Transmission

Abstract

The invention relates to a transmission: comprising a first gearwheel (1), which has an internal toothing system and can be rotatably driven by a clutch; a first satellite gearwheel (2), which is rotatably mounted and is in an interlocking or meshing connection to the first gearwheel (1); a second satellite gearwheel (3), which is rotatably mounted and is in an interlocking or meshing connection to the first satellite gearwheel (2); a second gearwheel (4), which has an internal toothing system and is in an interlocking or meshing connection to the second satellite gearwheel (3); a first shaft (2a), which makes it possible to transmit an outgoing output force and is connected to the first satellite gearwheel (2); and a second shaft (3a), which is connected to the second satellite gearwheel (3); characterized in that the second gearwheel (4) is stationary, and the second satellite gearwheel (3), which can be driven via the first satellite gearwheel (2) and the first gearwheel (1), exerts or transmits, in a driven state, a force on movable gearwheel carriers (5, 6) via the second shaft (3a), such that the first and second satellite gearwheel (2, 3) perform a rotation about the respective satellite gearwheel axis of rotation (y, z) and a coaxial movement about a gearwheel axis of rotation (x).

Description

[0001] TRANSMISSION

[0002] The present invention relates to a transmission comprising a first gear which has internal teeth and is rotatably driven by an incoming driving force, a first satellite gear which is rotatably mounted and is in an interlocking or meshing connection with the first gear, a second satellite gear which is rotatably mounted and is in an interlocking or meshing connection with the first satellite gear, a second gear which has internal teeth and is in an interlocking or meshing connection with the second satellite gear, and a first shaft which enables the transmission of an outgoing output force and is connected to the first satellite gear.

[0003] BACKGROUND OF THE INVENTION

[0004] A gearbox is a mechanical device for converting motion and force, its function based on the principles of kinematics. In kinematics, work is based on the lever principle, where the relationship between the applied force and the distance traveled is proportional. As the active force increases, the distance traveled decreases, and conversely, as the distance traveled increases, the active force decreases. The applied force determines the maximum distance that can be traveled and the time required to do so. If one wants to increase the maximum traversable distance, an increase in the active force is unavoidable.

[0005] A gearbox is described, for example, in WO 2017 / 072551 Al, in which an input and an output shaft are provided, the input shaft being coupled via gears with planetary or internal teeth. An eccentric gear ratio ensures a change in speed between the shafts, with the output shaft rotating at a lower speed than the input shaft.

[0006] Problems with such transmissions, according to the prior art, include friction losses and mechanical losses in the transmission system. The purpose of the present invention is to describe a transmission system that overcomes the aforementioned disadvantages. BRIEF DESCRIPTION OF THE INVENTION

[0007] The object of the present invention is therefore to provide a transmission which takes into account the kinetic energy and reactive energy in such a way as to increase efficiency and effectiveness.

[0008] This problem is solved by a transmission comprising a first gear having internal teeth and rotatable drive, a first satellite gear rotatably mounted and in meshing or interlocking connection with the first gear, a second satellite gear rotatably mounted and in meshing or interlocking connection with the first satellite gear, a second gear having internal teeth and in meshing or interlocking connection with the second satellite gear, a first shaft enabling the transmission of an outgoing output force and connected to the first satellite gear, and a second shaft connected to the second satellite gear, characterized in that the second gear is stationary and the second satellite gear,which can be driven via the first satellite gear and the first gear, exerts or transmits a force via the second shaft to movable gear carriers, such that the first and second satellite gears perform a rotation about the respective satellite gear rotation axis and a coaxial movement about a gear rotation axis.

[0009] Because the second gear is stationary, the second satellite gear is forced to transfer some of its kinetic energy to the gear carriers or exert force on them. This exerted force corresponds to a reactive force applied at a third engagement point C. At the third engagement point C, the second satellite gear is in an interlocking or meshing connection with the second gear. The force coupling that arises between a second engagement point B and the third engagement point C is converted into an active force via a fourth engagement point D, where at the second engagement point B, the first satellite gear is in an interlocking or meshing connection with a second satellite gear, and at the fourth engagement point D, the second shaft is connected to the first and second gear carriers.Through this conversion, a fifth engagement point E, and the first shaft, a coaxial movement of the second satellite gear occurs. Consequently, the conversion of the reactive force into an active force forces a movement of the gear carrier, and this forced movement results in the satellite gears performing a dual motion. This dual motion consists of, firstly, a rotation around the respective satellite gear rotation axes Y and Z, and secondly, a coaxial movement around the gear rotation axis X. This dual motion thus both enhances the kinetic energy of the two satellite gears and reduces the reactive forces, whereby a portion of the reactive force is converted, and the remainder remains in the form of frictional forces. This optimizes and increases the efficiency and effectiveness of the gearbox. Furthermore, very high forces can be transmitted through this gearbox.These characteristics make the gearbox suitable for use in various vehicles and machines. Furthermore, a compact gearbox design and increased flexibility in the arrangement of the drive components are possible.

[0010] Preferably, a vehicle is provided which comprises an engine, a drive train and a transmission, wherein the transmission is designed according to the invention and wherein the first gear is connected to the engine and the first shaft is connected to the drive train.

[0011] A gear carrier is a support that holds the satellite gears in a circular motion around the gear rotation axis X and enables rotation around the respective satellite gear rotation axes Y and Z. Preferably, the first gear is connected to the motor via a coupling. While the first gear completes a full rotation or a 360° rotation, the gear carrier completes a half rotation or a 180° rotation.

[0012] Furthermore, the gears, i.e., first and second gear as well as first and second satellite gear, can each have an axial axis, with the respective axial axis passing through the center of the teeth of the respective gear.

[0013] In a preferred embodiment, the axial axis of the first satellite gear is displaced radially to the left or right of the axial axis of the first gear, preferably by at least half the gear width of the first gear. The same applies to the second satellite gear and the second gear, such that each axial axis of the gears—first and second satellite gears, as well as the second gear—is displaced radially to the left or right of the axial axis of the first gear. The two satellite gears can be designed as externally toothed spur gears, while the two gears can be designed as internally toothed ring gears. The first gear preferably has a connection for a coupling to drive the first gear in a rotatable manner.

[0014] In a preferred embodiment, the two internally toothed gears have the same diameter. Furthermore, the two gears can also have the same tooth width.

[0015] In a preferred embodiment, the first satellite gear has a diameter larger than that of the second satellite gear. This dimensioning of the satellite gears makes it possible to utilize the lever principle for the system's kinematics. For example, this allows the force coupling to occur at half the diameter of a gear twice the size. Utilizing the lever principle enables an amplification of the transmitted force and more efficient power transmission. This results in an efficiency that increases with the size of the second satellite gear or the length of the lever arm. Furthermore, in a reversible motion mode, the directions of rotation, lever ratios, lever arms, gear speeds, satellite gear speeds, and the direction of frictional forces (reaction forces generated by the work) can be reversed, thus reducing the active force.

[0016] If, for example, the first and second satellite gears are in a 1:3 ratio, then the lever arm between the gear's rotation axis X and the fifth gripping point E, and between the gear's rotation axis X and the fourth gripping point D, is in a 3:1 ratio. According to the law of conservation of energy, the second satellite gear absorbs a portion of the force from the first satellite gear, theoretically approximately 1% of the force. In practice, however, the second satellite gear will absorb exactly the amount of force required for the coaxial movement of the first satellite gear. Regardless of the magnitude of this force, it is doubled at the fourth gripping point D by the force coupling between the second gripping point B and the third gripping point C. Due to the 3:1 lever ratio, this doubled force is amplified by a factor of 3 at the fifth gripping point E.Based on coaxial motion, the second satellite gear rotates around its gear rotation axis X, while the first gear rotates the second satellite gear around its own satellite rotation axis Y. This creates frictional forces between the output shaft and the first shaft. This frictional relief enables the second satellite gear to fully leverage its position between the engagement points A and B. Consequently, the efficiency is further increased through the interplay of the lever principle and the dual motion.

[0017] Furthermore, the satellite gear rotation axes Y and Z exhibit a certain distance from the gear rotation axis X in the vertical direction due to the diameters of the satellite gears. This distance between the gear rotation axis X and the satellite gear rotation axes Y and Z depends on the diameter of the respective satellite gear. For example, an increasing diameter of the first satellite gear causes the distance between its satellite gear rotation axis Y and the gear rotation axis X to decrease, while simultaneously the diameter of the second satellite gear decreases, thus increasing the distance between the gear rotation axis X and the satellite gear rotation axis Z of the second satellite gear. Besides the distance between the rotation axes, the different diameters of the satellite gears can also influence the rotational speeds of the two satellite gears.The individual axes of rotation are arranged parallel to each other.

[0018] The coaxial movement around the gear's rotation axis X can occur along the direction of rotation of the second satellite gear. This allows for greater power transmission in a smaller space, as well as more efficient power transmission, resulting in increased efficiency.

[0019] Furthermore, the second satellite gear can be arranged offset from the first satellite gear along the gear rotation axis X. This allows the first satellite gear to be connected only to the first and second satellite gears, while the second satellite gear is connected only to the second and first satellite gears.

[0020] The first satellite gear can exert a force on an output shaft, preferably located outside the gearbox, via the first shaft and coaxial movement around the gear's rotation axis X. This arrangement allows for maximum flexibility in the arrangement of the drive components.

[0021] In one embodiment, the thickness of the internal teeth of the first gear is less than the thickness of the first satellite gear. This also facilitates the first satellite gear being in contact only with the first gear and the second satellite gear.

[0022] In another embodiment, the thickness of the internal teeth of the second gear is less than the thickness of the second satellite gear. This also facilitates the fact that the second satellite gear is only in contact with the second gear and the first satellite gear.

[0023] In a special embodiment, the thickness of the satellite gears is twice as large as the thickness of the gears.

[0024] The sum of the outer diameters of the satellite gears can be equal to the diameter of the first or second gear.

[0025] The first and second gears can each be connected to each other on the left and right sides by a mounting bracket. These brackets can be attached to the gears using fasteners such as screws. This results in the most stable construction possible.

[0026] DETAILED DESCRIPTION OF THE INVENTION

[0027] Details and advantages of the invention are explained with reference to the figures and the figure description.

[0028] Figs. a1a and b show an assembled configuration of a gearbox according to the invention in different sectional views.

[0029] Fig. 2 shows a sectional view of an assembled configuration of a gearbox according to the invention with an output shaft.

[0030] Fig. 3 shows a sectional view of an assembled configuration of a transmission according to the invention with two output shafts rotating at the same speed. Fig. 4 shows a sectional view of an assembled configuration of a transmission according to the invention with two output shafts rotating at different speeds.

[0031] Fig. 5 shows a sectional view of an assembled configuration of the gearbox according to the invention with an output shaft.

[0032] Figures 1a and 1b show an assembled configuration of a transmission according to the invention in different sectional views. Specifically, a first gear 1, designed as an internally toothed ring gear, is connected to or arranged on a drive force. The drive force causes the first gear 1 to rotate, and the first gear 1 can rotate about a gear rotation axis X. The gear rotation axis X also forms the main axis of the entire transmission. At a first engagement point A, the first gear 1 is in an interlocking or meshing connection with a first satellite gear 2, whereby, due to the thickness of the first satellite gear 2, which is twice the thickness of the first gear 1, only a partial area of ​​the tooth flanks of the first satellite gear 2 is in contact with the tooth flanks of the first gear 1.Specifically, the teeth of the first gear 1 engage with the right half of the teeth of the first satellite gear 2 across their entire width. Due to its active function in the transmission, the first gear 1 serves exclusively to transmit the drive force, for example from a motor, to the first satellite gear 2. This first satellite gear 2 is connected to a first shaft 2a and is rotatable about a satellite gear rotation axis Y, which is parallel to the gear rotation axis X. In the vertical direction, the satellite gear rotation axis Y is offset from the gear rotation axis X by a distance that depends on the diameter of the first satellite gear 2. Furthermore, the satellite gear rotation axis Y also forms the rotation axis of the first shaft 2a.At a second gripping point B, the first satellite gear 2 is in an interlocking or meshing connection with a second satellite gear 3. The teeth of the first satellite gear 2 are in interlocking contact with the right half of the teeth of the second satellite gear 3, with the left side of the teeth meshing. The second satellite gear 3 has a second shaft 3a and is rotatable about a satellite gear rotation axis Z. The satellite gear rotation axis Z is also arranged parallel to the gear rotation axis X, with the satellite gear rotation axis Z maintaining a certain vertical distance from the gear rotation axis X. This distance, in turn, depends on the diameter of the second satellite gear 3.The second satellite gear 3 is also offset from the first satellite gear 2 along the gear rotation axis X, so that only a partial surface of the tooth flanks of the second satellite gear 3 is in contact with a partial surface of the tooth flanks of the first satellite gear 2. This offset prevents contact between the second satellite gear 3 and the first gear 1. At a third engagement point C, the second satellite gear 3 is in an interlocking or meshing connection with a second gear 4, with the left side of the second satellite gear 3 engaging across the entire width of the second gear 4. To make this possible, the second satellite gear 3 is twice as thick as the second gear 4. The second gear 4 is stationary.Designed to be immobile, so that the second satellite gear 3, which can be driven via the first satellite gear 2 and the first gear 1, exerts a force on a movable first and second gear carrier 5, 6 at a fourth gripping point D in a driven state.

[0033] At the fourth gripping point D, the first shaft 2a is connected to the first and second gear carriers 5, 6, with ball bearings 11, 14 arranged between the first shaft 2a and the two gear carriers 5, 6. The ball bearings 11, 14 have oil seals, for example, oil seals, and retaining rings for fastening. The force exerted on the gear carriers 5, 6 results in a forced movement of the gear carriers 5, 6, which occurs in the direction of rotation of the first satellite gear 2 and is enabled by ball bearings 10, 15. The ball bearings 10, 15 are arranged between the gear carrier 5, 6 and the respective gear 1, 4. The ball bearings 10, 15 have oil seals, for example, oil seals, and retaining rings for fastening. This forced movement is accompanied by the conversion of the reactive force at a fifth gripping point E into an active force or conversion of kinetic energy.At the fifth engagement point E, the second shaft 3a is connected to the first and second gear carriers 5, 6, with needle bearings 12, 13 arranged between the second shaft 3a and the two gear carriers 5, 6. Due to the conversion of the reactive force into an active force, the two satellite gears 2, 3 perform a dual motion. The two satellite gears 2, 3 rotate about their respective axes of rotation Y, Z, and simultaneously perform a coaxial motion about the gear axis of rotation X. This increases the efficiency of the power transmission and consequently also the overall efficiency. The second gear 4 has a purely passive function in the gearbox, as it is stationary and serves to cause the second satellite gear 3 to move along its inner circumference.

[0034] The first and second gears 1, 4 can each be connected to each other on the left and right sides by a mounting plate 8, 9. The respective mounting plate 8, 9 is connected to the first and second gears 1, 4 via fastening elements 18, 19.

[0035] Furthermore, the two gears 1 and 4 have the same diameter and tooth width. Additionally, the sum of the outer diameters of the satellite gears 2 and 3 is equal to the diameter of the first or second gear 1 or 4.

[0036] The force coupling of the first satellite gear 2, which lies between the first gripping point A and the second gripping point B, exerts a double active force on an output shaft 7 via the first shaft 2a. The transmission of an outgoing driven force is possible via the output shaft 7, and consequently, for example, a driven machine can be connected to the output shaft.

[0037] Furthermore, the satellite gears 2 and 3 have a dual function in the gearbox. The first satellite gear 2 drives the second satellite gear 3 and simultaneously transmits the power via the first shaft 2a outside the gearbox to an output shaft 7. The second satellite gear 3, by moving along the inner circumference of the stationary second gear 4, causes a forced movement of the gear carriers 5 and 6.

[0038] The gear carriers 5 and 6 also fulfill a dual function in the gearbox. On the one hand, the gear carriers 5 and 6 support the satellite gears 2 and 3, which corresponds to a passive function. On the other hand, the gear carriers fulfill an active function. Here, the force transmitted by the second satellite gear 3 at the fourth engagement point D is transferred to the fifth engagement point E, causing a forced coaxial movement of the first satellite gear 2.

[0039] The kinematics of the transmission are based on the lever principle. Accordingly, the diameter of the first satellite gear 2 is dimensioned such that it is larger than the diameter of the second satellite gear 3. For example, this results in force coupling at half the diameter of a gear twice the size. This gear ratio between the first and second satellite gears 2 and 3 allows, on the one hand, the distance between the respective satellite gear rotation axes Y and Z and the gear rotation axis X to be changed. On the other hand, this gear ratio allows the rotational speeds of the satellite gears to be adjusted.

[0040] Furthermore, it can be seen in Fig. 1a that each gear 1, 2, 3, 4 has an axial axis which passes through the center of the teeth of the gear 1, 2, 3, 4.

[0041] Each axial axis of the gears 2, 3, 4 is radially displaced to the left or right of the axial axis of the first gear 1, wherein the axial axis of the gears 2, 3, 4 is preferably displaced by at least half the gear width of the first gear 1.

[0042] Figures 2 to 5 each show a variant of the previously described transmission and differ only slightly from the description above.

[0043] Figures 2 and 5 each show a sectional view of an assembled configuration of an embodiment of a transmission according to the invention with an output shaft. Accordingly, Figure 2 shows a cardan shaft as the output shaft 7, while Figure 5 shows a double chain as the output shaft 7. Furthermore, in both illustrations, the transmission according to the invention is arranged in a housing 20.

[0044] In contrast, a sectional view of an assembled configuration of an embodiment of a transmission according to the invention with two output shafts rotating at the same speed is shown in Fig. 3. The two opposing output shafts 7, 7' operate synchronously and transmit the output power at identical speeds.

[0045] Finally, Fig. 4 shows a sectional view of an assembled configuration of an embodiment of a transmission according to the invention with two output shafts rotating at different speeds. The power transmission of the two opposing output shafts 7 is asymmetrical. One output shaft 7 is designed as a cardan shaft, while the other output shaft 7' is designed as a gear transmission.

[0046] Reference symbol list:

[0047] 1 First gear 2 First satellite gear

[0048] 2a First wave

[0049] 3 Second satellite gear

[0050] 3a Second wave

[0051] 4 Second gear

[0052] 5 First gear carrier

[0053] 6 Second gear carrier

[0054] 7, 7' Output shaft

[0055] 8, 9 Mounting flat irons

[0056] 10, H, 14, 15, 16 ball bearings

[0057] 12, 13 needle bearings

[0058] 17 ball bearing housings

[0059] 18, 19 Fasteners

[0060] 20 cases

[0061] A First gripping point

[0062] B Second gripping point

[0063] C Third gripping point

[0064] D Fourth gripping point

[0065] E Fifth gripping point

[0066] X gear rotation axis

[0067] Y, Z satellite gear rotation axis

Claims

REQUIREMENTS 1. Gearbox, comprising • a first gear (1) which has internal teeth and is rotatably driven, • a first satellite gear (2) which is rotatably mounted and is in an interlocking or meshing connection with the first gear (1), • a second satellite gear (3) which is rotatably mounted and is in an interlocking or meshing connection with the first satellite gear (2), • a second gear (4) which has internal teeth and is in an interlocking or meshing connection with the second satellite gear (3), • a first shaft (2a) which enables the transmission of an outgoing driven force and is connected to the first satellite gear (2), and • a second shaft (3a) which is connected to the second satellite gear (3), characterized in that the second gear (4) is stationary and the second satellite gear (3), which can be driven via the first satellite gear (2) and the first gear (1), exerts or transmits a force on movable gear carriers (5, 6) via the second shaft (3a) in a driven state, so that the first and second satellite gears (2, 3) perform a rotation about the respective satellite gear rotation axis (Y, Z) and a coaxial movement about a gear rotation axis (X).

2. Gearbox according to claim 1, characterized in that the first satellite gear (2) has a diameter which is larger than the diameter of the second satellite gear (3).

3. Gearbox according to claim 1 or 2, characterized in that the coaxial movement about the gear rotation axis (X) occurs along the direction of rotation of the second satellite gear (2).

4. Gearbox according to any one of claims 1 to 3, characterized in that the second satellite gear (3) is arranged offset from the first satellite gear (2) along the gear rotation axis (x).

5. Gearbox according to one of claims 1 to 4, characterized in that a force can be exerted on an output shaft (7), which is preferably arranged outside the gearbox, via the first satellite gear (2) via the first shaft (2a) and the coaxial movement about the gear rotation axis (X).

6. Gearbox according to one of claims 1 to 5, characterized in that the thickness of the internal teeth of the first gear (1) is less than the thickness of the first satellite gear (2).

7. Gearbox according to one of claims 1 to 6, characterized in that the thickness of the internal teeth of the second gear (2) is less than the thickness of the second satellite gear (3).

8. Gearbox according to one of claims 1 to 7, characterized in that the first and second gear (1, 4) are connected to each other on the left and right sides by a fastening flat iron.

9. Gearbox according to one of claims 1 to 8, characterized in that the gears (1, 2, 3, 4) each have an axial axis, wherein the respective axial axis passes through the center of the teeth of the respective gear (1, 2, 3, 4).

10. Gearbox according to claim 9, characterized in that the first and second satellite gear (2, 3) and the second gear (4) are displaced radially to the left or right of the axial axis of the first gear (1).

Images