EP1687538B1 - Oscillating slide machine - Google Patents

Abstract

The invention relates to an oscillating slide machine working on an eccentric circulatory motion, whereby the oscillation guide grooves ( 19 ) on the inner rotor ( 5 ) are provided with groove front edges ( 20 ) and groove rear edges ( 21 ) of differing heights, such that the diameter of the imaginary circle ( 17 ), connecting all groove front edges ( 20 ), is smaller than the diameter of the circle connecting all the groove rear edges ( 21 ).

Description

The invention relates to a working by means of an eccentric orbiting pendulum slide machine.

In the prior art were already in the FR 980 766 as well as in the DE 195 32 703 C1 Pendulum slide machines with a rotatably mounted inner rotor and a Pendelmitnehmer driven, also rotatably mounted outer rotor, in which the flow rate can be varied by the variation of the eccentricity between the inner rotor and the outer rotor presented. The symmetrically constructed Pendelmitnehmer are in these designs with their respective circular head portion pivotally mounted in the pans of the rotatably mounted outer rotor, and arranged with its conical, the head portion opposite end slidably in the grooves of the inner rotor.

The synchronous running between the eccentrically running inner rotor relative to the outer rotor is ensured in these designs on the approved game between the inner rotor and the sliding in the grooves arranged Pendelmitnehmern.

In order to avoid distortion of the components at a still acceptable level of efficiency, very small permissible tolerance ranges must be observed in production. This results in the very high production costs for such pendulum slide machines.

As a result of the design-related power transmission from the inner rotor via the pendulum driver on the outer rotor acts on the pendulum driver a tilting moment, which leads to a non-uniform barrel and also has increased friction losses. In extreme cases, this can lead to jamming of the pendulum in the groove area.

Due to the extreme pressure peaks occurring in these designs, there is also a pulsation of the volume flow and also in the upper speed range to cavitation phenomena.

Like in the DE 101 02 531 A1 but also in the priority of DE 101 02 531 A1 claiming EP 1 225 337 A2 was presented in connection with a setting device for a variable-volume cell pump years ago, to use asymmetric pendulum driver.

However, the practical tests carried out with such asymmetrical pendulum drivers showed that these pendulum slide machines equipped with asymmetrical pendulum drivers (according to FIGS. 1, 5 and 6 of the aforementioned invention descriptions) had such serious disadvantages, such as a non-uniform torque curve, a strong pulsation (in particular at maximum eccentricity). , Control problems (which were caused especially by high clamping speeds), strong signs of wear in the area of the pendulum foot, stability problems in the area of the pendulum bar and the resulting strong limitation of the offset angle, as well as a low efficiency of about 5 to 10%, and this all with extremely high, but absolutely necessary manufacturing accuracies which in connection with the asymmetrical design of the pendulum drivers again the very high production costs of the conventional Pendelschieberma significantly increased, so that compared to the in the DE 195 32 703 C1 featured design of a pendulum pusher with symmetrical pendulum drivers the unbalanced Pendelmitnehmer used in such machines no advantages, on the contrary, even caused only disadvantages.

From an economic point of view was therefore used with these in the former pendulum slider machines, and in the DE 101 02 531 A1 described unsymmetrical pendulum drivers no effective, reliable continuous operation to ensure.

Therefore, even after a small series production of the use of such unbalanced pendulum driver by the applicant of DE 101 02 531 A1 discarded.

The object of the invention is now to develop a working by means of an eccentric orbital novel pendulum slide machine, which eliminates these aforementioned disadvantages of the prior art, and in conjunction with the use of asymmetric pendulum drivers the running characteristics significantly improved, causes a uniform torque curve, the pulsation clearly reduced and also at the same time the maximum eccentricity compared to conventional pendulum slide machines with the same space significantly increased, increases the volume, while avoiding the stability problems in the range of the pendulum even with significant extension of the offset angle, also causes optimal transmission of power between the individual components of the pendulum slider in all speed ranges , at the same time significantly reducing the susceptibility to cavitation even in very high engine speeds, thereby improving controllability, the conveying effect of the pendulum pusher significantly increased, also significantly reduces the overall wear, but especially in the critical area of the pendulum foot, while minimizing friction losses, also significantly increases the efficiency, but also at the same time significantly reduces the required for a reliable operation permanent manufacturing accuracy significantly Lowers manufacturing costs and also not only the arrangement of an odd number of pendulum webs (6) (from five pendulum webs (6)) but also the arrangement of an even number of pendulum webs (from six pendulum webs (6)) allows.

This object is achieved by a pendulum pusher with at least one set of rotors, consisting of a on a drive shaft (4) arranged inner rotor (5), which by pendulum heads (7) and pendulum feet (12) provided pendulum webs (6) with a rotatable, direct in the housing (1) or indirectly, for example, in a control slide (2) mounted outer rotor (3) is connected, wherein the pendulum webs (6) are constructed such that at the Pendulum backside of the pendulum head, opposite the connecting line between the center of the pendulum head circle and the pendulum foot center in the direction of the pendulum foot (12) inclined pendulum head plate (9) is arranged, which at its free end approximately at right angles to a Pendelrückseitenabgleitkurve (11), wherein the circular pendulum head (7) on the other hand via a pendulum head groove (8) into a pendulum foot (12) extending pendulum front side slip curve (10) passes. These thus constructed pendulum webs (6) are arranged with their pendulum heads (7) evenly over the circumference of the outer rotor (3) distributed pan grooves (14), wherein at the front of the pan groove (14) a pendulum receiving web (15) and at the back of the Pfannennut (14) an inclined pendulum stop surface (16) is arranged, and the pendulum webs (6) with their pendulum feet (12) in Pendelführungsnuten (19) are arranged, solved, which is characterized in that the Pendelführungsnuten (19) of the inner rotor (5 ) with different high groove leading edges (20) and

Nuthinterkanten (21) are provided such that the imaginary connecting circle diameter (17) of all groove leading edges (20) is smaller than the connecting circle diameter of all Nuthinterkanten (21).

On the basis of this solution according to the invention required from the required for the transmission and dynamic stability pendulum cross-section, and required for optimal promotion "crank" of the pendulum, the respectively required, invention difference of the connecting circle diameter is set.

Due to the height difference according to the invention, it is possible on the one hand to significantly increase the load-bearing material thickness of the pendulum webs (6) in the neck region and at the same time to realize "a larger tilt angle".

In conjunction with the height difference according to the invention, the rear Abgleitkurve (11) of the pendulum is redefined, so that in the sequence of the inventive arrangement of different high Nutvorderkanten (20) and Nuthinterkanten (21) all hitherto occurring insoluble problems almost simultaneously an optimal solution be supplied.

Thus, for example, on the basis of these invention differently high groove leading edges (20) and trailing edges (21) on the one hand, the elimination of all stability problems in the area of the pendulum web while significantly increasing the offset angle and causes a uniform torque curve and a significant improvement in running characteristics, also but also a significant reduction in the pulsation while significantly increasing the maximum eccentricity and reduced susceptibility to cavitation even in very high speed ranges, and this while improving the conveying effect and a substantial improvement in the controllability of the pendulum slider machine in conjunction with a significant reduction in overall wear, but in particular in the area of the pendulum foot.

The compared to the Nutvorderkanten (20) higher Nuthinterkanten (21) allow in cooperation with the other components of the invention thereby a smooth running with low wear and high efficiency even at maximum eccentricity, so that it is possible by the inventive solution, even in the inner rotor (5 ) arranged pendulum web (6) as much play between the Pendelführungsnut (19) and the respectively associated two Abgleitkurven (the pendulum web (6)) assign that even with maximum eccentricity and very large permissible manufacturing tolerances jamming of these assemblies is excluded.

As a result, the high manufacturing accuracies required for the production of pendulum pusher machines (both with and without asymmetrical pendulum) were substantially reduced and thus the total cost of manufacturing the pendulum pusher machines was reduced to an acceptable level for the first time.

By means of the solution according to the invention, it has also succeeded for the first time for a functionally reliable continuous operation with a pendulum pusher so far absolutely necessary arrangement of an odd number of pendulum webs (6) (from five pendulum webs (6)) to overcome, and even with the arrangement of an even number of pendulum webs (from six pendulum webs (6)) to ensure a functionally reliable continuous operation.

It was made possible by the inventive solution for the first time the actual loads occurring as well as an optimal promotion at the same time expectant dimensioning of the cranked pendulum geometry, so that in all speed ranges optimal power transmission between the individual components of the pendulum slider machine, at a significant increase in the maximum eccentricity compared to conventional pendulum slide machines with the same space, a significantly reduced pulsation and

Cavitation susceptibility, with minimal friction losses, significantly improved runnability and a significantly increased delivery volume with a significant improvement in efficiency, was possible.

The invention, in their (imaginary) connecting circle diameters offset arrangement of the groove leading edges (20) against the Nuthinterkanten (21) of the inner rotor (5) simultaneously allows a special inventive design of the outer rotor (3), so that in connection with the present invention become highly cranked and thereby very stable design of the pendulum webs (6) a "outside" laid, the circumferential force optimally from the inner rotor (5) directly via the pendulum head (7) in the socket groove (14) initiating, direct power transmission between these modules in the driving area can be achieved ,

It is also characteristic that the imaginary connecting circle diameter (17) of all pendulum receiving webs (15) is well within the other inner contour of the outer rotor (3), and between each pendulum stop surface (16) and the pendulum receiving web (15) of the respective adjacent pendulum (6) an outer rotor groove (18) is arranged.

According to the invention, moreover, an inner rotor groove (23) is arranged between the trailing edge (21) and the groove leading edge (20) of the respectively following pendulum guide groove (19).

It is furthermore essential to the invention that the pendulum front-side slide-out curve (10) is connected to the pendulum back-side deflection curve (11) in the area of the pendulum foot (12) via a pendulum foot groove (13).

The specially designed by the arrangement of outer rotor grooves (18) and inner rotor grooves (23) pump chambers (24) in conjunction with the by the Pendelfußrille (13) and below the pendulum web (6) specially designed pump chamber in cooperation with the other features of the solution according to the invention a further significant reduction of the pulsation, as well as a cavitation-free filling at very high speeds even in the region of maximum eccentricity, so that very high volume flows can be optimally promoted by means of the inventive solution.

The pendulum foot groove (13) stabilizes and at the same time guides the pendulum web (6) during the entire course of motion in the pendulum guide groove (19) filled with pumped medium and thus helps to jam a pendulum web (6) in the pendulum guide groove (19), even with very large manufacturing tolerances. at the same time also minimizes the friction losses in the Pendelführungsnut (19).

It is also essential to the invention that on the pendulum back of the pendulum webs (6) arranged on the pendulum head pendulum head plate (9), opposite the connecting line between the center of the pendulum head circle and the Pendelfußmitte by an angle α of 40 ° to 55 ° in the direction of the pendulum foot (12) is arranged inclined, wherein the circular pendulum head (7) between the contact line with the pendulum head plate (9) and arranged on the pendulum front pendulum head groove (8) forms an angle β of 280 ° to 310 °.

The totality of this arrangement according to the invention then effects an optimized solution of the task according to the invention.

Further details and features of the invention will become apparent from the following description of the embodiment according to the invention in conjunction with the claims and the drawings for the solution according to the invention.

The invention will now be explained in more detail with reference to an embodiment in conjunction with 4 figures.

Figur 1 :

eine mögliche Ausführungsform der erfindungsgemäßen Pendelschiebermaschine in einer Seitenansicht im Schnitt;

Figur 2 :

die Seitenansicht eines erfindungsgemäß eingesetzten Pendelsteges;

Figur 3 :

die Detaildarstellung eines erfindungsgemäß aufgebauten Rotorsatz der Pendelschiebermaschine gemäß der Figur 1, in der Seitenansicht;

Figur 4 :

den Innenrotor der erfindungsgemäßen Pendelschiebermaschine gemäß der Figur 1 in der Seitenansicht;

Figur 5 :

den Außenrotor der erfindungsgemäßen Pendelschiebermaschine gemäß der Figur 1 in der Seitenansicht.

It shows the

FIG. 1:

a possible embodiment of the pendulum pusher machine according to the invention in a side view in section;

FIG. 2:

the side view of a pendulum web used in the invention;

FIG. 3:

the detailed representation of a rotor set according to the invention of the pendulum pusher machine according to the figure 1, in the side view;

FIG. 4:

the inner rotor of the pendulum pusher machine according to the invention according to the figure 1 in side view;

FIG. 5:

the outer rotor of the pendulum pusher machine according to the invention according to the figure 1 in side view.

In the figure 1 one of the possible embodiment of the pendulum pusher machine according to the invention is shown in a side view in section.

In a housing 1, a spool 2 is arranged. In this, the outer rotor 3 of a rotor set is rotatably arranged.

This rotor set consists of a arranged on a drive shaft 4 inner rotor 5, which is connected via seven pendulum webs 6 rotatably connected to the outer rotor 3.

The individual chamber volumes of the pump chambers 24 formed between the adjacent pendulum webs 2, the outer rotor 3 and the inner rotor 5 are successively brought to a maximum and immediately thereafter to a minimum volume (or vice versa) at each revolution of the drive shaft 4.

When increasing the volume of the pump chambers 11, the medium to be conveyed is sucked into the pump chambers 24 via the suction cups / n 25 arranged in the housing 1 and / or in the housing cover.

In the direction of rotation of the drive shaft 4 takes place, offset by 180 °, at the same time a reduction in volume of the pump chambers 24 due to the eccentricity between the inner rotor 5 and the outer rotor 3 instead, so that there the medium to be conveyed via the arranged on the housing 1 and / or in the housing cover / n Druckniere / n 26 exits the pump chambers 11.

The illustrated in Figure 2, the invention pendulum web 6 is constructed such that at the pendulum back on the pendulum head 7, opposite the connecting line between the center of the pendulum head circle 7 and the

Center of the pendulum foot 12 a by an angle α of 43 ° in the direction of the pendulum foot 12 inclined pendulum head plate 9 is arranged.

This goes at its free end approximately at right angles in a pendulum back exhaust curve 11.

The circular pendulum head 7 passes between the line of contact with the pendulum head plate 9 and arranged on the pendulum front Pendelkopfrille 8 an angle β of 296 °.

About this pendulum head groove 8 is the circular pendulum head 7 in a running to the pendulum foot 12 Pendelvorderseitenabgleitkurve 10 via.

The pendulum front side slid curve 10 is connected in the area of the pendulum foot 12 to the pendulum back slid curve 11 by means of a pendulum foot groove 13.

FIG. 3 shows a detailed view of the inventively constructed rotor set of the pendulum pusher machine according to FIG. 1 in a side view. The seven pendulum webs 6 are arranged with their pendulum heads 7 in evenly distributed over the circumference of the outer rotor 3 pan grooves 14.

At the front of the pan groove 14 is in each case a pendulum receiving web 15 and at the back of each pan groove 14 an inclined pendulum stop surface 16 which merges into the outer rotor groove 18. Between each pendulum stop surface 16 and the respective next pendulum receiving web 15 each have an outer rotor groove 18 is arranged.

The pendulum webs 6 are arranged with their pendulum feet 12 in the shuttle guide grooves 19 inner rotor 5.

FIG. 4 shows the inner rotor 5 of the oscillating slide machine according to the invention according to FIGS. 1 and 3 in side view with the shuttle guide grooves 19.

It is essential here that the pendulum guide grooves 19, as shown in Figure 4, are provided with different high groove leading edges 20 and Nuthinterkanten 21.

The imaginary connecting circle diameter of all groove leading edges 20 is always smaller than the connecting circle diameter 17 of all Nuthinterkanten 21. Between each Nuthinterkante 21 and the next following Nutvorderkante 20 each an inner rotor groove 23 is arranged.

In the figure 5, the outer rotor 3 of the pendulum pusher machine according to the invention according to the figure 1 is shown in the side view.

As can be seen from this illustration, the connecting circle diameter 17 of all pendulum receiving webs 15 is clearly within the other inner contour of the outer rotor. 3

At maximum eccentricity, as shown in Figures 1 and 3, the inventive solution presented here initially in the lower speed range, that at the beginning of the "Mitnahmebereiches" the Nuthinterkante 21 rests with its lower portion on the pendulum back exhaust curve 11 and then over the entire "Takeaway area" at the Pendelrückseitenabgleitkurve 11 moves along such that the pendulum web 6 dips into the Pendelführungsnut 19 of the inner rotor 5 until the transition region of the Pendelrückseitenabgleitkurve 11 abuts the pendulum head plate 9 at the raised Nuthinterkante 21 of the inner rotor.

In all phases of this sequence of movements in the "driving range" the pendulum head groove 8 of the pendulum web 6 is almost at the pendulum receiving web 15 of the outer rotor 3 and ensures optimal position in this end position due to their positive positioning.

During this motion sequence just described, the "immersion process", the solution presented here causes the line of action of acting on the respective pendulum web 6 radial thrust force always within the Pendelführungsnutbereiches the pendulum web 6, so that even with very large eccentricity and high operating pressures in combination with the arrangement of a Pendelfußrille 13 on the pendulum foot 12 always optimal guidance of the pendulum web 6 is guaranteed at "flying clamping", whereby tilting and / or distortion of the pendulum webs 6 in the pendulum guide 19 is excluded.

The arranged on the pendulum foot 12 Pendelfußrille 13 thereby also causes that located under the pendulum groove 13, from the pendulum foot 12 to be conveyed medium during the delivery process while avoiding pressure peaks can be optimally displaced.

With increasing speed occurs from a dependent of the respective structural design and the respective eccentricity speed, as a result of the inventive design of Pendendelführungsnuten (19) of the inner rotor (5), the related design of the pendulum webs 6 and the inventive design of Pendendelführungsnuten (19) of the inner rotor 5 associated design of the outer rotor 3 (due to the centrifugal forces occurring in conjunction with the pressure building up in the Pendelführungsnut 19) a pre-run of the outer rotor 3 relative to the inner rotor 5.

This surprisingly occurring in the design according to the invention always, not to be expected operating condition causes at a constant flow rate a significant reduction in the required drive power and thereby surprisingly contributes to a further, repeated, very significant increase in efficiency.

In this very optimal operating state of the "pre-run" inventively "lowered" groove leading edge 20 abuts on the pendulum front side slip curve 10 and guaranteed due to the design of the invention a synchronous running to very high speed ranges with optimized power transmission properties.

In almost centric run, however, all pendulum webs 6 move in an almost similar position which would inevitably lead to jamming of the pendulum webs 6 in the respective shuttle guide grooves 19.

Due to the inventive design of the Pendelführungsnutbereiche in conjunction with the thus becoming possible special design of the pendulum webs 6 with the arranged on these pendulum head plates 9 and the respectively associated, arranged on the outer rotor pendulum stop surfaces 16, is ensured by the inventive solution even with almost centric run that the pendulum webs 6 do not jam in the associated shuttle guide grooves 19.

The specially designed by the outer rotor grooves 18 and the inner rotor grooves 23 pump chambers 24 at the same time in conjunction with an increase in the respective filling cross-section even at very high speeds and very high flow rates always a pulsation and cavitation free filling and emptying.

With the help of the solution according to the invention, it has thus been possible to develop a working by means of an eccentric orbital novel pendulum slide machine, which significantly improves the running characteristics in conjunction with the use of asymmetric pendulum drivers, causes a uniform torque curve, significantly reduces the pulsation and also the maximum eccentricity significantly increased compared to conventional pendulum slide machines with the same size space, increases the delivery volume, thereby avoiding the stability problems in the range of the pendulum bar even with significant expansion of the offset angle, also causes optimal transmission of power between the individual components of the pendulum slider machine in all speed ranges, at the same time the Kavitationsanfälligkeit even in very Significantly reduced high speed ranges, while improving the controllability, the conveying effect of the pendulum slider significantly increased, also significantly reduces the overall wear, but especially in the critical area of the pendulum foot, while minimizing friction losses, also significantly increases the efficiency, moreover, at the same time for a functionally reliable continuous operation required manufacturing accuracy significantly reduced, at the same time significantly reduced manufacturing costs and also not only d The arrangement of a (starting from five pendulum webs (6)) odd number of pendulum webs (6) but also the arrangement of an even number of pendulum webs (from six pendulum webs (6)) allows.

REFERENCE SYMBOL

1

casing

2

spool

3

outer rotor

4

drive shaft

5

inner rotor

6

swing bridge

7

pendulum head

8th

Pendulum head groove

9

This swivel plate

10

Pendelvorderseitenabgleitkurve

11

Pendelrückseitenabgleitkurve

12

pendulum

13

Pendelfußrille

14

Pfannennuten

15

Pendulum female web

16

Pendulum stop surface

17

connecting circuit

18

Outer rotor groove

19

Pendelführungsnut

20

Nutvorderkante

21

Nuthinterkante

22

groove base

23

Inner rotor groove

24

pump chamber

25

suction kidney

26

pressure kidney

Claims (5)

1. Oscillating slide machine with at least one set of rotors, consisting of an interior rotor (5) fitted on a drive shaft (4) which is connected with moving bars (6) provided with moving heads (7) and moving feet (12) to a pivoting exterior motor (3) directly mounted in the casing (1) or indirectly in a guide collar (2) for example, where the moving bars (6) are fitted in such a way that a moving head plate (9) is located at the rear side of the moving head so that it tilts towards the moving foot (12) in comparison to the connection line between the centre point of the circle formed by the moving head and the centre of the moving foot and changes over at its free end more or less at right angles to form the rear side of an moving guide curve (11) and the moving head (7) on the other side changes over by travelling down an moving head groove to the moving foot (12) to form the front side of an moving guide curve (10), the moving bars (6) fitted in this way are uniformly distributed with their moving feet over the extent of the seating slots (14), so that one moving flange holder (15) is fitted at the front side of the seating slot (14) and a tilted moving contact surface (16) is fitted at the rear side of the seating slot (14), where the moving bars (6) are fitted in moving guide slots (19), characterized in that the moving guide slots (19) of the interior rotor (5) are provided with front edge grooves (20) and rear edge grooves (21) of differing heights so that the intended diameter of the circumference of the connection (17) of all the front edge grooves (20) is smaller than the diameter of the circumference of the connection (17) of all the rear edge grooves (21).
2. Oscillating slide machine according to claim 1 characterized in that the circumference of the connection (17) of all the moving flange holders (15) clearly lies inside the other inside edge of the exterior rotor (3) and that an exterior rotor groove (18) is located between each moving contact surface (16) and the moving holder (15) of the respective, adjacent moving bar.
3. Oscillating slide machine according to claim 1, characterized in that an interior rotor groove (23) is located between the rear edge of the groove (21) and the front edge of the groove (20) of the next following moving guide slot (19).
4. Oscillating slide machine according to claim 1, characterized in that the moving head plate (9) fitted on the moving head at the rear side of the moving bars (6) is tilted in the direction of the moving foot (12) in relation to the connection line between the centre point of the moving head circumference and the centre of the moving foot to form an angle α of 40° to 55° where the circular moving head (7) forms an angle, β of 280° to 310° between the moving head plate (9) and a moving head groove (8) located on the front side of the moving bar.
5. Oscillating slide machine according to claim 4, characterized in that the guide curve for the moving front side (10) is connected to the guide curve for the moving rear side (11) in the area of the moving foot (12) via a moving foot groove(13).

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