Rotary piston pump, method for fixing rotary pistons of a rotary piston pump and method for dismantling rotary pistons of a rotary piston pump

Abstract

A method for fixing rotary pistons in a rotary piston pump and a method for dismantling rotary pistons of a rotary piston pump, where the rotary piston pump has two counter-rotating rotary arranged in a pump space on drive shafts. The rotary pistons each include a seating for the drive shafts. The respective drive shaft is arranged and fixed with an end region in the seating of the respective rotary piston. A diameter of the drive shafts in the end region can be widened elastically. In an operational state, in which the rotary pistons are arranged on the respective drive shafts, a frictional connection is formed between the respective seating of the rotary piston and the end region of the respective drive shaft.

Claims

1. A rotary piston pump comprising: at least two counter-rotating rotary pistons arranged in a pump space on drive shafts, wherein each rotary piston comprises a seating and wherein each drive shaft has an end region that is arranged and fixed in the seating of the respective rotary piston, wherein a diameter of each drive shaft in the end region is configured to be widened elastically, and wherein in an operational state, in which the rotary pistons are arranged on the respective drive shafts, a frictional connection or a frictional and form-fit connection is formed between the respective seating of the rotary piston and the end region of the respective drive shaft in response to the diameter of the respective drive shaft being widened, so that a power transmission takes place in a play-free manner.

2. The rotary piston pump according to claim 1, wherein at least one of the rotary pistons includes a gripping device that fixes the rotary piston by means of a frictional connection to the respective drive shaft, the gripping device being disposed at at least one of the end region of the respective drive shaft or the seating of the rotary piston.

3. The rotary piston pump according to claim 2, wherein the gripping device comprises at least one of size-variable hydraulic elements or size-variable pneumatic elements, or wherein the gripping device comprises mechanical elements.

4. The rotary piston pump according to claim 2, wherein each drive shaft is constituted as a hollow shaft with a continuous hollow space with a first inner diameter (d2) along a respective longitudinal axis (L), wherein the hollow space in the end region of the respective drive shaft in the pump space has a widened cross-section with at least one second inner diameter (d3), wherein the at least one second inner diameter (d3) is greater than the first inner diameter (d2).

5. The rotary piston pump according to claim 4, wherein each drive shaft has a first outer diameter (d1) along the respective longitudinal axis (L), wherein the gripping device is configured to widen or enlarge the first outer diameter (d1) in the end region arranged in the pump space.

6. The rotary piston pump according to claim 4, wherein a tool for acting on the gripping device is insertable through the continuous hollow space along the respective longitudinal axis (L) of the drive shafts.

7. The rotary piston pump according to claim 2, wherein the gripping device is a clamping device.

8. A method for fixing at least two counter-rotating rotary pistons to respectively assigned drive shafts in a pump space of a rotary piston pump, the method comprising: pushing the rotary pistons onto free end regions of the respective drive shafts arranged in the pump space; aligning the rotary pistons on the respective drive shafts; widening the end regions of the drive shafts to produce a frictional connection between a seating of the rotary piston and the end region of the respective drive shaft for fixing the rotary piston.

9. The method according to claim 8, wherein the widening of the end region of the respective drive shaft takes place by means of a gripping device assigned to at least one of the end region of the respective drive shaft or the seating of the rotary piston.

10. The method according to claim 9, wherein the gripping device comprises at least one of hydraulic elements or pneumatic elements, wherein the end region of the respective drive shaft is widened inside the seating of the rotary piston by filling at least one of a hydraulic fluid or a gas into the gripping device.

11. The method according to claim 9, wherein the gripping device comprises mechanical elements in the form of conical elements, wherein the end region of the respective drive shaft is widened by displacing the conical elements at least one of in the region of the seating of the rotary piston or inside the end region of the drive shaft arranged in the pump space inside the seating of the rotary piston.

12. The method according to claim 9, wherein the gripping device is adjusted by means of a tool in such a way that an outer diameter (d1) of the end region of the respective drive shaft arranged in the pump space is widened inside the seating of the rotary piston by means of the gripping device and the end region of the drive shaft is clamped detachably inside the seating of the rotary piston.

13. The method according to claim 12, wherein the tool is insertable through a hollow space along a respective longitudinal axis (L) of the respective drive shaft to the gripping device.

14. The method according to claim 9, wherein the gripping device is a clamping device.

15. The method according to claim 8, wherein the rotary piston is fixed to the respective drive shaft by adjusting the gripping device, so that torques and axial forces are transmitted play-free from the respective drive shaft into the rotary piston.

16. The method according to claim 8, wherein a diameter of each drive shaft in the end region is configured to be widened elastically and wherein in an operational state, in which the rotary pistons are arranged on the respective drive shafts, the frictional connection is formed between the respective seating of the rotary piston and the end region of the respective drive shaft, so that a power transmission takes place in a play-free manner.

17. A method for dismantling at least two counter-rotating rotary pistons of a rotary piston pump, the rotary pistons being arranged in a pump space on drive shafts, wherein each rotary piston includes a seating and wherein each drive shaft has an end region that is arranged and fixed in the seating of the respective rotary piston, wherein an outer diameter of each drive shaft in the end region is configured to be widened elastically, and wherein in an operational state, in which the rotary pistons are arranged on the respective drive shafts, a frictional connection or a frictional and form-fit connection is formed between the respective seating of the rotary piston and the end region of the respective drive shaft in response to the diameter of the respective drive shaft being widened, so that a power transmission takes place in a play-free manner, the method comprising: releasing the frictional connection between the seating of the rotary piston and the end region of the drive shaft by reducing the outer diameter of the end region of the drive shaft removing the rotary piston from the respective drive shaft.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Examples of embodiment of the invention and its advantages are explained in greater detail below with the aid of the appended figures. The size ratios of the individual elements with respect to one another in the figures do not always correspond to the actual size ratios, since some forms are represented simplified and other forms magnified compared with other elements for the sake of better clarity.

(2) FIG. 1 shows a diagrammatic view of a rotary piston pump according to the known prior art.

(3) FIG. 2 shows a first embodiment of a fastening device for fastening a rotary piston on a drive shaft.

(4) FIG. 3 shows a cross-sectional representation of the first embodiment of the fastening of the rotary piston to a drive shaft according to FIG. 2 along a cross-sectional line A-A.

(5) FIG. 4 shows a second embodiment of a fastening device for fastening a rotary piston on a drive shaft.

(6) FIG. 5 shows a third embodiment of a fastening device for fastening a rotary piston on a drive shaft.

DETAILED DESCRIPTION

(7) Identical reference numbers are used for identical or identically acting elements of the invention. Furthermore, for the sake of a clearer view, only reference numbers are represented in the individual figures that are required for the description of the respective figure. The represented embodiments only represent examples as to how the device according to the invention or the method according to the invention can be constituted and do not represent a conclusive limitation.

(8) FIG. 1 shows a diagrammatic view of a rotary piston pump 1 with two rotary pistons 8, 9 according to the known prior art. A motor 3 is arranged on a machine stand. This motor drives two drive shafts 6, 7 in opposite directions. Rotary pistons 8, 9 are arranged respectively on the drive shafts in a pump housing 4, said rotary pistons being driven via drive shafts 6, 7 and rotating simultaneously and in opposite directions around the axes of drive shafts 6, 7. During the rotation of rotary pistons 8, 9, there is always contact between rotary pistons 8, 9 and pump housing 4 of rotary piston pump 1. The product to be delivered is sucked through pump chambers 5 thus being formed, conveyed in transport direction TR through rotary piston pump 1 and expelled at the opposite side of the pump. Seals (not represented) are arranged on drive shafts 6, 7 in order to seal the pump space with respect to the surroundings.

(9) FIG. 2 shows a first partial view of a first embodiment of a rotary piston pump 30 constituted according to the invention with a fastening of a rotary piston 24 on a specially constituted drive shaft 10 and FIG. 3 shows a cross-sectional representation of the first embodiment of the fastening of a rotary piston 24 on a drive shaft 10 according to FIG. 2 along a cross-sectional line A-A.

(10) In the region of the passage of drive shaft 10 through pump housing 4, an installation space 20 is provided for slip-ring seals 22 or other suitable sealing elements for sealing the pump space with respect to the surroundings. Rotary piston 24 is arranged on end region 12 of drive shaft 10 that lies opposite to the drive side of drive shaft 10. In particular, a seating 25 with a circular cross-section for the seating of drive shafts 10 is provided on rotary piston 24. The fastening of rotary piston 24 to drive shaft 10 takes place with the aid of a gripping device 15 assigned to end region 12 of drive shaft 10.

(11) The drive shaft 10 is constituted as a so-called hollow shaft 11. In particular, a first hollow space 13 extends along longitudinal axis L of drive shaft 10. Hollow shaft 11 has an outer diameter d1 over its entire length. Furthermore, hollow shaft 11 has in sections a first inner diameter d2, which defines first hollow space 13.

(12) The drive shaft 10 is constituted in a more slender form in end region 12, i.e. in the region in which rotary piston 24 sits via seating 25 on drive shaft 10. In particular, a second widened hollow space 14 with a second inner diameter d3 is provided in end region 12 of drive shaft 10. It is the case that outer diameter d1 of drive shaft 10 is greater than second inner diameter d3 of widened, second hollow space 14 in end region 12 of drive shaft 10 and the latter is in turn greater than first inner diameter d2 of first hollow space 13 along longitudinal axis L of drive shaft 10.

(13) As a result of the widening of second hollow space 14 in end region 12 of drive shaft 10, wall thickness W12 in this region is smaller than general wall thickness W10 of drive shaft 10. In particular, general wall thickness W10 is calculated from 0.5 times the difference between outer diameter d1 and first inner diameter d2:
W10=0.5*(d1d2).

(14) Resultant wall thickness W12 in end region 12 of drive shaft 10 is calculated from 0.5 times the difference between outer diameter d1 and second inner diameter d3:
W12=0.5*(d1d3).

(15) Seating 25 of rotary piston 24 has an inner diameter which largely corresponds to outer diameter d1 of drive shaft 10, in particular the inner diameter of seating 25 is slightly greater than outer diameter d1, so that rotary piston 24 sits with a small amount of play on end region 12 of drive shaft 10.

(16) On account of reduced wall thickness W12 of drive shaft 10, it is possible to press drive shaft 10 in end region 12 from the inside outwards against seating 25 of rotary piston 24. This leads to a non-rotatable fixing of drive shaft 10 in seating 25 of rotary piston 24. It is thus possible to transmit torques and axial forces play-free from drive shaft 10 into rotary piston 24.

(17) The gripping of rotary piston 24 at end region 12 of drive shaft 10 can take place in various ways. Examples of this are represented in FIGS. 2 to 5. Conical elements can for example be inserted into drive shaft 10 (see FIGS. 4 and 5), or hydraulic and/or pneumatic elements (see FIGS. 2 and 3) can also be used.

(18) According to the represented embodiment, rotary piston 24 is closed at side 26 facing away from drive shaft 10. Rotary piston 24 is preferably pushed onto drive shaft 10, so that end region 12 of drive shaft 10 is seated at least partially in seating 25 of rotary piston 24.

(19) The installation of rotary piston 24 in rotary piston pump 30 according to the invention takes place in the following process steps according to a preferred embodiment of the invention: a slip-ring seal 22 is first pushed in each case onto drive shafts 10, a rotary piston 24 then being pushed in each case onto drive shafts 10. Rotary pistons 24 are aligned. For this purpose, use is made for example of a template similar to the prior art described in DE 102012003066 B3 and in DE 102013101185 A1. A tool is then introduced through hollow space 13 from the drive side of drive shafts 10 and rotary pistons 24 are fixed to respective shaft 10 by tightening up/screwing down gripping device 15.

(20) According to an embodiment of the invention, gripping device 15 is arranged in seating 25 of rotary piston 24. When rotary piston 24 is pushed onto drive shaft 10, gripping device 15 is pushed into second, widened hollow space 14 of end region 12 of drive shaft 10.

(21) According to an alternative embodiment, gripping device 15 is arranged in second, widened hollow space 14 of end region 12 of drive shaft 10, so that rotary piston 24 is simultaneously pushed onto drive shaft 10 and gripping device 15.

(22) FIG. 4 shows a second embodiment of a fastening device for fastening a rotary piston (not represented) on a drive shaft 10b. Provision is made here such that widened hollow space 14b in end region 12b widens conically in the direction of the rotary piston. Gripping means 15b is constituted as a cone or truncated cone 35, wherein the cross-section of cone or truncated cone 35 tapers away from the rotary piston. Cone or truncated cone 35 has an outer diameter dB in the region of its bottom face 36, which is at least slightly greater than greatest inner diameter d3max of widened hollow space 14b. For the fixing of the rotary piston (not represented) to drive shaft 10b, truncated cone 36 is pushed or drawn, with the aid of a suitable tool, farther into widened hollow space 14b of drive shaft 10. This leads to a widening of outer diameter d1 (see FIG. 2) of drive shaft 10b and therefore to gripping of rotary piston 24 in seating 25 (see FIG. 2).

(23) FIG. 5 shows a third embodiment of a fastening device for fastening a rotary piston 24c on a drive shaft 10c of a rotary piston pump 30c. Gripping means 15c is formed here from a conical element 40 incorporated in drive shaft 10c and a corresponding conical seating 28 arranged inside seating 25c of rotary piston 24c.

(24) When rotary piston 24c is pushed onto drive shaft 10c, conical seating 28 is pushed onto conical element 40 arranged in widened hollow space 14 of end region 12 of drive shaft 10.

(25) Rotary piston 24c is drawn, with the aid of a suitable tool, farther onto drive shaft 10c for the fixing of rotary piston 24c on drive shaft 10c. Truncated cone 40 is thus pushed farther into conical seating 28. This leads to an at least partial splaying of conical seating 28. As a result of a transfer of the splaying forces to the wall of drive shaft 10c in end region 12 with reduced wall thickness W12, the widening of outer diameter d1 (see FIG. 2) of drive shaft 10c is brought about in this region and drive shaft 10c is thus gripped in seating 25c of rotary piston 24c (see also FIG. 2).

(26) The invention has been described by reference to a preferred embodiment. It is however conceivable for the person skilled in the art that modifications or changes to the invention can be made without departing from the scope of protection of the following claims.