EP2504579A2

EP2504579A2 - Vane pump

Info

Publication number: EP2504579A2
Application number: EP10781521A
Authority: EP
Inventors: Theodor Hüser; Alexander RÜTHER; Udo Schubert
Original assignee: Hella KGaA Huek and Co
Current assignee: Hella GmbH and Co KGaA
Priority date: 2009-11-26
Filing date: 2010-11-25
Publication date: 2012-10-03
Also published as: WO2011064290A3; US20130052057A1; WO2011064290A2; DE102009055945A1; US9212660B2; CN102782327A; DE102009055945B4

Abstract

The invention relates to a vane pump (1) comprising an electrical drive unit having an electric motor and a motor shaft (6), a pump chamber (2) connecting to the electrical drive unit, a rotor (7) having a quantity of sliders (8) and disposed concentrically to the motor shaft (6) within the pump chamber (2), wherein the motor shaft (6) engages with the rotor (7) by means of a pusher dog (9) rotationally fixed to the motor shaft (6) and the pusher dog (9) comprises at least one tappet (90) engaging in a corresponding rotor recess (72), wherein the at least one rotor recess (72) is oval in shape and the tappet (90) is contoured such that two first slightly curved contour segments (91, 92) each form a contact region with one elongated surface segment (721) of the rotor recess (72).

Description

Vane pump

The present invention relates to a vane pump comprising an electric drive unit having an electric motor and a motor shaft, a pump chamber adjoining the electric drive unit, and a rotor having a number of sliders disposed within the pump chamber concentric with the motor shaft the motor shaft via a rotatably connected to the motor shaft driver associated with the rotor is engaged and the driver has at least one driver pin which engages in a corresponding thereto Rotorausneh- mung.

Vane pumps of the type mentioned, which are often referred to as rotary vane pumps, are already known from the prior art in various embodiments. Examples of vane pump are provided by DE 100 24 699 A1, DE 199 36 644 B4, DE 10 2006 058 977 A1, DE 10 2006 058 978 A1, DE 10 2006 058 979 A1 and DE 10 2006 058 980 A1.

From the prior art it is known to realize the non-rotatable connection of the rotor to the drive shaft by means of a driver having one or more cylindrically shaped driving pins with a circular cross-section. The / the driving pin is / are doing with correspondingly shaped recesses of the rotor in engagement.

It has been shown that due to the cylindrical driving pin geometry, the surface pressure with the contact surfaces of the rotor recesses is very high. The driving pins can thereby work deep into the material, so that the service life of the driving pins and / or the rotor can be significantly reduced.

This is where the present invention sets out and makes it its task to provide a vane pump of the type mentioned at the outset, in which the Wear of the rotor can be reduced and thus the life of the rotor can be increased.

The solution to this problem provides a vane pump of the type mentioned above with the features of the characterizing part of claim 1. The dependent claims relate to advantageous developments of the invention.

A vane pump according to the invention is characterized in that the at least one rotor recess is oval and that the driving pin is contoured such that two first slightly curved contour sections each form a contact region, each with an elongated surface portion of the rotor recess. It has been shown that due to the oval shape of the at least one rotor recess and the corresponding configuration of the driving pin, the surface pressure can be reduced, so that the life of the rotor compared to the known from the prior art solutions in which the driving pins are cylindrical and have a circular cross-section, can be increased. The reduction of the surface pressure is in particular due to the particular contour of the driving pin, which has increased radii in the contact region with the contact surfaces of the rotor recesses. The driving pins no longer work deeply into the material due to the reduced surface pressure, so that the service life of the driving pins and / or the rotor can be increased.

In a particularly advantageous embodiment, it is proposed that the first contour sections of the driver have a larger radius of curvature than two second contour sections adjoining two mutually opposite, sectionally substantially semicircular surface sections of the rotor recess.

In order to improve the connection of the rotor to the motor shaft, in particular in the case of very powerful vane pumps, it is provided in a particularly advantageous embodiment that the rotor comprises two rotor recesses and that the driver has two corresponding driving pins which are in engagement with the rotor recesses. Preferably, the two rotor recesses can be formed offset by 180 ° within the rotor. The driving pins are in this embodiment also offset by 180 ° formed on the driver.

In order to simplify the mounting of the rotor on the driver, it is provided in a particularly advantageous embodiment that each driver pin extends orthogonal to a transverse center plane of the rotor.

In a particularly advantageous embodiment, there is the possibility that the cross section of each driver pin are formed mirror-symmetrically with respect to two central axes, which intersect at a central point and are oriented orthogonal to one another.

In order to simplify the production of the rotor recesses, a particularly advantageous embodiment is provided that each of the rotor recesses is formed as a slot.

In order to facilitate the mounting of the driver, it is provided in a particularly advantageous embodiment that the driver is formed in sections annular and extends around the motor shaft.

Reference to the accompanying drawings, the invention is explained in more detail below. Showing:

1 shows a longitudinal section through a vane pump according to a preferred embodiment of the present invention.

Fig. 2 shows a section through the vane pump along the line D-D according to

Fig. 1;

Fig. 3 is an enlarged detail view of the longitudinal section of FIG. 1, the

Area shows, in which the torque transmission takes place;

Fig. 4 is a plan view of the rotor of the vane pump;

5 is an enlarged view of Fig. 4th

The basic structural design and the basic operating principle of a vane pump 1, which is constructed according to a preferred embodiment of the present invention, are known from the prior art and will be explained in more detail below. The vane pump 1 comprises an electric drive unit, which is accommodated in a housing of the vane pump 1 and has an electric motor with a motor shaft 6. The vane pump 1 (rotary vane pump) can be designed in particular as a vacuum pump for generating a vacuum, which operates on the so-called displacement principle. Via a fluid inlet channel 15, which in the present case is designed as a fluid inlet nozzle, air or another fluid medium is sucked in during operation of the vane pump 1 and flows into a pump chamber 2 of the vane pump 1 and is compressed there.

The pump chamber 2 comprises a base plate 4 (motor side), a pump ring 3 and an axially offset to the base plate 4 cover plate 5, which are interconnected. The pump ring 3 has an elliptical in this embodiment nenkontur (in particular in Fig. 3 to recognize) with a correspondingly shaped inner wall 30. There is an alternative embodiment, the possibility that the pump ring 3 is annular and has a circular inner contour.

Inside the pump chamber 2, a cylindrical rotor 7 is arranged, which is in operative connection with the motor shaft 6 of the drive unit, which extends through a central opening of the base plate 4. The rotor 7 is driven during operation of the vane pump 1 by the motor shaft 6 of the electric motor and thereby set in rotation. For this purpose, the rotor 7 is rotatably connected to the motor shaft 6 via a correspondingly shaped driver 9, on the structural design will be discussed in more detail below. The driver 9 is in turn rotatably mounted on the motor shaft 6 of the electric motor.

The rotor 7 has a number of guide slots 70, which are each suitable for receiving a slider 8. In this embodiment, the rotor 7 distributed in the circumferential direction a total of eight guide slots 70 which extend from the outer periphery rotors inwardly. In each of the guide slots 70 each one of the slide 8 is slidably disposed. The rotor 7 is driven during operation of the vane pump 1 by the motor shaft 6 of the electric motor and thereby set in rotation. As can be seen in FIG. 3, the slides 8, depending on their rotational position, form differently sized working cells with the inner wall 30 of the pump ring 3, the outer wall 71 of the rotor 7 and possibly adjacent slides 8.

Further, the vane pump 1, a mounting plate 1 1, at which a not explicitly shown here housing, in which the electric motor is housed, is attached. The mounting plate 1 1 may alternatively be part of the housing. Furthermore, a sealing ring 13 is provided, which is arranged during assembly on the mounting plate 1 1. The sealing ring 13 is suitable for sealing a muffler cap 14 which terminates the vane pump 1 at the end. The muffler cap 14 is screwed by means of suitable fastening screws 12 with the mounting plate 1 1. During operation of the vane pump 1, the fluid flows through the fluid inlet channel 15 and from there through corresponding fluid outlet openings of the mounting plate 1 1 and then by two 180 ° offset from each other (and thus opposite each other) arranged fluid inlet openings 40 which formed in the base plate 4 are in the pump chamber 2 a. The slides 8 of the rotating rotor 7 compress the fluid and drive it to two fluid outlet openings not shown here, which are preferably provided offset by 180 ° in the cover plate 5 of the pump chamber 2 and preferably to the fluid inlet openings 40 of the base plate 4 by about 90 ° offset and formed as elongated shaped openings

The damping volume of the muffler means 10 is presently defined spatially substantially by the surface of the cover plate 5 and the muffler cap 14, which include the damping volume. The fluid flows after passing through the pump chamber 2 through the two fluid outlet openings of the cover plate 5 in the muffler volume of the muffler means 10. From there, the fluid flows to a fluid outlet 19 (see Fig. 3) and flows through this out of the vane pump 1 out. Optionally, a pre-silencer means may be housed within the damping volume.

With further reference to Figs. 3 to 5 will be explained in more detail below the structural design of the driver 9, which is used in the vane pump 1 described above. As already explained briefly above, the rotor 8 by means of the driver 9 rotatably connected to the motor shaft 6 of the electric motor whose free end extends through a central opening of the rotor 7, respectively. In this exemplary embodiment, the rotor 7 has two rotor recesses 72, which are offset by 180 ° with respect to one another and which are in the present case oval-shaped and designed as elongated holes. The driver 9 is annular and extends around the motor shaft around and is rotatably connected to the motor shaft 6. The driver 9 has two Mitnehmerzap- fer 90 corresponding with the two rotor recesses 72, which are also arranged offset by 180 ° to each other and Ortho extend gonal to a transverse center plane of the rotor 7. The two driver tap 90 are shaped so that they can engage in the two Rotorausnehmungen 72 of the rotor 7, and thus therefore serve to transmit the torque from the motor shaft 6 to the rotor 7 of the vane pump. 1

The driver 9 is designed so that caused by the driving pin 90 surface pressure in the slot-like recesses 72 of the rotor 3 can be minimized. This is achieved in that the two driving pins 90 have an oval cross section, which is adapted to the shape of the oval rotor recesses 72, in which the driving pins 90 can engage. As can be seen in the enlarged illustration in Fig. 5, the cross section of the two driving pins 90 is mirror-symmetrical with respect to two central axes, which intersect in the middle and are oriented orthogonal to each other. In the present case, the outer contour of the driving pins 90 has four contour sections 91, 92, 93, 94 with two different radii of curvature R1 and R2. The two first contour portions 91, 92, which bear against the straight surface portions 721 of the slot-like recesses 72 of the rotor 7 are slightly curved and have a radius of curvature R1, which is chosen so large that the surface pressure in the Rotorausnehmungen 72 can be minimized ,

The radii of the two second contour sections 93, 94, which are opposite to the curved, substantially semicircular in cross-section surface portions 720 of the slot-shaped recesses 72 and do not touch, have a radius R2 <R1. The two second contour portions 93, 94 are thus substantially more curved than the first two contour portions 91, 92. The radii of curvature R1 of the two first contour portions 91, 92 are thus greater than the radii of curvature R2 of the two second contour portions 93, 94. The in this way designed first contour portions 91, 92 respectively form the contact areas of the driving pin 90 with the straight surface portions 721 of the slots designed as slots 72. It has been shown that due to the large radii R1 and the weak curvature of the first two contour portions 91, 92, the surface pressure in the recesses 72 compared to cylindrically executed Drivers with a circular cross-section can be substantially reduced. Due to the reduced surface pressure, the driving pins 90 no longer work deeply into the material, so that the service life of the driving pins 90 and / or of the rotor 7 can be increased.

LIST OF REFERENCE NUMBERS

1 vane pump

2 pump chamber

3 pump ring

4 base plate

5 cover plate

6 motor shaft

7 rotor

8 slides

9 drivers

1 1 mounting plate

12 fixing screw

13 sealing ring

14 silencer cap

15 fluid inlet channel

19 fluid outlet area

30 inner wall

70 guide slot

71 outer wall

72 rotor recess

90 driving pin

91 contour section

92 contour section

93 contour section

94 contour section

720 semicircular section

721 straight section

Claims

Vane pump claims

1. vane pump (1) comprising

an electric drive unit with an electric motor and a motor shaft (6),

a pump chamber (2) adjoining the electric drive unit,

a rotor (7) with a number of slides (8) arranged inside the pump chamber (2) concentric with the motor shaft (6),

wherein the motor shaft (6) via a rotatably connected to the motor shaft (6) driver (9) with the rotor (7) is engaged and the driver (9) has at least one driving pin (90) in a corresponding thereto Rotorausnehmung ( 72), characterized in that the at least one rotor recess (72) is oval and in that the driving pin (90) is contoured such that two first slightly curved contour sections (91, 92) each have a contact area, each with an elongated surface section (721 ) form the rotor recess (72).

2. vane pump (1) according to claim 1, characterized in that the first contour portions (91, 92) of the driver (90) have a larger radius of curvature than two second contour portions (93, 94), the two opposite, partially substantially semicircular surface portions (720) of the rotor recess (72) are adjacent.

3. vane pump (1) according to claim 1 or 2, characterized in that the rotor (7) comprises two rotor recesses (72) and that the driver (9) has two corresponding driver pin (90), which with the Rotorausnehmungen (72) engage.

4. vane pump (1) according to claim 3, characterized in that the two rotor recesses (72) offset by 180 ° within the rotor (7) are formed.

5. vane pump (1) according to one of claims 1 to 4, characterized in that each driver pin (90) extends orthogonal to a transverse center plane of the rotor (7).

6. vane pump (1) according to one of claims 1 to 5, characterized in that the cross section of each driver pin (90) is formed mirror-symmetrically with respect to two central axes which intersect at a center and are oriented orthogonal to each other.

7. vane pump (1) according to one of claims 1 to 6, characterized in that each of the rotor recesses (72) is formed as a slot.

8. vane pump (1) according to one of claims 1 to 7, characterized in that the driver (9) is partially annular and extends around the motor shaft (6).