EP1279834B1 - Vane pump - Google Patents

Abstract

The pump has a housing of cylinder (1) and cover (8A), and a rotor (3) with rotary slides. There is power introduction on at least one side of the rotor via a centering shaft section (13). The section forms part of a further cover element (8B) and is connected to the rotor via fastener elements, so that in extension of the drive shaft (7), a drive shaft (7') with second increased diameter (d2) is formed. A chamber (4) formed between drive shaft and internal rotor wall (21) is connected via channels (5) to the pump chamber (19) between two rotary slides.

Description

The invention relates to a rotary vane pump with the features mentioned in the preamble of claim 1.

Circulation pumps, including so-called rotary vane pumps or rotary vane pumps, are known.

Rotary vane pumps have a rotor which has substantially radially movable sealing slide. The seals are usually stored individually and are guided independently of each other in the rotor. The sealing slides are supported either by centrifugal forces or by springs, whereby they are pressed against a peripheral wall of a pump housing. It is also known to provide so-called inner curves or control rings, so that the sealing slides are forcibly guided on the outer circumference of the at least one control ring on the inner wall of the pump housing. In this case, the control ring can be arranged within a rotary vane pump rotor. The pressure and volume flow is effected by the chamber volume which forms between the sealing slides being used in the delivery area between inlet and outlet for increasing the pressure.

From the utility model 85 011 40 U1, for example, a rotary vane pump is known, which has a rotor arranged eccentrically in the cylinder, whose pivot vanes are received in axially parallel recesses of the rotor and applied under the action of centrifugal force and optionally by springs against the cylinder wall. In addition, the rotor has a number of channels when the pivot vanes are fully pivoted between the rotor and the fully pivoted pivot vanes.

From the prior art continues from the published patent application DE 40 12 789 A1 discloses a circulation pump of the type mentioned. The pump has a rotor with radially displaceable coupled sealing slides, which are guided in a hub displaceable. In doing so, the hub body and the sealing surfaces of the sealing slides seal in the sealing part between outlet and inlet and in the conveying area only the sealing slides. By suitable design of radii and curves as well as the sealing slide, a gentle pumping mode can be achieved.

Finally, US 3,361,076 also teaches a pump having a housing, a rotor and a stator assembly. The rotor has substantially radially displaceable wings to the axis of rotation. On one side there is a force input through a flange-like outlet of a rotor shaft into the rotor, wherein the flange-like outlet of the rotor is connected to a rotor main part, arranged in it with rotary slide-like elements, via fastening elements.

For the rotary vane pumps applies that the forces that transmit the rotary valve on the rotary valve rotor and thus on the drive shaft, are limited by the fact that the possible power consumption of the drive shaft is not exceeded. In particular, for the realization of small sizes of rotary vane pumps with high performance and delivery volume, which are achieved by arranging the slide with the largest possible effective slide area in the conveying range of the rotary vane pump and high speeds, the forces that can accommodate the drive shaft, achieved quickly. A disadvantage of the known solutions is that the effective slide surfaces can not be further increased on the one hand and thereby smaller speeds can not be adjusted in favor of gentle promotion of a pumped medium to achieve certain pressures and delivery volumes. Especially in versions of rotary vane pumps with eccentrically arranged drive shaft, the forces acting on the rotary vane rotor and thus on the rotary vane pump are distributed unfavorably. Desirable are low speeds with simultaneously high flow rates and delivery pressures, which would ensure energy-saving promotion of the rotary vane pump. These features, coupled with a particularly space-saving design, can not disclose the circulating pumps known from the prior art.

It is therefore an object of the present invention to provide a rotary vane pump, which allows it with their inventive features to realize very gentle pumping and minimal size very high discharge pressures and delivery volumes.

The rotary vane pump according to the invention with the features mentioned in claim 1 offers the advantage that on the one hand to realize a higher force input to the drive shaft on both sides of the rotary vane rotor force input by a Zentrierwellenteil takes place by the Zentrierwellenteil as Component of a second cover is connected via fasteners to the rotary valve rotor, which on both sides in extension of the drive shaft, a second diameter reinforced drive shaft is formed, and that on the other hand, to avoid a unilateral force input with force peaks a between the drive shaft and a Drehschieberrotor- Inner wall formed space is connected via at least one connecting channel with the pump space between each two rotary valves. This makes it possible in a simple manner, while maintaining the small size to realize a higher force input to the drive shaft.

The rotary vane pump according to the invention has the advantage that the space formed between the drive shaft and the rotary vane rotor inner wall is connected via at least one connecting channel with the pump space between two rotary valves, so that acting on the drive shaft force peaks balanced and unilaterally acting on the drive shaft forces on the entire circumference of the drive shaft are distributed.

It is particularly effective that the force input of the rotary valve rotor takes place on both sides via a Zentrierwellenteil as part of the second cover via fasteners with the rotary valve rotor, which is formed on both sides of a reinforced drive shaft. For this purpose, the centering shaft part has a centering bolt, which corresponds in the assembled state with a centering hole. The centering shaft part has at least one through hole for receiving a fastening element. The rotary valve rotor has threaded holes corresponding to the through holes. The Zentrierwellenteil is thus connected to the rotary valve rotor via the at least one fastening element which engages over the through hole of the Zentrierwellenteils in the at least one threaded bore of the rotary valve rotor.

In the embodiment according to the invention, the centering shaft part engages with its centering pin in the centering hole of a pump rotor axis part of the drive shaft.
As a result, the centering shaft part has a reinforced drive shaft with the second diameter, which is larger than a first diameter of a non-amplified drive shaft according to the prior art.

In a preferred embodiment of the invention, the connecting channels between the space formed by the drive shaft and a rotary valve rotor inner wall and a pump space are arranged substantially radially to the axis of rotation of the rotary slide rotor. Between this space and the pump chamber, the connecting channels according to the method according to the invention cause a partial flow to be branched off from a main flow and this partial flow makes it possible to operate the rotary slide in the direction of a running surface of a cylinder of the pump. The rotary valves are controllable by the centrifugal forces and a pressure difference between the space inside the rotary valve rotor and the pump chamber.

By this preferred solution can be dispensed with arranged control rings for positive control of the rotary valve alternatively in an embodiment of the invention.

Further preferred embodiments of the invention will become apparent from the remaining, mentioned in the dependent claims characteristics.

Figur 1

einen Schnitt in einer Draufsicht auf eine Drehschieberpumpe in bisheriger und neuer Ausführung und

Figur 2

einen Schnitt A-A in einer Seitenansicht.

The invention will be explained in more detail in an embodiment with reference to the accompanying drawings. Show it:

FIG. 1

a section in a plan view of a rotary vane pump in previous and new design and

FIG. 2

a section AA in a side view.

FIG. 1 shows a rotary vane pump 10 in an upper illustration and a lower illustration. The upper illustration shows the rotary vane pump 10 in an older version with a first cover element 8A according to the prior art and the lower illustration shows the new solution with a new second cover element 8B.

The housing of the rotary vane pump 10 has hitherto been designed so that a cylinder 1 was closed on both sides with the first cover 8A. According to FIG. 1, the solution according to the invention consists, on the one hand, in the rotary vane pump 10 on both sides with the second cover element 8B and a centering shaft part 13 according to the invention, which is part of the second Cover element is to close. For clarity, Figure 1 shows the previous (top) and the inventive solution (bottom view).

In the rotary valve pump 10, a rotary valve rotor 3 is arranged, which is rotatable about an eccentric axis of rotation 20 in both directions. The rotary valve rotor 3 has a pump rotor shaft part 15, which merges into a drive shaft 7. The drive shaft 7 previously had a first diameter d1. Figure 1 also shows that the rotary valve rotor 3 via its pump rotor shaft part 15 on the one hand in the first previous cover 8A and on the other hand (lower illustration) via a centering hole 16 centered on a centering pin 14 is arranged. The centering hole 16 and the centering pin 14 correspond to each other and are preferably connected to each other in a fitting connection.
The centering pin 14 belongs to the centering shaft part 13, which forms in extension of the drive shaft 7 an extended, reinforced drive shaft 7 'with a second diameter d2. The power transmission of the rotary valve rotor 3 is effected by the Zentrierwellenteil 13 characterized in that in the centering shaft 13 through holes 23 for fastening elements 24, preferably threaded screws are. In the rotary valve rotor 3 corresponding threaded holes 6 are arranged. By screw the rotary valve rotor 3 is connected to the centering shaft 13. Thus, a power flow over this connection can be realized. The centering shaft part 13 thus forms the reinforced drive shaft 7 '.

As is further apparent from Figure 1, the drive shaft 7 ', which, as already mentioned above, on the Zentrierwellenteil 13 and the second cover 8 B is carried out on both sides of the rotary valve rotor 3, the larger second diameter d2. This second diameter d2 is for example 18 mm. The drive shaft 7 'can also be performed in the second diameter d2 with 20 mm or 25 mm and more. The first diameter d1 is for example only 12 mm. At a first diameter d1 and high pressures, for example 20 bar, a simple reinforcement by increasing the diameter d1 of the drive shaft 7 without centering shaft part 13 is no longer sufficiently stable enough. The solution according to the invention is therefore used especially for higher pressures.

The centering shaft part 13 is covered with respect to the cylinder 1 with the second cover member 8B and forms a guide 25 for the amplified drive shaft 7 '.

The figures also show the arrangement of connecting channels 5 in the rotary valve rotor 3 on the other. Through the connecting channels 5, a pressure distribution in the housing of the rotary vane pump 10 can be effected. The forces acting on the drive shaft 7 and 7 'are uniformed and force peaks are compensated. It does not come to a unilateral force entry into the drive shaft 7 or 7 '. Fatigue fractures and one-sided high wear are avoided.

Furthermore, the connecting channels 5 have a further significance, which is apparent in particular from FIG. 2 and which will be discussed later.

Figure 1 shows first between the drive shaft 7 and rotary valve rotor inner wall 21, a first space 4A and a second space 4B. Alternatively, a first control ring 9A and a second control ring 9B may be disposed in the first and second spaces 4A and 4B, respectively. By the first control ring 9A and the second control ring 9B is a forced control of rotary valves 18, which are not shown in Figure 1.

FIG. 1 furthermore shows the pump space 19 between a rotary valve rotor outer wall 17 and a running surface 2 of the cylinder 1.

The pump space 19 and the first space 4A and a second space 4B are connected to each other via the connection channels 5. Therefore, a pressure equalization takes place here via the connecting channels 5.

Figure 2 shows a section A-A through the rotary vane pump 10. The same reference numerals denote the same parts as in Figure 1.

FIG. 2 shows an inlet 11 and an outlet 12 on both sides, since the rotary vane pump 10 can be operated selectively in both directions about the axis of rotation 20.

Also visible is the cylinder 1, in which offset by 90 ° to the drive shaft 7, the inlet 11 and the outlet 12 are arranged. Also visible is the centering pin 14 in the centering hole 16 of the drive shaft 7. On the drive shaft 7, the second control ring 9B can be seen. The control ring 9A is located behind the control ring 9B and is not visible in FIG. The second control ring 9B runs on the eccentric rotation axis 20 on the drive shaft 7 in the space 4B. The space 4B is connected to the pumping space 19 and the inlet area 11 and the outlet area 12 via the connection channels 5. The rotary valve 18 are movably guided in hubs 22 in the rotary valve rotor 3.

Between two rotary valves 18, the pump space 19 is formed between the rotary valve rotor outer wall 17 and the running surface 2 of the cylinder 1.

Also visible are the threaded holes 6 in the rotary valve rotor 3 on which - as Figure 1 shows - is fastened by means of the fastening elements 24 of the centering shaft 13 via its through holes 23 and the power flow to the reinforced drive shaft 7 'is redirected.

The operation of the rotary vane pump 10 is explained according to the figure 2 following. When using the first and second control rings 9A and 9B, the rotary valves 18 are pushed out of the rotary valve rotor 3 mechanically, so that the pump chamber 19 is formed. In the upper part of the rotary valve 18 are pressed by the eccentric axis of rotation 20 on the tread 2 of the cylinder 1 in the rotary valve rotor 3. In the arrangement of the connecting channels 5 also takes place a pressure equalization between the first and second spaces 4A and 4B. In addition, a partial flow TS of a main flow HS is pressed into the first and second spaces 4A and 4B.

By this mode of action takes place on the one hand, a relief of the drive shaft 7 and on the other hand is given the opportunity to actuate the rotary valve 18 in the direction of the tread 2 of the cylinder 1. The mode of operation can be realized without the first and second control rings 9A and 9B when connecting channels 5 are arranged.

Alternatively, if the first and second control rings 9A and 9B are omitted, the connection channels 5 alone allow the actuation of the rotary valves 18.

As a result of the pressure building up in the pumping chamber 19, the rotary valves 18 are pressed outward in the direction of the first and second chambers 4A and 4B in addition to the centrifugal forces acting. The partial flow TS will flow into the interior of the rotary valve rotor 3 in the first and second spaces 4A and 4B. In the region of lower pressures, for example in the inlet region 11, a partial flow TS will flow from the first and second chambers 4A and 4B into the region between rotary valve rotor outer wall 17 and cylinder 1 as a function of a pressure difference.

The volume flow of the partial flow TS is also dependent on a diameter of the connecting channels. 5

By the inventive solution of the second cover 8B with the centering shaft 13 and the connecting channels 5 higher forces on the drive shaft 7 and the rotary valve rotor 3 can be realized on the one hand. On the other hand, as mentioned above, the control rings 9A and 9B are dispensed with.

The rotary vane pump can be used for the following branches of industry. It is used in the chemical industry for alkalis, gases and viscous liquids. In the food industry, for example, it can be used as a honey, mustard, jam and syrup pump. In addition, there is a field of application in the field of medical technology as a metering pump and in the fire department as a spray pump. For disaster relief, the rotary vane pump can be used for pumping off used oil at sea or for pumping out floods during floods. Further uses arise in agriculture and environmental technology for irrigating fields or as a pressure booster for a photovoltaic system. These areas of application are only examples and can be extended as desired for other areas.

LIST OF REFERENCE NUMBERS

1

cylinder

2

tread

3

Rotary vane rotor

4

Room (for control rings)

4A

first room

4B

second room

5

Connection channels (flow holes)

6

threaded bore holes

7

drive shaft

7 '

reinforced drive shaft

8th

cover

8A

first cover element

8B

second cover element

9

control ring

9A

first tax ring

9B

second tax ring

10

Rotary vane pump

11

inlet

12

outlet

13

centering shaft

14

centering

15

Pump rotor axis part

16

centering

17

Rotary vane rotor outer wall

18

Rotary valve (lamella slider)

19

pump chamber

20

axis of rotation

21

Rotary vane rotor inner wall

22

hub

23

Through Hole

24

fasteners

25

guide

d1

first diameter

d2

second diameter

HS

main power

TS

partial flow

Claims (21)

1. A vane pump (10) which comprises a housing consisting of a cylinder (1) and cover elements (8A) with a rotary vane rotor (3) which is supported in the housing on both sides via a drive shaft (7) designed in a first diameter (d1), in which controllable rotary vanes (18) are arranged which are displaceable essentially radially to a rotational axis (20), which form a pump area (19) between an inlet (11) and an outlet (12) and a rotary vane rotor outer wall (17) and the housing, characterized in that in order on the one hand to realise a higher force application onto the drive shaft (7) on both sides of the rotary vane rotor (3), a force is applied using a centring shaft piece (13), whereby the centring shaft piece (13) is connected as an integral part of a second cover element (8B) via fastening elements (24) with the rotary vane rotor (3), as a result of which on both sides in an extension of the drive shaft (7), a reinforced drive shaft (7') is formed in a second diameter (d2), while on the other hand, in order to avoid a single-sided force application with force peaks, an area (4) which is formed between the drive shaft (7) and a rotary vane rotor inner wall (21) is connected via at least one connection channel (5) with the pump area (19) in each case between two rotary vanes (18).
2. A vane pump (10) according to claim 1, characterized in that the centring shaft piece (13) comprises a centring pin (14) which when mounted corresponds with a centring hole (16).
3. A vane pump (10) according to claim 2, characterized in that the centring shaft piece (13) comprises at least one through hole (23).
4. A vane pump (10) according to claim 1, characterized in that the rotary vane rotor (3) comprises threaded bore holes (6).
5. A vane pump (10) according to claims 1, 3 and 4, characterized in that at least one fastening element (24) engages with the at least one threaded bore hole (6) of the rotary vane rotor (3) via the through hole (23) of the centring shaft piece (13).
6. A vane pump (10) according to claim 2, characterized in that the centring shaft piece (13) engages with its centring pin (14) in the centring hole (16) of a pump rotational axis part (15) of the drive shaft (7).
7. A vane pump (10) according to claim 1, characterized in that the centring shaft piece (13) comprises a reinforced drive shaft (7') with a second diameter (d2), which is larger than the first diameter (d1).
8. A vane pump (10) according to claim 1, characterized in that the second cover (8B) comprises a guide (25).
9. A vane pump (10) according to claims 7 and 8, characterized in that the second cover (8B) and the centring shaft piece (13) close the cylinder (1) while surrounding the drive shaft (7') using the guide (25).
10. A vane pump (10) according to claim 1, characterized in that the at least one connection channel (5) is a through-flow hole.
11. A vane pump (10) according to claims 1 and 10, characterized in that the connection channel (5) is arranged essentially radially to the rotational axis (20) of the rotary vane rotor (3).
12. A vane pump (10) according to claim 1, characterized in that between the drive shaft (7) and the rotary vane rotor inner wall (21), a first area (4A) and a second area (4B) are arranged.
13. A vane pump (10) according to claim 1 and claims 10 to 12, characterized in that the rotary vanes (18) are controllable via the centrifugal force acting on the rotary vanes (18) and a differential pressure between the area (4A) and/or the area (4B) and the pump area (19).
14. A vane pump (10) according to claim 10, characterized in that between the drive shaft (7) and the rotary vane rotor inner wall (21), the first area (4A) is arranged with a first control ring (9A) and/or the second area (4B) is arranged with a second control ring (9B).
15. A vane pump (10) according to claims 10 and 14, characterized in that the rotary vanes (18) are controllable via the first and/or the second control rings (9A) and/or (9B) which act on the rotary vanes (18).
16. A vane pump (10) according to claim 13 and/or 14, characterized in that the rotary vanes (18) in the pump area (19) lie on a running surface (2).
17. A vane pump (10) according to claims 1 to 16, characterized in that from a main supply current (HS), a branch current (TS) is diverted and this branch current (TS) causes the actuation of the rotary vanes (18) in the direction of the running surface (2) of a cylinder (1) of the pump.
18. A vane pump according to claim 17, characterized in that the branch current (TS) is guided from one pump area (19) via at least one connection channel (5) to an area (4) inside a rotary vane rotor (3) to the rotary vanes (18).
19. A vane pump according to claims 17 and 18, characterized in that via the at least one connection channel (5) a pressure compensation is conducted between the at least one area (4) and the pump area (19).
20. A vane pump according to claims 17 to 19, characterized in that a specific current volume is diverted as a branch current (TS) depending on a differential pressure between the at least one area (4) and the pump area (19).
21. A vane pump according to claims 17 to 20, characterized in that a specific current volume is diverted as a branch current (TS) depending on a diameter of the at least one connecting element (5).

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