Transmission

FIELD: machine building.

SUBSTANCE: transmission consists of gear (40) with internal teeth (41) and rotation axis (40a) in form of hollow cylinder with end sides (49) wherein there are installed driven input shaft (10) and output element. The output element consists of two elements of rotation (50, 50') conjugated one with another without turning and having round cross section in plane perpendicular to rotation axis (40a), between which there is positioned at least one gear (30) and also elements (70) converting planetary motions of gear (30) into rotating motions of the output element. Forces facilitating connection of the output element, and forces of a support, acting between the output element and gear (40), are independent from each other in this transmission.

EFFECT: simplified assembly of transmission and increased specific power at maintaining same dimensions.

19 cl, 17 dwg

 

The invention relates to a transmission that converts the planetary movement of the wheel during rotational movement of the output element.

Known transmission containing a Cup-shaped wheel, which includes internal teeth and the axis of rotation (PL, 169808, B1). In the wheel for rotation around the axis of rotation has a drive input shaft and the output element. Output element consists of the element of the rotation of circular cross section, placed perpendicularly to the axis of rotation. Between the first feature and the base of the Cup-shaped wheel, there are two gears that are in mesh with the wheel with internal teeth, and the elements, transforming the planetary movement of the wheel during rotational movement of the output element. The input shaft is set in rotation in the base element and the rotation in the wheel and the input shaft. However, access is provided only on one side, in particular the drive and PTO, and the installation is difficult due to the lack of control when installed in a closed one side of the Cup wheel.

Known transmission containing the wheel with internal teeth (EP, 0474897, A1). The wheel is rotatably mounted a drive input shaft and the output shaft. The output element is connected with the output shaft can move in the axial direction. Output ELEH the UNT contains two placed at a distance from each other element of the rotation of circular cross section, placed perpendicular to the input and output shaft. The input and output shafts installed on both elements of rotation at right angles. Revolve tightly matched or paired together. Between the elements of the rotation, there are two gears that are in mesh with the wheel with internal teeth, and the elements, transforming the planetary movement of the wheel during rotational movement of the output element. Output element without support is supported in the radial direction relative to the wheel through engagement with the internal teeth of the wheels. Mounting of the output element in the axial direction relative to the wheels does not exist or it is also made without the support, so that axial movement of the output element are inhibited only by contact with the cover or with the wheel or with the side surfaces of the internal teeth. However, the described transmission has low productivity in combination with the expected significant level of wear and tear, caused by the deterioration of the output element, without which supports installed in the wheel.

Known transmission containing made in the form of a hollow cylinder with end sides of the wheel, which includes internal teeth and the axis of rotation (WO 95/22017). In the wheel for rotation around the axis of rotation has a drive input shaft and the output element. echodnou element contains two placed at a distance from each other element of the rotation of circular cross section, placed perpendicular to the axis of rotation. The rotation axis is perpendicular to both the rotation. Revolve tightly matched or paired together. Between the elements of the rotation is at least one gear wheel which engages with a wheel with internal teeth, and the elements, transforming planetary wheel movement into rotational movement of the output element. The input shaft is mounted on both sides in the elements of the rotation of the output element, which, in turn, on both sides mounted on bearings in the wheel, made in the form of a hollow cylinder.

Both drives fitted on the supports directly on or in the wheel, resulting in a force that ensures the connectivity of both elements of the rotation, at the same time contributes to support both elements of the rotation. This leads to jamming of the bearings, increased wear and heat, and in the worst case - the transfer lock.

In addition, such transfer has a rather complicated structure, as part placed between the elements of the rotation, you must install after the feature has already been posted in the wheel.

In addition, external forces acting on the gear especially in the axial direction, is transmitted into the transmission and cause there snakeprint the s load lead to the deterioration of the strength characteristics.

When this bearing is designed so that each radial bearing creates support each individual element of rotation with respect to the radial forces acting perpendicular to the axis of rotation with each end face of the wheel.

In addition, each thrust bearing creates a support for each of the two located on both sides of the wheel revolves in relation to the respective axial components of force directed along the rotation axis side of the wheel with each end face of the wheel.

The input shaft is installed on the elements of the rotation on the same principle.

Thrust bearings that serve as a support for the input shaft to revolve when exposed to axial forces are, however, exactly the opposite, as thrust bearings that serve as a support for the wheel.

This means that the input shaft is installed on both elements of the rotation in each case with one thrust bearing, which respectively transmits axial forces acting on the input shaft in the direction of the axis of rotation and away from the wheel, the element of rotation that is located in each case on the outer side of the wheel in the direction of the force. Combined radial-thrust bearings can perform both functions simultaneously.

Importantly, without the interface is between the two elements of the rotation will happen separation of transmission. To prevent this, both the rotation of the output element are connected to each other with the possibility of separation, by means of connecting elements, for example screws.

In this connection elements perform several functions. On the one hand, they enable the creation of the same number of turns and equal torque on both sides of the power take-off (usually on the working side) of the transmission formed by the two elements of the rotation. On the other hand, linking together the connecting elements, the elements of the rotation hold together and transmission parts located between the elements of the rotation of the wheel along the axis of rotation. These parts are mainly one or more of the elements contained in the eccentric movement of the input shaft and being in mesh with a wheel with internal teeth of the wheel itself, the input shaft and the elements, transforming the planetary movement of the wheel or wheels in rotational motion of the output element.

In addition, the connecting elements transmit axial forces acting on the input shaft and/or output element, the elements of the rotation, the axial bearing which, in turn, can transmit the corresponding axial forces on the wheel. Such axial force or a pair of axial forces can occur across the axis of rotation, for example, in financial p is Tata impact points on the input shaft and/or output element. In addition, the connecting elements to prevent separation of bearings located between the output element and the input shaft and the output element and the wheel, pressing revolve on two sides to the end surfaces of the rolling wheels.

However, if you want to achieve a particularly smooth running and high gear ratios and quality when transmitting power from the drive side to the side of the PTO, the versatility of connecting elements creates certain difficulties.

For example, for the transmission of axial forces and/or couples axial forces acting on the input shaft and/or output element through the bearings of the elements of the rotation wheel, the connecting elements are firmly gripping both ends of the rotation, because otherwise these forces would dilute the elements of the rotation.

If the elements of the rotation were divorced, to ensure reliable and accurate gear, which in most cases is a crucial factor, it would be impossible. To create a corresponding significant efforts compression, you need to choose the appropriate large dimensions of the connecting elements. However, the connecting elements of large dimensions require more space and increase the weight of such transfer.

The bearings between the input shaft and the elements of rotation and between which the elements of the rotation and the wheel is not too hard to compress in the axial direction. This can cause excessive heat transfer due to friction losses in the bearings.

However, because the dimensional tolerances of the transmission parts located between the elements of the rotation along the axis of rotation, are summarized as dimensional tolerances of the elements of the rotation of the wheel, then the above requirements are the opposite.

On the one hand, this is because, if adverse to the sum of the tolerances for the parts located between the elements of the rotation, these parts can also be compressed at the required large compression elements of the rotation. As a result, may experience large losses due to friction between these parts, which will lead to overheating and destruction of the transmission. In the worst case it is even possible jamming of these parts.

On the other hand, this is because, if adverse to the sum of the tolerances of the elements of the rotation of the wheel and/or elements of the rotation of the input shaft there is also the possibility of compression of the thrust bearings between the elements of the rotation and the wheel and/or thrust bearings between the input shaft and both elements of the rotation at the required large tension elements of the rotation. This can also lead to large losses by friction in the thrust bearings, which can cause overheating and premature failure of the transmission.

Finally, in this regard, the important and then, that result can occur even concave deformation of the elements of the rotation.

Another disadvantage, due to the versatility of connecting elements, is that the compression force created by the connecting elements, during the operation can fail, especially as the connecting transmission elements are constantly under stress.

Thus, the disadvantages of transmission known from the prior art, can be summarized as follows:

a) the presence of dynamic loads acting in opposite directions to revolve;

b) the need to produce all of the parts of the output element with a high degree of accuracy by fitting them under the relevant details of the wheel, resulting in a long chain of tolerances, and therefore, is a cause other negative consequences;

c) the stiffness of the output element when the tilting is limited by the elasticity which runs in the axial direction of the connecting elements (screws);

d) a large starting torque transmission.

The basis of the invention is to eliminate the above described disadvantages and, in particular, the creation of a standard transmission that does not require undue cost on the design, so that when a simpler method of manufacture of individual parts and assemblies transfer obespechiyola high resistance to twisting, as well as increased power density while maintaining the same size.

The task was solved by creating a transmission according to the invention, containing the wheel with the front sides, which includes internal teeth and the axis of rotation. The wheel is rotatably mounted a drive input shaft and the output element. The output element contains two elements of rotation, matched or paired among themselves without the possibility of twisting. Revolve a round cross-section and is placed perpendicular to the axis of rotation. Between the elements of the rotation is at least one gear wheel. In a preferred embodiment, the gear wheel is in mesh with internal teeth. Between the elements of the rotation are the elements that transform the planetary movement of the wheel during rotational movement of the output element. Power, connectivity of parts of the output element, this transfer does not depend on the efforts of a support force between the output element and the wheel.

In order to achieve independence forces, ensuring the connectivity of parts of the output element from the efforts of the bearing force between the output element and the wheel, it is preferable to provide for the application of the axial components of the forces, ensuring the connectivity of parts of the output element among elements of the rotation o the underwater element. Acting between the output element and the wheel axial force supports should be attached at a point between only one of the two components of rotation of the output element and the wheel.

The axial components of the forces, ensuring the connectivity of parts of the output element, preferably applied indirectly through the active elements on the plot between the elements of the rotation of the output element.

Thrust bearing acting between the output element and the wheel, preferably applied indirectly through the elements affecting only one of the two elements of the rotation of the output element.

It should be recognized that the invention will be carried out in any case when a conventional planetary gear output element, is supplied, as a rule, two parallel elements of rotation is placed at a certain distance, will be installed on supports so that two such elements of rotation, only one was installed directly in or on the wheel.

Both ends of the rotation form two end side of the output element and the wheel.

External forces acting on the output element in the process of transmission, at least in the axial direction, almost fully perceived from the first feature that is installed directly in or on the wheel.

On the other side of the wheel the second element of the rotation is almost not affected by the action of external forces and, in particular, is not under the influence of external forces, at least in the axial direction. At the same time, this feature is not in working contact with the wheel.

The only important force that acts on an element of rotation that is not installed on or in the wheel for rotation, or only indirectly mounted on or in the wheel for rotation, either mounted directly on or in the wheel rotatably to resist radial forces, is the static force exerted by the fasteners, typically screws, in order to keep the overall output element made in the form of structural node.

This configuration prevents transmission to another element of the rotation of the external forces acting on the element of rotation, located directly on the wheel or in the wheel, at least in the axial direction.

In the result of the only parts of the transmission that must be processed with a high degree of accuracy, will be provided to support the output element of the contact surface and the rolling surface of the wheel, element rotation, installed directly on the sludge is in the wheel, as well as holding the wheel.

Because access to these surfaces easily provided in one direction, the production time of transmission can be reduced by half.

Another advantage of this technical solution according to the invention is that due to the special positioning of the support elements is provided by a sizeable increase in the working of the internal space of the transmission, and hence a significant increase in the transmission power while maintaining the same size and a substantial reduction in weight.

In General, the key idea of the invention is applicable in the planetary gear of any type.

To preserve independence, the support reactions and effort, ensuring the connectivity of the elements of the rotation, preferably, in the transmission according to the invention only one of the elements of the rotation was set directly in the wheel, at least in relation to axial forces.

In addition, it is preferable that the transfer was provided by the annular holding the wheel tightly mating with the front side, which creates a support for the installed directly in the wheel element of rotation by means of the support element.

While it is preferable that the retaining wheel was made in the form of easily machinable thick cut t the UBA, both end sides must now only be sanded and execute them in the appropriate holes for the screws.

In addition, mounted directly in the wheel element rotation can build on the wheel using the same or other supporting elements.

Compared with the above-described analogs advantage of the transmission according to the invention is that now, thanks to one-sided, at least in relation to the axis of the support efforts of the output element in the area of only one element rotation fasteners, typically screws, to the extent possible, do not experience stress.

Now the transfer of effort from mounted on a support element of rotation to the frame containing the transmission is completely bypassing, at least with respect to the axial forces unsupported second element of rotation, and, therefore, bypass connecting both ends of the rotation with each other connecting elements.

Along with eliminating known from the prior art drawbacks transmission according to the invention has the additional advantage that it is much easier to manufacture and installation. This advantage, inter alia, due to the fact that the supporting elements for the installation of the elements of the rotation directly on the wheel or in the wheel and to create emphasis, hence, is her least with respect to the action of the axial forces must be placed only on one side of the wheel.

Since these supporting elements are preferably the only means of connecting parts located between the elements of the rotation, and a wheel, the manufacture of transmission according to the invention can occur in a more convenient format in several successive stages.

First, you can mount all the parts located between the elements of the rotation, and position them as desired relative to each other by connecting both elements of the rotation.

Then the entire unit, consisting of elements of rotation and located between the parts can be placed in the wheel.

In contrast to the above-described analogs to mount the elements of rotation and located between the parts when they are already in the wheel, is no longer required.

For example, according to the invention to install the supporting elements between the wheel and mounted on a support element rotation is only necessary during placement and installation of pre-assembled unit in the wheel. This reduces the duration of installation and to reduce the number committed during Assembly errors.

Elements, transforming the planetary movements of the toothed wheel in the rotational motion of the output element may provide the identification of a, for example, the direction converting element (WO 95/22017) can be moved in two orthogonal directions, located between the toothed wheel and the elements of the rotation.

On the other hand, the elements, transforming the planetary movements of the toothed wheel in the rotational motion of the output element can be performed, for example, in the form of sleeves in the form of an eccentric ring (WO 2006/058743), located between the slots in the gear ring or element of rotation, and in rotation or in the gear wheel, and spikes protruding in the recess in the gear wheel and the element of rotation.

It is important that for fixing the output element in the wheel of one of the elements of the rotation is preferably mounted on or in the wheel bearings for rotation.

For fastening of the output element in the wheel of one of the elements of the rotation to create emphasis, at least in relation to the action of the axial forces can be mounted on a support for rotation directly in or on the wheel, while the other element rotation is not installed in or on the wheel, or it is installed in or on the wheel for rotation, but only indirectly, or it is installed directly in or on the wheel for rotation only to create emphasis with respect to the action of radial forces.

One of the elements of BP is recorded can be installed on the pole directly in or on the wheel rotatably how to create a stop against the action of the axial forces and to create emphasis with respect to the action of radial forces.

Mounted rotatably in or on the wheel element rotation, preferably, is supported by means of supporting elements for holding the wheel tightly matched or paired with one end side.

One preferred embodiment of the invention provides accommodation support elements near the front side, which is holding the wheel.

It considerably facilitates the manufacture of transmission according to the invention in comparison with the manufacture of transmission known from the prior art, as by providing a much greater availability of raceways for cylinders supporting elements, and due to the simplified positioning cylinder supporting elements.

According to another preferred variant implementation of the invention, at least in rotation, installed directly in or on the wheel, and the wheel for the provision of raceways for cylinders serving base element rotation in the wheel, for example, in the form of planes and/or grooves with polished and hardened surfaces.

Additional preferred embodiment of the invention provides that at least the supporting elements, and t is the train, preferably, the respective rolling surface used for podpiranja element rotation, mounted directly on or in the wheel against the action of the forces passing in the axial direction toward the internal teeth are offset outward in the radial direction in the area of the element, which is designed to convert the planetary movements of the toothed wheel in the rotational motion of the output element and which is located on the same side of the internal teeth, which is mounted directly on or in the wheel element rotation.

The resulting advantage is that due to the offset outward in the radial direction of the cylinder, employees support elements, for example, in the field of transformative element that converts the planetary movements of the toothed wheel in the rotational motion of the output element, is created gear with a very small outer dimensions and, in particular, with much less constructive in length.

Especially preferred embodiment of the invention provides that at least the supporting elements, and also, preferably, the respective rolling surface, placed in a closed path around the axis of rotation and provided for podpiranja element rotation, fitted the frame directly on or in the wheel, against the action of the forces passing in the axial direction are offset in the direction of the rotation axis in the direction from the inner teeth of the opposite element, which is designed to convert the planetary movements of the toothed wheel in the rotational motion of the output element and which is located on the same side of the internal teeth, which is mounted directly on the wheel or in the wheel element rotation.

The resulting advantage is that there is an increase in internal space to accommodate the moving parts between the elements of the rotation.

This is due to the fact that the cylinders that serve as support elements are shifted in the axial direction with respect to the parts located between the elements of the rotation, and are arranged with a certain offset in the radial direction. This allows you to make a more durable transmission while maintaining the same outer diameter as, for example, converting items get much more space in the wheel radial direction.

Another, particularly preferred embodiment of the invention provides for the execution of the supporting elements in the form of spherical rolling elements, which rely on mounted directly on or in the wheel element rotation in axial and R is dialnum direction, and are located in a common annular space bounded by the running surfaces formed on the retaining wheel and is directly mounted on the wheel or in the wheel element rotation, and placed in a closed path around the axis of rotation in the area of the face side where the retaining wheel.

The option provides complete advantage lies in the fact that in order to pass through the common rolling elements all axial and radial forces acting on the element of the rotation of the wheel to its associated by means of the fasteners holding the wheel need only a single annular space.

Additional, especially preferred embodiment of the invention provides for the execution of the supporting elements in the form of a cylindrical rolling elements, which rely on mounted directly on the wheel or in the wheel element rotation in the axial and in the radial direction, and are located in a common annular space bounded by the running surfaces formed on the wheel, holding the wheel, and mounted directly on or in the wheel element rotation and arranged in each case at an angle of 45° to the axis of rotation in a closed path around the axis of rotation in the area of the face side where the retaining wheel.

The advantage of this variant is that unlike options, involving the use of spherical rolling elements, a cylindrical rolling elements can withstand higher loads, since they rely on their respective rolling surface in a single point, and are with them in linear contact.

According to a preferred variant implementation of the invention provides that the side facing the element rotation, which is unsupported, or only indirectly mounted on a support on the wheel or in the wheel, or installed directly on or in the wheel only to resist the radial forces, the transmission is equipped with a cover that protects from dirt moving parts inside it.

Preferably, the lid was equipped located in the middle of the hole, through which the input shaft, for example, for communication with the drive motor.

To prevent ingress of impurities gear between the cover and input shaft in the area of the Central hole can accommodate a seal going around the perimeter.

Especially preferred is when the lid perform a rolling surface for supporting elements through which the input shaft is installed on the cover is on the side of the shaft, facing the element rotation, which is unsupported, or only indirectly mounted on a support on or in the wheel, or installed directly on or in the wheel only to resist radial forces.

This eliminates the effects of axial forces on the unsupported element rotation, which, in turn, eliminates the need to transfer axial forces between the elements of the rotation by means of connecting elements, connecting both ends of the rotation with each other.

Preferably, between mounted directly on the wheel or in the wheel element rotation and holding the wheel was provided by passing around the perimeter seal to prevent contamination in the transmission from the PTO.

According to a preferred variant implementation of the invention, the side of the transmission facing the element rotation, installed directly on the wheel or in the wheel, made in the form of side of the PTO, and the side of the transmission facing the element rotation, which is unsupported, or only indirectly mounted on a support on or in the wheel, or installed directly on or in the wheel only to resist radial forces, made in the form of the drive.

As experience shows, the load from the side of the PTO are usually higher loads on the drive side, it is therefore advisable to place the side of the PTO have installed on the supports of the first feature, since it allows to reduce the moments acting on the supporting elements, and the resulting pairs of forces.

The invention is hereinafter explained in more detail several examples of how to perform transmission according to the invention and the attached drawings on which is shown:

Figure 1 is a first embodiment of a transmission according to the invention, longitudinal section,

Figa is the same as in figure 1, the section along the line a-a (figure 1),

Fig.1b is the same as in figure 1,the section along the line B-B (figure 1),

Pigs is the same as in figure 1, the section along the line C-C (figure 1),

Fig.1d - gear transmission shown in figure 1,

File first element of the rotation of the transmission shown in figure 1 forms the first part of the output element

Fig.1f - the second element of the rotation of the transmission shown in figure 1, forming a second portion of the output element

Figd - transforming transmission element shown in figure 1,

2 is a second embodiment of the transmission according to the invention, longitudinal section,

Figa is the same as in figure 2, a section along the line a-a (Figure 2) or In (2),

Figure 3 - the third embodiment of the transmission according to the invention, longitudinal section,

4 is a fourth embodiment of the transmission according to the invention, food is inoe section

5 is a fifth embodiment of the transmission according to the invention with a drive motor attached to the flanges, longitudinal section,

6 - same as figure 5, the first embodiment of the fragment VI (figure 5),

Fig.7. - same as figure 5, a second example of execution fragment VI (figure 5),

Fig is the same as in figure 1, an embodiment of a fragment VIII (fig.1b),

Figure 9 - exploded view of the transmission shown in figure 5.

All fully or partially shown in figure 1-9 transmission contain the wheel 40, is made in the form of a hollow cylinder with end sides 49, having internal teeth 41 and the axis 40A of rotation, which is rotatably mounted a drive input shaft 10 and the output element.

The output element contains two elements 50, 50' of rotation. Revolve is made mainly disc-shaped. Disc-shaped side elements 50, 50' of rotation are located at some distance from each other. The elements 50, 50' of rotation can be tightly matched or paired together. The elements 50, 50' of rotation of a round cross-section and is placed perpendicular to the axis 40A of rotation. Between the elements 50, 50' of rotation are the wheels 30. Wheel 30 with its outer teeth 33 are in engagement with the internal teeth 41 of the wheel 40. In addition, between the elements 50, 50' of rotation are the elements that transform the PLA is Marnie movement of the wheels 30 in the rotational motion of the output element. The transmission shown in figures 1-9, in each case only one of the two elements 50, 50' of rotation, namely the rotation element 50 is mounted directly to the wheel 40. In addition, provided for holding the wheel 40', tightly mating with the front side 49 and is made in the form of a ring. Element rotation 50 both in axial and in radial direction by means of the elements 43A, 43b, and 43C rolling (figures 1 and 9) or elements 43A, 43r rolling (figure 2), or elements 43g rolling (figure 3), or elements of the 43d, 43e rolling (figure 4) is based directly on located on the front side 49 of the wheel 40 holding the wheel 40'

This functional arrangement of moving parts located between the elements 50, 50' of rotation of the wheel 40, the same in all variants of execution, shown in figures 1-9. The input element 10 in the form of the input shaft has two eccentric section 17, mutually offset by an angle of 180°. Eccentric sections 17 offset from the axis 40A on the eccentricity that is, each of the Cam sections 17 mounted for rotation wheel 30. Thus, the eccentricity e corresponds to the distance between the rotation axis 30A of the wheel 30 and the axis 40A of rotation of the wheel 40. Between the Cam sections 17 and wheels 30 posted by the rolling elements 12 that are designed to reduce friction losses, rolling resistance which occurs povashemu the perimeter of each of the Cam sections 17. To do this around the perimeter of the eccentric sections 17 are made of a raceway for rolling elements 12 that serve as supporting elements for the wheels 30. The wheel 30 has external teeth 33 and a Central hole with an inner surface 31 of the raceway for rolling elements 12.

Wheels 30 have several end-to-end axial bore 32 located radially offset relative to the Central hole has an internal surface 31 of the rolling elements, and these openings 32 are evenly distributed around the axis 30A of the wheel 30. Axis 30A of the wheels 30 parallel to the axis 40A of rotation of the input element 10 and the output element is formed by two elements 50, 50' of rotation. The axis 40A of rotation is simultaneously the axis of symmetry of the wheel 40. As shown in figure 5, the input element 10 is connected with the shaft of a drive motor 8 by means of pins (not shown). The drive motor 8 is connected with the wheel 40 having internal teeth 41 and is made in the form of a hollow crown gear, with the cover 94 and screws (not shown). The drive motor 8 is located on the side of the transmission opposite to the rotation element 50 that is installed in the wheel 40. This aspect forms thus the drive side, while the rotation element 50 is installed in the wheel 40, forms a side of the PTO transmission.

Coles are located in the middle between the two elements 50, 50' of rotation, formed by a circular outer contour or located perpendicular to the axis 40A of rotation of a circular cross section, and the elements 50, 50' of rotation are connected to each other by connecting elements 60, 62 with the possibility of separation and together form the output element of the gearing. On the rotation element 50 is located remote elements 52, provided with holes 53A, 53b and the clamping elements 59A, 59b thread for fastening the connecting elements 60, 62. Remote elements 52 contactless placed in the holes 32 of the wheel 30 so that the elements 50, 50' rotation rigidly joined by means of the wheel 30. The output element is formed by two connected to each other by elements 50, 50' of rotation, is mounted for rotation around the axis 40A of rotation relative to the wheel 40 having internal teeth 41.

The internal teeth 41 of the wheel 40 engages with the external teeth of the wheels 30. The axis of the wheels 30 are parallel to the axis 40A of rotation of the wheel 40, but is offset from the receipt of eccentricity that is, the Elements 50, 50' of rotation provided with guide tracks 54A, 54b, creating a linear guide 50b. Linear guide 50b is directed across the axis of rotation 40A elements 50, 50' of rotation. Each wheel 30 has guide work surfaces 34a, 34b defining LINEST is Yu guide 30b, moreover, this linear guide 30b are oriented transversely to the axis 30A of the wheel 30. On both sides of the transmission between the rotation element 50 or 50' of rotation and the wheel 30 is cross transformative element 70. Transforming element 70 has two spaced perpendicularly to each other working surfaces a, 74b or 75A, 75b, which are connected with the linear guides 50b and 30b corresponding element 50, 50' of rotation or wheel 30 so that relative to the corresponding element 50, 50' rotation with one hand and relative to the wheel 30 on the other hand the transformative element 70 is located so that they can move in two perpendicular to each other. One linear guide 50b performed on the element 50 of rotation or the element 50' rotation, while transforming element 70 is located so that they can move in the other direction on the guide rail 30b on the wheel 30.

Both elements 50, 50' of rotation, and transforming elements 70 provided with Central openings 51, 51' or 71. The input shaft 10 of two of its ends mounted in the Central hole 51, 51' of the elements 50, 50' of rotation. The Central openings 51, 51' formed on its inner surfaces of the raceway for supporting elements 3. By supporting elements 3 the ends of the input shaft 10 is installed in the centre of the material of the openings 51, 51' elements 50, 50' of rotation. The input shaft 10 passes with clearance through a hole 71 conversion element 70. The inner diameter of the hole 71, at least on the 2nd larger than the outer diameter of that segment of the input shaft 10, which passes through the opening 71. The guiding surfaces 54A and 54b on every element 50, 50' rotation performed on opposite sides of the protrusions 55A and 55b. The protrusions 55A and 55b made in the form of asymmetric pairs and are located on the front side of the corresponding element 50, 50' of rotation. The guiding surfaces 54A and 54b are made directly on the protrusions 55A and 55b of the elements 50, 50' of rotation. They can be made in the form of flat strips, which can be mounted on opposite sides of the projections 55A, 55b.

Guides working surfaces 34a, 34b, which is provided with each wheel 30, is made on opposite sides of the protrusions 35b. They are formed with centrally located opposite each other in pairs, are made on the front of the wheel 30. The axial bore 32 of the wheel 30 are uniformly distributed on a circle between the projections 35A, 35b. Guides working surfaces 34a, 34b are made directly on the projections 35A, 35b of the wheel 30. However, they can be made also in the form of flat bars rigidly mounted on opposite sides of the projections 35A, 35b.

On Fig detail as shown in the assembled state, the elements 80, 90 rolling elements located between the shoulders 74 directing surfaces a, 74b or 75a, 75b. Boundary surface 76, 76' limit actual length of the guide surfaces a, 74b or 75a, 75b on the shoulders 74 along which can move elements 80, 90 rolling. The value of w indicates the width of the shoulder 74. In addition, as shown in Fig, the inner circumference RS internal teeth 41 passes through the symmetry axis of the needle elements 41b rolling elements arranged in axial grooves 41A. The outer circumference 41fc internal teeth 41 passes through the base of the axial grooves 41A.

The internal teeth 41 of the wheel 40 are composed of needle-like elements 41b raceway is installed in the axial grooves 41A on the inner perimeter of the wheel 40. Axial grooves 41A are evenly distributed on the inner perimeter of the wheel 40. It, therefore, is about the gears, the teeth are preferably made in the form of horizontally-oriented cylinder. External teeth 33 of the wheels 30 are made in accordance with Volnoe is different.

The protrusions 55A and 55b of the rotation element 50 is located remote elements 52. These remote elements 52 with a gap located in the axial hole 32 of the wheel 30, and thus they are provided with axial holes 53A, 53b, and the clamping elements thread 59A, 59b. Holes 53A, 53b and the clamping carving elements 59A, 59b are provided for fastening the connecting elements 60, 62. The connecting element 60 is made in the form of screws, connecting elements 62 in the form of fingers (Fig.9). Due to the delay made in the form of screws 60 connecting elements 60 to the face side of the remote elements 52 set the position of both elements 50, 50' of rotation.

Unlike element 50' of rotation mounted not directly on the wheel 40, the rotation element 50 is supported directly by the support elements radially relative to the wheel 40 in the direction perpendicular to the rotation axis 40A, and the axis relative to the wheel 40 and holding the wheel 40' in the direction of the axis 40A of rotation. Supporting elements include directly the bearing 42 of the rolling element 50 of rotation of the wheel 40. From the front side 49 of the wheels 40 are holes 47 for fasteners 95, through which the retaining wheel 40' is mounted on the wheel 40.

In the transmission shown in figures 1, 1a, 1b, 1c, 5 and 9, the bearing 42 is formed by rolling cylinders 43A, 43b, and 43C, which move in a closed path around the axis 40A of the rotation surfaces 42A, 42b, 50C, 50d, 40 a rolling performed on the wheel 40, the element 50 of rotation and holding the wheel 40'.

The cylinders 43A are located between the surface 42A of the roller and the surface 50C of the rolling element 50 rotation facing the inner teeth 41. The surface 42A of the roller forms an annular stepped flange which is placed at right angles to the axis 40A of rotation is approximately flush with the inner teeth 41. Surface 50C of the rolling elements, which move the cylinders 43A directly on the rotation element 50 represents the outer ring surface element 50 rotation facing the inner teeth and located at right angles to the axis 40A of rotation. In this case the axis a cylinders 43 are perpendicular to the axis 40A of rotation of the rotation element 50.

The cylinder 43b are located between the surface 40 a rolling and surface 50C of the rolling element 50 of rotation facing in the direction opposite to the internal teeth 41. The surface 40 a rolling is the inner ring flat surface holding the wheel 40'facing the element 50 of rotation, which runs at right angles to the axis 40A of rotation. Surface 50C of the rolling elements, which move the cylinder 43b on the rotation element 50, is an annular surface perpendicular to the axis 40A BP is of a stepped ledge on the side of the element 50 of rotation, facing in the direction opposite to the internal teeth. Axis 43b1 cylinder 43b also run perpendicular to the rotation axis 40A of the element 50 of the rotation.

The cylinders 43A and 43b to provide support directly to the element 50 of rotation in both axial directions relative to the wheel 40 and relative to holding the wheel 40'.

Cylinders and 43C are located between the surface 42b of the rolling element passing around the axis 40A of rotation, and the surface 50d of the rolling element 50 of rotation located on the side of the element 50 of rotation facing in the direction opposite to the internal teeth 41, and also passing around the axis 40A of rotation. Surface 42b of the roller is an internal lateral surface of the cylinder extending in the axial direction parallel to the axis 40A of rotation on the inner side of the wheel 40 is turned to the rotation element 50. Surface 50d of the raceway is formed by the outer lateral surface of the cylinder, which is formed by the projection on the element of rotation, and this ledge is located on the side of the element rotation, reverse the internal teeth 41. Axis s cylinders and 43C are parallel to the axis of rotation of the element 40A of rotation 50. Cylinders and 43C support element rotation 50 in the radial direction relative to the wheel 40.

The cylinders 43A are located in the cage of the bearing 45. In principle, it is possible that all the cylinders 43A, 43b, and 43C times escaut in bearing cages, providing the distance of the cylinders 43A, 43b, and 43C from each other, resulting in between them cannot occur friction losses.

As rolling elements 43A, 43b, and 43C can be applied to conventional and well-proven parts, serially manufactured with high accuracy, namely the cylinders that do not require customization.

To reduce the weight of the input shaft 10 provided with a through hole 4, is made coaxial with the axis 40A of rotation. As shown in figure 5, the hole 4 can simultaneously serve for fastening and/or connection to the drive shaft of a drive motor 8.

In the transmission shown in figures 1, 1a, 1b, 1c, 5 and 9, the cylinders 43A are arranged with a radial offset outward in the area of transformative element 70. This allows to achieve high compact design of the transmission, which is much shorter and very small dimensions, in particular, in the axial direction. Because the cylinder 43A is a transformative element 70, which is offset inward in the radial direction and does not purely rotational motion around the axis 40A of rotation, and a combination of rotational movement around the axis 40A of rotation and linear movement perpendicular to the axis 40A of rotation of the cylinders 43A can't stay on their places on the inner perimeter of the wheel 40 through transformative ale the NTA 70. For this purpose the annular supporting element 46 located between the rotation element 50 and the wheel 30, the retaining cylinders 43A in their places. In addition, the cylinders 43A are located in the cage of the bearing. Another feature shown in figure 1, 1a, 1b, 1c, 5 and 9 of the transfer is that the cylinder 43b and 43C and that support an item of rotation in the radial direction and in the axial direction opposite to the cylinders 43A, are located in a common annular space bounded by surfaces 40 a, 42b, 50C and 50d rolling.

The transmission shown in figure 2 and 2A, has a more solid design than the transmission shown in figures 1, 1a, 1b, 1c, 5 and 9. On the one hand, this is due to the fact that, as in the first annular space bounded by surfaces 40 a, 42b, 50C and 50d rolling, and in the second annular space bounded by surfaces 42A, 42b, 50C and 50d rolling, are respectively as cylinders 43r, which serve as direct support in the radial direction for an element of rotation 50 of the wheel 40, and the cylinders 43A, directly supporting in the axial direction of the element 50 for rotation of the wheel 40, and holding the wheel 40'. The function of the cylindrical elements 43r rolling corresponds to the function of the cylinder and 43C according to figures 1, 1a, 1b, 1c, 5 and 9. In this case, the axis of the cylinders 43A, perpendi ularly to the axis 40A of rotation, while the axis of the cylindrical elements 43r rolling parallel to the axis 40A of rotation. Both annular space limited by the General ledge formed by the surfaces 42A and 42b of the roller, which is separated from the internal teeth 41 of the wheel 40 by a distance equal to the width of the conversion element 70. As a result, the cylinders 43A, which are used to create the direct support element 50 of rotation of the wheel 40, and holding the wheel 40' with respect to forces acting in the axial direction, are offset relative to the conversion element 70 located on the same side of the internal teeth 41, and the rotation element 50, in the direction of the rotation axis 40A in the direction from the inner teeth 41. The resulting advantage is that due to the arrangement of the rolling elements forming the supporting elements, offset in the axial direction and shift them outwards relative to the parts located between the elements 50, 50' of rotation, it is possible to increase the size of the interior space available for moving parts between the elements 50, 50' of rotation. The result is that the transmission can be made more durable while maintaining the same outer diameter or the same external dimensions as to accommodate transforming elements 70 have much balsamita in the wheel 40 in the radial direction.

In the transmission shown in figure 3, instead of the cylinders 43A, 43b, and 43C, 43r are spherical elements 43g raceway, located in space, with the appropriate form and limited holding the wheel 40', the wheel 40, and the rotation element 50. Spherical elements 43g rolling in combination with a suitably form the annular space can create a support element 50 of rotation in the axial and in the radial direction directly on the wheel 40, and holding the wheel 40'. The annular space is limited closed concave surfaces 40 a, 42A, 50C, 50d rolling enveloping the axis of rotation. Each surface 40 a, 42A, 50C, 50d roller is tilted relative to the axis 40 of rotation at an angle of about 45°. Thus, the surface of the roller 40 a represents in this embodiment, the concave surface holding the wheel 40', aimed at an angle to the axis 40A of rotation and the internal teeth 41. Accordingly, the surface 42A of the roller is a in this embodiment, the concave surface of the wheel 40, aimed at an angle to the axis 40A of rotation and away from the internal teeth 41. Accordingly, the surface 50 with rolling represents in this embodiment, the concave surface of the element 50 of rotation directed at an angle to the axis 40A of the rotations the Oia and away from the internal teeth 41. Accordingly, the surface 50d rolling represents in this embodiment, the concave surface of the element 50 of rotation directed at an angle from the axis 40A of rotation and the wheel 40. The option provides complete advantage is that in order to transfer all axial and radial forces acting on the rotation element 50 directly to the wheel 40 and the associated by fasteners 95 holding the wheel 40' through the common elements 43g rolling, rather only a single annular space.

In gear, presented in figure 4, to create a direct bearing element 50 of rotation in the axial and in the radial direction relative to the wheel 40 and holding the wheel 40' is provided by cylindrical elements of the 43d, 43e rolling. Cylinders 43d, 43e are located in the annular space, which is inclined approximately at an angle of 45° relative to the axis 40A of rotation and has a square cross-section and surrounds the axis 40A of rotation. In this case the axis 43d1 and a cylinder 43d and 43th inclined in each case approximately 45° relative to the axis 40A of rotation in opposite directions. The annular space is limited to holding the wheel 40', the wheel 40, and the rotation element 50. On holding the wheel 40', on the wheel 40 and the rotation element 50 are in each case is e closed surfaces 40 a, 42A, 50C, 50d rolling, bending around the axis of rotation and forming an annular space.

Thus, the surface 40 a rolling represents in this embodiment, the flat surface holding the wheel 40', oriented relative to the axis 40A of rotation and directed at an angle of 45° to the axis 40A of rotation and the internal teeth 41. Accordingly, the surface 42A of the roller is a in this embodiment, the flat surface of the wheel 40, oriented relative to the axis 40A of rotation and directed at an angle of 45° to the axis 40A of rotation and away from the internal teeth 41. Accordingly, the surface of the roller 50C represents in this embodiment, the flat surface of the element rotation 50, oriented relative to the axis 40A of rotation and directed at an angle of 45° away from the axis 40A of rotation and internal teeth 41. Accordingly, the surface of the rolling 50d represents in this embodiment, the flat surface of the element 50 of rotation oriented relative to the axis 40A of rotation and directed at an angle of 45° away from the axis 40A of rotation and the wheel 40. The option provides complete advantage is that in order to transfer all axial and radial forces acting on the rotation element 50 directly to the wheel 40 and the associated by fasteners 95 the maintenance wheel 40' through the elements of the 43d, 43th rolling, rather only a single annular space. The advantage of this variant transmission compared to the variant shown in figure 3, is that, in contrast to spherical elements 43g rolling, cylindrical elements of the 43d, 43th rolling withstand higher loads, since they rely on their respective rolling surface in a single point, and are with them in linear contact.

Another embodiment of the transmission are presented on figure 5 and 9. In this gear on the drive side, where, according to figure 5 is the drive motor 8 connected to its drive shaft with the input shaft 10, there is a cover 94, which protects from dirt moving parts inside the transmission.

The cover 94 is provided with a protrusion, which is formed by stepwise narrowing its external volume. This stepwise narrowing corresponds to a tight fit on the inner diameter of the wheel 40.

Cover 94 is closed at its outer perimeter flush with the outer perimeter of the wheel 40. The cover 94 has a Central opening through which passes the input shaft 10. Between the cover 94 and the input shaft 10 is located a seal 92, passing around the perimeter to prevent the ingress of dirt.

Similarly, according to Fig.9 between element 50 of rotation and holding the Olsen 40' may be provided by passing around the perimeter seal 93, which prevents contaminants from entering the transmission from the PTO.

In addition, in the Central hole of the cover 94, as shown in figure 5 and 9, may be performed surface 91 for rolling supporting elements 3, through which the input shaft 10 is installed on the lid 94, instead of unsupported or not installed directly on the wheel 40 of the element 50' rotation, as provided in figures 1-4. This eliminates the effects of axial forces on the unsupported element 50' of rotation that is not installed or not installed directly on the wheel 40, which, in turn, eliminates the need to transfer the axial forces resulting from external influences between elements 50, 50' of rotation, through the connecting elements 60, 62, connecting both elements 50, 50' rotation with each other.

Common to all programs, described in different versions of the is the fact that they have stepped tapering section of the wheel 40 in step 44. Step 44 can be used to mount the transmission to the frame 1. Thanks to the step 44 of the mounting 95 can serve for fastening the retaining wheel 40' on the wheel 40 and simultaneously to secure the transmission to the frame 1. The notch 44 is formed by the outer end side 44a, and a rotating side surface of the 44th. Inside on the wheel 40, on the side of the transmission facing the stupa and 44, provided internal centering surface 44i for centering the cover 94.

This centering surface 44i can be performed, as shown in Fig.6 and 7. Figure 6 shows the internal centering surface 44i, made in the form area on the inner side surface of the wheel 40. As a result, the cover 94 can simply be put on the wheel 40, because it is self-centering. The centering surface 44i, shown in Fig.7, is made in the form of a cylindrical inner surface, which may simultaneously serve as a rolling surface for radial bearings 5, which guide the rear element 50' of rotation in the radial direction relative to the wheel 40. It is important that the radial bearings 5 is free to move in the direction of the rotation axis 40A, so that they could not perceive and transmit axial forces. In the connecting elements 60, 62 should not be passed to the external axial force or axial force due to external influences that occur between the elements 50, 50' of rotation.

It is important to emphasize that the transmission according to the invention can also be implemented with only one wheel 30, which converts the element 70 and the two elements 50, 50' of rotation. To compensate for the imbalance caused by the conversion element 70, can be provided is to be opposed.

It is also important to emphasize that, in principle, the transmission according to the invention the input shaft, an output element or wheel discretion, may constitute the drive side, the side of the PTO or the stationary element, without affecting the work of this distribution. In the only change gear ratio. Shown in figure 1-9 examples of the transfer, provided in each case, the input shaft 10 to actuate the transmission by means of a drive motor 8, and a side of the actuator, preferably, is that side of the transmission, which is the element 50' rotation, which is unsupported or not installed directly on the wheel 40. Side PTO is formed by the rotation element 50 mounted directly to the wheel 40. As experience shows, the load of the PTO are usually higher loads on the drive side, so it is advisable to run side PTO has installed directly on support element 50 of the rotation.

Significant features and benefits of the proposed transfer are that only mounted directly on the wheel element 40 50 rotation is exposed to almost all of the forces which act on the transfer or inside the transmission as the result of external loads and the and effort. Unsupported or not installed directly on the wheel 40, the element 50' of rotation are subject only to the action of internal static forces that originate from the connective elements. The rotation element 50 mounted directly on the wheel, forms, usually loaded working side of the transmission. However, the resulting forces and loads are not transmitted to the unsupported element 50' of rotation or element 50' rotation set is not directly on the wheel 40. Thus, the connecting elements, preferably made in the form of screws, can have a simpler construction. They have now only to hold together the output element.

The function is unsupported or not installed directly on the wheel 40 of the element 50' rotation is only to Supplement the output element. Thus, the thickness of the element 50' rotation is made, usually in the form of a circular disk and which is either unsupported or not installed directly on the wheel 40 can be minimized, which, in turn, leads to the fact that the length of the transmission axis can also be reduced. Holding the wheel 40', interacting with rotation element 50 mounted directly on the wheel 40, may be the most common variant of the manufacturing to be a section of pipe that is not bhodemon only sanded the ends and run holes in it for screws. Thus, complex and costly processing methods holding the wheel become no longer needed. The inner diameter of the retaining wheels aligned with the outer diameter of the rotation element 50 mounted directly on the wheel 40, and the wheel 40.

Between the rotation element 50 mounted directly on the wheel 40, the wheel 40 and the retaining wheel 40' defined space rolling, hosts the rolling elements. If the rotation element 50 mounted directly on the wheel 40, is installed on both the face side, it is possible to use a cylindrical supporting elements, some of which is placed along the axis, and the other in the radial direction. The second space of the rolling element is in the plane of the cross-shaped element, which leads to a reasonable reduction of the length of the transmission axis (about the thickness of the cruciform element), and hence to reduction of weight. The placement of the rotation element 50 according to the invention on a support directly on the wheel 40 leads to a noticeable decrease of the ratio of the outer diameter of the cylindrical wheel to its maximum inner diameter in comparison with analogues. It also lets you choose and to optimize the dimensions of the cross-shaped element, wheels, holes and other parts of the planetary gear that the torsion capacity before the Chi (while maintaining without change of the outer diameter can be increased to max 80% with much lower weight.

The invention can find application in industry, particularly in manufacturing or planetary cycloidal gears, for example, for use in industrial robots, in the manufacture of electric Parking brakes in vehicles, in General, in all those cases where you want a lightweight transmission, occupying minimum space and with a large reduction ratio and high performance.

1. Transmission containing made in the form of a hollow cylinder with end sides of (49) wheel (40)having internal teeth (41) and the axis of rotation (40A), which is rotatably mounted a drive input shaft (10)and the output element and the output element contains two elements of rotation (50, 50'), matched or paired among themselves without the possibility of rotation, having a circular cross-section in the plane perpendicular to the axis of rotation (40A), between which there is at least one gear wheel (30)and items (70), which converts the planetary movements of the toothed wheel (30) in the rotational motion of the output element, wherein the output element has a one-way bearing, only one of these elements of the rotation (50 or 50') is mounted directly in or on the wheel (40) and used as specified is odnostoronnei support, and in ensuring the independence of the actions specified support efforts between the output element and the wheel (40) and the forces that ensure the connectivity of the elements of the rotation (50, 50') of the output element by ensuring that their actions in different areas of the specified element rotation (50 or 50'), which specified the backbone of the output element.

2. Transmission according to claim 1, characterized in that to preserve the independence forces, ensuring the connectivity of the output element from the efforts of the bearing force between the output element and the wheel (40), between the elements of the rotation (50, 50') of the output element form the axial components of force of the connectivity of the output element, while the application of the axial forces bearing acting between the output element and the wheel (40), provide between the element rotation (50 or 50') of the output element, which is his arm, and a wheel (40).

3. Transmission according to claim 2, characterized in that the axial components of the forces, ensuring the connectivity of the output element, is formed indirectly through elements (60)installed between the elements of the rotation (50, 50') of the output element.

4. Transmission according to claim 2, characterized in that the output element is mounted on the wheel (40) through tightly mating with the front side (49) of the wheel (40) retaining wheel (40'), and the application of the axial forces support, existing IU the DN output element and the wheel (40), provide indirectly through the wheel (40) and the retaining wheel (40'), affecting only one element of rotation (50 or 50') of the output element, which is the backbone of the output element.

5. Transmission according to claim 4, characterized in that the retaining wheel (40') has an annular shape.

6. Transmission according to claim 4, characterized in that the element rotation (50 or 50'), which is the backbone of the output element rests on the retaining wheel (40') with support elements (43A, 43b, and 43C, 43d, 43e, 43g, 43r).

7. Transmission according to claim 6, characterized in that the supporting elements (43A, 43b, and 43C, 43d, 43e, 43g, 43r) are located in the area of the face side (49) of the wheel (40)facing the retaining wheel (40').

8. Transmission according to claim 6, characterized in that the supporting elements (43A, 43b, and 43C, 43d, 43e, 43g, 43r) made in the form of rolling elements, and element rotation (50 or 50'), which is the backbone of the output element and the wheel (40) is provided raceway (50C, 50d, 42a, 42b) to accommodate these rolling elements (43A, 43b, and 43C, 43d, 43e, 43g, 43r).

9. Transmission according to claim 4, characterized in that at least the supporting elements (43A), the supporting element rotation (50 or 50'), which is the backbone of the output element, to counter the efforts taking place in the axial direction in the inner side of the teeth (41), are offset outward in the radial direction in the area of the element (70)that converts PL is Netanya movement of the gear wheel (30) in the rotational motion of the output element and located on the same side of the internal teeth (41), that element of rotation (50 or 50'), which is the backbone of the output element.

10. Transmission according to claim 4, characterized in that at least the supporting elements (43A), the supporting element rotation (50 or 50'), which support the output member for counteracting the efforts taking place in the axial direction are offset in the direction of the axis of rotation (40A) of the wheel (40) in the direction from the inner teeth (41)opposite element (70)that converts the planetary movements of the toothed wheel (30) in the rotational motion of the output element and located on the same side of the internal teeth (41), and that element rotation (50 or 50'), which is the backbone of the output element.

11. Transmission of claim 8, characterized in that the bearing rolling elements (43A, 43b, and 43C, 43d, 43e, 43g, 43r) made in the form of spherical rolling elements (43g), which rely on the element of rotation (50 or 50'), which is the backbone of the output element as in the axial and in the radial direction, and are located in a common annular space bounded by the surfaces of the raceways (40 a, 42A, 50C, 50d)are formed on the retaining wheel (40') and the wheel (40), as well as the surfaces of the specified element rotation (50 or 50'), which is the backbone of the output element, in the area of the face side (49) of the wheel (40), where the retaining wheel (40').

12. Transmission of claim 8, characterized in that Thu is supporting elements (43A, 43b, and 43C, 43d, 43e, 43g, 43r) made in the form of cylindrical rolling elements (43d, 43e, relying on the element of rotation (50 or 50'), which is the backbone of the output element as in the axial and in the radial direction, and are located in a common annular space bounded by the surfaces of the raceways (40 a, 42A, 50C, 50d)are formed on the retaining wheel (40') and the wheel (40), as well as the surfaces of the specified element rotation (50 or 50'), which is the backbone of the output element, is inclined in each case at an angle of 45° relative to the axis of rotation in the area of the face side (49) of the wheel (40), where the retaining wheel (40').

13. Transmission according to claim 4, characterized in that the protruding end of the input shaft (10) is equipped with a cover (94)having a Central hole to accommodate the specified end of the input shaft (10).

14. Transmission 13, characterized in that around the perimeter between the cover (94) and input shaft (10) in the area of the Central hole is placed a seal (92).

15. Transmission 13, characterized in that the cover (94) performed the rolling surface (91) for supporting elements (3)through which the input shaft (10) is installed in the Central hole of the cover (94).

16. Transmission according to claim 4, characterized in that between the element rotation (50) and retaining wheel (40') is provided by passing around the perimeter of Platania (93).

17. Transmission according to claim 1, characterized in that the side of the transmission facing the element rotation (50 or 50'), which is the backbone of the output element, is designed as part of the PTO, and the side of the transmission facing the element rotation (50 or 50'), which is not the reference made in the form of the drive.

18. Transmission according to claim 1, characterized in that the elements (70), which converts the planetary movements of the toothed wheel (30) in the rotational motion of the output element includes an element (70) in the form of a cruciform element.

19. Transmission p, wherein the transforming element (70), made in the form of cross-shaped element is movable relative to the wheel (30) and elements of rotation (50, 50') and adapted for transverse movement relative to the axis of the input shaft (10).



 

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Gear mechanism // 2250340

FIELD: mechanical engineering.

SUBSTANCE: rotor axis of gear mechanism, performing a planetary movement, is displaced relatively to stator axis for distance of engagement eccentricity. As source auxiliary contour ellipse is used, while proportional coefficient k, determining radius of guiding circle, is taken equal to half necessary number of teeth z of wheel (k = z/2), optimal shape of its teeth is provided by rational combination of ellipse shape coefficient λ, equal to relation of lengths of its semi-axes and eccentricity coefficient of auxiliary contour, in form of relation of length of greater ellipse semi-axis to rolling circle radius, while inner and outer profiles are made in form of elliptic profiles from common ellipse contour.

EFFECT: simplified manufacture.

3 cl, 11 dwg

Reduction gear // 2250398

FIELD: mechanical engineering; summing-up rotary motion from several shafts.

SUBSTANCE: proposed reduction gear has housing 2 with covers 1, detachable horizontal shafts 5 and vertical shafts 10 and 11 with gears 7 and 9. Housing 2 is provided with cavities 6 for gears 7 with holes 3 and mounting seats for horizontal shafts 5 and mounting seats for vertical seats 10 and 11 in center of housing. Mounting seats for vertical upper shaft 11 and lower shaft 10 are made in centers of covers 1. Shafts 5 are located symmetrically and they are diametrically opposite relative to circle. Gears 9 of vertical shafts 10 and 11 are thrown into engagement with all gears 7 of horizontal shafts 5.

EFFECT: summing-up rotation of several quick revolving shafts into rotary motion of two shafts at low angular velocity.

2 dwg

FIELD: mechanical engineering.

SUBSTANCE: two-speed planet cycloidal reduction gear comprises housing (1), cover(2), input shaft (1), output shaft (18), corner eccentric of the first gearing, satellite pinion (5), and central pinions (4) and (7), pinion (7) being movable. All the pinions are mounted on output shaft (1) via bearings (9), (19), and (20). Satellite pinion (5) is made of a spring whose turns have a round concave profile. Central pinions (4) and (7) are made of springs the turns of which have round convex profile and which are welded to define a single structure. The number of teeth of all pinions differ from these of adjacent pinions, and from their left and right sections by the unit.

EFFECT: expanded functional capabilities.

8 cl, 3 dwg

FIELD: instrument industry.

SUBSTANCE: electric drive comprises first and second electric motors, planet gearings, and differential. Stators (5) and (6) of the electric motors are secured to housing (2) of the electric drive. Shaft (7) of rotor (3) of the first electric motor is mounted on base (1) and is connected with central pinion (16) of the differential through a clutch. Shaft (10) of rotor (4) of the second electric motor bears on shaft (7) of rotor (3) and is connected with the hollow central pinion (17) of the differential through a clutch. Central pinion (16) is mounted in the space of central pinion (17) and engages satellites (19). Satellites (19) engage satellites (21) in pair. Central pinion (16) is interposed between two spherical bearings (22) and (23). Carriers (20), (27), and (30) of the differential and first and second planet gearings are made in block with central pinions (25), (29), and (33) of the first, second, and third planet gearings, respectively. Satellites (26) and (32) engage common gearing wheel (34) which is secured to housing (2). Carrier (37) of the planet gearing is made in block with output shaft (40). First (42), second (43), and third (44) supports are interposed between central pinions (25), (29), and (33) and carriers (27), (30), and (37), respectively.

EFFECT: simplified manufacturing and assembling of the electric drive.

cl, dwg

FIELD: mechanical engineering.

SUBSTANCE: reduction gear comprises housing (1), teeth-rollers freely mounted in the recesses of the housing, driving shaft with eccentrics (9), driven flange, and satellites with teeth-rollers (15) freely mounted in the recesses. Teeth-rollers (15) engage teeth-rollers (14). The satellites transmit torque to the driven flange through pins (12). Teeth-rollers (15) of satellites and teeth-rollers (14) of housing (1) cooperate with each other through intermediate set of rollers (16).

EFFECT: enhanced efficiency.

1 cl, 3 dwg

FIELD: mechanical engineering.

SUBSTANCE: planetary-spool reducer has turning case, motionless flange, second flange, drive shaft with eccentrics disposed uniformly around it, satellites with epicycloidal teeth, roller teeth mounted freely inside internal grooves of turning case. Drive shaft has axis of rotation shifted relatively turning case. Second flange is rigidly tied with first flange by bridges crossing windows of satellites. Drive shaft is mounted in roller supports of flanges which supports are disposed eccentrically.

EFFECT: improved efficiency of reducer.

3 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: planet high-power reduction gear comprises housing (1), low-speed shaft made in block with carrier (5), satellites, solar wheel (14), and floating central wheel (2) that is composed of two rims whose teeth are directed oppositely. Solar wheel (14) is secured to driving wheel (13). Housing (1) of the reduction gear is made in block with the common intermediate link provided with inner teeth for receiving the floating central wheel (2) having outer teeth (gearing compensating clutch). The outer diameter of carrier (5) is provided with two end pins for rolling bearings to engage carrier (5) with low-speed shaft through them. The carrier is provided with the central setting opening for receiving driving shaft with solar wheel (14) mounted on the rolling bearings and coaxially-radial setting single-sided openings for receiving satellite gearing compensating clutches (8) mounted on the rolling bearings. Carrier (5) from the side of driving shaft (13) has bearing radially face flange (15) which connects driving shaft (13) and axles with the satellite gearing compensating clutches (8).

EFFECT: enhanced reliability and reduced metal consumption.

3 dwg

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