DE102023108107A1 - PLANETARY GEAR - Google Patents

Abstract

The invention relates to a self-locking planetary gear (1), which has a pinion (2) with at least one gear (21), a ring gear (3) with a plurality of teeth (31) and a plurality of planetary gears (4) between the pinion (2 ) and the ring gear (3). Each planetary gear (4) has a plurality of gear teeth (41) which mesh with the gear teeth (31, 21) of the ring gear (3) and the pinion (2). The gear teeth (21, 31, 41) are contoured in such a way that, during operation, rotating the pinion (2) induces a corresponding rotation of the planet gears (4), while rotating the planet gears (4) induces a force (F2/1), which is not sufficient to induce a corresponding rotation of the pinion (2).

Description

Technical field of the invention

The invention relates to the field of planetary gears. In particular, but not exclusively, the present invention also relates to a drive assembly which has a motor coupled to the pinion of a planetary gear and a tubular motor having the arrangement.

Technical background

Tubular motor assemblies, which have motors coupled to the pinions of planetary gears, are commonly used, for example in systems with windable motorized elements.

Such tubular motor assemblies are usually also used in motorized roller shutter systems. The EP3470616A1 describes such a system in which the tubular motor assembly has a planetary gear driven by a brushless motor.

Brief description of the invention

The invention aims to mitigate the problems observed when using motor assemblies with planetary gears in applications where reversibility is not desired (drive of the gear input by output rotation is not desired).

The invention relates to a self-locking planetary gear, which has: a pinion with at least one gear, a ring gear with a plurality of gear teeth; and one or more planetary gears between the pinion and the ring gear, the or [sic] each planetary gear having a plurality of toothings that mesh with the gear teeth of the ring gear and the pinion. According to the invention, the gear teeth are contoured such that, in operation, rotating the pinion induces a corresponding rotation of the one or more planetary gears, while rotating the one or more planetary gears induces a force that is insufficient to induce a corresponding rotation of the pinion .

The invention thus creates a planetary gear with gear contours that ensure a self-locking function when the output of the gear drives. This self-locking function is therefore particularly useful in applications where the transmission output can be driving. This can be the case, for example, if the gear train is coupled to a brushless motor.

This means that high reduction ratios can also be achieved.

In operation, rotation of the pinion may induce an effective force extending away from the center of the or each planetary gear to induce corresponding rotation of the one or more planetary gears. By rotating the one or more planet gears, an effective force may be induced near the center of the pinion so as not to induce corresponding rotation of the pinion.

The teeth can be helical.

The tooth or each tooth of the pinion can always be in contact with at least one tooth of the or each planetary gear. The helix angle and the width of the gears can be adjusted so that the or each tooth of the pinion can always be in contact with at least one tooth of the or each planetary gear.

The tooth or each tooth of the pinion can always be in contact with at least two teeth of the or each planetary gear. The helix angle and the width (b) of the gears can be adjusted so that the tooth or each tooth of the pinion can always be in contact with at least two teeth of the or each planetary gear.

The tooth or each tooth of the pinion can always be in contact with at least three teeth of the or each planetary gear. The helix angle and the width (b) of the gears can be adjusted so that the or each tooth of the pinion can always be in contact with at least three teeth of the or each planetary gear.

At least two teeth of the or each planetary gear can always be in contact with the respective teeth of the ring gear.

The helix angle of the teeth of the one or more planetary gears and/or the ring gear can be at least 20°. The helix angle of the teeth of the one or more planetary gears and/or the ring gear can be between 20° and 40°. The helix angle of the teeth of the one or more planetary gears and/or the ring gear can be between 25° and 35°, for example approximately 30°.

The pinion may have three or fewer teeth. The pinion may have two or fewer teeth. The pinion can have a single tooth.

The gear teeth can be contoured so that the pressure angle corresponding to the or each plane tenrad and the pinion is such that, in operation, rotating the pinion induces a corresponding rotation of the one or more planetary gears, while rotating the one or more planetary gears induces a force that is insufficient to cause a corresponding rotation of the To induce pinion.

The invention also relates to a self-locking planetary gear, comprising: a pinion with at least one gear; a ring gear with a plurality of gear teeth; and one or more planet gears between the pinion and the ring gear, the or each planet gear having a plurality of gear teeth meshing with the gear teeth of the ring gear and the pinion; wherein the pressure angle common to the or each planetary gear and the pinion is selected such that, in operation, rotating the pinion induces a corresponding rotation of the one or more planetary gears, while rotating the one or more planetary gears induces a force, which is not sufficient to induce a corresponding rotation of the pinion.

The pressure angle common to the or each planetary gear and the pinion, in particular the transverse pressure angle, can be between 30° and 60°, for example approximately 35°. The pressure angle common to the or each planetary gear and the pinion, in particular the transverse pressure angle, can be between 35° and 55°. The pressure angle common to the or each planetary gear and the pinion, in particular the transverse pressure angle, can be between 35° and 45°. The pressure angle common to the or each planetary gear and the pinion, in particular the transverse pressure angle, is preferably between 35° and 40°.

The gear teeth of the pinion and/or the one or more planetary gears may be selected such that the coefficient of friction between them, in operation, is between 0.08 and 0.14. Preferably, the gear teeth of the pinion and/or the one or more planet gears can be selected so that the coefficient of friction between them in operation is between 0.10 and 0.12, for example approximately 0.11.

The gear teeth of the one or more planetary gears and/or the ring gear can also be selected so that the coefficient of friction between them during operation is between 0.08 and 0.14, preferably between 0.10 and 0.12, for example approximately 0 .11.

The one or more planetary gears have at least three planetary gears, for example four planetary gears. The one or more planetary gears can have several planetary gears. The plurality of planetary gears can have at least three planetary gears, for example four planetary gears.

The ring gear can have at least one spline, for example for engagement in a tubular housing in which the self-locking planetary gear is to be stored.

The invention further relates to a drive assembly, comprising a motor which is coupled to the pinion of a self-locking planetary gear as described above.

The motor may comprise a brushless motor. The drive assembly can have a first stage, which is formed by the self-locking planetary gear. The drive assembly can have a second planetary gear stage. The drive assembly can have one or more additional planetary gear stages. The second stage or the further stages of the planetary gear may not be self-locking.

The invention further relates to a tubular motor assembly having a drive assembly, as described above.

For the avoidance of doubt, all features described herein also apply to every aspect of the invention.

Within the scope of this application it is expressly provided that the various aspects, embodiments, examples and alternatives disclosed in the preceding paragraphs, in the claims and/or in the following description and drawings, in particular their individual features, can be used individually or in any combination. In other words, all embodiments and/or features of each embodiment can be combined in any way as long as these features are compatible.

For the avoidance of doubt, the terms "may", "and/or", "for example", "for example" [sic: repeated expression] and any other similar term used herein must be interpreted as non-limiting, so that any feature described herein is not must absolutely be present. Of course, any combination of optional features is expressly contemplated without departing from the scope of the invention, whether expressly claimed or not. The applicant reserves the right to amend an originally filed claim or to file a new claim accordingly, including the right to amend an originally filed claim so that it depends on another claim and/or includes a feature of another claim even though it is not originally claimed in this way.

Short description of the characters

• [1] 1 einen erfindungsgemäßen Getriebezug veranschaulicht;
• [2] 2 eine Explosionsansicht des Getriebezugs in 1 veranschaulicht;
• [3] 3 eine Querschnittsansicht des Getriebezugs der 1 und 2 veranschaulicht, die die Kontaktkräfte zwischen den Zähnen des Ritzels und einem der Planetenräder zeigt;
• [4] 4 die Kontaktkräfte zwischen den Zähnen eines Ritzels und einem Planetenrad eines anderen Getriebezugs, wobei die Auswirkung der Reibung gezeigt ist;
• [5] 5 die Kontaktkräfte im Fall der Reibung null an den Zähnen des Ritzels und eines der Planetenräder des Getriebezugs der 1 bis 3 veranschaulicht, wobei die Zähne jeweils eine erste Kontur aufweisen;
• [6] 6 die Kontaktkräfte an den Zähnen des Hohlrads und eines der Planetenräder des Getriebezugs der 1 bis 3 veranschaulicht, wobei die Zähne jeweils eine erste Kontur aufweisen;
• [7] 7 die reibungslosen Kontaktkräfte an den Zähnen des Ritzels und eines der Planetenräder des Getriebezugs der 1 bis 3 veranschaulicht, wobei die Zähne jeweils eine zweite Kontur aufweisen;
• [8] 8 die Kontaktkräfte an den Zähnen des Hohlrads und eines der Planetenräder des Getriebezugs der 1 bis 3 veranschaulicht, wobei die Zähne jeweils eine zweite Kontur aufweisen;
• [9] 9 die reibungslosen Kontaktkräfte an den Zähnen des Ritzels und eines der Planetenräder des Getriebezugs der 1 bis 3 veranschaulicht, wobei die Zähne jeweils eine dritte Kontur aufweisen;
• [10] 10 die Kontaktkräfte an den Zähnen des Hohlrads und eines der Planetenräder des Getriebezugs der 1 bis 3 veranschaulicht, wobei die Zähne jeweils eine dritte Kontur aufweisen;
• [11] 11 ein Diagramm veranschaulicht, das verschiedene Wirkungsgradkurven in Abhängigkeit von dem Eingriffswinkel zeigt;
• [12] 12 eine Antriebsbaugruppe veranschaulicht;
• [13] 13 eine Rohrmotorbaugruppe veranschaulicht, die die Antriebsbaugruppe in 12 aufweist.

Further features and advantages of the invention will appear from the following detailed description, taken in conjunction with the accompanying drawings, in which:

• [ 1 ] 1 illustrates a gear train according to the invention;
• [ 2 ] 2 an exploded view of the gear train in 1 illustrated;
• [ 3 ] 3 a cross-sectional view of the gear train 1 and 2 illustrating the contact forces between the teeth of the pinion and one of the planetary gears;
• [ 4 ] 4 the contact forces between the teeth of a pinion and a planetary gear of another gear train, showing the effect of friction;
• [ 5 ] 5 the contact forces in the case of zero friction on the teeth of the pinion and one of the planet gears of the gear train 1 until 3 illustrated, wherein the teeth each have a first contour;
• [ 6 ] 6 the contact forces on the teeth of the ring gear and one of the planet gears of the gear train 1 until 3 illustrated, wherein the teeth each have a first contour;
• [ 7 ] 7 the frictionless contact forces on the teeth of the pinion and one of the planet gears of the gear train 1 until 3 illustrated, wherein the teeth each have a second contour;
• [ 8th ] 8th the contact forces on the teeth of the ring gear and one of the planet gears of the gear train 1 until 3 illustrated, wherein the teeth each have a second contour;
• [ 9 ] 9 the frictionless contact forces on the teeth of the pinion and one of the planet gears of the gear train 1 until 3 illustrated, wherein the teeth each have a third contour;
• [ 10 ] 10 the contact forces on the teeth of the ring gear and one of the planet gears of the gear train 1 until 3 illustrated, wherein the teeth each have a third contour;
• [ 11 ] 11 illustrates a diagram showing various efficiency curves depending on pressure angle;
• [ 12 ] 12 illustrates a drive assembly;
• [ 13 ] 13 a tubular motor assembly illustrating the drive assembly in 12 having.

Detailed description of the invention

Various aspects of various embodiments of the invention are described below with reference to 1 until 13 described in more detail.

• - ein Ritzel 2 mit zumindest einem Zahnradzahn 21;
• - ein Hohlrad 3 mit einer Vielzahl von Zahnradzähnen 31; und
• - eine Vielzahl von Planetenrädern 4 zwischen dem Ritzel und dem Hohlrad, wobei jedes Planetenrad eine Vielzahl von Zahnradzähnen 41 aufweist, die in die Zahnradzähne (21, 31) des Hohlrads und des Ritzels eingreifen.

The 1 until 3 illustrate an overall view of a self-locking planetary gear 1 according to the invention. This gear train features:

• - a pinion 2 with at least one gear tooth 21;
• - a ring gear 3 with a plurality of gear teeth 31; and
• - a plurality of planet gears 4 between the pinion and the ring gear, each planet gear having a plurality of gear teeth 41 which mesh with the gear teeth (21, 31) of the ring gear and the pinion.

The gear train is mounted on a carriage 11, which has an axle 12 on which the pinion 2 is mounted, and an axle 14 for each planet gear 4. Those skilled in the art will understand that the pinion 2 includes a coupling device (not shown) for coupling to a motor in use. The carriage 11 also has an output gear 16.

3 schematically illustrates the application of at least an effective contact force F _1/2 from the pinion 2 to a planetary gear 4 and a counterforce F _2/1 from the planetary gear 4 to the pinion 2. The application of the applied forces will be discussed below with reference to 4 until 11 discussed in more detail.

The 4 until 11 (explained in more detail below) illustrate the tooth contours and the various effective contact forces on the gear teeth (21, 31, 41) of the self-locking planetary gear 1.

According to the invention, the gear teeth of the self-locking planetary gear 1 are advantageously contoured in such a way that, during operation, a corresponding rotation of the planet gears is induced by rotating the pinion, while rotating A force is induced in the planet gears that is not sufficient to cause the pinion to rotate accordingly.

The invention thus creates a planetary gear with gear contours that ensure a self-locking function. As a result, high reduction ratios can be achieved and the motor can be prevented from driving when driving the output, which can be useful in certain applications, for example if the gear train is coupled to a brushless motor with little or no cogging torque (resistive magnetic torque).

Like in the 3 and 4 shown, in operation, rotating the pinion 2 can induce an effective force F extending away from the center of each planet gear 4 to induce a corresponding rotation of the planet gears 4. By rotating the planet gears 4, an effective force running near the center of the pinion 2 can be induced so as not to induce a corresponding rotation of the pinion 2.

• • entspricht FN_1/2 der Kraft des Ritzels 2 auf ein Planetengetrieberad 4 ohne Berücksichtigung der Reibung. Diese Kraft ist an einer Berührungsfläche zwischen dem Ritzelzahn 21 und dem Planetenradzahn 41 normal und entlang einer Wirkungslinie L ausgerichtet, die als Tangente zu einem Basisradius rb2 des Planetenrades definiert ist, der durch die Berührungspunkte zwischen dem Ritzelzahn 21 und dem Planetenradzahn 41 verläuft.
• • ist F_1/2 die Kraft des Ritzels auf das Planetengetrieberad unter Berücksichtigung der Reibung: $${\mathrm{<figure-callout\; id="1"\; label="F"\; filenames="DE102023108107A1\_0004.png,DE102023108107A1\_0005.png"\; state="\{\{state\}\}">F</figure-callout>}}_{1/2}=\frac{{\mathrm{<figure-callout\; id="1"\; label="F\; N"\; filenames="DE102023108107A1\_0004.png,DE102023108107A1\_0005.png"\; state="\{\{state\}\}">F</figure-callout>}}_N}{cos\rho }$$
  
• • ist φ der Reibungswinkel, der Winkel, der zwischen den Richtungen der beiden Kräfte FN_1/2 und F_1/2 gebildet ist.
• • ist tan (φ) der Reibungskoeffizient.
• • ist rb2 der Basisradius des Planetenrads 4.
• • ist rb1 der Basisradius des Ritzels 2.
• • ist d2 der Abstand zwischen der Achse des Planetenrades 4 und der Richtung der Kraft F_1/2. d2 ist abhängig von der Lage der Kontaktfläche zwischen einem Ritzelzahn 21 und einem Planetenzahn 41, dem Eingriffswinkel und dem Reibungskoeffizienten.
• • ist d1 der Abstand zwischen der Kraft mit der Reibung F_1/2 und der Drehachse 20 des Ritzels 2. Ist d1 null oder negativ, so entspricht dies dem Szenario der Selbsthemmung.

In the 3 and 4 :

• • FN corresponds _{to 1/2} of the force of the pinion 2 on a planetary gear 4 without taking friction into account. This force is normal to a contact surface between the pinion tooth 21 and the planet gear tooth 41 and is aligned along a line of action L, which is defined as a tangent to a base radius rb2 of the planet gear, which runs through the points of contact between the pinion tooth 21 and the planet gear tooth 41.
• • F _1/2 is the force of the pinion on the planetary gear, taking friction into account: $${\mathrm{<figure-callout\; id="1"\; label="F"\; filenames="DE102023108107A1\_0004.png,DE102023108107A1\_0005.png"\; state="\{\{state\}\}">F</figure-callout>}}_{1/2}=\frac{{\mathrm{<figure-callout\; id="1"\; label="F\; N"\; filenames="DE102023108107A1\_0004.png,DE102023108107A1\_0005.png"\; state="\{\{state\}\}">F</figure-callout>}}_N}{cOs\rho }$$
  
• • φ is the angle of friction, the angle formed between the directions of the two forces FN _1/2 and F _1/2 .
• • tan (φ) is the coefficient of friction.
• • rb2 is the base radius of planet gear 4.
• • rb1 is the base radius of pinion 2.
• • d2 is the distance between the axis of the planet gear 4 and the direction of the force F _1/2 . d2 depends on the position of the contact surface between a pinion tooth 21 and a planetary tooth 41, the pressure angle and the coefficient of friction.
• • d1 is the distance between the force with friction F _1/2 and the axis of rotation 20 of pinion 2. If d1 is zero or negative, this corresponds to the self-locking scenario.

The efficiency of the mechanism is now discussed in detail:

Calculating the efficiency with the drive pinion 2: $$\eta =\frac{{\mathrm{<figure-callout\; id="1"\; label="F"\; filenames="DE102023108107A1\_0004.png,DE102023108107A1\_0005.png"\; state="\{\{state\}\}">F</figure-callout>}}_{1/2}\cdot d2}{{\mathrm{<figure-callout\; id="1"\; label="F\; N"\; filenames="DE102023108107A1\_0004.png,DE102023108107A1\_0005.png"\; state="\{\{state\}\}">F</figure-callout>}}_N\cdot \mathrm{<figure-callout\; id="2"\; label="r\; b"\; filenames="DE102023108107A1\_0005.png,DE102023108107A1\_0007.png"\; state="\{\{state\}\}">r</figure-callout>}b2}=\frac{\frac{{\mathrm{<figure-callout\; id="1"\; label="F\; N"\; filenames="DE102023108107A1\_0004.png,DE102023108107A1\_0005.png"\; state="\{\{state\}\}">F</figure-callout>}}_N}{\text{cos}\rho }\cdot d2}{{\mathrm{<figure-callout\; id="1"\; label="F\; N"\; filenames="DE102023108107A1\_0004.png,DE102023108107A1\_0005.png"\; state="\{\{state\}\}">F</figure-callout>}}_N\cdot \mathrm{<figure-callout\; id="2"\; label="r\; b"\; filenames="DE102023108107A1\_0005.png,DE102023108107A1\_0007.png"\; state="\{\{state\}\}">r</figure-callout>}b2}=\frac{d2}{\mathrm{<figure-callout\; id="2"\; label="r\; b"\; filenames="DE102023108107A1\_0005.png,DE102023108107A1\_0007.png"\; state="\{\{state\}\}">r</figure-callout>}b2\cdot \text{cos}\rho }$$

Ist tan (φ) null, dann beträgt der Wirkungsgrad η 1.Calculating the efficiency with the drive planetary gear 4: $$\mathrm{\eta }=\left(\text{<figure-callout id="2" label="F" filenames="DE102023108107A1\_0005.png,DE102023108107A1\_0007.png" state="{{state}}">F</figure-callout>}2/\text{I}\times \text{dI}\right)/\left(\mathrm{<figure-callout\; id="2"\; label="F\; \eta "\; filenames="DE102023108107A1\_0005.png,DE102023108107A1\_0007.png"\; state="\{\{state\}\}">F</figure-callout>}\mathrm{\eta }\mathrm{}2/\text{I}\times \text{rbI}\right)$$

If tan (φ) is zero, then the efficiency η is 1.

Advantageously, the teeth can be helical.

• - der Zahn oder jeder Zahn 21 des Ritzels 2 stets mit zumindest einem Zahn 41 jedes Planetenrades 4 in Kontakt stehen;
• - der Zahn oder jeder Zahn 21 des Ritzels 2 stets mit zumindest zwei Zähnen 41 jedes Planetenrades 4 in Kontakt stehen;
• - der Zahn oder jeder Zahn 21 des Ritzels 2 stets mit zumindest drei Zähnen 41 jedes Planetenrades 4 in Kontakt stehen.

Regarding the 4 , 5 , 7 and 9 and the width (b) of the gears and their helix angle can advantageously be:

• - the tooth or each tooth 21 of the pinion 2 is always in contact with at least one tooth 41 of each planetary gear 4;
• - the tooth or each tooth 21 of the pinion 2 is always in contact with at least two teeth 41 of each planetary gear 4;
• - The tooth or each tooth 21 of the pinion 2 is always in contact with at least three teeth 41 of each planetary gear 4.

Advantageously, in relation to the 6 , 8th and 10 at least two teeth 41 of each planetary gear 4 are always in contact with the respective teeth 31 of the ring gear 3.

According to a variant of the invention, the helix angle of the teeth 41, 31 of the planetary gears 4 and/or the ring gear 3 can be at least 20°.

According to a further variant of the invention, the helix angle of the teeth 41, 31 of the planetary gears 4 and/or the ring gear 3 can be between 20° and 40°.

According to a further variant of the invention, the helix angle of the teeth 41, 31 of the planetary gears 4 and/or the ring gear 3 can be between 25° and 35°, for example approximately 30°.

According to the invention, the pinion 2 can have three or fewer teeth 21.

According to the invention, it was found that the number of teeth 21 of the pinion 2 must be reduced in order to significantly improve the self-locking. The number of teeth 41 of the planet gear 4 has little effect on the efficiency, be it as the drive planet gear 4 (for which the efficiency remains very low or zero) or as the drive pinion 2 (for which the efficiency remains very high).

According to a variant of the use of the pinion 2, the pinion 2 can have two or fewer teeth 21.

According to another variant of the use of the pinion 2, the pinion 2 can have a single tooth 21.

As in 11 shown, a common transverse pressure angle for each planetary gear 4 and the pinion 2 can advantageously be between 30° and 60°, for example approximately 35°.

According to a variant, the transverse pressure angle common to each planetary gear 4 and the pinion 2 can be between 35° and 55°.

According to a variant, the transverse pressure angle common to each planet gear 4 and the pinion 2 can be between 35° and 45°.

According to another variant, the transverse pressure angle common to each planet gear 4 and the pinion 2 is preferably between 35° and 40°.

For example, in the 5 and 6 the common transverse pressure angle is 35°, the pressure angle in the 7 and 8th 45° and the pressure angle in the 9 and 10 55°.

In the 6 , 8th and 10 a distance AB is illustrated, which illustrates a contact length (on a corresponding line of action) between a tooth of a planetary gear 4 and a tooth of the ring gear 3.

According to the invention, it has been shown that the radius of the contact surface must be increased to improve self-locking (drive wheel) (Ø pinion head 2).

According to the invention, the efficiency of the drive pinion 2 increases only slightly as the radius of the contact surface increases.

The inventors have also found that the pressure angle must be increased to improve self-locking.

In addition, the pressure angle, although still marginal, must still be reduced in order to improve the efficiency with the drive pinion 2.

The gear teeth 21, 41 of the pinion 2 and/or the planet gears 4 can be selected so that the coefficient of friction between them is between 0.08 and 0.14 during operation.

Preferably, the gear teeth 21, 41 of the pinion 2 and/or the planet gears 4 can be selected so that the coefficient of friction between them during operation is between 0.10 and 0.12, for example approximately 0.11.

The gear teeth 41, 31 of the planet gears 4 and/or the ring gear 3 can also be selected so that the coefficient of friction between them during operation is between 0.08 and 0.14, preferably between 0.10 and 0.12, for example approximately is 0.11.

According to the invention, the inventors have determined that the coefficient of friction must be reduced in order to improve the efficiency of the drive pinion 2.

According to the invention, the assembly of the self-locking planetary gear 1 can have only one or more planet gears 4. The one or more planetary gears 4 can have a plurality of planetary gears 4. The plurality of planetary gears 4 can have at least three planetary gears 4, for example four planetary gears 4.

The ring gear 3 can have at least one spline 5, for example for engagement in a tubular housing in which the self-locking planetary gear is to be stored.

As in 12 illustrated, the invention further relates to a drive assembly 100, having a motor 10 which is coupled to the pinion 2 of the self-locking planetary gear 1 described above. The motor 10 may include a brushless motor. The drive assembly 100 can have a first stage, which is formed by the self-locking planetary gear 1.

The drive assembly 100 can have one or more further planetary gear stages 110, 120. The other stages 110, 120 may not be self-locking.

The invention also relates to a tubular motor assembly 1000, having a drive assembly 100 described above.

It is known to those skilled in the art that several variants of the aforementioned embodiments are conceivable without departing from the scope of the invention.

Throughout the specification and claims of this specification, the words "comprising" and "including" and variations thereof mean "including, but not limited to", and are not intended to exclude (and do not exclude) other parts, additions, components, integers or steps out of). Throughout the specification and claims of this specification, the singular shall include the plural unless the context requires otherwise. In particular, when the indefinite article is used, the patent specification is to be understood to take into account both the plural and the singular unless the context requires otherwise.

Features, integers, properties, compounds or groups described in connection with a particular aspect, embodiment or example of the invention are to be understood as applying to any other aspect, embodiment or example, as described herein, unless inconsistent therewith. All features disclosed in this specification (including all claims, abstracts and accompanying drawings) and/or all steps of a method or process so disclosed may be combined in any combination, except combinations in which at least some of these features and/or steps mutually exclusive. The invention is not limited to the details of all previous embodiments. The invention extends to any novel feature or combination of the features disclosed in this specification (including the claims, abstract and accompanying drawings) or to any novel feature or combination of the steps of a method or process so disclosed.

The reader's attention is drawn to all publications and documents filed contemporaneously with or prior to this specification in connection with this application and which are open for public inspection with this patent specification, and the entire contents of such publications and documents are incorporated herein by reference .

Reference symbol list

1

Self-locking planetary gear

10

engine

11

Sleds

12

Pinion axle

14

Planetary gear axle

16

driven gear

100

Drive assembly

110

another planetary gear stage

120

another planetary gear stage

1000

Tubular motor

2

pinion

20

Axis of rotation of the pinion

21

Pinion tooth

3

ring gear

31

ring gear tooth

4

Planetary gear

41

Planetary gear

5

spline

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 3470616 A1 [0003]

Claims (10)

Self-locking planetary gear (1), comprising: a pinion (2) with at least one gear tooth (21); a ring gear (3) with a plurality of gear teeth (31); and one or more planet gears (4) between the pinion and the ring gear, the or [sic] each planet gear having a plurality of gear teeth (41) which mesh with the gear teeth of the ring gear and the pinion; wherein the gear teeth are contoured such that, in operation, rotating the pinion induces a corresponding rotation of the one or more planetary gears, while rotating the one or more planetary gears induces a force that is insufficient to induce a corresponding rotation of the pinion . Self-locking planetary gear Claim 1 , characterized in that the teeth (21, 31, 41) are helical. Self-locking planetary gear Claim 2 , characterized in that the tooth or each tooth (21) of the pinion (2) is always in contact with at least one tooth (41) of the or each planetary gear (4). Self-locking planetary gear Claim 2 or 3 , characterized in that at least two teeth (41) of the or each planetary gear (4) are always in contact with the respective teeth (31) of the ring gear (3). Self-locking planetary gear according to one of the Claims 2 until 4 , characterized in that the pinion (2) has a single tooth (21). Self-locking planetary gear according to one of the Claims 2 until 5 , characterized in that the transverse pressure angle which is common to the or each planet gear (4) and the pinion (2) is between 35° and 55°. Self-locking planetary gear according to one of the Claims 1 until 6 Claims, characterized in that the one or more planetary gears (4) have at least three planetary gears. Drive assembly (100), comprising a motor (10) which is connected to the pinion (2) of a self-locking planetary gear (1) according to one of Claims 1 until 7 is coupled. drive assembly Claim 8 , characterized in that the motor (10) has a brushless motor. Tubular motor assembly (1000), which has a drive assembly (100). Claim 8 or Claim 9 having.

Images