DE102010028061A1 - Vane pump - Google Patents

Abstract

The invention relates to a vane pump 1 with a pump housing 26 and a rotor 10, which is arranged in a cavity 27 of the pump housing 26 along an axis of rotation 21, the pump housing 26 comprising a first end face 30, on the opposite a second end face 31 of the rotor 10 is arranged, wherein a device 24, 25 is arranged on the first end face 30 of the pump housing 26 and / or on the second end face 31 of the rotor 10, the device 24, 25 by a rotation of the rotor 10 about the axis of rotation 21 a pressure between the first end face 30 of the pump housing 26 and the second end face 31 of the rotor 10 builds up.

Description

The invention relates to a vane pump with a pump housing and a rotor which is arranged in a cavity of the pump housing along a rotation axis, wherein the pump housing comprises a first end face on which a second end face of the rotor is arranged opposite.

State of the art

From the DE 10 2008 059 981 A1 is a controllable vane pump known. The vane pump includes a cylindrical pump housing defining an inner cylindrical cavity. The pump housing includes an inlet port and an outlet port. Arranged on an axis offset from the axis of the inner cylindrical cavity is a rotor. The pump rotor is cylindrical and includes a plurality of axially extending and radially oriented narrow slots that freely slidably receive and retain a like plurality of blades. The vanes are held in close contact with the surface of the inner cylindrical cavity by a centrifugal force as the pump rotor rotates. The rotor of the vane pump is axially supported by the fact that the end faces of the rotor abut against the opposite surfaces of the cavity of the pump housing.

It is the object of the invention to provide an improved vane pump.

Disclosure of the invention

This object is achieved by a vane pump according to claim 1. Preferred embodiments of the invention are indicated in the dependent claims.

According to the invention, it has been recognized that an improved vane pump can be provided in that the vane pump comprises a device on a first end face of the pump housing and / or on a second end face, the pressure between the first end face of the pump housing by rotation of the rotor about an axis of rotation and the second end face of the rotor builds. In this way, a friction of the rotor on an inner wall of the pump housing can be avoided, so that simply the efficiency of the vane pump is increased. Furthermore, this reduces wear on the rotor and / or on the pump housing.

In a further embodiment of the invention, the device has at least one surface structure which is designed such that a distance between a surface of the surface structure and the opposite end surface decreases in the direction of rotation. In this way, simply a pressure between the end faces of the rotor and the pump housing can be constructed so that the two end faces of the pump housing and the rotor do not rub against each other.

In a further embodiment of the invention, the device comprises at least one compression groove, which is arranged obliquely to the rotational direction of the rotor. In this way, a pressure between the end faces of the rotor and the pump housing can also be generated, which prevents the rotor from grinding on an inner wall of the pump housing.

In a further embodiment of the invention, the rotor on a peripheral side to the rotation axis aligned slots, in each of which a wing is arranged, wherein disposed between the slots at least a first Verdichtungsnut and a second Verdichtungsnut. The first compression groove extends in the direction of the axis of rotation of the rotor and the second compression groove in the direction of the slot. In this case, a wall is arranged at one end of the second compression groove, which delimits the second compression groove of the slot. In this way, the surface on which the pressure acts against the end face of the pump housing, can be easily increased, so as to avoid tilting of the rotor in the storage.

In a further embodiment of the invention, the compression groove is formed spirally in the direction of the axis of rotation. The helical formation allows the provision of a high pressure between the two end faces of the pump housing and the rotor.

In a further embodiment of the invention, the compression groove is bounded radially on the outside and / or inside by a further wall. In this way, the pressure generated by the compression groove can be reliably distributed over the end face of the rotor by limiting the compression groove.

In a further embodiment of the invention, the compression groove has a first region and a second region, wherein the second regions are helical and converge towards one another and meet in a third region. In this way, tilting of the rotor is avoided by a radially further outward pressure build-up.

In a further embodiment of the invention, the surface structure is convex in the direction of rotation. This way will streamlined increases the pressure between the end face of the rotor and the end face of the pump housing.

In a further embodiment of the invention, the surface structure comprises at least a first and a second stage, wherein the first stage and the second stage are arranged so that the distance between the first stage and the opposite end face and the second stage and the opposite end face in Direction of the rotational direction of the rotor decreases. The step-shaped design allows for easy manufacturing of the vane pump.

In a further embodiment of the invention, the surface structure has at least one groove, which is aligned approximately in the direction of the axis of rotation of the rotor. In this way, air or another flow medium is reliably tracked into the surface structure.

In a further embodiment of the invention, the surface structure has at least one boundary web which delimits a region of the end surface without a surface structure and / or the surface structure with respect to a radially outer circumferential surface. In this way, the pressure generated in the surface structure can be reliably maintained in the region of the surface structure.

The invention will be explained in more detail with reference to figures. Showing:

1 a perspective view of a vane pump with a first rotor;

2 a plan view of the first rotor;

3 a plan view of a second rotor;

4 a plan view of a third rotor;

5 a plan view of a fourth rotor;

6 a plan view of a fifth rotor;

7 a perspective view of the vane pump with a first surface structure of a sixth rotor;

8th a section along a direction of rotation of a seventh rotor through a second surface structure;

9 a section along the rotational direction of an eighth rotor through a third surface structure;

10 a section along the rotational direction of a ninth rotor through a fourth surface structure; and

11 a perspective view of a section of a tenth rotor with a fifth surface structure.

1 shows a perspective view of a vane pump 1 , The vane pump 1 includes a drive 28 , a pump housing 26 and one in the pump housing 26 arranged first rotor 10 , The pump housing 26 comprises a rotationally symmetrical about a cylinder axis 48 trained cavity 27 in which the first rotor 10 is arranged. The pump housing 26 includes an inlet opening 52 and an outlet opening 53 , The first rotor 10 has an axis of rotation 21 spaced apart to a cylinder axis 48 of the cavity 27 is arranged offset. The first rotor 10 is cylindrical, on a rotor shaft 59 arranged and includes several slots 22 parallel to the axis of rotation 21 run. In the slots 22 is each a wing 23 arranged. The cavity 27 of the pump housing 26 has a first end face 30 on, opposite to a second end face 31 of the first rotor 10 is arranged. At the second end face 31 of the first rotor 10 are several compression grooves 24 . 25 arranged. The compression grooves 24 . 25 are between the slots 22 for the wings 23 arranged and to the first end face 30 of the pump housing 26 opened. A cross section of the compression grooves 24 . 25 reduces along the course of the compression groove 24 . 25 radially from the outside to the axis of rotation 21 out. A first compaction groove 24 becomes spiral in the direction of the axis of rotation 21 towards a radially inner region of the second end face 31 guided. A second compression groove 25 is just like the first compression groove 24 spirally formed, runs in the direction of the slot 22 and ends away from it. The first compression groove 24 is opposite a rotor shaft 59 through a first wall 45 limited. The second compression groove 25 is from the slot 22 through a second wall 46 separated.

Will be the first rotor 10 through the drive 28 clockwise around the axis of rotation 21 set in rotation, so are the wings 23 pushed outwards by the centrifugal force until it reaches the pump housing 26 issue. The wings 23 are designed, along a pump housing inner wall 51 to slide along and a fluid from the inlet port 52 to the outlet opening 53 to promote. Due to the rotation, the pumped fluid will be in the compression grooves radially outward 24 . 25 passed, wherein the compression grooves 24 . 25 by its course the fluid from the first rotor 10 radially inward on the inside. This builds a pressure along the compression grooves 24 . 25 on. At the radially inner end of the compression grooves 24 . 25 is the fluid due to the end of the compression grooves 24 . 25 forced the compression grooves 24 . 25 leave and head towards the first face 30 to emerge from the pump housing. By the rotation of the first rotor 10 The fluid is in the compression grooves 24 . 25 subjected to a pressure acting as a force against the first end face 30 of the pump housing 26 acts. In this way it is ensured that the first rotor 10 axially spaced from the first end face 30 of the pump housing 26 is stored. This has the advantage that a sliding of the first rotor 10 on the pump housing 26 is avoided, so that the friction of the first rotor 10 on the pump housing 26 is reduced.

2 to 7 show various principal embodiments of Verdichtungsnuten in a rotor 10 . 12 . 13 . 14 . 15 . 16 , The direction of rotation of the rotors 10 . 12 . 13 . 14 . 15 . 16 is clockwise.

2 shows a plan view of the first rotor 10 which is at the second end face 31 several compression grooves 24 . 25 includes. The first rotor 10 has a driver 61 for transmitting the torque from the rotor shaft 59 on the first rotor 10 on. The compression grooves 24 . 25 are formed spirally and promote a fluid from the radially outer circumferential surface 34 inside. At the end of the compression grooves 24 . 25 the volume flow of the pumped fluid is through the end of the compression groove 24 . 25 in the direction of the first end face 30 of the pump housing 26 derived. The promotion of the pumped medium from the outside inwards ensures a high pressure of the pumped medium close to the rotor shaft 59 of the first rotor 10 so that the first rotor 10 Reliable to the pump housing 26 is stored spaced in the axial direction.

3 shows a plan view of a second rotor 13 , The second rotor 13 includes several compression grooves 54 facing the in 2 shown first Verdichtungsnuten 24 are made shortened and the diameter of the radially inner end of the slots 22 end up. The second rotor 13 has the radially inner, to the third compression grooves 54 arranged first wall 45 on. The first wall 45 borders the third compression grooves 54 from the rotor shaft 59 from. Furthermore, the second rotor 13 the second wall 46 on, the third compression grooves 54 from the slots 22 demarcates. Further, by the third compression grooves 54 generated pressure radially outward than in 2 shown in the direction of the first end face 30 of the pump housing 26 derived, leaving the second rotor 13 opposite the first rotor 10 is mounted axially stable against tilting.

4 shows a plan view of a third rotor 14 , which has several fourth compression grooves 55 includes. In this case, the pumped medium in contrast to the in 1 to 3 shown rotors 10 . 13 conveyed radially from the inside to the outside, wherein the third rotor 14 no walls 45 . 46 , as in 1 to 3 shown. The fourth compression grooves 55 are for reversing the conveying direction relative to the in 2 to 3 shown Verdichtungsnuten 24 . 25 . 54 directed in the opposite direction. A promotion of the conveying medium radially from the inside outwards provides a tilt-stable axial bearing of the third rotor 14 ready.

5 shows a plan view of a fourth rotor 15 similar to the one in 4 shown fourth rotor 14 fifth compression grooves 56 has, compared to the fourth Verdichtungsnuten 55 shortened are executed. In order to increase the delivery pressure of the pumped medium, the fourth rotor has 15 a radially outer third wall 47 on. This ensures a reliable pressure build-up with respect to the first end face 30 of the pump housing 26 and prevents drainage of the pumped medium in the direction of the peripheral surface 34 of the fourth rotor 15 ,

6 shows a plan view of a fifth rotor 16 , which has several sixth compression grooves 57 having a radially outer first region 42 and a radially inner second region 43 include. The two areas 42 . 43 are spirally formed, with the two areas 42 . 43 run towards each other and in a third area 44 to meet. The sixth compression grooves 57 be through the second wall 46 in the area of the slots 22 limited, so the first and second areas 42 . 43 at the third slots 22 no third area 44 form. The delivery of the pumped medium takes place both radially from the inside to the outside and radially from outside to inside. In this case, the resulting pressure in the direction of the first end face 30 of the pump housing 26 in the third area 44 distracted. Assign the sixth compression grooves 57 only one of the two areas 42 . 43 on, in the sixth compression grooves 57 generated pressure on the second wall 46 in the direction of the first end face 30 of the pump housing 26 distracted. The training form of the sixth compression grooves 57 of the fifth rotor 16 has the advantage that a higher pressure than from a promotion from the inside out, as in 4 to 5 can be provided, wherein at the same time the tilting stability of the fifth rotor 16 increased compared to in 2 to 3 shown embodiment.

7 shows a perspective view of a sixth rotor 12 , The sixth rotor 12 points to its second end face 31 a first surface structure 33 on. The first surface structure 33 contains individual segments 58 , each by a groove 32 are separated from each other. The groove 32 is about in the direction of the axis of rotation 21 of the sixth rotor 12 aligned and the first surface texture 33 is radially outward lying on the second end face 31 arranged. The first surface structure 33 gets through the slots 22 interrupted. Opposite to the first surface structure 33 is the first face 30 of the pump housing 26 arranged. A surface of the first surface structure 33 is wedge-shaped, wherein the distance in the direction of rotation to the first end face 30 decreases.

Will be the sixth rotor 12 in rotation counterclockwise about the axis of rotation 21 offset, so the medium is between the first surface structure 33 and the first end face 30 in the individual segments of the first surface structure 33 compacted. Compressing the fluid at the first surface structure causes the sixth rotor 12 spaced from the first end face 30 of the pump housing 26 is axially supported and a grinding of the rotor 11 at the first end face 30 avoided or reduced. By the rotation of the sixth rotor 12 flows radially from the inside the fluid through the grooves 32 into the individual segments 58 the first surface structure 33 to. In this way it is ensured that sufficient conveying medium between the first surface structure 33 and the first end face 30 for storage of the sixth rotor 12 ready.

8th shows a section along the direction of rotation of a seventh rotor 18 through a second surface structure 37 whose segments 58 through the groove 32 are separated from each other. The second surface structure 37 is concave and symmetrical to the grooves 32 educated. The symmetrical design of the second surface structure 37 allows rotation of the rotor in both directions of rotation, wherein the distance of the surface of the second surface structure 37 in the direction of rotation between the first end face 30 of the pump housing 26 and the second end face 31 with the second surface structure 37 decreases.

9 shows a section along the direction of rotation of an eighth rotor 19 through a third surface structure 38 , The third surface structure 38 includes individual segments 58 , each through the groove 32 are separated. A surface of the surface structure 38 is concave, with a single segment 58 the surface structure 38 has an approximately wedge-shaped basic shape. The direction of rotation is at the third surface structure 38 opposite the second surface structure 37 set, however, can have more segments 58 the surface structure 38 due to the narrower design of the individual segments 58 on the second end face 31 on the eighth rotor 19 to be ordered. The distance of the surface of the third surface structure increases 38 along the direction of rotation of the eighth rotor 19 opposite the first end face 30 of the pump housing 26 from.

10 shows a section along the rotational direction of a ninth rotor 20 through a fourth surface structure 39 , The fourth surface structure 39 includes a first stage 40 and a second stage 41 , The first stage 40 and the second stage 41 are so on the face 31 of the ninth rotor 20 arranged that a distance of the first stage 40 to the first end face 30 and the distance of the second stage 40 to the first end face 30 decreases in the direction of rotation. The formation of the fourth surface structure 39 by means of steps 40 . 41 enables a simple and cost-effective production of the fourth surface structure 39 of the ninth rotor 20 , Individual segments 58 the fourth surface structure 39 , each one a first and a second stage 40 . 41 include, are through the groove 32 separated.

11 shows a perspective view of a section of a tenth rotor 17 , The tenth rotor 17 includes a fifth surface structure 49 , The fifth surface structure 49 is similar to the one in 8th shown first surface structure 33 educated. The fifth surface structure 49 includes individual segments 58 passing through the grooves 32 are separated from each other. The fifth surface structure 49 is wedge-shaped, with a wedge-shaped area 50 through an inner first boundary web 35 and by a radially outer second boundary web 36 from one area 60 the face 31 is separated, in which no surface structure is arranged. Furthermore, the second radially outer boundary web separates 36 the wedge-shaped area 50 from a peripheral surface 34 of the tenth rotor 17 , The boundary webs 35 . 36 avoid the drainage of the fluid from the wedge-shaped area 50 so as to have a higher pressure between the fifth surface structure 49 and the first end face 30 of the pump housing 26 build. The wedge-shaped area 50 is aligned so that in the direction of rotation of the distance of the surface of the wedge-shaped region 50 to the opposite first end face 30 of the pump housing 26 decreases.

In the illustrated embodiments, the compression grooves and the surface structures are each disposed on the rotor. Alternatively, though also conceivable to arrange the compression grooves or the surface structure on the first end face of the pump housing. Furthermore, it is also conceivable to combine the compression grooves with the surface structure, so as to provide an increased pressure between the two end faces of the pump housing and the rotor and so reliably to store the rotor axially in the pump housing with low friction.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102008059981 A1 [0002]

Claims (11)

Vane pump ( 1 ) with a pump housing ( 26 ) and a rotor ( 10 ; 12 ; ...; 20 ) located in a cavity ( 27 ) of the pump housing ( 26 ) along a rotation axis ( 21 ), wherein the pump housing ( 26 ) a first end face ( 30 ), on the opposite side a second end face ( 31 ) of the rotor ( 10 ; 12 ; ...; 20 ), characterized in that a device ( 33 ; 37 ; 38 ; 39 ; 49 ; 24 ; 25 ; 54 ; ...; 57 ) at the first end face ( 30 ) of the pump housing ( 26 ) and / or at the second end face ( 31 ) of the rotor ( 10 ; 12 ; ...; 20 ), wherein the device ( 33 ; 37 ; 38 ; 39 ; 49 ; 24 ; 25 ; 54 ; ...; 57 ) by a rotation of the rotor ( 10 ; 12 ; ...; 20 ) around the axis of rotation ( 21 ) a pressure between the first end face ( 30 ) of the pump housing ( 26 ) and the second end face ( 31 ) of the rotor ( 10 ; 12 ; ...; 20 ). Vane pump ( 1 ) according to claim 1, characterized in that the device has at least one surface structure ( 33 ; 37 ; 38 ; 39 ; 49 ), which is formed such that a distance between a surface of the surface structure ( 33 ; 37 ; 38 ; 39 ; 49 ) and the opposite end face ( 30 . 31 ) decreases in the direction of rotation. Vane pump ( 1 ) according to claim 1 or 2, characterized in that the device has at least one compression groove ( 24 ; 25 ; 54 ; ...; 57 ), which is arranged obliquely to the rotational direction of the rotor. Vane pump ( 1 ) according to claim 3, characterized in that the rotor ( 10 ; 12 ; ...; 20 ) on a peripheral side ( 34 ) to the rotation axis ( 21 ) aligned slots ( 22 ), in each of which a wing ( 23 ), wherein between slots ( 22 ) at least one first compression groove ( 24 ) and a second compression groove ( 25 ), wherein the first compression groove ( 24 ) in the direction of the axis of rotation ( 21 ) of the rotor ( 10 ; 12 ; ...; 20 ) and the second compression groove ( 25 ) in the direction of the slots ( 22 ), wherein at one end of the second compression groove ( 25 ) a wall ( 46 ) is arranged, which the second compression groove ( 24 ; 25 ; 54 ; ...; 57 ) from the slot ( 22 ) delimits. Vane pump ( 1 ) according to claim 3 or 4, characterized in that the compression groove ( 24 ; 25 ; 54 ; ...; 57 ) spirally in the direction of the axis of rotation ( 21 ) is trained. Vane pump ( 1 ) according to one of claims 3 to 5, characterized in that the compression groove ( 24 ; 25 ; 54 ; ...; 57 ) radially on the outside and / or inside by a further wall ( 45 . 47 ) is limited. Vane pump ( 1 ) according to one of claims 3 to 6, characterized in that the compression groove ( 24 ; 25 ; 54 ; ...; 57 ) a first area ( 42 ) and a second area ( 43 ), the two areas ( 42 . 43 ) are spiral-shaped and run towards one another and in a third area ( 44 ) meet. Vane pump ( 1 ) according to one of claims 2 to 7, characterized in that the surface structure ( 37 ; 38 ) convex in the direction of rotation ( 21 ) is trained. Vane pump ( 1 ) according to one of claims 2 to 8, characterized in that the surface structure ( 39 ) at least a first and a second stage ( 40 . 41 ), wherein the first and the second stage ( 40 . 41 ) are arranged so that the distance between the first stage ( 40 ) and the opposite end face ( 30 . 31 ) and the second stage ( 41 ) and the opposite end face ( 30 . 31 ) in the direction of the rotation direction of the rotor ( 10 ; 12 ; ...; 20 ) decreases. Vane pump ( 1 ) according to one of claims 2 to 9, characterized in that the surface structure ( 33 ; 37 ; 38 ; 39 ; 49 ) at least one groove ( 32 ), which is approximately in the direction of the axis of rotation ( 21 ) of the rotor ( 10 ; 12 ; ...; 20 ) is aligned. Vane pump ( 1 ) according to one of claims 2 to 10, characterized in that the surface structure ( 32 ; 33 ; 37 ; 38 ; 39 ; 49 ) at least one boundary web ( 35 . 36 ), which is formed in the direction of rotation and the surface structure ( 33 ; 37 ; 38 ; 39 ; 49 ) radially inwardly and / or radially outwardly delimits.

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