CA2136327A1 - Planetary gear with two driven shafts - Google Patents
Planetary gear with two driven shaftsInfo
- Publication number
- CA2136327A1 CA2136327A1 CA002136327A CA2136327A CA2136327A1 CA 2136327 A1 CA2136327 A1 CA 2136327A1 CA 002136327 A CA002136327 A CA 002136327A CA 2136327 A CA2136327 A CA 2136327A CA 2136327 A1 CA2136327 A1 CA 2136327A1
- Authority
- CA
- Canada
- Prior art keywords
- stage
- gear
- driven
- shaft
- speed
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
- B04B—CENTRIFUGES
- B04B1/00—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles
- B04B1/20—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles discharging solid particles from the bowl by a conveying screw coaxial with the bowl axis and rotating relatively to the bowl
- B04B1/2016—Driving control or mechanisms; Arrangement of transmission gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
- B04B—CENTRIFUGES
- B04B1/00—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles
- B04B1/20—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles discharging solid particles from the bowl by a conveying screw coaxial with the bowl axis and rotating relatively to the bowl
- B04B1/2016—Driving control or mechanisms; Arrangement of transmission gearing
- B04B2001/2025—Driving control or mechanisms; Arrangement of transmission gearing with drive comprising a planetary gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H2001/2881—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output
Abstract
This specification discloses an epicyclic gear with two driven shafts which rotate at different speeds, the speed of the second driven shaft being reducible or increasable by means of a second gear stage, the input shaft of which can be varied in its speed, functioning as a control shaft, the magnitude of the speed difference between the two driven shafts depending solely on the speed of the control shaft and not on the input speed, so that even if there is a change in the input speed, a constant speed difference between the two driven shafts is maintained automatically without a change in the speed of the control shaft.
Description
213632~
Epicyclic qear with two driven shafts Description The invention relates to an epicyclic gear in accordance with the precharacterizing clause of Patent Claim 1.
There are many machines in which it is necessary to drive two shafts with a variable speed difference. In mixers, for example, it may be necessary to vary the speed difference between two stirring tools in order to adapt it to the viscosity of the material to be pro-cessed.
German Offenlequngsschrift 2,811,887 has dis-closed a gear of the generic type, in this case for the purpose of driving a helical conveyor centrifuge. A
helical conveyor centrifuge has a driveable drum and a conveyor screw rotating in the latter. To process dif-ferent materials, it is not only necessary for the speed of the drum to be variable but also the speed of the screw or the speed difference between the drum and the screw.
In order to allow infinitely variable control of the speed difference with just one driving motor, the drive disclosed in German Offenlegungsschrift 2,811,887 for this helical conveyor centrifuge has a driving motor which drives the peripheral wheels of two epicyclic gears via the gear casing, the said gears being coupled to the drum 80 that the drum rotates at a speed proportional to the speed of the driving motor. The output shaft of the first epicyclic gear iQ coupled to the screw and is driven by the driven shaft of the second epicyclic gear.
If the driving shaft of the ~econd epicyclic gear is held fast, the driven shaft of the second epicyclic gear, driven by way of the peripheral wheel of the gear, rotates in accordance with the transmission ratio between the peripheral wheel and the driven shaft of the second epicyclic gear. If, however, the input ~haft of the second epicyclic gear i8 driven by a variable-speed motor, the speed of the driven shaft of the second 2136~27 epicyclic gear decreases or increa~e~ independently of the speed of the drum, dep~n~;ng on the direction of rotation of the input shaft.
If the speed of the drum i8 changed by means of a change in the speed of the driving motor, the speed difference between the drum and the screw also changes.
Thus if the drum is to be driven at a constant speed difference with respect to the screw, the speed dif-ference must be correspo~;ngly readjusted by means of the variable-speed motor when there is a change in the speed of the drum.
The object of the invention is to provide a gear in which the adjustable speed difference between two driven shafts can be maintained irrespective of the speed of the drive.
This object is achieved, according to the inven-tion, by means of the features of Patent Claim 1.
The gear in accordance with this patent claim follows the fundamental principle of the solution, namely that of reducing or increasing the speed of that driven shaft of the first gear stage which, in a helical con-veyor centrifuge for example, drives the screw, by means of the second gear stage, one input shaft of which is variable in its speed, acting as a control shaft, the magnitude of the change in speed being dependent solely on the speed of this control shaft.
In a gear constructed in accordance with this principle, the speed difference between the driven shafts of the first stage is thus now dependent only on the speed of the control shaft of the second stage. A change in the speed of the driving means, for example of a driving motor, no longer affects the speed difference.
According to Patent Claim 1, one driven shaft of the first gear stage, which, according to Claim 14, is designed as a gear casing with a peripheral wheel, is driveable by a driving means, the input shaft of this first gear stage being driven by an output shaft of the second gear stage, which is arranged on its input side.
This one driven shaft of the first gear stage is 21~63~
accordingly coupled directly to the driving means, for example a driving motor, and is thus driven without any further speed transformation at the speed of the driving motor. The other driven shaft of the first stage is driven via the casing and the planetary gear of the first stage is driven by the driving means, their speed in turn being dependent on the speed of the input shaft and of the driven casing and peripheral wheel of the first stage. As already mentioned, this input shaft is driven by one of the two output shafts of the second gear stage.
This output shaft referred to is driveable by a driven element of the second gear stage, this driven element interacting via first planet wheels with a sun wheel of the control shaft.
With this arrangement alone, it would already be possible to vary the speed difference between the first and the second driven shaft of the first stage by way of the control shaft of the second stage. However, the speed difference would not be dependent solely on the speed of the control shaft since if the speed of the control shaft or the input shaft of the first gear stage remains con-stant but the speed of the driving means and hence of the peripheral wheel of the first gear stage decreases, the speed difference between the driven shafts obviously changes.
This is made clearer below in the description of the figures by means of a numerical example.
This unwanted change in the speed difference is eliminated by means of a gear arrangement in the form of a further engagement means in one output shaft of the second gear stage. The aim of this arrangement is to change the speed of the input shaft of the first stage in such a way, the speed of the control shaft remaining constant, that the influence of the change in the speed of the driving means is compensated.
In the gear in accordance with Patent Claim 1, this is accomplished by virtue of the fact that one output shaft, which, according to Claim 2 or 4, is designed as the gear casing of the second stage and is rigidly connected to the driven shaft designed as the - gear casing of the first stage, has an engagement means which acts on the driven element of the second stage via second planet wheels operatively connected to the first planet wheels, the second planet wheels being operatively connected to a further input shaft of the second stage by way of a second sun wheel.
According to Claim 2, this solution is implemen-ted in terms of construction by designing the driven element as a first peripheral wheel which is connected for rotation in common to the output shaft of the second stage and the engagement means is in the form of a second peripheral wheel in the casing of the second gear stage, which, like the casing or peripheral wheel of the first gear stage, is driven by the driving means. This inter-acts by way of the second planet wheels with the second sun wheel, the second planet wheels having the same web carrier as the first planet wheels of the second gear stage. If the second sun wheel is now held fast, the rotation of the second peripheral wheel brings about a rotation of the web carrier, which also carries the first planet wheels, which interact with the first peripheral wheel, which is in turn connected to the output shaft of the second gear stage and hence to the input shaft of the first gear stage. A change in the input speed at a constant speed of the control shaft thus leads to a change in the speed of the input shaft of the first gear stage which precisely compensates the unwanted change in the speed difference which would otherwise occur.
In the gear in accordance with Patent Claim 4, a similar approach is adopted but in this the output shaft of the second gear stage is connected for rotation in common to a first web carrier of the first gear stage, this web carrier forming the driven element of this stage and carrying the first planet wheels, which interact with a freely rotating peripheral wheel and the sun wheel of the control shaft, a second web carrier connected for rotation in common to the driven gear casing acting as the engagement means and carrying the second planet wheels, which intera-ct with the peripheral wheel and the second sun wheel. The second web carrier is here driven by the driving means via the casing of the second stage.
If the second sun wheel iB fixed, the peripheral wheel is rotated and an influence i~ therefore exerted on the speed of the first web carrier, which is connected to the input shaft of the first gear stage.
The invention furthermore has, especially when used on helical cG-,veyor centrifuges, a number of advan-tages over the prior art with respect to the necessarydrives for the machine.
When starting up the helical conveyor centrifuge, the main drive of the ~-ch;ne~ an electric motor for example, has to provide considerable acceleration forces, resulting from the mass moment of inertia of the drum, the conveyor screw and the charge in the drum to be overcome. In addition, shearing forces can arise within the charge where the drum and the screw rotate at different speeds. This means that in the start-up phase of the machine, a zero speed difference is desirable in order to minimize the driving force, the speed difference in normal operation being set by means of the control shaft only when the desired speed of, for example, the drum is reached. In the epicyclic gear according to the invention, all that is required to achieve a zero speed difference in the start-up phase is for the control shaft to be held fast. Accordingly, the variable-speed motor for driving the control shaft is stationary in this phase and it is only to set the desired speed difference that it is simply accelerated from stationary to a relatively low speed of revolution in a predetermined direction of rotation. The variable-speed motor can thus be of rela-tively low-power design and, in addition, the individual bearings of the control shaft and of the adjoining epicyclic gear are subjected to only low speeds of revolution.
According to Patent Claim 3, the input shaft of the second ~tage is rigidly connected to a third peri-pheral wheel, which acts via third planet wheels mounted on the web carrier on the second, in this case freely rotating, sun wheel. This special design offer~ addi-tional advantages over the embodiment in which a rigid connection is provided between the input shaft and the second sun wheel of the second stage.
If, namely, in this design in accordance with Claim 3, the control shaft of the second stage is fixed, the speed difference between the driven shafts of the first stage can be set by means of the rotatable further input shaft of the second stage independently of the main drive speed and specifically, in this case, with a speed ratio of 1:1 between the further input shaft and the output shaft of the second stage. If, on the other hand, the further input shaft is held fast and, instead, the control shaft of the second stage is used to set the speed difference, the same relationships as in the embodiment according to the invention in accordance with Claim 2 are once again established.
According to Patent Claim 5, the input shaft of the second stage is advantageously designed 80 as to be fixed, thereby reducing the manufacturing outlay for the gear while nevertheless providing the desired control-lability. If, on the other hand, the second sun wheel is, in accordance with Patent Claim 5, designed to be drive-able via the input shaft, the speed difference can beadditionally varied via this input shaft.
According to Patent Claims 8 and 9, the gear casing is used to drive the second peripheral wheel or the second web carrier. This makes the gear simpler in construction since the gear casing, which is present in any case, is at the same time used to drive the gear.
However, it is also possible that a stationary gear casing will be desired, for safety reasons for example, and in this case the gear elements to be driven can be driven by way of conventional driving means such as gear wheels and shafts, c~;n~ or belt drives.
According to Patent Claim 10, the common peri-pheral wheel provided for the first and second planet wheels of the second gear stage has separate tracks for 213~327 the planet wheels. This makes it possible to provide the tracks with different toothing optimally suited to the respective requirements.
It is, of course, also possible for separate peripheral wheels to be provided in the second gear stage and for these to be coupled or at least capable of being coupled to one another.
It is possible to use both planetary gears and cycloid gears for the epicyclic gear described. Nor is there a problem in combining a planetary gear stage with a cycloid gear stage to obtain an ideal epicyclic gear dep~n~;ng on requirements as to the transmission ratio, loadability and r~nning properties.
Further advantageous developments of the inven-tion form the sub~ect-matter of the rema;n;ng subclaims.
The invention will now be explained in greater detail with reference to the figures by means of a number of exemplary embodiments.
Figure 1 shows the entire epicyclic gear in a first ~hodiment, Figure 2 shows, in a sketch, the second gear stage of an epicyclic gear in accordance with Figure 1, Figure 3 shows, in a sketch, the second gear stage of an epicyclic gear in accordance with a second embodiment, Figure 4 shows, in a sketch, the second gear stage of an epicyclic gear in accordance with a third embodiment and Figure 5 shows, in a sketch, the second gear stage of an epicyclic gear as a further development of the gear shown in Figure 2.
The epicyclic gear in accordance with Fig. 1 consists of a first, cycloid gear stage and of a second planetary gear stage. A gear casing 3 of the first gear stage has a toothing 2 via which rotation is imparted to the gear casing 3 by a driving motor (not shown). The gear casing 3 simultaneou~ly serves as the first driven shaft of the first gear stage, to which the drum of a helical conveyor centrifuge can be connected, for 2136~27 example. A second driven shaft 4 of the first gear stage is formed by the output shaft proper of the epicyclic gear, which is operatively connected via the cycloid gear to the casing 1 of the first stage.
The second gear stage likewise has a ca~ing 1, which is rigidly connected to the casing 3 of the first stage and, together with the latter, forms a common casing body for the epicyclic gear. A control shaft 5 of the second stage, which is connected to a variable-speed motor (not shown), is situated on a side of the common casing body remote from the second driven shaft 4 of the first stage. Situated on this side, coaxially with the control shaft 5, is a further input shaft 6 of the second stage.
The mode of operation of the epicyclic gear is explained below by means of the construction of the gear, starting from the input side.
The gear casing 1, 3 is rotated by means of the toothing 2. An internal gear ring 7 of the cycloid gear stage is rigidly connected to the gear casing 1, 3, the said gear ring rotating with the gear casing 1, 3. The internal gear ring 7 interacts via two cam discs 8 with two eccentrics 10 seated on an output shaft 9 of the second gear stage and serving, in this exemplary embodi-ment, as the input shaft of the first gear stage. The cam discs 8 are mounted on pins 11 which, in turn, are con-nected to the second driven shaft 4 of the first stage.
In the first exemplary embodiment, the input shaft of the first stage is formed by the eccentrics 10 of the cycloid gear. However, it is also possible to provide the input shaft as an external component on which correspo~;ng eccentrics are arranged in a manner fixed in terms of rotation and which is coupled to the output shaft 9 of the second gear stage by means of a suitable shaft coupling.
If the input shaft of the first gear stage, i.e.
the output shaft 9 of the second gear stage, is held fast, the driving motor rotates the internal gear ring 7, whereby the cam discs 8 are rotated in accordance with 21~6327 g the transmission ratio. The rotary motion of the cam discs 8 is in turn transmitted via the pins 11 to the second driven shaft 4 of the second stage. If the output shaft 9 of the second stage is rotated in addition, the speed of the second driven shaft 4 of the first stage is reduced or increased, dep~n~;ng on the direction of rotation of the output shaft 9 of the second stage.
The mode of operation of the second gear stage is explained by means of its construction, starting from the control shaft 5.
According to the first exemplary embodiment in Figs. 1 and 2, the control shaft 5 is connected for rotation in common to a first sun wheel 12 which drives first planet wheels 13 mounted on webs 14 of a freely rotating web carrier 15. The first planet wheels 13 interact with a peripheral wheel 16, which is connected for rotation in common to the output shaft 9 of the second gear stage or input shaft of the first gear stage.
The further input shaft 6 of the second stage is provided with an integral, second sun wheel 17, which interacts by way of second planet wheels 18 mounted on the same webs 14 as the first planet wheels 13 with a second peripheral wheel 19 which is connected for rota-tion in common to the gear casing 1 of the second stage, driven by the driving motor.
The construction of the second gear stage is somewhat clearer from the sketch in accordance with Figure 2.
In normal operation, the input shaft 6 of the second stage is fixed and the speed difference between the two driven shafts 3, 4 of the first stage thus depends solely on the speed of the control shaft 5.
If the transmission ratio of the internal gear ring 7 and the driven shaft 4 of the first ~tage i8 56:55, then, with the input shaft of the first stage fixed, the driven shaft 4 rotates at a speed of 4072.7 rpm when the speed of the internal gear ring 7 is 4000 rpm. If the transmi~sion ratio of the input shaft and the driven shaft 4 of the first stage is 55:1, then, - 21~6~27 '- - 10 -with the internal gear ring 7 held fast, the driven shaft 4 rotates at a speed of -29.1 rpm when the speed of the input shaft of the first stage is 1600 rpm.
If the internal gear ring 7 and the input shaft of the first stage are rotated at the speeds given in a direction of rotation in which the speeds are added together, the resulting speed at the driven shaft 4 is 4044 rpm. The speed difference between the driven shaft 4, as the output shaft proper of the epicyclic gear, and the casing of the first stage as a second driven shaft 3 of the epicyclic gear, the latter shaft rotating at the input speed of 4000 rpm, is thus 44 rpm.
If the speed of the internal gear ring 7 now decreases to 3600 rpm while the speed of the input shaft of the first stage remains the same, the resulting speed at the driven shaft 4 is 3636 rpm, the speed difference thus being 36 rpm.
In order to achieve a constant speed difference, even when the input speed of the gear casing 1, 3 changes, the speed of the input shaft of the first stage must be changed as the input speed changes. In the abovementioned case, the speed of the input shaft of the first stage must be reduced to 1200 rpm. This change in speed is performed in the second gear stage. The reduc-tion in the speed of the second peripheral wheel 19(attached to the gear casing 1) of the second stage due to the reduced input speed results in a change in the speed of the web carrier 15 and the speed of the first peripheral wheel 16 - rigidly connected to the output shaft 9 of the second stage - and hence of the input shaft of the first stage is thereby reduced, with the gear design selected, by 400 rpm, with the result that the desired speed difference of 44 rpm between the two driven shafts 3 and 4 of the first stage is maintained automatically.
Figure 3 shows the second gear stage in accor-dance with a second embodiment. In this embodiment, the first gear stage is identical with that in the first embodiment. The first gear stage is therefore not .
- 2136~27 described again.
Basically, the second embodiment depicted differs from the first embodiment in that the first and second sets of planet wheels 113, 118, which act on the first and second sun wheel 112, 117 respectively of the second stage, have a common freely rotating satellite 120 but in this case are mounted on separate webs 114, 121. The first planet wheels 113 are mounted on first webs 114, which are connected by a first web carrier 115 to the output shaft 109 of the second stage. Second webs 121 are connected to the gear casing 101 of the second stage, the casing being driven by the driving motor. Thus, in con-trast to the first embodiment, the rotation of the gear casing 101 does not influence the speed of the web carrier but the speed of the common freely rotating satellite 120; influencing the speed of the satellite 120 in turn influences the speed of the first webs 114 and hence that of the driven shaft 109 of the second stage.
Figure 4 shows the second gear stage of a third embodiment correspon~;ng in terms of the construction of the gear to the second embodiment in accordance with Fig.
3. The difference with respect to the second embodiment is, however, that a cycloid gear is used for the second gear stage instead of a planetary gear.
The first sun wheel is here replaced by a first double eccentric 212 and the second sun wheel is replaced by a second double eccentric 217. The double eccentrics 212, 217 interact with cam discs 213, 218 which replace the planet wheels. The cam discs 213 interacting with the first double eccentric 213 are mounted on first pins 214, which replace the first webs and are again rigidly con-nected to the driven shaft 209. The second cam discs 218 are mounted on second pins 221 which, like the second webs of the second embodiment, are rigidly connected to the gear casing 201, which is driven by the driving motor. The mode of operation of this gear stage is accordingly identical with that of the second P~hodiment.
Figure 5 shows another exemplary embodiment of the second gear stage of the epicyclic gear according to 213~:~27 the invention.
- According to this exemplary embodiment, the output shaft 9 of the second stage is formed integrally with a first peripheral wheel 16, which acts via planet wheels 13 mounted on freely movable web carriers 14, 15 on a sun wheel 12 which is integrally connected to the control shaft 5 of the second stage. Second planet wheels 18 are mounted on the web carriers and these planet wheels make rolling contact with a peripheral wheel 19 attached to the gear casing 1 of the second stage and are in engagement with a second, freely rotating sun wheel 17. According to Fig. 5, this second sun wheel 17 is mounted on the control shaft 5 of the second stage and has another toothed track, in which the teeth of third planet wheels 20 engage. The third planet wheels are likewise mounted on the web carriers 14, 15 and have ~;m~n~ions correspo~;ng to those of the first and second planet wheels.
The third planet wheels 20, for their part, make rolling contact with a third peripheral wheel 21, which is rigidly connected to a further input shaft 6 of the second ~tage and has the same rolling diameter as the first peripheral wheel 16 of the second stage. As in the previous exemplary embodiments, the control shaft 5 and the further input shaft 6 are arranged coaxially, the input shaft 6 being designed as a hollow shaft in which the control shaft 5 is mounted so as to be rotatable relative to the input shaft 6.
If, in this exemplary embodiment, the further input Yhaft 6 of the second gear stage is fixed as in the exemplary e_bodiments described above, it is po~sible to adjust the speed difference between the first and second driven shafts 3, 4 of the first gear stage exclusively by means of the speed of the control shaft 5, a change in the speed of the control shaft resulting in a change in the speed difference concerned in accordance with the transmission ratio of the second gear stage.
If, however, the control shaft 5 of the second stage is now held fast in the exemplary embodiment in - 2136~7 _ - 13 -accordance with Fig. 5 and the change in the speed difference i8 performed by means of the further input shaft 6, different transmission ratios are obtained between the input shaft 6 and the output shaft 9 of the second stage, which latter shaft is rigidly connected to the input shaft of the first stage. According to Fig. 5, the third peripheral wheel 21, which i~ connected to the input shaft 6, is of identical design to the first peripheral wheel 16, which is connected to the output shaft 9 of the second gear stage. This means that it is possible to perform a change in the speed of the output shaft 9 and hence of the input shaft of the first stage in a ratio of 1:1 to the change in the speed of the further input shaft 6 of the second stage m~k; ng it possible to adjust the speed difference between the two driven shafts 3, 4 of the first stage in a simple manner at the variable-speed drive itself.
Epicyclic qear with two driven shafts Description The invention relates to an epicyclic gear in accordance with the precharacterizing clause of Patent Claim 1.
There are many machines in which it is necessary to drive two shafts with a variable speed difference. In mixers, for example, it may be necessary to vary the speed difference between two stirring tools in order to adapt it to the viscosity of the material to be pro-cessed.
German Offenlequngsschrift 2,811,887 has dis-closed a gear of the generic type, in this case for the purpose of driving a helical conveyor centrifuge. A
helical conveyor centrifuge has a driveable drum and a conveyor screw rotating in the latter. To process dif-ferent materials, it is not only necessary for the speed of the drum to be variable but also the speed of the screw or the speed difference between the drum and the screw.
In order to allow infinitely variable control of the speed difference with just one driving motor, the drive disclosed in German Offenlegungsschrift 2,811,887 for this helical conveyor centrifuge has a driving motor which drives the peripheral wheels of two epicyclic gears via the gear casing, the said gears being coupled to the drum 80 that the drum rotates at a speed proportional to the speed of the driving motor. The output shaft of the first epicyclic gear iQ coupled to the screw and is driven by the driven shaft of the second epicyclic gear.
If the driving shaft of the ~econd epicyclic gear is held fast, the driven shaft of the second epicyclic gear, driven by way of the peripheral wheel of the gear, rotates in accordance with the transmission ratio between the peripheral wheel and the driven shaft of the second epicyclic gear. If, however, the input ~haft of the second epicyclic gear i8 driven by a variable-speed motor, the speed of the driven shaft of the second 2136~27 epicyclic gear decreases or increa~e~ independently of the speed of the drum, dep~n~;ng on the direction of rotation of the input shaft.
If the speed of the drum i8 changed by means of a change in the speed of the driving motor, the speed difference between the drum and the screw also changes.
Thus if the drum is to be driven at a constant speed difference with respect to the screw, the speed dif-ference must be correspo~;ngly readjusted by means of the variable-speed motor when there is a change in the speed of the drum.
The object of the invention is to provide a gear in which the adjustable speed difference between two driven shafts can be maintained irrespective of the speed of the drive.
This object is achieved, according to the inven-tion, by means of the features of Patent Claim 1.
The gear in accordance with this patent claim follows the fundamental principle of the solution, namely that of reducing or increasing the speed of that driven shaft of the first gear stage which, in a helical con-veyor centrifuge for example, drives the screw, by means of the second gear stage, one input shaft of which is variable in its speed, acting as a control shaft, the magnitude of the change in speed being dependent solely on the speed of this control shaft.
In a gear constructed in accordance with this principle, the speed difference between the driven shafts of the first stage is thus now dependent only on the speed of the control shaft of the second stage. A change in the speed of the driving means, for example of a driving motor, no longer affects the speed difference.
According to Patent Claim 1, one driven shaft of the first gear stage, which, according to Claim 14, is designed as a gear casing with a peripheral wheel, is driveable by a driving means, the input shaft of this first gear stage being driven by an output shaft of the second gear stage, which is arranged on its input side.
This one driven shaft of the first gear stage is 21~63~
accordingly coupled directly to the driving means, for example a driving motor, and is thus driven without any further speed transformation at the speed of the driving motor. The other driven shaft of the first stage is driven via the casing and the planetary gear of the first stage is driven by the driving means, their speed in turn being dependent on the speed of the input shaft and of the driven casing and peripheral wheel of the first stage. As already mentioned, this input shaft is driven by one of the two output shafts of the second gear stage.
This output shaft referred to is driveable by a driven element of the second gear stage, this driven element interacting via first planet wheels with a sun wheel of the control shaft.
With this arrangement alone, it would already be possible to vary the speed difference between the first and the second driven shaft of the first stage by way of the control shaft of the second stage. However, the speed difference would not be dependent solely on the speed of the control shaft since if the speed of the control shaft or the input shaft of the first gear stage remains con-stant but the speed of the driving means and hence of the peripheral wheel of the first gear stage decreases, the speed difference between the driven shafts obviously changes.
This is made clearer below in the description of the figures by means of a numerical example.
This unwanted change in the speed difference is eliminated by means of a gear arrangement in the form of a further engagement means in one output shaft of the second gear stage. The aim of this arrangement is to change the speed of the input shaft of the first stage in such a way, the speed of the control shaft remaining constant, that the influence of the change in the speed of the driving means is compensated.
In the gear in accordance with Patent Claim 1, this is accomplished by virtue of the fact that one output shaft, which, according to Claim 2 or 4, is designed as the gear casing of the second stage and is rigidly connected to the driven shaft designed as the - gear casing of the first stage, has an engagement means which acts on the driven element of the second stage via second planet wheels operatively connected to the first planet wheels, the second planet wheels being operatively connected to a further input shaft of the second stage by way of a second sun wheel.
According to Claim 2, this solution is implemen-ted in terms of construction by designing the driven element as a first peripheral wheel which is connected for rotation in common to the output shaft of the second stage and the engagement means is in the form of a second peripheral wheel in the casing of the second gear stage, which, like the casing or peripheral wheel of the first gear stage, is driven by the driving means. This inter-acts by way of the second planet wheels with the second sun wheel, the second planet wheels having the same web carrier as the first planet wheels of the second gear stage. If the second sun wheel is now held fast, the rotation of the second peripheral wheel brings about a rotation of the web carrier, which also carries the first planet wheels, which interact with the first peripheral wheel, which is in turn connected to the output shaft of the second gear stage and hence to the input shaft of the first gear stage. A change in the input speed at a constant speed of the control shaft thus leads to a change in the speed of the input shaft of the first gear stage which precisely compensates the unwanted change in the speed difference which would otherwise occur.
In the gear in accordance with Patent Claim 4, a similar approach is adopted but in this the output shaft of the second gear stage is connected for rotation in common to a first web carrier of the first gear stage, this web carrier forming the driven element of this stage and carrying the first planet wheels, which interact with a freely rotating peripheral wheel and the sun wheel of the control shaft, a second web carrier connected for rotation in common to the driven gear casing acting as the engagement means and carrying the second planet wheels, which intera-ct with the peripheral wheel and the second sun wheel. The second web carrier is here driven by the driving means via the casing of the second stage.
If the second sun wheel iB fixed, the peripheral wheel is rotated and an influence i~ therefore exerted on the speed of the first web carrier, which is connected to the input shaft of the first gear stage.
The invention furthermore has, especially when used on helical cG-,veyor centrifuges, a number of advan-tages over the prior art with respect to the necessarydrives for the machine.
When starting up the helical conveyor centrifuge, the main drive of the ~-ch;ne~ an electric motor for example, has to provide considerable acceleration forces, resulting from the mass moment of inertia of the drum, the conveyor screw and the charge in the drum to be overcome. In addition, shearing forces can arise within the charge where the drum and the screw rotate at different speeds. This means that in the start-up phase of the machine, a zero speed difference is desirable in order to minimize the driving force, the speed difference in normal operation being set by means of the control shaft only when the desired speed of, for example, the drum is reached. In the epicyclic gear according to the invention, all that is required to achieve a zero speed difference in the start-up phase is for the control shaft to be held fast. Accordingly, the variable-speed motor for driving the control shaft is stationary in this phase and it is only to set the desired speed difference that it is simply accelerated from stationary to a relatively low speed of revolution in a predetermined direction of rotation. The variable-speed motor can thus be of rela-tively low-power design and, in addition, the individual bearings of the control shaft and of the adjoining epicyclic gear are subjected to only low speeds of revolution.
According to Patent Claim 3, the input shaft of the second ~tage is rigidly connected to a third peri-pheral wheel, which acts via third planet wheels mounted on the web carrier on the second, in this case freely rotating, sun wheel. This special design offer~ addi-tional advantages over the embodiment in which a rigid connection is provided between the input shaft and the second sun wheel of the second stage.
If, namely, in this design in accordance with Claim 3, the control shaft of the second stage is fixed, the speed difference between the driven shafts of the first stage can be set by means of the rotatable further input shaft of the second stage independently of the main drive speed and specifically, in this case, with a speed ratio of 1:1 between the further input shaft and the output shaft of the second stage. If, on the other hand, the further input shaft is held fast and, instead, the control shaft of the second stage is used to set the speed difference, the same relationships as in the embodiment according to the invention in accordance with Claim 2 are once again established.
According to Patent Claim 5, the input shaft of the second stage is advantageously designed 80 as to be fixed, thereby reducing the manufacturing outlay for the gear while nevertheless providing the desired control-lability. If, on the other hand, the second sun wheel is, in accordance with Patent Claim 5, designed to be drive-able via the input shaft, the speed difference can beadditionally varied via this input shaft.
According to Patent Claims 8 and 9, the gear casing is used to drive the second peripheral wheel or the second web carrier. This makes the gear simpler in construction since the gear casing, which is present in any case, is at the same time used to drive the gear.
However, it is also possible that a stationary gear casing will be desired, for safety reasons for example, and in this case the gear elements to be driven can be driven by way of conventional driving means such as gear wheels and shafts, c~;n~ or belt drives.
According to Patent Claim 10, the common peri-pheral wheel provided for the first and second planet wheels of the second gear stage has separate tracks for 213~327 the planet wheels. This makes it possible to provide the tracks with different toothing optimally suited to the respective requirements.
It is, of course, also possible for separate peripheral wheels to be provided in the second gear stage and for these to be coupled or at least capable of being coupled to one another.
It is possible to use both planetary gears and cycloid gears for the epicyclic gear described. Nor is there a problem in combining a planetary gear stage with a cycloid gear stage to obtain an ideal epicyclic gear dep~n~;ng on requirements as to the transmission ratio, loadability and r~nning properties.
Further advantageous developments of the inven-tion form the sub~ect-matter of the rema;n;ng subclaims.
The invention will now be explained in greater detail with reference to the figures by means of a number of exemplary embodiments.
Figure 1 shows the entire epicyclic gear in a first ~hodiment, Figure 2 shows, in a sketch, the second gear stage of an epicyclic gear in accordance with Figure 1, Figure 3 shows, in a sketch, the second gear stage of an epicyclic gear in accordance with a second embodiment, Figure 4 shows, in a sketch, the second gear stage of an epicyclic gear in accordance with a third embodiment and Figure 5 shows, in a sketch, the second gear stage of an epicyclic gear as a further development of the gear shown in Figure 2.
The epicyclic gear in accordance with Fig. 1 consists of a first, cycloid gear stage and of a second planetary gear stage. A gear casing 3 of the first gear stage has a toothing 2 via which rotation is imparted to the gear casing 3 by a driving motor (not shown). The gear casing 3 simultaneou~ly serves as the first driven shaft of the first gear stage, to which the drum of a helical conveyor centrifuge can be connected, for 2136~27 example. A second driven shaft 4 of the first gear stage is formed by the output shaft proper of the epicyclic gear, which is operatively connected via the cycloid gear to the casing 1 of the first stage.
The second gear stage likewise has a ca~ing 1, which is rigidly connected to the casing 3 of the first stage and, together with the latter, forms a common casing body for the epicyclic gear. A control shaft 5 of the second stage, which is connected to a variable-speed motor (not shown), is situated on a side of the common casing body remote from the second driven shaft 4 of the first stage. Situated on this side, coaxially with the control shaft 5, is a further input shaft 6 of the second stage.
The mode of operation of the epicyclic gear is explained below by means of the construction of the gear, starting from the input side.
The gear casing 1, 3 is rotated by means of the toothing 2. An internal gear ring 7 of the cycloid gear stage is rigidly connected to the gear casing 1, 3, the said gear ring rotating with the gear casing 1, 3. The internal gear ring 7 interacts via two cam discs 8 with two eccentrics 10 seated on an output shaft 9 of the second gear stage and serving, in this exemplary embodi-ment, as the input shaft of the first gear stage. The cam discs 8 are mounted on pins 11 which, in turn, are con-nected to the second driven shaft 4 of the first stage.
In the first exemplary embodiment, the input shaft of the first stage is formed by the eccentrics 10 of the cycloid gear. However, it is also possible to provide the input shaft as an external component on which correspo~;ng eccentrics are arranged in a manner fixed in terms of rotation and which is coupled to the output shaft 9 of the second gear stage by means of a suitable shaft coupling.
If the input shaft of the first gear stage, i.e.
the output shaft 9 of the second gear stage, is held fast, the driving motor rotates the internal gear ring 7, whereby the cam discs 8 are rotated in accordance with 21~6327 g the transmission ratio. The rotary motion of the cam discs 8 is in turn transmitted via the pins 11 to the second driven shaft 4 of the second stage. If the output shaft 9 of the second stage is rotated in addition, the speed of the second driven shaft 4 of the first stage is reduced or increased, dep~n~;ng on the direction of rotation of the output shaft 9 of the second stage.
The mode of operation of the second gear stage is explained by means of its construction, starting from the control shaft 5.
According to the first exemplary embodiment in Figs. 1 and 2, the control shaft 5 is connected for rotation in common to a first sun wheel 12 which drives first planet wheels 13 mounted on webs 14 of a freely rotating web carrier 15. The first planet wheels 13 interact with a peripheral wheel 16, which is connected for rotation in common to the output shaft 9 of the second gear stage or input shaft of the first gear stage.
The further input shaft 6 of the second stage is provided with an integral, second sun wheel 17, which interacts by way of second planet wheels 18 mounted on the same webs 14 as the first planet wheels 13 with a second peripheral wheel 19 which is connected for rota-tion in common to the gear casing 1 of the second stage, driven by the driving motor.
The construction of the second gear stage is somewhat clearer from the sketch in accordance with Figure 2.
In normal operation, the input shaft 6 of the second stage is fixed and the speed difference between the two driven shafts 3, 4 of the first stage thus depends solely on the speed of the control shaft 5.
If the transmission ratio of the internal gear ring 7 and the driven shaft 4 of the first ~tage i8 56:55, then, with the input shaft of the first stage fixed, the driven shaft 4 rotates at a speed of 4072.7 rpm when the speed of the internal gear ring 7 is 4000 rpm. If the transmi~sion ratio of the input shaft and the driven shaft 4 of the first stage is 55:1, then, - 21~6~27 '- - 10 -with the internal gear ring 7 held fast, the driven shaft 4 rotates at a speed of -29.1 rpm when the speed of the input shaft of the first stage is 1600 rpm.
If the internal gear ring 7 and the input shaft of the first stage are rotated at the speeds given in a direction of rotation in which the speeds are added together, the resulting speed at the driven shaft 4 is 4044 rpm. The speed difference between the driven shaft 4, as the output shaft proper of the epicyclic gear, and the casing of the first stage as a second driven shaft 3 of the epicyclic gear, the latter shaft rotating at the input speed of 4000 rpm, is thus 44 rpm.
If the speed of the internal gear ring 7 now decreases to 3600 rpm while the speed of the input shaft of the first stage remains the same, the resulting speed at the driven shaft 4 is 3636 rpm, the speed difference thus being 36 rpm.
In order to achieve a constant speed difference, even when the input speed of the gear casing 1, 3 changes, the speed of the input shaft of the first stage must be changed as the input speed changes. In the abovementioned case, the speed of the input shaft of the first stage must be reduced to 1200 rpm. This change in speed is performed in the second gear stage. The reduc-tion in the speed of the second peripheral wheel 19(attached to the gear casing 1) of the second stage due to the reduced input speed results in a change in the speed of the web carrier 15 and the speed of the first peripheral wheel 16 - rigidly connected to the output shaft 9 of the second stage - and hence of the input shaft of the first stage is thereby reduced, with the gear design selected, by 400 rpm, with the result that the desired speed difference of 44 rpm between the two driven shafts 3 and 4 of the first stage is maintained automatically.
Figure 3 shows the second gear stage in accor-dance with a second embodiment. In this embodiment, the first gear stage is identical with that in the first embodiment. The first gear stage is therefore not .
- 2136~27 described again.
Basically, the second embodiment depicted differs from the first embodiment in that the first and second sets of planet wheels 113, 118, which act on the first and second sun wheel 112, 117 respectively of the second stage, have a common freely rotating satellite 120 but in this case are mounted on separate webs 114, 121. The first planet wheels 113 are mounted on first webs 114, which are connected by a first web carrier 115 to the output shaft 109 of the second stage. Second webs 121 are connected to the gear casing 101 of the second stage, the casing being driven by the driving motor. Thus, in con-trast to the first embodiment, the rotation of the gear casing 101 does not influence the speed of the web carrier but the speed of the common freely rotating satellite 120; influencing the speed of the satellite 120 in turn influences the speed of the first webs 114 and hence that of the driven shaft 109 of the second stage.
Figure 4 shows the second gear stage of a third embodiment correspon~;ng in terms of the construction of the gear to the second embodiment in accordance with Fig.
3. The difference with respect to the second embodiment is, however, that a cycloid gear is used for the second gear stage instead of a planetary gear.
The first sun wheel is here replaced by a first double eccentric 212 and the second sun wheel is replaced by a second double eccentric 217. The double eccentrics 212, 217 interact with cam discs 213, 218 which replace the planet wheels. The cam discs 213 interacting with the first double eccentric 213 are mounted on first pins 214, which replace the first webs and are again rigidly con-nected to the driven shaft 209. The second cam discs 218 are mounted on second pins 221 which, like the second webs of the second embodiment, are rigidly connected to the gear casing 201, which is driven by the driving motor. The mode of operation of this gear stage is accordingly identical with that of the second P~hodiment.
Figure 5 shows another exemplary embodiment of the second gear stage of the epicyclic gear according to 213~:~27 the invention.
- According to this exemplary embodiment, the output shaft 9 of the second stage is formed integrally with a first peripheral wheel 16, which acts via planet wheels 13 mounted on freely movable web carriers 14, 15 on a sun wheel 12 which is integrally connected to the control shaft 5 of the second stage. Second planet wheels 18 are mounted on the web carriers and these planet wheels make rolling contact with a peripheral wheel 19 attached to the gear casing 1 of the second stage and are in engagement with a second, freely rotating sun wheel 17. According to Fig. 5, this second sun wheel 17 is mounted on the control shaft 5 of the second stage and has another toothed track, in which the teeth of third planet wheels 20 engage. The third planet wheels are likewise mounted on the web carriers 14, 15 and have ~;m~n~ions correspo~;ng to those of the first and second planet wheels.
The third planet wheels 20, for their part, make rolling contact with a third peripheral wheel 21, which is rigidly connected to a further input shaft 6 of the second ~tage and has the same rolling diameter as the first peripheral wheel 16 of the second stage. As in the previous exemplary embodiments, the control shaft 5 and the further input shaft 6 are arranged coaxially, the input shaft 6 being designed as a hollow shaft in which the control shaft 5 is mounted so as to be rotatable relative to the input shaft 6.
If, in this exemplary embodiment, the further input Yhaft 6 of the second gear stage is fixed as in the exemplary e_bodiments described above, it is po~sible to adjust the speed difference between the first and second driven shafts 3, 4 of the first gear stage exclusively by means of the speed of the control shaft 5, a change in the speed of the control shaft resulting in a change in the speed difference concerned in accordance with the transmission ratio of the second gear stage.
If, however, the control shaft 5 of the second stage is now held fast in the exemplary embodiment in - 2136~7 _ - 13 -accordance with Fig. 5 and the change in the speed difference i8 performed by means of the further input shaft 6, different transmission ratios are obtained between the input shaft 6 and the output shaft 9 of the second stage, which latter shaft is rigidly connected to the input shaft of the first stage. According to Fig. 5, the third peripheral wheel 21, which i~ connected to the input shaft 6, is of identical design to the first peripheral wheel 16, which is connected to the output shaft 9 of the second gear stage. This means that it is possible to perform a change in the speed of the output shaft 9 and hence of the input shaft of the first stage in a ratio of 1:1 to the change in the speed of the further input shaft 6 of the second stage m~k; ng it possible to adjust the speed difference between the two driven shafts 3, 4 of the first stage in a simple manner at the variable-speed drive itself.
Claims (14)
1. Epicyclic gear with a first gear stage which has two driven shafts (3, 4) and one (3) of whose driven shafts is driven by a driving means, and with a second gear stage which has two output shafts (9, 109, 209, 1, 101, 201) and a control shaft (5, 105, 205) and one (1, 101, 201) of whose output shafts is rigidly connected to the driven shaft (3) of the first stage and the other (9, 109, 209) of whose output shafts is coupled to an input shaft of the first stage and, to adjust the speed difference between the two driven shafts (3, 4), can be driven by a driven element (16, 115, 215) of the second stage, the said driven element interacting by way of first planet wheels (13, 113, 213, 214) with a sun wheel (12, 112, 212) of the control shaft (5, 105, 205), characterized in that one output shaft (1, 101, 201) of the second stage has an engagement means (19, 121, 221) which acts on the driven element (16, 115, 215) of the second stage via second planet wheels (18, 118, 218) operatively connected to the first planet wheels (13, 113, 213, 214), the second planet wheels (18, 118, 218) being operatively connected to an input shaft (6, 106, 206) of the second stage via a second sun wheel (17, 117, 217).
2. Epicyclic gear according to Claim 1, characterized in that the driven element (16) is designed as a first peripheral wheel which is connected for rotation in common to the other output shaft (9) and interacts via the first planet wheels (13), which are mounted on a freely rotating web carrier (15), with the sun wheel (12) of the control shaft (5), and the engagement means (19) is designed as a second peripheral wheel, which is connected to one output shaft (1) of the second stage, the said output shaft being designed as a gear casing, and interacts via the second planet wheels (18) mounted on the web carrier (15) with the second sun wheel (17).
3. Epicyclic gear according to Claim 2, characterized in that the input shaft (6) of the second stage is connected for rotation in common to a third peripheral wheel, which acts via third planet wheels mounted on the web carrier (15) on the second, freely rotating sun wheel (17).
4. Epicyclic gear according to Claim 1, characterized in that the driven element (115, 215) is designed as a first web carrier which is connected for rotation in common to the other output shaft (109, 209) and which carries the first planet wheels (113, 213), which interact with a freely rotating peripheral wheel (120, 220) and with the sun wheel (112, 212) of the control shaft (105, 205), and the engagement means (121, 221) is designed as a second web carrier (121, 221), which is fixed in one output shaft (101, 201) - designed as a gear casing - of the second stage and carries the second planet wheels (118, 218), which interact with the freely rotating peripheral wheel (120, 220) and the second sun wheel (117, 217).
5. Epicyclic gear according to one of Claims 1 to 4, characterized in that the input shaft (6, 106, 206) of the second stage is of fixed design.
6. Epicyclic gear according to one of Claims 1 to 4, characterized in that the second sun wheel (17, 117, 217) is driveable via the input shaft (6, 106, 206).
7. Epicyclic gear according to one of Claims 1, 2 or 4, characterized in that the input shaft (6, 106, 206) is rigidly connected to the second sun wheel (17, 117, 217).
8. Epicyclic gear according to one of Claims 4 to 7, characterized in that the second web carrier (121, 221) is driven by the driving means via one output shaft (101, 201) - designed as a gear casing - of the second stage.
9. Epicyclic gear according to one of Claims 1 to 3, characterized in that the second peripheral wheel (19) is driven by the driving means via one output shaft (1) - designed as a gear casing - of the second stage.
10. Epicyclic gear according to one of Claims 4 to 8, characterized in that the peripheral wheel (120, 220) of the second gear stage has two separate tracks for the first (113, 213) and second planet wheels (118, 218).
11. Epicyclic gear according to Claim 10, characterized in that the tracks are of different design.
12. Epicyclic gear according to one of Claims 1 to 11, characterized in that at least one gear stage is designed as a cycloid gear, two eccentrics (212, 217) of the cycloid gear forming sun wheels, two cam discs (213, 218) of the cycloid gear forming planet wheels and a peripheral wheel (220) of the cycloid gear forming the peripheral wheel of a planetary gear.
13. Epicyclic gear according to one of Claims 4 to 8, characterized in that the peripheral wheel (120, 220) of the second gear stage has a track of identical design for the first (113, 213) and second planet wheels (118, 218).
14. Epicyclic gear according to one of Claims 1 to 13, characterized in that one driven shaft (3) - designed as a gear casing with a peripheral wheel - of the first gear stage is driven by one output shaft (1) - designed as a gear casing of the second gear stage.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4310158A DE4310158C1 (en) | 1993-03-29 | 1993-03-29 | Orbital gearbox with two output shafts |
| DEP4310158.5 | 1993-03-29 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2136327A1 true CA2136327A1 (en) | 1994-10-13 |
Family
ID=6484135
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002136327A Abandoned CA2136327A1 (en) | 1993-03-29 | 1994-03-15 | Planetary gear with two driven shafts |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP0642637A1 (en) |
| JP (1) | JPH07507623A (en) |
| KR (1) | KR950701721A (en) |
| CN (1) | CN1108458A (en) |
| CA (1) | CA2136327A1 (en) |
| DE (1) | DE4310158C1 (en) |
| WO (1) | WO1994023223A1 (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19511749A1 (en) * | 1995-03-30 | 1995-10-05 | Horst Wandelt | Planetary mechanical drive with two take-off shafts |
| FR2746675B1 (en) * | 1996-03-29 | 1998-05-07 | Guinard Centrifugation | REDEX MODULE CENTRIFUGAL DECANTER |
| SE507365C2 (en) * | 1996-09-23 | 1998-05-18 | Scandrive Hallstahammar Ab | Control device for effecting angular changes between two rotatable elements |
| GB2329905B (en) | 1997-08-29 | 1999-12-15 | Nsk Ltd | Lubricant composition for a rolling apparatus |
| WO2002081094A1 (en) * | 2001-04-04 | 2002-10-17 | Centriquip Limited | A gearbox for a centrifuge, such as a decanter centrifuge |
| DE102006028803A1 (en) * | 2006-06-23 | 2007-12-27 | Westfalia Separator Ag | screw centrifuge |
| DE102006028804A1 (en) † | 2006-06-23 | 2007-12-27 | Westfalia Separator Ag | Slug centrifuge with drive device |
| KR101394918B1 (en) * | 2007-10-23 | 2014-05-14 | 카이퍼 게엠베하 운트 코. 카게 | Gear stage |
| CN101956816A (en) * | 2009-07-14 | 2011-01-26 | 金昱诚 | Control device for continuously variable transmission |
| CN104074930B (en) * | 2014-07-17 | 2016-08-31 | 天津职业技术师范大学 | A kind of coaxial single input homonymy dual output cycloidal reducer |
| CN104455234B (en) * | 2014-12-02 | 2016-08-24 | 孙建宁 | A kind of infinitely variable transmission of many power Mixed design pair/mono-output |
| DE102016118428A1 (en) * | 2016-09-29 | 2018-03-29 | Schunk Gmbh & Co. Kg Spann- Und Greiftechnik | cycloidal drive |
| DE102016118427A1 (en) * | 2016-09-29 | 2018-03-29 | Schunk Gmbh & Co. Kg Spann- Und Greiftechnik | cycloidal drive |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2196368A (en) * | 1938-09-01 | 1940-04-09 | Thomson James | Epicyclic gearing |
| GB1131579A (en) * | 1967-02-28 | 1968-10-23 | Hitachi Shipbuilding Eng Co | Improvements relating to centrifugal separating machines with differential drives |
| FR2070485A5 (en) * | 1969-12-05 | 1971-09-10 | Defontenay Paul | Control system for centrifuge - to produce differential rotation |
| FR2177242A5 (en) * | 1972-03-21 | 1973-11-02 | Holweg Const Mec | |
| FR2247641A1 (en) * | 1973-10-16 | 1975-05-09 | Weingarten Ag Maschf | Gear drive with output to input phase control - for machine tools can operate when machine is running |
| DE2811887C2 (en) * | 1978-03-18 | 1991-07-18 | Westfalia Separator Ag, 4740 Oelde | Drive for a continuously working screw centrifuge |
| FR2610058A1 (en) * | 1987-01-26 | 1988-07-29 | Maag France | Power transmission device with speed reduction between a rotating assembly and a shaft mounted coaxially inside the latter |
| GB2239924B (en) * | 1990-01-08 | 1993-06-30 | Alfa Laval Sharples Ltd | Centrifuge gearboxes |
| NO171328C (en) * | 1990-10-01 | 1993-02-24 | Ken Lillevik | GIR DEVICE |
-
1993
- 1993-03-29 DE DE4310158A patent/DE4310158C1/en not_active Expired - Lifetime
-
1994
- 1994-03-15 KR KR1019940704250A patent/KR950701721A/en not_active Application Discontinuation
- 1994-03-15 EP EP94911892A patent/EP0642637A1/en not_active Withdrawn
- 1994-03-15 CA CA002136327A patent/CA2136327A1/en not_active Abandoned
- 1994-03-15 CN CN94190236A patent/CN1108458A/en active Pending
- 1994-03-15 WO PCT/EP1994/000809 patent/WO1994023223A1/en not_active Application Discontinuation
- 1994-03-15 JP JP6521602A patent/JPH07507623A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| WO1994023223A1 (en) | 1994-10-13 |
| EP0642637A1 (en) | 1995-03-15 |
| CN1108458A (en) | 1995-09-13 |
| DE4310158C1 (en) | 1994-12-22 |
| JPH07507623A (en) | 1995-08-24 |
| KR950701721A (en) | 1995-04-28 |
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