EP1687538A1

EP1687538A1 - Oscillating slide machine

Info

Publication number: EP1687538A1
Application number: EP04818376A
Authority: EP
Inventors: Günther Beez
Original assignee: Lademann Sven
Current assignee: Lademann Sven
Priority date: 2003-11-08
Filing date: 2004-11-05
Publication date: 2006-08-09
Anticipated expiration: 2024-11-05
Also published as: US7438543B2; WO2005047703A1; DE502004005927D1; EP1687538B1; CN100406735C; DE10352267A1; ATE383515T1; DE112004002648D2; CN1875190A; JP2007510082A; JP4909078B2; US20060191360A1

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

Pendulum slide machine

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

In the prior art, FR 980 766 as well as in DE 195 32 703 C1 pendulum slide machines with a rotatably mounted inner rotor and a pendulum-driven, also rotatably mounted outer rotor, in which the flow rate by varying the eccentricity between the inner rotor and the outer rotor can be varied. In these designs, the symmetrically designed pendulum drivers are pivotable in the pans of the rotatably mounted outer rotor with their respective circular head region and slidably arranged in the grooves of the inner rotor with their conical end opposite the head region. The synchronous running between the eccentrically running inner rotor with respect to the outer rotor is ensured in these designs by the permitted play between the inner rotor and the pendulum drivers slidingly arranged in its grooves.

In order to avoid distortion of the components while the efficiency is still reasonable, very low permissible tolerance ranges must be observed in production. This results in the very high manufacturing costs for such pendulum slide machines.

As a result of the design-related power transmission from the inner rotor via the pendulum driver to the outer rotor, a tilting moment acts on the pendulum driver, which leads to uneven running and also results in increased friction losses. In extreme cases, this can cause the pendulum to jam in the groove area.

Due to the extreme pressure peaks occurring with these designs, there is also a pulsation in the volume flow and, in addition, cavitation in the upper speed range. As described in DE 101 02 531 A1 but also in EP 1 225 337 A2 claiming the priority of DE 101 02 531 A1, unsymmetrical pendulum drivers were considered years ago in connection with an adjusting device for a quantity-adjustable cell pump.

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 abovementioned descriptions of the invention) had such serious disadvantages as, for example, a non-uniform torque curve, a strong pulsation (in particular with maximum eccentricity) , Control problems (which were particularly caused by clamping effects at high speeds), strong signs of wear in the area of the pendulum foot, stability problems in the area of the pendulum web and, as a result, a strong limitation of the crank angle, as well as a low efficiency of approx. 5 to 10%, and this all with extremely high, but absolutely necessary manufacturing accuracies which, in conjunction with the asymmetrical design of the pendulum drivers, again the very high manufacturing costs of conventional pendulum valves machines significantly increased, so that compared to the design of a pendulum slide machine with symmetrical pendulum drivers presented in DE 195 32 703 C1, the asymmetrical pendulum drivers used in such machines did not produce any advantages, on the contrary, even only disadvantages.

From an economic point of view, it was therefore not possible to guarantee effective, functionally reliable continuous operation with these asymmetrical pendulum drivers used in the pendulum slide machines at that time and described in DE 101 02 531 A1.

Therefore, the applicant of DE 101 02 531 A1 has already rejected the use of such asymmetrical pendulum drivers after a small series production. The object of the invention is to develop a novel pendulum slide machine that works by means of an eccentric orbital movement, which eliminates these aforementioned disadvantages of the prior art and, in conjunction with the use of asymmetrical pendulum drivers, significantly improves the running properties, produces a uniform torque curve, and clearly causes the pulsation reduced and at the same time the maximum eccentricity compared to conventional pendulum slide machines with the same installation space significantly increased, the delivery volume increased, thereby avoiding the stability problems in the area of the pendulum web even with a significant increase in the offset angle, and also ensures optimal power transmission between the individual components of the pendulum slide machine in all speed ranges , at the same time significantly reduces susceptibility to cavitation even in very high speed ranges, thereby improving controllability the conveying effect of the pendulum slide machine is significantly increased, also the overall wear, but especially significantly reduced in the critical area of the pendulum foot, thereby minimizing friction losses, also significantly increasing the efficiency, but also significantly reducing the manufacturing accuracy required for reliable long-term operation, significantly that Manufacturing costs are reduced and 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)).

This task is accomplished by a pendulum slide machine with at least one rotor set, consisting of an inner rotor (5) arranged on a drive shaft (4), which is rotatable directly in the housing by means of pendulum webs (6) provided with pendulum heads (7) and pendulum feet (12) (1) or indirectly, for example in a spool (2) mounted outer rotor (3), the pendulum webs (6) being constructed such that at the Pendulum back on the pendulum head, opposite the connection line between the center of the pendulum head circle and the pendulum foot center, a pendulum head plate (9) inclined in the direction of the pendulum foot (12) is arranged, which at its free end merges approximately at right angles into a pendulum backside sliding curve (11), the circular pendulum head (7) on the other hand merges via a pendulum head groove (8) into a pendulum front sliding curve (10) extending to the pendulum foot (12). These pendulum webs (6) constructed in this way are arranged with their pendulum heads (7) in pan grooves (14) distributed evenly over the circumference of the outer rotor (3), a pendulum receiving web (15) on the front of the pan groove (14) and on the back of the Pan groove (14) an inclined pendulum stop surface (16) is arranged, and the pendulum webs (6) with their pendulum feet (12) are arranged in pendulum guide grooves (19), which is characterized in that the pendulum guide grooves (19) of the inner rotor (5 ) are provided with differently high groove leading edges (20) and groove trailing edges (21) such that the imaginary connecting circle diameter (17) of all groove leading edges (20) is smaller than the connecting circle diameter of all groove trailing edges (21). On the basis of this solution according to the invention, the respective required inventive difference of the connecting circle diameter is determined from the pendulum web cross section required for the power transmission and the dynamic stability and the "cranking" of the pendulum required for optimal conveyance.

The height difference according to the invention makes it possible, on the one hand, to significantly increase the load-bearing material thickness of the pendulum webs (6) in the neck area and at the same time to realize “a larger tilt angle”. In connection with the height difference according to the invention, the rear sliding curve (11) of the pendulum is also redefined, so that, as a result of the arrangement according to the invention of groove front edges (20) and groove rear edges (21) of different heights, all problems which have hitherto appeared to be unsolvable are almost optimally solved at the same time. For example, on the basis of these groove front edges (20) and groove rear edges (21), which according to the invention are of different heights, on the one hand, all stability problems in the area of the pendulum web are eliminated with a simultaneous widening of the offset angle and, as a result, a uniform torque curve and a significant improvement in the running properties are achieved but also a significant reduction in pulsation with a significant increase in the maximum eccentricity and reduced susceptibility to cavitation even in very high speed ranges, and this with an improvement in the conveying effect and a substantial improvement in the controllability of the pendulum slide machine in connection with a significant reduction in wear overall, but in particular in the area of the pendulum foot.

The groove rear edges (21), which are higher than the groove front edges (20), in cooperation with the other assemblies according to the invention enable smooth running with little wear and high efficiency even with maximum eccentricity, so that the solution according to the invention also succeeds in the inner rotor (5 ) arranged pendulum web (6) so much play between the pendulum guide groove (19) and the respectively assigned two sliding curves (the pendulum web (6)) that even with maximum eccentricity and very large approved manufacturing tolerances jamming of these assemblies is excluded.

As a result, the high manufacturing accuracies required for the production of pendulum slide machines (both with and without asymmetrical pendulums) were significantly reduced and the manufacturing costs of the pendulum slide machines were reduced to an acceptable level for the first time.

By means of the solution according to the invention, the arrangement of an odd number of pendulum webs which was previously absolutely necessary for functionally reliable continuous operation with a pendulum slide machine has also been achieved for the first time (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 reliable long-term operation.

The solution according to the invention made it possible for the first time to carry out a dimensioning of the cranked pendulum geometry which at the same time met the occurring loads as well as optimal conveying, so that in all speed ranges an optimal power transmission between the individual components of the pendulum slide machine with a significant increase in the maximum eccentricity compared to conventional pendulum slide machines with the same installation space, a significantly reduced pulsation and susceptibility to cavitation, with minimized friction losses, significantly improved running properties and a significantly increased delivery volume with a significant improvement in efficiency.

The arrangement of the groove leading edges (20) with respect to the groove trailing edges (21) of the inner rotor (5) according to the invention, offset in their (imaginary) connecting circle diameters, at the same time enables a special design of the outer rotor (3) according to the invention, so that in connection with the strongly cranked that is possible according to the invention and at the same time very stable design of the pendulum webs (6) a direct transmission of force between these assemblies in the entraining area, which leads optimally from the inner rotor (5) directly via the pendulum head (7) into the socket groove (14) and is transferred to the outside area ,

It is also characteristic that the imaginary connecting circle diameter (17) of all pendulum receiving webs (15) is clearly within the other inner contour of the outer rotor (3), and an outer rotor groove between each pendulum stop surface (16) and the pendulum receiving web (15) of the adjacent pendulum (6) (18) is arranged. According to the invention, an inner rotor groove (23) is also arranged between the groove rear edge (21) and the groove front edge (20) of the next following pendulum guide groove (19).

It is also essential to the invention that the pendulum front sliding curve (10) is connected to the pendulum rear sliding curve (11) in the region of the pendulum foot (12) via a pendulum foot groove (13).

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

The pendulum foot groove (13) stabilizes and at the same time guides the pendulum web (6) during the entire movement sequence in the pendulum guide groove (19) filled with the medium to be conveyed, and thus helps to ensure that a pendulum web (6), even with very large manufacturing tolerances, jams in the pendulum guide groove (19). to avoid, and at the same time minimizes the friction losses in the pendulum guide groove (19). It is also essential to the invention that the pendulum head plate (9) arranged on the pendulum head on the pendulum webs (6) on the pendulum head, relative to the connecting line between the center of the pendulum head circle and the pendulum foot center, by an angle α of 40 ° to 55 ° in the direction of the pendulum foot (12) is arranged inclined, the circular pendulum head (7) between the line of contact with the pendulum head plate (9) and a pendulum head groove (8) arranged on the front of the pendulum forming an angle β of 280 ° to 310 °.

The entirety of this arrangement according to the invention then brings about an optimized solution of the task according to the invention. Further details and features of the invention result from the following description of the exemplary 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 using an exemplary embodiment in conjunction with 4 figures.

The shows

Figure 1: a possible embodiment of the pendulum slide machine according to the invention in a side view in section; Figure 2: the side view of a pendulum web used according to the invention; Figure 3: the detailed representation of a rotor set constructed according to the invention of the pendulum slide machine according to Figure 1, in side view; Figure 4: the inner rotor of the pendulum slide machine according to the invention according to Figure 1 in side view; Figure 5: the outer rotor of the pendulum slide machine according to the invention according to Figure 1 in side view.

1 shows one of the possible embodiment of the pendulum slide machine according to the invention in a side view in section. A control slide 2 is arranged in a housing 1. The outer rotor 3 of a rotor set is rotatably arranged therein. This rotor set consists of one arranged on a drive shaft 4

Inner rotor 5, which is rotatable with seven pendulum webs 6

External rotor 3 is connected.

The individual chamber volumes between the neighboring ones

Pendulum webs 2, the outer rotor 3 and the inner rotor 5 formed

Pump chambers 24 are successively brought to a maximum and immediately afterwards to a minimum volume (or vice versa) with each revolution of the drive shaft 4.

When the volume of the pump chambers 11 increases, this is to be pumped

Medium via the arranged in the housing 1 and / or in the housing cover

Suction kidney (s) 25 are sucked into the pump chambers 24.

In the direction of rotation of the drive shaft 4 takes place, offset by 180 °, at the same time

Volume reduction 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 exits from the pump chambers 11 via the pressure kidneys 26 arranged on the housing 1 and / or in the housing cover.

The pendulum web 6 according to the invention shown in Figure 2 is constructed such that on the back of the pendulum on the pendulum head 7, opposite the

Connection line between the center of the pendulum head circle 7 and the

Center of the pendulum foot 12 at an angle α of 43 ° in the direction of

Pendulum foot 12 inclined pendulum head plate 9 is arranged.

At its free end, this goes approximately at a right angle into one

Pendulum backside slip curve 11 over.

The circular pendulum head 7 sweeps between the line of contact with the pendulum head plate 9 and one arranged on the front of the pendulum

Pendulum head groove 8 an angle β of 296 °.

About this pendulum head groove 8, the circular pendulum head 7 goes into one

Pendulum foot 12 extending pendulum front slip curve 10 over.

The pendulum front slip curve 10 is connected in the region of the pendulum foot 12 to the pendulum back slide curve 11 by means of a pendulum foot groove 13. Figure 3 shows the detailed representation of the constructed according to the invention

Rotor set of the pendulum slide machine according to Figure 1 in side view.

The seven pendulum webs 6 are arranged with their pendulum heads 7 in pan grooves 14 evenly distributed over the circumference of the outer rotor 3.

At the front of the pan groove 14 there is one

Pendulum receiving web 15 and on 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 next following one

An outer rotor groove 18 is arranged in each case in the pendulum receiving web 15.

The pendulum webs 6 are with their pendulum feet 12 in the pendulum guide grooves

19 inner rotor 5 arranged.

Figure 4 shows the inner rotor 5 of the invention

Pendulum slide machine according to FIGS. 1 and 3 in a side view with the pendulum guide grooves 19.

It is essential here that the pendulum guide grooves 19, as shown in FIG. 4, have groove front edges 20 and groove rear edges of different heights

21 are provided.

The imaginary connecting circle diameter of all groove leading edges 20 is always smaller than the connecting circle diameter 17 of all groove trailing edges 21.

An inner rotor groove 23 is arranged between each groove rear edge 21 and the next groove leading edge 20.

5, the outer rotor 3 is the one according to the invention

Pendulum slide machine shown in Figure 1 in side view.

As can be seen from this illustration, the connecting circle diameter lies

17 of all pendulum support webs 15 clearly within the other inner contour of the outer rotor 3.

With maximum eccentricity, as shown in FIGS. 1 and 3, the solution according to the invention presented here initially brings about the lower one

Speed range that at the beginning of the "driving range" the groove rear edge

21 rests with its lower area on the pendulum back sliding curve 11 and then over the entire “driving area” on the Pendulum rear side sliding curve 11 is moved along such that the pendulum web 6 is immersed in the pendulum guide groove 19 of the inner rotor 5 until the transition region from the pendulum rear side sliding curve 11 to the pendulum head plate 9 bears against the raised groove rear edge 21 of the inner rotor.

In all phases of this movement sequence in the “entrainment area”, the pendulum head groove 8 of the pendulum web 6 is almost in contact with the pendulum reception web 15 of the outer rotor 3 and ensures optimum force transmission in this end position due to its form-fitting positioning. During this movement sequence just described, the “immersion process”, causes Solution presented here that the line of action of the radial thrust force acting on the respective pendulum web 6 always acts within the pendulum guide groove area on the pendulum web 6, so that even with very large eccentricity and high operating pressures in connection with the arrangement of a pendulum foot groove 13 on the pendulum foot 12, there is always optimal guidance of the pendulum web 6 is guaranteed with "flying clamping", whereby tilting and / or bracing of the pendulum webs 6 in the pendulum guide groove 19 is excluded.

The pendulum foot groove 13 arranged on the pendulum foot 12 also has the effect that the medium located under the pendulum foot groove 13 and to be conveyed by the pendulum foot 12 can be optimally displaced during the conveying process while avoiding pressure peaks.

With increasing speed occurs from a speed dependent on the respective design and the respective eccentricity, due to the inventive design of the pendulum guide grooves (19) of the inner rotor (5), the related design of the pendulum webs 6 and the inventive design of the pendulum guide grooves (19) of the inner rotor 5 in connection with the design of the outer rotor 3 (due to the centrifugal forces occurring in connection with the pressure building up in the pendulum guide groove 19), the outer rotor 3 leads to the inner rotor 5. This operating state, which surprisingly always occurs in the design according to the invention and cannot be expected under any circumstances, brings about a substantial reduction in the required drive power with a constant delivery volume flow and thereby surprisingly contributes to a further, yet again, very substantial increase in the efficiency. In this very optimal operating state of the "lead", the "lowered" groove leading edge 20 according to the invention rests on the pendulum front sliding curve 10 and, due to the design according to the invention, guarantees synchronous running up to very high speed ranges with optimized power transmission properties. In the case of an almost centric run, however, all the pendulum webs 6 move into an almost similar position which inevitably would lead to the pendulum webs 6 jamming in the respective pendulum guide grooves 19. As a result of the inventive design of the pendulum guide groove areas in connection with the special design of the pendulum webs 6 with the pendulum head plates 9 arranged thereon and the respectively associated pendulum stop surfaces 16 arranged on the outer rotor, the solution according to the invention ensures that even with almost centric running that do not jam the pendulum webs 6 in the associated pendulum guide grooves 19.

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

With the help of the solution according to the invention, it has thus been possible to create a new type that works by means of an eccentric rotary movement

To develop pendulum slide machine which, in conjunction with the use of asymmetrical pendulum drivers, significantly improves the running properties, causes an even torque curve, significantly reduces the pulsation and, at the same time, also maximizes the eccentricity Compared to conventional pendulum slide machines with the same installation space, the delivery volume increased, while avoiding the stability problems in the area of the pendulum web even with a significant increase in the offset angle, and in addition, in all speed ranges, an optimal transmission of force between the individual components of the pendulum slide machine is effected, at the same time, the susceptibility to cavitation is very high high speed ranges significantly reduced, the controllability improved, the conveying effect of the pendulum slide machine significantly increased, also the overall wear, but significantly reduced in particular in the critical area of the pendulum foot, at the same time minimizing friction losses, and also significantly increasing the efficiency, and at the same time significantly increasing the efficiency for one Functionally reliable continuous operation, the required manufacturing accuracy is significantly reduced, at the same time the manufacturing costs are significantly reduced and not only d he arrangement of an (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)) enables.

REFERENCE SYMBOL

1 Housing 2 Control spool 3 Outer rotor 4 Drive shaft 5 Inner rotor 6 Pendulum web 7 Pendulum head 8 Pendulum head groove 9 Pendulum head plate

10 pendulum front slip curve

11 Pendulum rear slip curve

12 pendulum foot

13 pendulum foot-lily

14 pan grooves

15 pendulum mounting bridge

16 pendulum stop surface

17 connecting circle

18 outer rotor groove

19 Pendulum guide groove

20 groove front edge

21 groove rear edge

22 groove base

23 inner rotor groove

24 pump chamber

25 suction kidney

26 pressure kidneys

Claims

claims

1. Pendulum slide machine with at least one rotor set, consisting of an inner rotor (5) arranged on a drive shaft (4) which is provided with pendulum webs (6) with pendulum heads (7) and pendulum feet (12) with a rotatable one, directly in the housing (1) or indirectly connected, for example, in a control slide (2) mounted outer rotor (3), the pendulum webs (6) being constructed in such a way that on the back of the pendulum on the pendulum head, opposite the connecting line between the center of the pendulum head circle and the center of the pendulum foot, one in the direction of the pendulum foot ( 12) inclined pendulum head plate (9) is arranged, which at its free end merges at approximately a right angle into a pendulum rear sliding curve (11), and the circular pendulum head (7) on the other hand via a pendulum head groove (8) into a pendulum front sliding curve extending up to the pendulum foot (12) 10) passes over, these pendulum webs (6) constructed in this way are even with their pendulum heads (7) Pan grooves (14) distributed over the circumference of the outer rotor (3) are arranged, with a pendulum receiving web (15) on the front of the pan groove (14) and an inclined pendulum stop surface (16) on the back of the pan groove (14), the pendulum webs (6) are arranged with their pendulum feet (12) in pendulum guide grooves (19), characterized in that the pendulum guide grooves (19) of the inner rotor (5) are provided with groove front edges (20) and groove rear edges (21) of different heights such that the imaginary one Connection circle diameter (17) of all groove front edges (20) is smaller than the connection circle diameter of all groove rear edges (21).

2. Pendulum slide machine according to claim 1, characterized in that the imaginary connecting circle diameter (17) of all pendulum receiving webs (15) is clearly 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 adjacent one Pendulum (6) an outer rotor groove (18) is arranged.

3. Pendulum slide machine according to claim 1, characterized in that an inner rotor groove (23) is arranged between the groove rear edge (21) and the groove front edge (20) of the next following pendulum guide groove (19).

4. Pendulum slide machine according to claim 1, characterized in that the pendulum head plate (9) arranged on the pendulum back of the pendulum webs (6) on the pendulum head opposite the connecting line between the center of the pendulum head circle and the center of the pendulum foot by an angle α of 40 ° to 55 ° in the direction of the pendulum foot (12) is inclined, the circular pendulum head (7) between the line of contact with the pendulum head plate (9) and a pendulum head groove (8) arranged on the front of the pendulum forming an angle β of 280 ° to 310 °.

5. Pendulum slide machine according to claim 4, characterized in that the pendulum front sliding curve (10) is connected to the pendulum back sliding curve (11) in the region of the pendulum foot (12) via a pendulum foot groove (13).