state lies sealingly against the O-ring 68.4. As a result, the air bores 232 are sealed off by the locking nut 66 in the assembled state of the pump 10.4.

The shaft support 50.4 can, as already described for the pumps above, be screwed onto the rear wall 14.4 by means of screws 16. The structural part which can be pulled off the rear wall 14.4 by loosening the screws 16 is shown partially pulled out to the right in the axial direction in FIG. 4.

The rotor collar 120.4 of the rotor 70.4 present in the interior of the pump 10.4 is shown with an axially central region. Furthermore, two axial end positions of the collar 120.4 are shown in dash-dot lines with the reference numbers 120.4a and 120.4b. The rotor collar 120.4 is always sealingly in an opening of the sealing slide 182 in the axial direction, right and left, as has also been described above.

In the pump 10.4 there is also a front sleeve 140 between the end wall 72.4 and the cover 28.4. The radial outside of the front sleeve 140, together with the rotor hub 74.4 and the outer surface 226 of the sleeve 220 and the outer surface of the retaining ring 160.4, represents the bottom of the suction space or the outlet space, via which the pump channel on the one hand with the inlet 152 and on the other hand with the one shown in FIG. 4 outlet (not shown) of the pumps 10.4 is connected in each case.

Claims

Expectations

01. Pump (10, 10.2, 10.3, 10.4) - with a rotor (70, 70.4), which is non-rotatably present on a drive shaft (60, 60.2, 60.3, 60.4) which can be connected to a motor drive and which has a radially protruding, undulating shape encircling rotor collar (120, 120.3, 120.4), - with the rotor collar in the axial direction delimiting on both sides, a pump channel (124) between free boundary surfaces, - with an inlet (152) and an outlet for the pump channel (124), - with an adjustable sealing slide (182), which adjoins the rotor collar (120, 120.3, 120.4) in the axial direction and seals the pump channel (124) between the inlet (152) and the outlet, - characterized in that - inside of the clearance area occupied by the rotor (70, 70.4) in the axial direction, there is a first bearing point for the drive shaft (60, 60.2, 60.3, 60.4) for supporting the drive shaft in the radial direction.

02. Pump according to claim 1, - characterized in that - this first bearing point has at least one bearing (80, 200, 202) which is present within the clearance area occupied by the rotor collar (120, 120.3) in the axial direction.

03. Pump according to one of the preceding claims, characterized in that - from the direction of the outer wall of the pump adjacent to the motor drive, a sleeve-shaped shaft carrier (50, 50.2, 50.3, carrying the drive shaft (60, 60.2, 60.3, 60.4), 50.4) is present, - this first bearing point for the drive shaft is present in the collar end region (76, 76.3) of the shaft carrier.

04. Pump according to claim 3, - characterized in that - the rotor (70, 70.4) in the collar end (64, 64.3) of the drive shaft (60, 60.2, 60.3, 60.4) is rotatably fixed, - the rotor (70, 70.4) is rotatably mounted in the manner of an end cap on the shaft support (50, 50.2, 50.3, 50.4).

05. Pump according to claim 3 or 4, - characterized in that - on the inside of the shaft support (50, 50.2) the first bearing for the drive shaft (60, 60.2) of the rotor and on the opposite outside of the shaft support (50, 50.2 ) there is a bearing for the rotor (70) for supporting the rotor in the axial direction.

06. Pump according to claim 5, - characterized in that - the existing in the collar end region (76, 76.3) of the shaft carrier first bearing point for the drive shaft and the bearing point for the rotor are present in the same axial cross-sectional plane (112).

07. Pump according to claim 4, - characterized in that - on the outside of the shaft carrier (50.3, 50.4) the first bearing point for the drive shaft (60.3, 60.4) is present, - this bearing point is also a bearing point for the rotor for supporting bearings of the rotor in the axial direction.

08. Pump according to one of the preceding claims, - characterized in that - the first bearing point consists of several bearings (200, 202).

09. Pump according to one of the preceding claims, - characterized in that - a second bearing point for the drive shaft (60, 60.2, 60.3, 60.4) is present in the region of the outer wall of the pump adjacent to the motor drive, - this second bearing point at least for supporting purposes Bearing the drive shaft is formed in the radial direction.

10. Pump according to one of the preceding claims, - characterized in that - it has a pump housing (12) and a bearing bracket (20) carrying the same, - the pump housing (12) with its axial rear wall (14, 14.2) on a holding flange ( 18, 18.2) of the bearing bracket (20) is releasably attached.

11. Pump according to claim 10, - characterized in that - the drive shaft (60, 60.2) penetrates the retaining flange (18, 18.2) and ends in the pump housing (12).

12. Pump according to claim 11, - characterized in that - a bearing for the drive shaft is present in the holding flange.

13. Pump according to one of claims 10 to 12, - characterized in that - the pump housing (12) in different rotational positions on the holding flange (18, 18.2) can be fastened, such as in particular screwed.

14. Pump according to one of claims 4 to 13, - characterized in that - the drive shaft (60, 60.2) for the rotor (70) in itself and in the pump housing (12) projecting shaft support (50, 50.2) on the Holding flange (18, 18.2) of the bearing bracket (20) can be fastened.

15. Pump according to one of the preceding claims, - characterized in that - the pump housing (12) on a flange (52.3) of the shaft support (50.3) can be screwed on, in particular in different rotational positions.

16. Pump according to one of the preceding claims, - characterized in that - a sleeve (220) on the inside of the rotor hub (74.4) of the rotor (70.4) is present in such a way that - the sleeve (220) of each after removal of the rotor Bearings (200, 202) freely accessible from the drive shaft are sealed.

17. Pump according to claim 16, - characterized in that - the sleeve (220) is rotatably mounted on the drive shaft (60.4).

18. Pump according to claim 16 or 17, - characterized in that - at least one ventilation channel (230, 232) is present in the rotor hub (74.4), through which when the rotor (70.4) is pushed onto the sleeve (220) or at Pulling the rotor from the bushing can allow air to flow.

19. Pump according to claim 18, - characterized in that - at least one vent hole (232) is provided in the end wall region (72.4) of the rotor hub (74.4) as a vent channel.

20. Pump according to claim 18, - characterized in that - as a ventilation channel, a ventilation groove (230) is molded into the inside of the rotor hub (74.4).

21. Pump according to claim 20, - characterized in that - the ventilation groove (230) is helical.

22. Pump according to one of the preceding claims, - characterized in that - the retaining ring (160.4) is sealed in the axial direction with respect to the sleeve (220).

23. Pump according to claim 22, - characterized in that - at least one slide ring (164.4, 166.4) is provided in the bushing (220), which can be pressed in the axial direction against at least one slide ring (165.4, 167.4) present in the retaining ring is.