WO2015002628A2

WO2015002628A2 - Gear mechanism of measuring instrument and electro-mechanical and mechanical watches containing the same

Info

Publication number: WO2015002628A2
Application number: PCT/UA2014/000058
Authority: WO
Inventors: Sergiy Vyacheslavovich SHEYKO
Original assignee: Sheyko Sergiy Vyacheslavovich
Priority date: 2013-07-03
Filing date: 2014-06-05
Publication date: 2015-01-08
Also published as: WO2015002628A3; WO2015002628A4

Abstract

The proposed invention relates to instrument engineering, namely, to indication systems in analog measuring devices and multi-stage information instruments, particularly in electro¬ mechanical and mechanical watches, and strives to improve their arrangements due to direct application of gear mechanism as a display module with optimal arrangement of power, drive and control systems, thus making the instrument more compact, reliable and visually comfortable. This purpose is attained in measuring instruments with escapement and/or drive with known linear dependence between its rotary speed and measured value, which comprises a multistage gear mechanism including nested coaxial planetary gearings with optional internal setting joinings and external kinematic relations. Some variants are also proposed for engagement in such mechanisms and aimed to increase their operational efficiency due to minimization of sliding friction in them by application of bearing gears that along with gearing engagement and radial rolling effected by cylindrical surfaces of coaxial end rollers, have axial rolling, namely, herringbone or arched engagement, or beveled teeth and rollers adjacent end faces.

Description

GEAR MECHANISM OF MEASURING INSTRUMENT AND ELECTRO-MECHANICAL AND MECHANICAL WATCHES CONTAINING THE SAME

FIELD OF THE INVENTION

The proposed invention refers to instrument engineering, and can be used for concentric display in analog measuring and multi-stage indication devices, such as counters, tachometers, watches, etc.

BACKGROUND OF THE INVENTION

It is known gear mechanisms utilized for multi-stage indication in measuring instruments that comprise a gearing system for transformation of rotary angle and/or speed at input to increased or decreased rotary angle and/or speed at output using one or several stages of gear or discontinuous transmissions. Such instruments comprise a multi-stage structure consisting of gearing and drive systems separated from display module, therefore, they are clumsy, contain construction elements, axes, bearings required to constrain of kinematic relations for efficient performance of the mechanism.

A known indicating gear mechanism ["Calculating device" Application WO 02/101481] comprises a gearing system consisting of barrels with cogs and slots interacting with long- toothed pinions and counter-rotating stoppers. The co-rotating barrels are installed on a single axle with small intervals between them. On those digits figures are applied which form a multi- digit number when the barrels are aligned together. When pinion of the first right barrel is driven, after each consecutive revolution the adjacent barrel rotates forward by one division, and thus revolution counter operates up to the order equal to the number of barrels.

Drawbacks of such calculator are purely digital discontinuous indication and presence of necessary additional axles and pinions, which do not participate in indication.

The closest on performance prototype is a reduction gear mechanism of measuring instrument comprising at least a housing part and a gearing system driving the indicating hands, where gears are installed on parallel axles in bearings on the housing part ["Analogic display module for a watch movement" Patent US 5222051 , prototype]. Its gear mechanism may be used in both electro-mechanical and mechanical watches with a drive or a mainspring and escapement as a drive respectively. On mounting plate, as a housing part, is installed drive and

SUB$ BMTIEl£fe£HI5BlDI(ELH6$ 26) gear mechanism containing different gearing systems, which are separated by dial from hand display module, the entire mechanism being mounted within a protective case with a transparent part for time flow observation. The gearing systems are joined to hands by axles and coaxial bushings through openings in the dial. Gearing systems of the mechanism mostly realize multiple linear dependences in rotary speeds of different indicating hands with due consideration of mechanical, kinematic, functional and structural requirements. This principle of gear reduction for hand display module drive with a different feature set is typical for a vast variety of analog watches that have features to measure hours, minutes, seconds and their derivative values.

From the point of view of aesthetic and jewelry application in watch industry this gear mechanism possesses a complicated structure without any symmetry and proportions due to

kinematic relations, which induces use of a dial separating gear mechanism from indicating hands for obvious time visualization, moreover a multilayer structure of gear mechanism with dial and hands makes watch thicker.

Various double row planetary gearing mechanisms are known having satellite gears joined into clusters. Their reduction principles are based on small difference of reduction ratios in each of coupled planetary gearings which causes a large difference in rotary speed between sun and ring gears at input and output ["Speed reducer " Patent US 3675510] and ["Planetary gearing mechanism" Patent RU 2404382]. Such double row planetary gearings are comprised of a case, sun and ring gears, and clusters of satellite gears constrained in axial direction by either teeth phase shifts, case, or a carrier.

The drawbacks of such mechanisms are increased wear and jamming of satellite gears under load operation, as they are restrained by only their teeth and slide of their end faces ["Speed reducer" Patent US 3675510], and the necessity to use a carrier with bearings leads to complication of the mechanism and increases the number of kinematic relations ["Planetary gearing mechanism" Patent RU 2404382].

The closest to technical essence is a gear mechanism described in ["Gear bearings" Patent US 2002/0031288 Al , prototype], which comprises a mechanism with double row planetary gearing. It satellite gears are joined in clusters and having rollers with cylindrical surfaces corresponding to the gear pitch circles, gear teeth engaging between such rollers and thus limiting radial and axial movement of satellite gears, permitting their free rolling along ring and sun gears of planetary gearing. Helical gearing attains the same effect, and even by small difference in gear ratios between these two planetary gearings, a multiple reduction effect may be obtained in a rigid and space-saving structure.

The drawback of this mechanism is sliding friction of teeth end faces, and even with helical gearing, the axial forces will appear on small sections of teeth, on their and rollers adjacent end faces, what results in: mechanism wear, gear misalignments and jamming of satellite gears under the load.

There is known an electro-mechanical watch Quinting ["Transparent analogue watch" Application DE 4334646C1, prototype] comprises a watch case with embedded: gearing system, electronic module, stepping motor drive system and power source. The watch indication system consists of 7 parallel transparent sapphire disks with antiglare coating: two protective disks joined to case and between them one holding and four rotatable pre-metallized with joint ring gears. The disks actuate minute and hour hands as well as date and second hands on their small dials.

In spite of absolute dial transparency, this watch has some disadvantages, namely: relatively large size for wristwatch due to the multi-layer indication system and thickened rim- type watch case with drive, power and control systems; increased fragility, complicated manufacture of parts, assembly and replacement of power source which is possible only at authorized dealers.

It is known a coaxial mechanical watch ["Coaxial horological movement" Application WO 2009/1 12884, prototype] comprises coaxially installed: a mainspring, systems with time indicating elements, kinematic relations for increase or decrease of speeds between mechanism

systems and escapement. Each mechanism system has cup-shaped form partially nested one into other/others. Moreover, the movement contains a differential gearing installed coaxially to mainspring in order to ensure its kinematic relation with one of the cups using main shaft and coaxial bushing, herewith the bushing serving to hold other cup/cups as well as the mentioned above kinematic relations.

In spite of the unique appearance, this watch mechanism has some disadvantages due to its multi-level structure, including gearing systems and large number of movable housing parts supported on several kinematic cascade relations, thus causing bulkiness, increased thickness and too strict requirements to manufacturing and assembling accuracy.

SUMMARY OF THE INVENTION

The principal object of this invention is developing a gear mechanism of analog measuring and information instruments in the form of multi-stage nested planetary gearings, particularly, consisting of bearing gears to be used as a indication system based on decorated gears or carriers, along with minimization of sliding friction in their engagements. Such technical results may be specified as high reliability due to multi-planetary structure with multi-level fixation system, on a par with best filling of mechanism space, optimal engagement in gearing system under least possible thickness of it, comprising basically a two-layer structure with few housing parts, as well as high intuitiveness, informativeness and visual attractiveness due to symmetrical planetary transparent structure and ability of more detailed observation of measured values. In addition, technical peculiarities of mechanical and electro-mechanical watches arrangement and control are marked with application of this mechanism: as indication-planetary gearing looks alike from both sides it may be used bilaterally.

DISCLOSURE OF THE INVENTION

The above objective is achieved by performing gear mechanism of measuring instrument comprising at least a housing part, rotation drive and a gearing system, wherein, according to the invention, the said gearing system includes nested coaxial planetary gearings, at least one of them being a double-row with at least one satellite gear per each of them. The mechanism arrangement is specified by joining of certain sun or ring gears to housing parts, and possible additional fixation of: satellite gear axes on carriers and/or carrier axes, sun or ring gears with housing parts or with other coaxial gears. Direct application of planetary gearings as a basis of indication system by movable gears or carriers substantially simplifies the mechanism, leads to possibility of optimal arrangement with drive, power source and control system. Usage of mostly bearing gears and/or herringbone gears in the gearing system improves kinematic relations due to simplified suspension, thus enabling maximum rolling engagement, as well as due to beveled adjacent end faces on teeth and rollers, mechanism efficiency is increased.

Then, housing part means the case itself or a part rigidly fixed on it or relative to it, whereas axial fixation means a bonding using: axles and anti-friction supports, plain or rolling bearings with all degrees of freedom, except rotational, constrained. Planetary gearing means at least one satellite gear with spin-orbital motion possibility and engagement with sun gear and/or ring gear, with possibly carrier installed on axles of satellite gears. Crown gear means a gear on carrier, or on sun gear, or on ring gear, which - engages neither of satellite gears. Larger gears are those that have larger pitch circle than comparable gears. Nested planetary gearing relative to external one has a movable ring gear or a carrier joined to movable sun gear or carrier of another,

external planetary gearing, and vice versa. Multi-stage nested system of planetary gearings is a concentric relative to common axis of all sun and ring gears planetary gearing system that has in radial direction, a central sun gear inside and/or a peripheral ring gear outside. In this planetary gearing system at orbital rotation speeds of nested planetary gearings being lower than those of external ones, at least sun gears have joints with housing parts, at least one of them per each single- or double-row planetary gearing, whereas at higher rotation speeds - only ring gears become joined. Usage of a carrier axially fixed relative to planetary gearing axis determines movement and engagement of satellite gears installed on it. The carrier may act as a frame unit with at least one escapement installed on it, which have drive connection to one of the sun gears or to a concentric gear joined to a housing part. Double-row planetary gearing is actually one planetary gearing consisting of two parallel: carriers, sun gears, ring gears and satellite gears with common axes used in pairs. In most cases of double-row planetary gearings satellite gears joined in clusters and reduction takes place from external planetary gearings to the nested, by joining of adjacent movable sun and ring gears. In these cases when in a cluster moment- transferring gear is smaller than gear engaged with housing part joining sun gear, orbital rotation of satellites of nested planetary gearing occur in the same direction as the cluster, and vice versa. The joining of parts is meant either one-piece manufacture or fixed joint assembly using: screws, bracers, threaded connection, pressure coupling, soldering, welding or gluing, or friction coupling in the form of sliding safety clutch or friction connection. The mechanism may be assembled from separate sectional parts or by joining with optional elastic and/or thermal deformation in the manufacturing sequence. Friction coupling may be performed for manufacturing purposes and/or for kinematic purposes with engagement force selected in such way to not slide spontaneously in operation and in setting modes. Carrier may also have a crown gear for engaging other gears or have a joining with another sun or ring gear. In order to widen the range of gear ratios or even to switch reduction modes satellite gears in pairs in at least in one of the double-row planetary gearings may only have axial fixation relative to each other along with their sun or ring gears pairwise: joining or even their external kinematic relation, that is in engagement via two crown gears on them and may be switchable via separated gearings. The mechanism may be driven either directly to one of sun or ring gear or carrier, or via a gear axially fixed on housing part engaging with a crown gear joined with either carrier or movable, namely, a sun central or ring peripheral gear.

In case of planetary gearing is assembled from gears, satellite gears must be axially fixed relative to carrier, whereas other movable gears and carriers axially fixed relative to housing part, or their movement must be limited by housing parts adjacent to planetary gearing, or by herringbone or arched engagement. To avoid this, instead of gears some bearing gears may be used in the form of gearwheels with cylindrical rollers on one or two end faces of them. The rollers diameters correspond to pitch circle of their gearwheels, and which have spur, helical, herringbone or arched engagement, as well as cycloidal, involute or roundscrew tooth profiles, whereas adjacent end faces on teeth and rollers may be either flat or beveled, as described below.

In each pair of conjugated bearing gears, their teeth engage between end rollers of each of them and conjugated rollers having equal heights. Neglecting clearance and assuming perfect accuracy, engagement of bearing gears is aimed at maximum rolling with minimum sliding friction of conjugated profiles in movement. End rollers ensure limiting of gear radial shift at their contact points, thus, along with their engagement, slip-free rolling motion of their conjugated pairs is implemented. Adjacent end faces of teeth and rollers limit axial shift of

conjugated bearing gears performing their plane-parallel motion. In such a way, using bearing gears as sun, ring and more than two satellites uniformly distributed among them the entire planetary gearing is arranged, and carrier may be used instead of ring or sun gears, or it may act as frame unit and transfer rotation from satellites, whereas limitation of carrier degrees of freedom would form redundant constraints or serve as additional basis for force distribution in mechanism. In case less than three bearing satellite gears are involved, at least axles of movable sun and/or of ring bearing gears should be fixed relative to housing parts.

To support at least one of movable sun central or of ring peripheral bearing gears or of carrier of one of planetary gearings they may be additionally engaged by a crown bearing gear with other axially fixed bearing gears on housing part or on a lever installed on it. These axially bearing gears may be driven and/or may have engagement and/or may be switchable with another crown gear of this planetary gearing.

As the mechanism mostly comprises nested planetary gearings, the space in its center and at periphery remains free and for mainly clockwork arrangement, it is most feasible to place, within planetary gearing system center of power source or of inertial generator in case of electromechanical watch, or of winding and setting mode rotary barrel with mainspring inside in case of mechanical watch. In case of electro-mechanical watch, it is reasonable to locate within watch rim-case or within bracelet a control system electronic module, mechanism drive and power source. Power source may be a power cell or a storage battery.

Materials of construction for at least of gearing may be, on a par with plastics, minerals, metals and alloys, also polycrystalline silicon, diamonds or diamond-coated silicon. Transparent elements may be made of organic or mineral glass or sapphire, whereas plain bearings may be of polished surfaces, ruby stones and anti-frictional bushings. Housing parts may be made of plastics, metals, hard alloys or high-tech ceramics.

BRIEF DESCRIPTION OF THE DRIWINGS

Examples of invention embodiments as described below are explained by attached drawings, wherein:

Fig.l Shows a schematic variant of a gear mechanism, specifying drive and semitransparent housing parts; Fig.2 Shows an increased piece of axial section view of gearing engagement of Fig.1 ;

Fig.3 Shows an increased piece of reduction switching in gearings of Fig.1 ;

Figs.4 - 12 Show elements of gearing kinematic diagrams for arrangement of nested planetary gearings, their suspensions and gear relations;

Fig.13 Shows engagement in a pair of bearing gears with beveled surfaces of adjacent end faces of teeth and of rollers;

Fig.14 Shows a half of tooth from smaller bearing gear of Fig.13;

Fig.15 Shows a piece of engagement of herringbone bearing gears;

Fig.16 Shows an increased pair of teeth from smaller bearing gear of Fig.15;

Fig.17 Shows a piece of embodiment of friction coupling between gears;

Fig.18 Shows a general view of the proposed electro-mechanical watch with cutaway of watch glass and of watch case along with drive, electronic circuits and control system represented symbolically;

Fig.19 Shows an increased cross sectional view along axis of satellite gears of Fig.18;

Fig.20 Shows a general view of the proposed mechanical watch with cutaway of watch glass and watch case to expose carrier with escapement installed on it;

Fig.21 Shows an increased piece of section view along axes of satellite gears of Fig.20;

Fig.22 Shows a detailed view of rotary barrel with mainspring and planetary-ratchet mechanism of watch presented in Fig.20;

Fig.23 Shows an increased piece view of escapement of watch presented in Fig.20.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Gear mechanism of measuring instrument according to Figs.1 -3 comprises at least housing parts 1 -6, rotation drive 7 and gearing system 8-30 separated by transparent housing part 2. The gearing system consists of nested coaxial planetary gearings with four satellites on each of them. Three of these planetary gearings are double-row and one single-row as well as one sun gear 8, 12, 16, 20 of each of them is joined to housing part 1. Central sun gear 8 is rolled by satellite gears 9 driven by ring gear 10. As this planetary gearing is final element of kinematic relations, it may be single-row. Then, the sun gear of external planetary gearing joined to ring gear 10 engages smaller satellite gear of each cluster 1 1 , whose larger gear engages sun gear 12, thus effecting multiple reduction to the nested planetary gearing. Larger one of satellite gears of each cluster 1 1 also engage ring gear 13 joined with sun gear of external planetary gearing. This sun gear engages smaller gear of each satellite cluster 14 axially fixed on carrier 15, whereas its larger gear engages with sun gear 16, thus effecting a double-row planetary gearing. One, in this case larger, satellite gear of each cluster 14 engages ring gear 17, which in turn is joined to sun bearing gear of external double-row planetary gearing. This sun bearing gear engages satellite bearing gears 18 axially fixed in pairs with bearing satellite gears 19, which in turn roll on sun bearing gear 20. Each of bearing gears 18 and 19 engages ring peripheral bearing gears 21 and 22 respectively. This two ring gears 21 and 22 may be either joined to each other, or have external kinematic relation between themselves, or even apply the reduction switching from control system, for example, via separated gearings, or, as shown in Figs.1 and 3, gear cluster 23 and pair of gear cluster 24 with idle gear 25 are axially fixed on turning lever 27 having axial fixation via openings 26 with housing part 5. Switching may also be effected by clutches on external kinematic relations with gearings axially fixed on housing parts. For additional mechanism suspension or drive on housing parts 3, 6, 4 gears or bearing gears 28, 29, 30 respectively may be axially fixed, which engagement with crown gear or bearing gear on one of ring peripheral bearing gears 21 or 22. In addition, at least one of gears 28, 29 or 30 may be rotatable driven, for instance, from stepping motor 7.

As an example of systems of kinematic relations, this gear mechanism possesses various means for axial constraint of planetary gearing movable elements. Thus, in radial direction, the first spur single-row planetary gearing satellite gears 9 are axially constrained by their end faces

between housing parts 1 , 2. In the second double-row planetary gearing the satellite gear clusters 1 1 are axially constrained by herringbone engagement, namely, with larger gears of clusters 1 1 engaged with gears 12 and 13, which also limited by smaller satellite gears the axial shift of movable sun gear 10 and, respectively, of ring gear of the nested planetary gearing. The third double-row planetary gearing is spur-type, without contacts of its movable gears end faces with housing parts, therefore, clusters of satellite gears 14 are axially fixed by carrier, which is axially fixed relative to sun bearing gear 20 of external planetary gearing, also movable sun gear 13 is axially fixed relative to sun gear 16 of this planetary gearing. The fourth double-row planetary gearing is supported by bearing gears in both axial and radial directions, and by mutual axial fixation in paired satellite bearing gears 18 and 19.

As shown in Figs. 1 and 2, satellites of planetary gearings 9, 1 1 , 14, 18, 19 may have the holes for decoration, for example, with transparent cylinders of different colors 31 , and/or possibly, on at least one of these satellites of each planetary gearing may be installed the direction indicator 32 for visualization of fractions of rotations.

In mechanism similar to the presented in Figs.1 -3, unless reduction switching is not provided and if planetary gearing ratios are available, in most cases, satellite gears 18 and 19 will be joined into clusters and used a single ring gear and/or carrier with a crown gear for its external drive or without it for the case of drive on nested planetary gearings.

As evident, the total indication system looks actually alike from both sides, therefore, it may be used for countdown by observing from another side or in case of reverse drive to be used with different gradation and/or decoration from both sides. In such case housing parts adjacent to indication gearing system may be made transparent, such as housing part 1 and partially shown housing part 2.

In the center of planetary gearing is supposed to dispose the barrel 33 including at least one the following: auxiliary kinematic relations of gearing system, drive, electronic circuits, generator, power source or decorations. The barrel may have a removable lid for technological or service purposes, such as replacement of power source, or have at least one transparent wall for visualization of processes inside it.

Parameters of mechanism gears presented in Figs.1-3 are specified in the table as an example of application in watch mechanism: G 8 9 10 1 1 12 13 14 16 17

R S M L R S M L R S

N 108 18 144 176 14 16 176 208 247 19 22 242 286 260

G 18 19 20 21 22 23 24 25 28-

R C R C M L M L 30

N 24 24 264 308 462 312 390 28 24 18 33 18 24 where: G - gear positions in Figs.1 -3; N - number of teeth in them; S- sun; R- ring;

M- smaller; L- larger; C -crown gear.

From rotation drive 7 to gear 30 at speed 30 RPM (revolutions per minute) via engagement of cluster 23 with crown gears of peripheral ring gears 21 and 22 of the first double-row planetary gearing, orbital rotation speed of pairwise satellite gears 18, 19 is effected at 1 RPM

along with spinning rotation speed of gears 18 at 12 RPM. Then kinematic relations to the second nested planetary gearing from ring gear 17 to larger gears of satellite clusters 14 ensure their orbital rotation speed at 1 RPH (revolutions per hour) and their spinning rotation speed at 12 RPH. In the third nested double-row planetary gearing satellite clusters 1 1 have orbital rotation speed at 2 RPD (revolutions per day) and their spinning rotation at 1 RPH, whereas with reduction transferred to the fourth planetary gearing satellite gears 9 have orbital rotation speed at 1 RPW (revolutions per week) and their spinning rotation speed at 1 RPD.

When crown gears of ring gears 21 and 22 engagements are switched from cluster 23 to cluster 24 with idle gear 25, the speeds of spinning rotation of drive and satellite gears 18 and 19 remain the same, however the speed of spinning rotation of satellite clusters 14 is increased in 181 times at the same gear ratios in subsequent nested planetary gearings. This permits to accelerate the settings of satellite gears positions without changing of their initial relative angular settings for cycle of motions at one-second minimal switching time-ratio.

On Figs.4-12 of elements of kinematic relations the left axial lines separate the figures and show the center of planetary gearings. These kinematic relations may be composed either of gears, as stated below or of bearing gears and may be used to arrange kinematic diagrams of proposed gear mechanisms, particularly in analog measuring instruments.

Fig.4 - planetary gearing consists of sun gear 34, satellite gear 35 and ring gear 36. The sun gear is joined to housing part; the rotation is applied to the gear 36. This planetary gearing could be used only as indication system by satellite gears and/or as a bearing;

Fig.5 - external crown-gear engagement of ring gear 37 transferring rotation. Gear 38 is axially fixed relative to housing part 39 and may serve as a drive directly or via gearings from a drive, or act as a bearing for crown gear support of ring gear;

Fig.6 - double-row planetary gearing wherein one of the sun gears 40 is joined to a housing part and whereas another sun gear 41 transfers rotation. The rotation is applied from ring gear 43 to top gear of satellite cluster 42;

Fig.7 - double-row planetary gearing wherein one of the sun gears 44 is joined to a housing part and whereas another sun gear 45 transfers rotation. The rotation is applied from ring gear 47 to bottom gear of satellite cluster 46; Fig.8 - planetary gearing wherein sun gear 48 is joined to a housing part, satellite gear 49 is axially fixed on carrier 50 and rotation is applied to ring gear 51 . The carrier is used at least to support satellite gears, or visa versa, or to transfer rotation. In this case, the rotation may be applied on the carrier without using of the ring gear;

Fig.9 - double-row planetary gearing, where on carrier 52 satellite gear cluster 53 is axially fixed. One of sun gears 54 is joined to a housing part, whereas another sun gear 55 transfers rotation. The rotation is applied to ring gear 56 engaging with one of the gears of each cluster 53. Carrier is used at least to support satellite gears, or visa versa, or to transfer rotation. In this case, the rotation may be applied on the carrier without using of the ring gear;

Fig.10 - double-row planetary gearing wherein one of sun gears 57 is joined to a housing part, whereas another sun gear 58 transfers rotation. On two ring gears 59 and 60 is applied the

rotation and they are joined into cluster 61 , satellite gears 62 and 63 are axially fixed to each other in pairs;

Fig.1 1 - gear mechanism with double-row planetary gearing wherein one of sun gears 64 is joined to a housing part, whereas another sun gear 65 transfers rotation, satellite gears 66 and 67 are axially fixed to each other in pairs, whereas two ring gears 68 and 69 are engaged with each other by their crown gears and gear cluster 70. The rotation is applied either to one of the ring gears 68 or 69, or to the gear cluster 70;

Fig.12 - gear mechanism with double-row planetary gearing wherein one of sun gears 71 is joined to a housing part, whereas another sun gear 72 transfers rotation, satellite gears 73 and 74 are axially fixed to each other in pairs, whereas two ring gears 75 and 76 are engaged with each other by their crown gears and gear cluster 77 with idle gear 78. The rotation is applied either to one of the ring gears 75 or 76, or to gear cluster 77.

By the description of Figs.4-12, under applying and transferring of rotation are meant either the joining or overlapping with at least one of Figs. 4-12 or rotational movement drive. Except left axial lines, by mirroring relative to the satellite gear axis on Figs.4-12, by substituting expression "sun" for "ring" and "nested" for "external", reverse kinematic diagrams may be obtained with reduction from nested planetary gearings to external ones. Also by changing applying on transferring reverse action may be obtained. Besides, at the mention of satellite gears or their clusters in singular it is implied that there may be more than one. Also relative dimensions, such as satellite gear diameters in clusters, are shown conventionally and may have different ratios.

In gear mechanisms presented in Figs.1 1 and 12 items 70, 77, 78 may be axially fixed relative to housing or to movable part, and in case several of such mechanisms used with a common planetary gearing their kinematic relations could be disengageable, for example, by clutches in gear clusters, or their engagement may be switched as shown, for the instance by lever, Figs.l and 3.

In case of double-row planetary gearings wherein satellite gears are joined into clusters for reduction from external planetary gearings to the nested ones, as in Fig.6 and similarly in Fig.7, for each double-row planetary gearing two sun and one ring gears are used which engage with satellite gear cluster of this double-row planetary gearing, one sun gear being joined to housing part, whereas another one transfers rotation. In reverse case, for double-row planetary gearings wherein satellite gears are joined into clusters for reduction from nested planetary gearings to the external ones; it is used one sun gear engaged with one of gears in each satellite cluster of this double-row planetary gearing and two ring gears, one of them being joined to housing part, whereas another one transfers rotation. Carriers, movable gears or their clusters may be arranged, being simply supported by bearing gears, by teeth slopes of herringbone or of arcuate engagements, or by adjacent housing parts to planetary gearing system, or they may be additionally axially fixed either to the housing parts or between themselves, and/or they may have a carrier Figs.8 and 9, which may act both as frame unit and as a transfer member in kinematic relations. In addition, more complicated relations from Figs.10, 1 1 and 12 may be composed with satellite gears axially fixed relative to each other in pairs. In such cases two sun and two ring gears are used, thus, this would be a double-row system with single-row planetary gearings, wherein one satellite gear acts as a carrier for another one, and vice versa. At that, one

sun or one ring gear will be joined to housing part, whereas two opposite sun or ring gears are joined between themselves Fig.10 or have external kinematic relations Figs. l 1 and 12.

Satellite, sun and ring gears and carriers may be directly used as indicators or as their basis for subsequent fashion: engraving, incrustation, faceting or decoration with hands, enamel, gems, etc. As stated above, for the more accurate indication, the engagements parameters may be so selected that, for the instance, centers of satellite gears performed one orbital cycle along with several full spinning revolutions, so direction indicators installed at the center of satellite gears allow to determine the fractions of the measured value. Also, a dial may be made in the form of digits figures and/or scale marks on the surface of at least one housing part, to which fixed sun and/or ring gears also belong.

In order to reduce sliding friction in bearing gears engagements on adjacent end faces of their gearwheels and rollers, the gearwheels teeth must be either made beveled and/or made with engagement by surfaces providing the efficient axial meshing. Below the implementations of bearing gears with beveled teeth and rollers adjacent end faces as well as herringbone engagement with minimum axial shift due to opposite slopes of teeth are proposed.

Engagement of bearing gears shown in Fig.13 includes a part of ring gear consisting of coaxial rollers 79, 80 with gearwheel 81 and one satellite gear consisting of coaxial rollers 82, 83 with gearwheel 84. The rollers 79 and 82, 80 and 83 interact between themselves in pairs and teeth of gearwheels 81 and 84 are in engagement. The adjacent end faces of tooth and of rollers are formed by cylindrical helical extrusions of tooth profile relative to the gearwheel axis, which are symmetrically cut the valleys in the roller up to tooth middle.

Fig.14 depicts a segment of bearing gear containing the tooth and roller parts from Fig.13 limited by planes 85 and 86 on gear axis. This segment reflection in one of the symmetry planes 85 or 86 and circular array of the number of teeth relative to gear axis forms the entire bearing gear. By other means, the adjacent end faces of teeth 87, 88 and of rollers 89, 90 surfaces are obtained by bidirectional swiping of tooth profile generatrix 91 along helical cylindrical symmetrical relative to inflection point lines 92 on top and 93 on bottom of tooth. The subsequent axial extrusion of teeth and intrusion of rollers up to this surfaces shape aforesaid end faces. Helical cylindrical lines may have different pitch at each of the end faces, however, teeth and rollers adjacent end faces, engaged in pairs, must be formed by helical lines of equal radius with pitch being proportional to reduction ratio. Engagement of herringbone bearing gears shown in Fig.15 includes satellite gear consisting of gearwheel 94 with rollers 95, 96 and part of sun gear consisting of gearwheel 97 with rollers 98, 99. Herringbone gearwheels 94 and 97 being engaged limit their mutual axial shift, therefore, end faces of teeth and adjacent (inner) end faces on paired contacting rollers 95, 98 and 96, 99 respectively may be made flat. Moreover, by arranging axial gap between engaged rollers and gearwheels due to larger gearwheel face width in addendum than in dedendum, sliding friction of teeth end faces may be avoided, as they will not have any end faces in contact.

Fig.16 shows two teeth of satellite gear depicted in Fig.15, limited by planes 100 and 101 on its axis. As seen in the figure, the face width of protruding teeth, that is, of teeth in addendum between edges 102 and 103, is smaller than the face width of valleys between them, thus,

namely, the distance in dedendum between inner rollers end faces 104 and 105; so, any contact between end faces of gearwheels and rollers is avoided.

Fig.17 shows a piece of friction coupling of nested planetary gearings in slots between their ring 106 and sun 107 gears by a wave ring spring gasket 108, which may facilitate assembly process and/or implement mechanism setup function using sliding of this friction connection at prescribed force. Inner cylindrical surfaces of slots in ring and/or sun gears may have smooth or knurled, rough or wavy longitudinal profiles for more accurate cohesion and to prevent arbitrary sliding under kinetic friction.

The proposed principles of gear mechanisms are fit for both electro-mechanical and mechanical watches. Hereinafter planetary gearings where satellite gears have orbital rotation speed of one revolution per week will be called weekly gearings, and respectively: two revolutions per day - daily gearings, one revolution per hour - hourly gearings, one revolution per minute - minute gearings.

An example of electro-mechanical watch wherein gear mechanism counting seconds, minutes, hours and week days is implemented in the form of nested single- and double-row planetary gearings with indication by satellite gears is shown in Figs.18 and 19. This mechanism is entirely composed by bearing gears, therefore, the word "bearing" is omitted in its description. In the center of planetary gearing system, within cylindrical barrel 109, power source 1 10 is located. The barrel has removable lid 1 1 1 for power source replacement. Disk glasses 1 12 and 1 13 by the inner rims are fixed on the edges of barrel 109, while the outer rims are fixed on the inner peripheries of the watch case 1 14, thus forming a single housing part. Within the watch case 1 14 four housing parts 1 15-1 18 are located, at that the gears 1 19-122 are axially fixed on each of them. On housing parts 1 15-1 18 are also installed: drives 123 and 124 for gears 1 19 and 121 , control buttons 125 and 126, drive pulse generator with control system 127, whereas electric circuits are located both in watch case and power source barrel and also are applied onto at least one glass 1 12, 1 13 and/or others housing parts.

Electric circuits on the glass may be made transparent or ultra-thin or have aesthetic function demonstrating both pattern and/or scale marks and/or digits figures. Watch drive may be at least one reversible stepping motor or several unidirectional ones, in this case, two motors 123 and 124 are shown in Fig.18, and they may run consecutively or simultaneously. For instance, two bipolar motors may consecutively perform a quarter-turn of their magnetic rotors and due to their kinematic relations perform the possibility of reverse drive by successive commutations of their coils. Drive reversibility may be used for mechanism operation in both directions, thus enabling watch usage from one or another side, and/or for time setting along with increased drive speed.

The gear mechanism of electro-mechanical watch consists of four concentric nested planetary gearings with pairwise joined movable ring and sun gears. Kinematically, as shown in Figs.18 and 19, in radial direction the first, single-row weekly gearing with double-row gears has engagement in accordance with Fig.4 and consists of gears 128, 129, 130, the second, daily gearing in accordance with Fig.7 consists of gears 131 , 130, 132, 133, the third, hourly gearing in accordance with Fig.6 consists of gears 134, 133, 135, 136, the fourth, minute gearing in accordance with Fig.7 consists of gears 137, 136, 138, 139, with sun gear joined 139 to crown gear, which in turn is engaged with each of driving 121 , 1 19 and suspension gears 1 1 - 122 in

accordance with Fig.5. Sun gears of planetary gearing system which have to be fixed in kinematic relations may be joined to barrel and either directly to one of watch glasses or to an additional housing part located between them. Thus, central sun gear 128 is joined to barrel 109, whereas three other sun gears 131 , 134, 137 - with watch glass 1 12.

As the suspension of gear mechanism is based on bearing gears engagements, except axial supports of gears 1 19-122, more than two uniformly distributed satellite bearing gears or their clusters are used per each planetary gearing.

This basic mechanism operates as follows, Figs.18 and 19. From power source 1 10, via clamps and electric circuits from barrel 109, through glass 1 12 and/or 1 13, watch case 1 14 and housing parts to control system 127, the power is supplied and transferred into actuating pulses for drives 123, 124. Buttons 125, 126 and/or sensor elements manage control system 127. Drives create torque on suspension gears 1 19 and 121 , which actuate crown gear joined to ring gear 139 of minute gearing as well as suspension gears 120 and 122. The gear 139 actuates rotation of satellite gear clusters 138, whose larger gears roll on the fixed sun gear 137, smaller gears, in turn roll on sun gear joined to ring gear 136 of hourly gearing, which in turn actuates rotation of satellite gear clusters 135, whose larger gears roll on fixed sun gear 134, smaller gears, in turn, actuate rotation of sun gear joined with ring gear 133 of daily gearing, this in turn actuates rotation of satellite gear clusters 132, whose larger gears roll on the fixed sun gear 131 , smaller gears, in turn, actuate rotation of sun gear joined to ring gear 130 of weekly gearing, and the last one actuates satellite gears or gear clusters 129, which roll on fixed sun gear 128.

Watch may be controlled by buttons located on its case, Fig.18 and/or by sensor elements, which can locate on watch case, barrel, or watch glasses. Each of the buttons 125, 126 consists of at least insulating housing part with key operated sealed switch inside. Sensor elements may be based on resistive, capacitive or projected capacitance touch technologies. Watch setting mode supposes the arrangement of indication elements, mostly satellites, in conformity with preset time. At watch operation mode drive parameters provide, in most cases, integer number of pulses per second and could be run in two directions. Time setting mode means drive operation at increased speed permitting the quick arrangement of indication elements positions.

At the center of planetary gearing system in barrel 109 instead of power source 1 10, a generator may be installed with inertial sector for charging of power source, and at least one of barrel walls may be made transparent to visualize oscillations of inertial sector. In this case, power source may be arranged in watch case or in bracelet using rotary cylindrical elements in it with flexible or sliding conductors to create a common electric circuit between power source and control system. As in wristwatch bracelet is fixed from two sides of its case, electro-mechanical watch may be manufactured with two power sources located in its bracelet.

An example of mechanical watch wherein gear mechanism counting seconds, minutes, hours and week days is implemented in the form of nested planetary gearings with indication by satellite gears is shown in Figs.20-23. On watch case 140 are fixed watch glasses 141 and 142 with bearing bushings 143 and 144 on their inner rims. The cylindrical barrel rotates within bushings 143 and 144 implementing slider bearing. This barrel constitutes a single housing part from: rings 145, 146 joined to power reserve visualization glasses 147, 148 joined to arbor 149 to which inner end of mainspring 150, as a power source, is joined. The outer end of mainspring 150 is fixed to drum 151 joined to sun gear of beveled planetary gearing. Satellite gears 152 are

axially fixed on carrier 153 with covering lids 154 and engaged with aforesaid sun gear and ring gear 155. On carrier 153 at least between one pair of satellite gears is axially fixed, from inside - the ratchet 156 loaded by spring 157, and from outside - cogged lever 159 with axially fixed ratchet 160 loaded by spring 158 performing ratchet-lever lock mechanism. Inner ratchet 156 engages with ratchet-wheel joined to ring 146, forming a ratchet mechanism that slides under arbor winding of mainspring 150 and turns carrier 153 activating satellite gears 152 for drum winding of mainspring 150. Outer ratchet 160 engages with ratchet-wheel inside sun gear 161 of weekly gearing. This ratchet engagement prevents rotation of carrier 153 during watch operation, performing transmission from sun gear of drum 151 via gears 152 up to ring gear 155, whereas under drum winding of mainspring 150 it slides, forming a differential for continuous drive of watch mechanism. A bearing may be installed between ring gear 155 and bearing bushing 144. Ratchet mechanisms on carrier 153 may be paired, disposed radially opposite one to another for uniform load distribution, in this case loadings on them would be reduced and their structure parameters simplified respectively. Four satellite gears 152 are preferred for more uniform watch mechanism operation and load distribution. Ring gear 155 is joined to ring bearing gear 162 by means of transparent disk 163. This ring gear 162 is engaged with one of bearing gears of each satellite cluster 164. These clusters are engaged with fixed sun bearing gear 165 as well as with movable sun bearing gear 166, thus forming double-row daily gearing. The gear 166 is joined to ring bearing gear of weekly gearing, which has satellite bearing gears 167 rolling on their sun bearing gear 161. From the other side ring bearing gear 162 is joined to sun bearing gear which is engaged with satellite bearing gear clusters 168, and those are also engaged with fixed sun bearing gear 169 and ring bearing gear 170, forming hourly gearing. Ring gear 170 of hourly gearing has specified force frictional coupling with sun bearing gear 171 of minute gearing. Fig.17 shows a detail drawing of the proposed friction coupling as sliding joining. The gear 171 via satellite bearing gear clusters 172 which are also engaged with fixed sun bearing gear 173 actuates carrier 174. On this carrier is arranged at least one escapement consisting of balance wheel-hairspring resonator 175, anchor with pallets 176 and escape wheel 177 joined into cluster with gear 178 engaged with ring gear 179 joined to watch case 140. It is possible to perform the solution without the gear 179, when gear 178 is engaged with the gear 173 or 171. Escapements moving parts are axially fixed by bearings on carrier 174 with joined bridges 180. Satellite bearing gears 181 and the clusters 172 support the carrier 174 in coaxial movement to its planetary gearing. In proposed watch mechanism on carrier of minute gearing is arranged two escapements disposed diametrically opposite to each other. Balance wheels oscillate in resonance to increase accuracy of oscillations and to balance the escapements. In case of single escapement it has to be counterweighted on the carrier. Also due to the conditionality of structure and of gear ratios, the using of two clusters 172 and two gears 181 are preferred. The gears 181 perform one revolution in five seconds and at least one of them or of others satellites may be decorated with a direction indicator for more precision counting of time.

The fixation of planetary gearing system sun gears: 161 , 165, 169, 173 supposes the joining of them to one of the watch glasses 141 and 142 directly or via an intermediate part, or on an additional housing part disposed between this glasses. Thus, central sun gear 161 is joined to bushing 143 and three other sun gears 165, 169, 173 - with watch glass 141.

The mechanism operates as follows, Figs.20 - 23. Ratchet mechanisms prevent rotation of carrier 153 and barrel with arbor 149. The mainspring 150 is initially wound-up and counterforced by the stationary arbor 149 and while untwisting transmits torque from freely

rotatable sun gear of drum 151 to satellite gears 152 axially fixed on stationary carrier 153. Satellite gears 152 actuate rotation of ring gear 1 55, which via disk 163 transmits torque to sun gear 162. The combined action of sun gear 162 and fixed ring gear 169 actuates increased orbital rotation of hourly satellite gears clusters 168. The clusters 168 increase rotation speed on ring gear 170, which transmit torque via friction coupling to sun gear 171 of minute gearing. The combined action of sun gear 171 and fixed sun gear 173 activates increased orbital rotation speed of satellite gear clusters 172 which via their axles fixed on carrier 174 transmit torque to at least one escapement which is actuated through gear 178 engaged with either one of sun gears 171 or 173 or gear 179 installed on housing part. From the other side ring gear 162 performs reduction to satellite gear clusters 164 of daily gearing which with larger gears roll on fixed sun gear 165 and with smaller gears actuate rotation of sun gear 166 joined to ring gear of weekly gearing. The latter ring gear by engagement actuates rotation of satellite gears 167, which roll on sun gear 161 and perform one orbital revolution per week.

The winding of watch is performed by rotation of barrel consisting of items 145- 149 rotating in bearing bushings 143 and 144. By counter-clockwise rotation of this barrel, its ratchet-wheel on ring 146 slides in ratchets 156 relatively to stationary carrier 153, and via its arbor 149 winds inner end of mainspring 150. At that, the outer end of mainspring 150 is almost stationary due to its fixation on the drum 151 with sun gear having gearings up to the escapement(s). By clockwise rotation of the barrel, its ratchet-wheel 146 via ratchets 156 actuates rotation of carrier 153, which by ratchets 160 slides relatively ratchet-wheel joined to fixed sun gear 161. The carrier 153 activates satellite gears 152 rolling on almost stationary ring gear 155, having gearings up to the escapement(s). The satellite gears 152 ensure almost doubled rotation speed of rotation at sun gear of drum 151 relative to the carrier and, respectively, relative to arbor 149, which finally winds the mainspring at speed close to speed of barrel rotation. In this way almost equal torque and speed of watch winding in both directions is attained.

Time setting of such watch is effected by accelerated rotation of satellite gears of hourly gearing with ensuing reduction in the daily and weekly gearings. The time setting principle is based on sliding of joining between minute and hourly gearings, and realized by exceeding of cohesion force threshold of friction coupling between movable sun 171 and ring 170 gears. By clockwise rotation of the barrel consisting of items 145-149, with exceeded full wind torque of mainspring 150 via coupling of ratchet-wheel on ring 146 with ratchet 156, the carrier 153 turns and via locked satellite gears 152, by means of sun gear joined to drum 151 which constrained by wound mainspring 150, transmit increased torque to ring gear 155 which via disk 163 transmits torque to sun gear 162. Gear 162 via hourly gearing creates increased torque at ring gear 170. Rotation speed of sun gear 171 of minute gearing, in turn, is limited by escapement(s). Thus, increased torque at ring gear 170 will try to break the friction coupling with sun gear 171. When the adhesion force is exceeded the gear 170 will slide relative to gear 171 , and the barrel will rotate at about twice times faster than hourly satellite gears orbital speed relative to the barrel axis.

By counter-clockwise rotation of the barrel, with exceeded full wind torque of mainspring 150 the tension folds the linkage of cogged lever 159 with ratchet 160. It is occurred, as the ratchet is thrust with one tooth against ratchet-wheel of sun gear 161 and with another one against slot of carrier 153; the cogged lever 159 is counterforced and loaded by carrier 153 and

spring 158. At that, the cogged lever 159 engages in ring gear 155, locks it to the carrier 153 and stops the watch. The parameters of the linkage of lever 159 with ratchet 160 and springl 58 and of the friction coupling of 170 with 171 gears with spring gasket 108 have to selected to fold linkage after full wind of the mainspring but before slide the coupling. If the counter-clockwise torque on watch barrel is exceeded, gear 170 slides relative to gear 171. Thus, time may be set at the watch in both directions.

After the watch counter-clockwise setting is finished, to initiate its start up the barrel must be slightly turned clockwise in order to liberate the cogged lever 159 from engagement with ring gear 155, then cogged lever will by spring 158 engage ratchet 160 with ratchet-wheel inside sun gear 161 and normal watch operation mode will be restored.

Application of the proposed invention in analog measuring and counting instruments substantially simplifies their arrangement due to symmetry and proportionality of nested coaxial structure. Application of movable gears and/or carriers of planetary gearings as indicators and/or their basis permits to omit bridges, housing parts and even dial which usually separates mechanism from display module. Usage of multiple ratios in engagements between indicators permits a more detailed counting of measured values in both orbital and spinning motions. Application of herringbone, arched or bearing gears as components of planetary gearings permits to omit most of housing parts and supports of movable parts, this reduces the number of kinematic relations and increases mechanism rigidness, accuracy and efficiency. By drives, power source, external kinematic relations, control systems and other items arrangement as inside as at periphery of planetary gearing system, the last remains visible from both sides what improves its attractiveness and permits its reverse usage. Also, considering the possibility of movable parts decoration the invention especially appeals for application in watch and jewelry industries.

SOURCES OF INFORMATION

1. Application WO02/101481

2. Patent US5222051

3. Application DE 4334646C1

4. Application WO 2009/1 12884

5. Patent US N° 3675510

6. Patent RU ½ 2404382

7. Application US jN° 2002/0031288 Alb

Claims

1. Gear mechanism of measuring instrument comprising at least housing part, rotation drive and gearing system, characterized in that system of gearing comprises nested coaxial planetary gearings, at least one of them being double-row, with at least one satellite gear in each of them, and one sun gear or ring gear of each of them is joined to housing part.

2. Gear mechanism according to Claim 1, characterized in that at least one planetary gearing comprises a carrier on which at least one satellite gear is axially fixed.

3. Gear mechanism according to any of Claims 1-2, characterized in that at least one sun or ring gear or carrier is axially fixed relative to housing part.

4. Gear mechanism according to any of Claims 1-3, characterized in that in at least one double-row planetary gearing one pair of satellite gears are joined between themselves.

5. Gear mechanism according to any of Claims 1-4, characterized in that in at least one external planetary gearing sun gear is joined to ring gear of nested planetary gearing.

6. Gear mechanism according to any of Claims 1-5, characterized in that in at least one external planetary gearing sun gear is joined to carrier of nested planetary gearing.

7. Gear mechanism according to any of Claims 1-6, characterized in that in at least one external planetary gearing carrier is joined to ring gear of nested planetary gearing.

8. Gear mechanism according to any of Claims 1-7, characterized in that in at least one double-row planetary gearing satellite gears in pairs are axially fixed relative to one another.

9. Gear mechanism according to Claim 8, characterized in that two ring gears or sun gears of at least one planetary gearing are joined between themselves.

10. Gear mechanism according to Claim 8, characterized in that in at least one of planetary gearings two ring gears or two sun gears with crown gears on each of them are engaged by gears that are axially fixed relative to housing part.

11. Gear mechanism according to Claim 8, characterized in that in at least one of planetary gearings two ring gears or two sun gears with crown gears on each of them have at least two separate gearings that switch their engagement in kinematic relations.

12. Gear mechanism according to any of Claims 1-11, characterized in that at least one carrier, ring or sun gear has a crown gear engaging with at least one gear that is axially fixed relative to housing part.

13. Gear mechanism according to any of Claims 1-12, characterized in that at least one gear or carrier is joined to rotation drive.

14. Gear mechanism according to any of Claims 1-13, characterized in that at least one joining is made as a one-piece or as fixed joint assembly of parts.

15. Gear mechanism according to any of Claims 1-14, characterized in that at least one joining is made as friction coupling with at least prescribed torque of cohesion and/or slippage.

16. Gear mechanism according to Claim 15, characterized in that friction coupling is made in the form of frictional wave spring gasket disposed in slots of concentric parts and surfaces in frictional contact being made smooth or corrugated.

17. Gear mechanism according to any of Claims 1-16, characterized in that at least one movable gear or carrier of at least one of planetary gearings from at least one of its sides serves as indicator or its base.

18. Gear mechanism according to Claim 17, characterized in that indication and/or fashion is disposed on at least one movable gear or carrier.

19. Gear mechanism according to any of Claims 1-18, characterized in that at least one dial is made in the form of digits figures or scale marks on the surface of at least one of housing parts.

20. Gear mechanism according to any of Claims 1-19, characterized in that at least one of its planetary gearings are adjacent to at least one of housing parts.

21. Gear mechanism according to any of Claims 1-20, characterized in that teeth of at least one pair of gears are made herringbone or arched.

22. Gear mechanism according to any of Claims 1-21, characterized in that at least one gearing engagement consists of bearing gears in the form of gearwheels with joined to their end faces cylindrical rollers, whose diameters correspond to pitch circle of their gearwheels.

23. Gear mechanism according to Claim 22, characterized in that gearwheels and rollers adjacent end faces are formed by cylindrical helical extrusions of teeth profiles relative to their gearwheels axis, which are symmetrically cut valleys in adjacent rollers up to teeth middle, teeth and rollers adjacent end faces, engaged in pairs, are formed by helical lines of equal radius with pitch being proportional to reduction ratio.

24. Gear mechanism according to Claim 23, characterized in that gearwheels teeth in them are made according to Claim 21, teeth and rollers adjacent end faces made according to Claim 23, or the distance between teeth end faces is smaller than between rollers inner end faces.

25. Gear mechanism according to any of Claims 22-24, characterized in that at least one bearing gear is made as a single piece.

26. Gear mechanism according to any of Claims 22-24, characterized in that at least one bearing gear in it is made as a fixed joint assembly.

27. Gear mechanism according to any of Claims 1-26, characterized in that in the center of planetary gearing a barrel is installed with at least one transparent wall and/or removable lid.

28. Electro-mechanical watch comprising at least a watch case, gear mechanism, control system, drive and power source, characterized in that its gear mechanism is made in accordance with Claims 1-27.

29. Electro-mechanical watch according to Claim 28, characterized in that power source is installed in its barrel.

30. Electro-mechanical watch according to Claim 28, characterized in that generator with inertial sector is installed in its barrel, whereas at least one power source is disposed in watch case and/or in its bracelet.

31. Electro-mechanical watch according to any of Claims 28-30, characterized in that electric circuits are disposed in barrel and on housing parts, whereas control systems and drive are disposed on at least one housing part.

32. Electro-mechanical watch according to any of Claims 28-31, characterized in that at least one stepping motor serves as drive.

33. Electro-mechanical watch according to any of Claims 28-32, characterized in that buttons or sensor elements of watch control system are disposed on at least one housing part.

34. Mechanical watch comprising at least a watch case, gear mechanism, escapement and barrel with mainspring, characterized in that its gear mechanism is made in accordance with Claims 1-27, whereas barrel with mainspring is axially fixed relative watch case.

35. Mechanical watch according to Claim 34, characterized in that its mainspring outer end is joined to sun gear of beveled planetary gearing whose carrier has at least one satellite gear and at least one ratchet mechanism with ratchet-wheel on housing part and/or on barrel, its ring gear being joined to one of sun gears or of carrier of watch nested planetary gearings.

36. Mechanical watch according to Claim 35, characterized in that at least one ratchet mechanism contains a ratchet-lever lock capable to switch couplings between ratchet-wheel and gear of mechanism under prescribed force.

37. Mechanical watch according to any of Claims 34-36, characterized in that on one carrier at least one escapement is disposed and engaged with movable gear or gear joined to housing part coaxially with carrier.