RU2292494C2 - Clutch - Google Patents

Abstract

FIELD: mechanical engineering.

SUBSTANCE: clutch comprises input axle, output axle, control mechanism, and U-shaped yoke of the output axle. The output axle is provided with the pin secured to one arm of the yoke. The axis of the control pin is placed in the plane formed by the output axle and axis defined by the pins of the jaw of the output axle and intersects the geometrical center of the clutch. The output axle has projection provided with control pin. The axis of the control pin of the input shaft is placed in the plane defined by input axle and axis of rotation of the projection and intersects the geometrical center of the clutch. The control mechanism is made for permitting locking the clutch members.

EFFECT: prolonged service life.

71 cl, 103 dwg

Description

The present invention relates to couplings between shafts, and in particular to universal joints, and more particularly, to couplings having equal instantaneous angular velocities of the input shaft and output shaft or providing approximately such speeds.

Technical field

The problem of connecting two rotating shafts, working at an angle to each other, is solved by engineers at least since the beginning of the industrial revolution. The “Cardan Connection”, originally developed by Cardan in the 16th century, in principle is still used today, despite its inherent disadvantages, and this connection can be seen, for example, in almost every car with rear-wheel drive.

An inherent disadvantage of the construction of a simple universal joint is that at any angle between the input and output shafts exceeding 180 degrees, the angular velocity of the output shaft changes in a sinusoid relative to the angular velocity of the input shaft.

Usually, again using the rear-wheel drive as an example, two cardan joints are used connecting the input and output shafts with the intermediate shaft. By ensuring parallel alignment between the input and output shafts and by matching the coupling elements, equal angular velocities can be ensured, the oscillations of which are now limited by the intermediate shaft.

But the vibrational stresses arising from changes in the angular velocities of the input and output shafts with respect to the intermediate shaft must be absorbed in two cardan joints. Moreover, in many applications, and in particular in automobiles, it is impossible to maintain a strict geometric relationship between the input and output shafts, resulting in vibrations, mechanical stresses and loss of power transmission.

A partial solution to the problem of ensuring alignment of the input and output shafts was developed in the form of the so-called "Double cardan joint", which is often called the Joint of Equal Angular Velocities and which is a node of two cardan joints connected to a short intermediate shaft together with a centering mechanism that restricts both joints in a given geometric relationship with each other, resulting in an input and output shafts form equal angles with the intermediate shaft. The main disadvantages of this design are the transfer of axial and radial loads to the centering mechanism, and this circumstance accelerates wear and friction losses.

To ensure the transmission of equal angular velocities between the shafts, many other couplings have been developed. All of them, as a rule, have the disadvantage that they are approximate solutions to the problem of ensuring strict geometric constraints of the coupling of truly equal angular velocities; or according to these solutions, approximation to the desired geometry is achieved due to large friction losses leading to wear of the sliding components.

An object of the present invention is to eliminate or at least reduce one of the disadvantages mentioned above, or at least provide a useful alternative.

SUMMARY OF THE INVENTION

Accordingly, according to one broad embodiment of the present invention, an equal angular velocity coupling is provided in which conditions for equal instantaneous angular velocity transmission between the input and output shafts are provided by a control mechanism, wherein said coupling comprises:

(a) the axis of rotation of the input shaft,

(b) the axis of rotation of the output shaft,

(c) a regulatory mechanism

however, the specified regulatory mechanism is configured to limit at least parts of the specified connection to ensure equal angular velocity characteristics.

The present invention also provides, in general terms, an equal-angle clutch in which the angle between the input shaft and the output shaft is adjusted to change the volumetric characteristics of the hydraulic ram bias device.

The present invention also provides in general terms a double clutch of equal angular velocities, in which the conditions for equal instantaneous transmission of angular velocities between the input and output axes are provided by a control mechanism, wherein said clutch contains:

(a) input axis

(b) output axis

(c) the input end plug,

(d) the plug of the output end,

(e) regulatory mechanism.

The present invention also provides in general terms a constant velocity joint having an input shaft rotatably connected to the output shaft by a universal joint mechanism; wherein said hinge comprises a mechanical adjusting means which holds said universal hinge with respect to said input axis and said output axis, as a result of which, during operation, the characteristic of equal angular velocities is provided in a predetermined angle range between said input shaft and said output shaft .

The present invention also provides in general terms a constant velocity joint comprising a control mechanism based on spherical geometry with respect to a geometric center defined as the intersection of a specified input axis and a specified output axis.

The present invention also provides, in general terms, centering means for a constant velocity joint; wherein said centering means comprises hinges defined with respect to spherical triangular structures in order to limit at least parts of said hinge on a homokinetic plane defined with respect to the intersection point of said input axis with said output axis.

The present invention also provides in general terms a method for limiting a first input shaft with respect to a second output shaft of a hinge of equal angular velocities to achieve substantially equal angular velocities; according to the specified method, control means are used, centered and pivotally mounted on one or more axes passing through the center of the coupling, determined by the intersection of the input shaft with the axis of the output shaft.

Brief Description of the Drawings

Embodiments of the present invention will now be described with reference to the accompanying drawings, in which:

Figure 1 is a perspective view of a fully assembled clutch of equal angular velocities according to a first preferred embodiment with input and output shafts located on one straight line,

Figure 2 is a perspective view of the coupling shown in Figure 1, the input and output shafts have some angular displacement;

Figure 3 is a perspective view of the coupling shown in Figure 1, some components are removed for clarity,

Figure 4 is a perspective view depicted in figure 2 of a coupling illustrating the principle of operation of the regulatory mechanism,

Figure 5 is a perspective view of a fully assembled control mechanism of the coupling depicted in Figure 1;

6 is an orthogonal view of the regulatory mechanism according to the second preferred embodiment,

7 is an orthogonal view of the linkage according to the third preferred embodiment,

FIG. 8 is a perspective view of an assembled clutch of equal angular velocities according to a fourth preferred embodiment,

Fig.9 is a perspective view depicted in Fig.8 coupling without a Central pipe,

Figure 10 is a perspective view of the components of the coupling depicted in Figure 9,

11 is a perspective view of the design of the coupling, made with the possibility of its functioning as a hydraulic motor, in accordance with the fifth implementation,

Fig.12 is a side view of the coupling depicted in Fig.11,

Fig.13 is a perspective view of the main components that make up the clutch depicted in Fig.11,

Fig.14.1-14.20 - different types of implementation from the sixth to the tenth,

Fig.15.1-15.4 - different types of the eleventh implementation,

Fig.16.1-16.14 - different types of implementations from the twelfth to fifteenth,

Fig.17.1-17.9 are views of the sixteenth implementation,

Fig.18.1-18.13 - types of the seventeenth implementation,

Fig. 19.1 is a perspective view of an eighteenth implementation,

Fig.20.1-20.9 are views of the nineteenth implementation,

Fig.21.1-21.5 - types of twentieth implementation,

22.1-22.7 are views of a twenty-first implementation, and

23 is a graphical depiction of a homokinetic plane and corresponding axes for explaining a general description of some common features of many of the above-mentioned embodiments.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

The following is a description of various embodiments of the invention. Various options generally relate to systems having an input shaft mechanically coupled to the output shaft such that torque can be transmitted from the input shaft to the output shaft while providing substantially substantially equal angular velocity characteristics. The characteristic of equal angular velocities must be ensured despite changes in the angle between the input and output shafts.

In this description, the characteristic of "equal angular velocities" refers to the characteristic according to which the instantaneous angular velocity of the input shaft is consistent with the instantaneous angular velocity of the output shaft during a complete rotation of the shafts. It is understood that the characteristic of equal angular velocities is the goal of the design, and various implementations can provide this characteristic to a greater or lesser extent on the basis of parameters that may include mechanical and structural changes in the assembled assembly.

In cases where a change in the angle between the input and output shafts is allowed, these joints in this description are called universal joints of equal angular velocities.

The characteristic of equal angular velocities of the input and output shafts is generally ensured by means of a control system, which according to the embodiments of the present invention is made in mechanical form and is referred to in various implementations as a control fork, a control mechanism, a lever mechanism, a limiting means, an interconnecting connecting element, a centering mechanism and centering agent.

In all implementations, the intersection point of the axes of the input and output shafts is called the center of the coupling or the geometric center and, in some cases, is called the “contact points” of the axes of the two shafts.

The value of the center of the coupling or the geometric center is that in a significant number of implementations this point becomes the common point of the hinge of equal angular velocities through which the rotation axes of all the hinges forming part of the control system (and also the axes of the input and output shafts by definition) pass.

Also, in a significant number of implementations, the universal joint mechanism can be defined as a mechanism forming a part of the coupling and, in particular, including parts controlled by a regulating system to ensure equal angular velocity characteristics. In this specification, a universal joint in most cases means an inner substantially round fork mounted inside an outer also substantially round fork and rotatable relative to it. The forks of the universal joint mechanism are in turn connected, with the possibility of rotation, with the corresponding input and output shafts. The universal joint is at least partially limited in its movements by a regulating mechanism; in most cases in the form of an adjusting fork and corresponding adjusting components, which give the characteristic of equal angular velocities to the mutual movements of the input and output shafts.

The limiting action necessary to ensure equal angular velocity characteristics is described in most embodiments with respect to the center of the coupling or geometric center and also with respect to the “homokinetic plane” of the coupling.

As can be seen from Fig.23, in this description, the homokinetic plane is the plane 300, which is located on the bisector 301 of the angle 302 between the input axis 303 and the output axis 304 of the illustrated coupling 305 of equal angular velocities. In particular, the homokinetic plane 300 is located at right angles to the plane defined by the input and output axes 303, 304. In the case of FIG. 23: if the input axis 303 and output axis 304 are in the page plane, then the homokinetic plane 300 will be located at right angles to the page.

In its particular views, the regulatory system is more clearly defined relative to the additional angle 306, which is formed, in this case, between the output axis 304 and the continuation of the input axis 303 through the center of the coupling or geometric center 307. From a mathematical point of view: the additional angle 306 is 180 ^° , minus the angle 302 between the input and output shafts.

The bisector 308 of the additional angle is the bisector of the additional angle 306 and passes through the center 307 and, by definition, is located at right angles to the homokinetic plane 300 and at right angles to the bisector 301. In Fig.23, the bisector 308 of the additional angle is designated as CC and corresponds to the C axis figure 4, described with reference to the first implementation.

A feature of many implementations of the present invention is that the regulatory system in the form of a regulating mechanism is centered on the axis 308 and acts symmetrically around this axis in all types of work. In separate implementations, the terms “spherical triangles” and “spherical geometry” are used in the context of linkages and axles for the control system 309, and they all rotate around the axes that pass through the center 307.

In some of its implementations, the entire regulatory system that provides a characteristic of equal angular velocities (or approximation, to one degree or another, of this characteristic) can be performed using hinges that rotate around these axes, for example, with ball or roller bearings, i.e. , t.s., using bearing surfaces for which load-bearing sliding surfaces are not required.

1. The first embodiment

A first preferred embodiment of a constant-angle coupling is described below with reference to FIGS. 1-5.

Figures 1 and 2 show a clutch 10 of equal angular velocities, in which the input shaft 11 is connected to the output shaft 12. The input shaft 11 is rigidly connected to the protrusion 13 of the input shaft. The output shaft 12 is rigidly connected to the plug 14 of the output shaft having pins 15.

The output shaft plug 14 is pivotally connected to the external plug 16 by means of the articulated shafts 17 and bearings (not visible) in the pins 18 of the external plug.

The protrusion 13 of the input shaft is made to rotate around the shaft 19 passing through the pins 20 of the inner fork.

The adjusting fork 21 is pivotally connected to the outer fork 16 and to the inner fork 22 by means of shafts 23 in the pins 24 of the adjusting fork and bearings (not visible) in the pins 25 of the outer fork and the pins 26 of the inner fork. The Y-Y axis defined by the adjusting yoke 21 and the pins of the outer yoke 16 and the inner yoke 22 is the main axis of the coupling 10.

As can be seen from Figs. 1 and 2, all hinge axes together with the axis 27 of the input shaft and the axis 28 of the output shaft intersect in the center 29 of the coupling.

As can be seen from Figure 3: the inner fork 22 and the outer fork 16 are not shown for clarity to show the first scissor mechanism 30, consisting of the first scissor link 31 and the first scissor link 32 and 33. Figure 3 also shows: a continuation of 34 input shaft and control pin 35 of the input shaft. The axis of the control pin 35 of the input shaft intersects the center 29 of the coupling and is located in a plane redistributed by the axis 27 of the input shaft and the axis 36 of the protrusion of the input shaft.

Turning to Figure 4, on which the input shaft 11 is not shown for clarity: the following are the geometric characteristics of the first half of the scissor control mechanism 30.

The output shaft plug 14 has an output shaft adjusting pin 37. The axis A of the adjusting pin 37 is in a plane defined by the axis 28 of the output shaft and the axis XX passing through the centers of the pins 15 of the output shaft fork and intersecting the center of the coupling 29.

The pivot pin 38 of the adjusting fork is rigidly connected in the center of the adjusting fork 21 so that its axis C intersects the center 29 of the coupling. The first scissor link 31 rotates around the pivot pin 38 of the adjusting fork and has at its outer ends pivot shafts 39, the axes of which also intersect in the center 29 of the coupling. The first scissor wings 32 and 33 are pivotally connected to the articulated shafts 39 of the first scissor link 31. The outer end of the first scissor link 32 is pivotally connected to the adjustment pin 35 of the input shaft (see FIG. 3), and the outer end of the first scissor link 33 is pivotally connected to the control pin 37 of the output shaft.

Since all the rotation axes of the first scissor mechanism 30 intersect in the center of the clutch 29, it is therefore clear that the rotational displacement of the input shaft adjusting pin 35 from the plane defined by the output shaft 28 and the axis XX will cause the control fork 21 to rotate about the axis XX. If the center-to-center distances of the articulated shafts 39 from the articulated pin 38 of the adjusting fork and the articulated centers of the wings 32 and 33 are equal, it follows that the angular displacement of the adjusting fork 21 will be half the angular displacement of the adjusting pin 35 of the input shaft.

This angular ratio is true if the axes A, B and C are limited by their presence in a common plane passing through the center 29 of the coupling. As can be seen from Figure 5, the scissor adjusting mechanism actually contains double symmetric scissor links and linkage mechanisms that ensure compliance with this condition. We can assume that this mechanism is located on several concentric spheres in such a way that the nominal points of the hinged intersection of the scissor links and the lever mechanisms are located on the tops of the spherical triangles and are limited so that the corresponding angles in the triangles remain equal when the orientation of the scissor mechanism changes due to the action of two adjusting pins.

For clarity: the examples below relate to only one half of the double scissor control mechanism, but it is understood that the movements mentioned here are governed by the full mechanism.

Turning to FIGS. 3 and 4, suppose that the axis 28 of the output shaft 12 is fixed in an orientation that is in a horizontal plane along the x-axis. Now, if the input shaft 11 rotates downward only around the axis X-X, i.e. the axis 27 of the input shaft 11 continues to be in the same vertical plane as the plane passing through the axis of the output shaft 12 and the YY axis, then the end of the axis B in its articulation with the first scissor link 32 will follow a path upward on the radius B of the sphere with the center In the center there are 29 couplings. This path is a small circle at a radius B of the sphere, and it is in a vertical plane parallel to the vertical plane passing through the axis of the input shaft 11 and output shaft 12. This shift of the link 32 causes the primary scissor link 31 to rotate around the hinge pin attached to the adjusting fork 21. 38 adjusting forks. But the scissor link 31 is limited by its connection to the linkage 33 and the adjusting pin 37 of the output shaft. If the angle between the plane defined by the x-axis and the rotated axis b and the horizontal plane passing through x-x is α, then the scissor link 31 and the wings 32 and 33 will rotate the c-axis into the plane through the x-axis at an angle α / 2. Now the angle between the axis 27 of the input shaft and the horizontal plane is also α, and it follows that the Y-Y axis bisects the angle (180-α) between the axis 27 of the input shaft and the axis 28 of the output shaft.

The Y-Y axis is now in a plane bisecting the obtuse angle between the axis 27 of the input shaft and the axis 28 of the output shaft and perpendicular to the plane defined by axes 27 and 28. This plane is the so-called homokinetic plane, and the Y-Y axis can be defined as the axis of symmetry of the coupling.

Obviously, the Y-Y axis satisfies this relationship with axes 27 and 28, i.e. it is in the homokinetic plane, for any relative angle between the input shaft 11 and the output shaft 12 - within the physical limitations of the coupling 10.

This satisfies the theoretical condition for the coupling of equal angular velocities, according to which the axes of the input and output shafts meet at some point, and the contact points between the two shafts are on the axis of symmetry in the homokinetic plane.

All relative movements of the components inside the coupling are rotational and implemented by roller bearings, thereby largely eliminating the loss of torque due to friction.

2. The second embodiment

According to a second preferred embodiment: the described scissor control mechanism can be replaced by gear mechanism 40 - Fig.6.

As can be seen from Figs. 3, 4 and 6, the center 45 of the main link 41 and the central gear 44 are rotatably mounted around the articulated pin 38 of the adjusting fork. Lever links 42 and 43 have engaging gear segments 48 and 49, respectively, and have hinge centers 46 and 47 at their outer ends. Lever links 42 and 43 are pivotally attached to main link 41 on shafts 50 and 51.

All rotational and articulated axes of the adjusting mechanism 40 are radial with respect to the geometric center 29 of the clutch 10 (see Figure 4). Lever links 42 and 43 have the same length and tighten equal angles with the main link 41. Therefore, the hinge centers 46 and 47 and the center of the central gear 44 are limited to their location on the arc of a large circle of a sphere whose center is located in the geometric center 29; and the center of the gear 44 is always at the midpoint of this arc of the large circle, regardless of the change in the length of this arc.

Assembled, the hinge 46 of the adjusting mechanism 40 is connected to the adjusting pin 35 of the input shaft, and the hinge 47 is connected to the adjusting pin 37 of the output shaft.

Obviously, any change in the angle between the input shaft 11 and the output shaft 12 will cause displacements of the lever links 42 and 43. For example, if we assume that the hinge center 47 of the lever link 43 remains stationary, then any displacement caused in the hinge center 46 by the adjusting pin 35 of the input shaft, will cause half of this displacement in the center of the gear 44. Therefore, the axis passing through the pivot pin 38 of the adjusting fork will constantly divide in half the additional angle between the input shaft 11 and the output shaft 12 and remain in the plane and determined by the axes of the shafts 11 and 12. From this, therefore, it follows that the Y-Y axis will be limited by its location in the above homokinetic plane.

3. Third Embodiment

According to a third preferred embodiment of FIG. 7, a lever system 60 is proposed that replaces the inner fork 26 and the outer fork 27 of the clutch 10 shown in FIGS. 1 and 2. The shaft 61 is rigidly connected at its outer ends to the lever elements 62 and 63, each of which at its outer end has a protrusion of 64 and 65, respectively. On the protrusion 64 and the protrusion 65 are mounted adjusting axle shafts 66 and 67, respectively. The lever system 60 also has lever links 68 and 69, the ends 70 and 71 of each of which are pivotally connected to the adjusting axle shafts 66 and 67, respectively. The outer ends 70 and 71 of the link arms 68 and 69 have trunnion shafts 74 and 75 of the output shaft forks.

The lever elements 62 and 63 and the lever links 68 and 69 are located in spherical shells, the center of which is at the point 80 of the intersection of the axis of the shaft 61 and the Y-Y axis, and all rotation axes of the lever system 60 intersect at the point 80 of the intersection of the axes.

On the axes of the assembly, the intersection point 80 coincides with the geometric center 29 of the coupling 10 according to FIG.

In this embodiment, the protrusion 13 of the input shaft on the input shaft 11 according to FIG. 1 rotates around the shaft 61 of the lever system 60 shown in FIG. 7; and the pins 15 of the output shaft forks on the output shaft plug 14 are connected to the trunnion shafts 74 and 75. The trunnion pins 24 on the adjusting fork 21 are connected to the trunnion adjusting shafts 74 and 75.

As in the previous embodiment, the axis of the Y-Y control fork is limited by its constant presence in the homokinetic plane through the use of either the scissor control mechanism or the gear control mechanism described above.

An advantage of arranging the Y-Y axis and shaft 61 at a preferred angle of 45 degrees in this embodiment is that the space thus created provides an increased degree of freedom of movement of the various rotation elements and control mechanisms described above.

4. Fourth Embodiment

In a fourth preferred embodiment illustrated in FIG. 7, an equal-velocity double coupling 100 is provided that includes an input shaft 111 and an output shaft 112. Each of the shafts 111 and 112 has forks 113 and 114, respectively, in which the shafts 111 and 112 pivotally connected around axes XX and X'-X '. The forks 113 and 114 are in turn pivotally connected to the connecting pipe 115, and each of the forks 113 and 114 is rotatable around the axes Y-Y and Y'-Y ', respectively.

As can be seen from Figs. 8 and 9, the input shaft 111 and the output shaft 112 have the same design, each of which has corresponding shaft extensions 116 and 117, respectively; each extension of the shaft has adjusting pins 118 and 119, respectively. The axes of the adjusting pins 118 and 119 are located in a plane bounded by the axis of the shaft and the axes of rotation X-X and X'-X 'of the shaft of the shafts 111 and 112, and intersect with the intersection of these axes.

In the center of the connecting pipe 115 (this pipe is not shown in FIGS. 8 and 9), a control unit 120 is installed comprising upper and lower transmission units 121 and 122, respectively. Blocks 121 and 122 are hinged around a pivot shaft 129 of the control block located on the central axis Z-Z of the connecting pipe 115. The shaft 129 is mounted in a fixed hinge (not shown for clarity) that is attached to the inner wall of the connecting pipe 115.

As can be seen from Fig. 8, all rotation axes at the end of the input shaft of the coupling 100 are radial with respect to the intersection of the axes X-X and Y-Y; likewise, all rotation axes at the output end of the coupling 100 are radial with respect to the intersection of the axes X'-X 'and Y'-Y'.

Any rotation within the physical limits of the input shaft clutch 111 around its rotation axes XX and YY will cause the connected linkage mechanisms 125 and 126 to shift by the control shaft 118, which in turn will cause the transmission units 121 and 122 to rotate around the pivot shaft 129. The corresponding linkage mechanisms 125 and 126 at the output end of the control unit 120 forcibly repeat the offset created at the input end, transferring the offset to the control shaft 119 connected by a linkage, thereby bringing the output shaft 112 to vuyuschie rotation about axes X'-X 'and Y'-Y'.

The angular displacements of the input shaft 111 and 112 are symmetrical around a plane perpendicular to the plane defined by the axes of the shafts 111 and 112 and passing through the center of the control unit 120. This plane itself is located at the intersection of the axes of the shafts 111 and 112, halving the angle between them and having an axis of symmetry . This plane is therefore a homokinetic plane, and the conditions of equal angular velocities of the input and output shafts are satisfied.

All relative movements between the coupling components in this embodiment are rotational and implemented by roller bearings, largely eliminating friction torque losses.

5. The fifth embodiment

According to a fifth embodiment, an equal angular velocity coupling is provided in which the angle between the input and output shafts is provided at a certain desired value by means of a regulating mechanism in order to change the volume displacement of the inclined disk acting as a hydraulic pump or motor. In this preferred embodiment, the reciprocating pump or motor elements form part of the coupling structure.

In this fifth preferred embodiment, the equal velocity coupling comprises a hydraulic biasing device in the form of an inclined disk.

11 shows an equal-velocity coupling 200 having an input shaft 211 and an output shaft 212. It will be apparent to those skilled in the art that the terms “input shaft” and “output shaft” in this embodiment can designate each of these elements depending from the specific application of the coupling.

The axis of each of the shafts 211 and 212 intersects a point 220 coinciding with the intersection of the axes X-X and Y-Y in FIG. 11; point 220 defines the geometric center of the coupling. The angle between the axes of the shafts 111 and 112 can be changed as desired within the physical limits of the coupling using an appropriate control mechanism. The regulating mechanism is also configured to provide the angle of the adjusting fork 213 in a fixed relationship with this angle defined between the shafts 211 and 212. This relationship is shown in Fig. 12, where if the additional angle between the shafts 211 and 212 is α, then the axis of rotation of the regulating fork 113 bisects the angle α. Therefore, the Y-Y axis is limited by rotation in the homokinetic plane, while fulfilling the conditions of the coupling of equal angular velocities.

Fig. 13 shows clutch elements that are different from the previous ones, including the adjusting yoke 213, the inner yoke 214, and the outer yoke 215. The input shaft 211 is rigidly connected to the tilt disk 216 having the taper shafts 217 of the tilt disk.

Assembly: the axle shafts 217 of the inclined disk are pivotally connected in the axles 218 of the inner fork on the inner fork 214. The inner fork 214 is articulated by its trunnion shafts 219 of the inner fork with the trunnions 221 of the outer fork on the outer fork 215. In turn, the outer fork 215 using its the trunnion shafts 222 of the outer fork are pivotally mounted in the trunnions 223 of the output shaft fork on the output shaft fork 224. The adjusting fork 213 (shown from its end) is pivotally connected using the trunnions 225 of the adjusting fork with the extended trunnion shafts 219 of the inner fork on the inner fork 214.

The output shaft 212 of the coupling 200 also has a cylindrical block 226. The cylindrical block 226 has a radial set of cylinders 227. A piston 228 is included in each of the cylinders 227, having a seal 229 at its compressive end and having a ball socket 230 at its opposite ends. Each piston 228 by its ball socket 230 is connected to the first end 231 of the connecting rod 232. The second end 233 of the connecting rod 232 is connected to the ball socket 234 of the inclined disk 216.

Assembled: when the output shaft 211 and the output shaft 212 are aligned, the surface of the inclined disk 216 is oriented perpendicular to the axis of the output shaft 212 and therefore to the axes of the cylinders 227. In this position, when the input shaft 211 and the output shaft 212 rotate around their common axis, the pistons 228 remain motionless in cylinders 227. If an angle α is created between the input shaft 211 and the output shaft 212 by an adjusting mechanism, then reciprocating axial movement is determined in each of the cylinders 227 by means of pistons 228 for each rotation of the coupling 200.

The volumetric displacements due to this reciprocating movement of the pistons 228 in the cylinders 227 during rotation of the coupling 200 increase with increasing angle α.

Possible advantages of this configuration:

A. Previously, equal-velocity joints of the Rzeppa type were used, in which the inner member of the joint of equal angular velocities was kept coaxially with the cylindrical body and the outer member of the joint of equal angular velocities, thereby forming an inclined disk. In this design, the entire torque of the assembly was transmitted through a constant velocity joint and torque transmission elements with a radius smaller than the inclined disk, as a result of which the torque transmission means were subjected to strong loads.

B. According to the proposed design, the torque can be transmitted to or from the inclined disk, in accordance with one of two methods, both of which exceed the prior art:

1. Torque transmitted by a shaft connected to the cylindrical body - In this case, the torque transmitting means is located at a larger radius than the inclined disk, as a result of which the torque transmitting elements are subject to lower torque loads than at a known level technicians.

2. Torque transmitted by the shaft connected to the inclined disk - In this case, the elements transmitting the torque of the hinge of equal angular speeds are not exposed to the working torque of the device; the only load transmitted through the coupling is the torque required to rotate the cylindrical body.

6. The sixth embodiment

This embodiment according to FIG. 14 provides a hinge of a type of modified Hooke hinge, in which the axis A5 is continuously on the homokinetic plane due to the action of the system of gears and levers, made in such a way that the frequency and angle of rotation of the first drive gear are always the same with frequency and angle rotation of the second drive gear by providing an angle of inclination between the axis A3 and the axis of the first drive gear equal to the angle of inclination between the axis A4 and the axis of the second drive gear Olesa. Or only a leverage system is provided in which the levers perform functions similar to those of said gears.

The following is a description of preferred methods for implementing this implementation. In each preferred method, two halves of the modified Hook joint of FIG. 14.6 are provided. It should be noted that the hinge shown in Fig. 14.6 is similar to the hinge according to Fig. 14.1, with the exception that the crosspiece 6 shown in Fig. 14.1 is not shown, and the round element 7 is positioned on the fork 4 in such a way that it can rotate freely around the axis A4. The size of the annular element 7 and the plug 4 is such that the assembly is able to fit snugly inside the annular element 5, which is attached to the plug 3. The components shown in FIG. 14.6 are common to all preferred embodiments of the present invention.

Fig. 14.7 shows a cross-piece, two shoulders of the same length which are longer than the other two shoulders, as a result of which the longer shoulders have a combined length of at least equal to the outer diameter of the larger annular element 5; and the two shorter arms have a combined length that is less than the inner diameter of the annular element 7, as a result of which, as an assembly, the longer arms connect the two halves of the hinge shown in Fig. 14.6 on axis A5; and the spider element is made with the possibility of free rotation on the axis A5 inside the annular element 7.

Fig. 14.8 illustrates the cross member shown in Fig. 14.7, with four engaged bevel gears, one of which is positioned on each of the shoulders of said cross member and is configured to rotate freely thereon. Two gears on the shorter shoulders of the spider element have a lever rigidly attached to them - not shown.

Fig. 14.9 shows one of the gears with a rigidly attached lever arm. The arm of the lever has a ball 25 at the end. In the parameters mentioned below, neither the length of the arm of the lever nor its displacement along the axis of the gear are significant. One of these gears is positioned on each of the shorter arms of the spider element, as a result of which the arm of the arm passes on opposite sides of the spider element. The lever arm attached to one of the gears should be half a tooth different from the alignment of the other arm arm and the gear, as a result of which the axis of the two longer arms of the cross piece will halve the angle between the two arms when they rotate in mesh with the other two gears.

Fig. 14.10 shows a fork with a ball element rigidly attached to the center of the inner surface of the fork; however, both forks have this ball attached to them.

Fig. 11.11 shows a connecting element, which is a rod with a ball socket at both ends and configured to connect, at one end, to the ball at the other end of the lever shown in Fig. 14.9, and, at the other end, to the ball in the center of the fork element shown on Fig.10.10.

The components mentioned above and shown in FIGS. 14.6, 7, 8, 9, 10 and 11 are assembled in such a way that the longer shoulders of the spider element pass through the holes in the ring elements 5 and 7 so that the ring elements are positioned relative to each other by longer shoulders of the spider element and have the possibility of free rotation around axis A5; and the spider element also has the possibility of free rotation on the axis A5. The position of the various components in assembled form is such that when the axes of the shaft 1 and the shaft 2 are located on the same straight line, the component parts of the assembly have a relative position according to Fig.14.12; and according to this drawing, the axes A3 and A4 and the axles of the gears on the shorter shoulders of the spider element are all coaxial, and the axis A5 is perpendicular to the plane of the axes A3, A4, A1 and A2.

The hinge shown in FIG. 14.12 is specifically shown with a plug 3 substantially larger than a plug 4, to illustrate the relationship between the various components. The lever element 13 (as shown in Fig. 14.11) is connected at one end to a ball at the end of a lever 11 and at the other end to a ball that is attached to the center of the inner surface of the yoke 3; and a similar lever element 14 is likewise connected in the other half of the hinge, and the length of each lever element and the length of the two lever arms 11 and 12 are determined as follows. An important circumstance is that the triangle formed between the axis point of the arm shoulder 11 of the lever and the center of the ball, which is attached to the center of the fork 3, and the center of the ball at the end of the lever 11, has the same internal angles as the triangle, similarly formed in another half of the hinge; those. the two triangles thus formed should be the same in this implementation - except for size.

If the center lines of the shoulders of the lever extend to the center of the spider element (or disk element described below), then the internal angles of the triangle remain the same all the time as the hinge rotates. But if the central lines of the shoulders of the lever extend to a point that is offset from the center of the spider element, then the internal angles of the triangle constantly change as the hinge rotates. If the center lines of the arm shoulders are offset from the center of the spider element, it is essential that both arms of the arm are offset to the extent that the same triangles form on both sides of the hinge.

Obviously, during the operation of the hinge described above, both of these triangles will swing effectively with respect to their respective bases and also swing around the point of the axis of the arms of the levers, resulting in: when the axes A3 and A4 are coaxial, then the axes of the two levers will also be coaxial with the axes A3 and A4; and when the axes A3 and A4 are not coaxial, the axis of the arms of the lever and the corresponding gears will always halve the angle between the axes A3 and A4 during their rotation around the axis A5, resulting in angles between the axis of the drive arms 11 and 12 and their respective the gears will always be equally inclined to the axes A3 and A4, respectively, and therefore, when the fork 3 rotates around the axis A3 and when the fork 4 rotates around the A4 axis, the levers 11 and 12 and their attached gears will rotate in the opposite direction around their axes from the other frequency and another rotation angle as compared with the rotation of plugs around the axes A3 and A4. But these levers and corresponding gears will rotate in the opposite direction with equal frequency and equal rotation angle with respect to each other, as a result of which the axis AS will be continuously on the homokinetic plane, and the hinge will act as a hinge of equal angular velocities in the sense that the angular velocity of the shaft 1 and shaft 2 will always be equal regardless of the angle of inclination of these shafts relative to each other, and will always be the same, even if the angle of inclination during operation will change.

7. Seventh embodiment

In accordance with yet another embodiment, the cross member according to FIG. 14 and the four bevel gears and corresponding levers are replaced by an element configured to hold two engaging gears in such a position that when the axles of the shaft 1 and the shaft 2 are on a straight line, then the corresponding axes are perpendicular to the axes of both gears, and axis A5 will be perpendicular to the plane between the axes of the two gears and central to that plane. The lever arm is rigidly attached to each gear and the ball is located at the end of each lever arm. Turning to FIG. 14.13: an element configured to hold two gears is a disk-shaped element, the diameter of which will fit inside ring 7. The disk element has two tides that are used to position and provide an axis for rings 5 and 7. The disk element has a rectangular hole to allow two gears to engage through the disk. The disk element is made with the possibility of free rotation on the axis A5. The disk element has two protrusions on each surface, and the axis for each of the gears is held by these protrusions. Fig.14.14 shows a side projection of a disk element with two gears mounted. The shoulders of the lever are partially shown, one of which is rigidly attached to each of the gears. The action of this disk-shaped element and the corresponding gears and levers is identical to the action described in detail above with respect to the spider element and four bevel gears, with the same comments.

8. The eighth embodiment

Another option, shown in Fig. 14, is a system of levers pivotally mounted on each of the four arms of the cross member described above, the action of which is similar to the assembly of four gears of mutual engagement.

9. The ninth embodiment

Another option, shown in Fig. 14 and which can be used either with a spider element and four bevel gears, or with a disk-shaped element and two gears, or only with a lever system, is made as follows. The ball element attached to the center of the inner surface of each fork is absent here, and each fork has an arcuate groove on the inner surface of the fork, as a result of which in the assembled position the ball at the end of the arms of the levers is located in this groove, and therefore during the operation of the hinge and when the angle between the axes A3 and A4 changes, then the ball on each lever as a result of this moves in the groove. In this design, the triangle mentioned above is missing, which provides the correct relationship between the axles of the drive gears and the axes A3 and A4, and therefore, to ensure the same inclination between the axles of the gears and the levers and axes of their respective drive forks, another means must be used. One such method is to use the scissor action of rings 5 and 7, which occurs when the angle between the axes A3 and A4 changes. One way of applying this scissor action is that the rod is rigidly attached to one of the longer arms of the cross member, or, as the case may be, to one of the tides of the disk-shaped element in such a way that it is oriented perpendicular to the plane of the four arms of the cross an element or surface of a disk-shaped element, as the case may be; two arms of the lever are used, one of which, with the possibility of rotation, is attached to each of the ring elements 5 and 7 at one end, and the other end is attached to the element that connects both shoulders of the lever at their other end using an element that slides according to the pin attached to the shoulder of the spider element or the disk element, depending on the particular case, and therefore the rod constantly bisects the angle between the ring elements 5 and 7. Fig.15.15 illustrates this particular scissor mechanism.

It should be noted that, within the scope of the present invention, various other configurations of gears and levers will also provide a relationship between the various components mentioned herein.

It should also be noted that, within the scope of the present invention, it is also possible to implement only a leverage instead of gears and levers of systems to provide the relationships described herein.

With regard to the sixth to ninth embodiments, it has been found that it is advisable to provide a separate means that ensures that the angle between the axes A3 and A4 is divided in half by the shorter shoulders of the spider element whenever they are not coaxial; and with respect to the seventh embodiment, it is also advisable to provide a separate means which will ensure that the angle element between the axes A3 and A4, represented in FIG. 14.13, is divided in half by the plane whenever they are not coaxial. In both cases, this centering device can use a scissor action between elements 5 and 7, as described above in relation to the eighth implementation.

10. The tenth embodiment

As can be seen from Fig. 14, a special and novelty means of providing constraints is proposed for forming a hinge of equal angular velocities by limiting the axis AS on the homokinetic plane.

This novelty means provides elements that describe two identical spherical triangles in each half of the hinge described below.

Here, the elements of the universal universal joints of equal angular velocities described above are used, but in this novel embodiment, with reference to FIG. elements 5 and 7 and form the axis A5. The disk-shaped element has an opening 17 in the center of the disk. When the two halves of the hinge shown in Fig. 14.6 are assembled using the disc-shaped element shown in Fig. 14.16, then all the axes A1, A2, A3, A4 and A5 intersect at some point. In this description, the point at which all of the indicated axes intersect is called the "geometric center."

As can be seen from Fig.17.17, also provided is a two-pointed cranked element with a connecting rod journal 18 at each end; in this case, the connecting rod journal has such an angle that, when assembled, the axis A6 of each connecting rod journal is located at a radius that intersects the geometric center.

Assembled, with reference to Fig.14.18: the shaft of the cranked element passes through the hole in the disk-shaped element shown in Fig.14.16, and therefore one connecting rod journal is located on one side of the specified disk-shaped element.

Fig.14.19 shows two hinge forks: a pin 19 is attached to the inner arc or surface of the fork elements 3, and another pin 20 is similarly attached to the inner side or to the arc of the fork 4, as a result of which the axis of each of these pins is also located on a radius that crosses the geometric center. The pins are arranged so that they are on the same side of the hinge, and not diagonally opposite each other.

As can be seen from Fig.14.20, another element 21 is proposed, which has an opening 22 at one end, and thus the element 21 can be positioned on the pin 19; and has another hole 23, whereby the other end of the element 21 can be positioned on the first pin 18; another similar element is positioned at the other end of the pin 20 and at the other end of the second pin 18. The length, or more precisely, the angle between the holes at both ends of the element 21 is set as follows.

In the assembled state of the hinge, and when the hinge is in a position in which the axes A1 and A2 are exposed are on the same straight line and the axes A3 and A4 are aligned, the axis of the connecting rods 18 is on the plane of the axes A5, A1 and A2, and each of the axes of the pins 19 and 20 is on the plane of the axis A3 and A4, and A1 and A2. The angle between the holes at both ends of the element 21 has a value at which the relationships indicated in this paragraph are maintained and valid.

When using the new limiting means described here, it is obvious that the spherical triangle is described by arcs of a large circle between, firstly, the axis of the pin 19 and the axis A1, and secondly, the axis A1 and the axis of the first connecting rod journal, and thirdly, the axis of the first connecting rod pin and pin axis 19. A similar spherical triangle is described between the respective components on the other side of the hinge. It will be obvious that when the assembled hinge is rotated at any time when the shafts 1 and 2 are inclined to each other, a certain spherical triangle is formed at each rotation point and with each angle of inclination, and this triangle is formed on each half of the hinge, as a result of which the crankshaft axis the element is equally inclined, firstly, to the axis A1 and, secondly, to the axis A2, as a result of which the plane of the disk-shaped element 15 and, therefore, the axis A5 are limited by their constant presence on the homokinetic plane of the hinge.

11. Eleventh embodiment

This embodiment according to FIG. 15 provides, firstly, the linkage mechanism according to FIG. 15.1, described below, and, secondly, the universal equal velocity joint described below using the linkage mechanism described below.

As can be seen from Fig. 15.1, the composition of the lever mechanism according to this embodiment is as follows: Elements 1 and 2 are two similar elements, each of which has a hole made at each end, while the axes of these holes intersect at some point. Elements 3 and 4 are also two similar elements and are also similar to elements 1 and 2, with the exception that elements 3 and 4 have holes formed at each end with a larger radius than elements 1 and 2. Elements 1 and 2 are connected to each other with another shaft 5. The positioning pin 6 connects the elements 1 and 3, as a result of which the elements 1 and 3 can rotate relative to each other around the axis A1. These elements are assembled in such a way that the perpendicular axis of the shaft 5 intersects the axis A1. Obviously, in this assembly the elements 1 and 2 connected together by the shaft 5 will rotate synchronously around the axis A1, as a result of which the perpendicular axis of the shaft 5 will rotate around the axis A1, and similarly, if the elements 3 and 4 have a fixed relationship with each other another, they will also rotate synchronously around the axis A1, as a result of which their axis, axis A2, will also rotate around the axis A1, and the axes A1, A2 and the perpendicular axis of the shaft 5 will always intersect at the geometric center of the lever mechanism described above.

One of the implementations using the linkage mechanism described above is the universal joint of equal angular velocities described below. Fig. 15.2 shows a shaft with a hole made at one end, as a result of which this shaft 5 can pass through the specified hole. Fig. 15.3 shows a plug commonly used in universal joints such as the conventional Hook joint (also known as the universal joint). The holes 13 and 14 are made in the shoulders of the fork so that the fork can be positioned relative to the described lever mechanism using the positioning pins 8 and 9 in the holes 13 and 14, respectively. The shaft 10 is mounted on the shaft 5 so that the axis A3, being the perpendicular axis of the shaft 10, intersects the axis A1 and A2 in the geometric center of the linkage. It should also be noted that in the node described above, the A4 axis, which is the perpendicular axis of the fork element 12, also intersects the axes A1 and A2 in the geometric center of the linkage. Obviously, in this node, whenever the axes A3 and A4 are not on the same straight line or aligned, the rotation of the shaft 10 and the yoke 12 around the axis A3 and A4, respectively, will cause the synchronous rotation of the elements 1 and 2 around the axis A1, and when the elements 3 and 4 will also rotate synchronously around the axis A1 in the opposite direction to the rotation of the elements 1 and 2. In this node: whenever the axes A3 and A4 are not on the same straight line or coaxial, and when the axis A2 and the perpendicular axis of the shaft 5 will not be on one straight line or coaxial, then the plane of rotation of the axis A1 will always be divided by Lam angle between the plane of rotation of the axis A2 and the perpendicular axis of the shaft 5; and the plane of rotation of the axis A1 is perpendicular to the plane between the axis A3 and A4, and therefore a hinge of equal angular velocities is always provided.

Fig. 15.4 shows a linkage mechanism consisting of a shaft 10 and a fork 12 with the formation of the hinge of equal angular velocities described above. According to this drawing, axes A3 and A4 are on the same straight line, and axis A2 and the perpendicular axis of the shaft 5 are also on the same straight line or in alignment. In this embodiment, the axis A2 and the perpendicular axis of the shaft 5 are on the plane of the paper, while the axis A1 enters the page from the bottom with a slope equal to the angle between the holes in the elements 1, 2, 3 and 4. In this embodiment, it is obvious that if the shaft 10 rotates counterclockwise on the paper plane, and if the yoke 12 rotates clockwise on the paper plane, then the shaft 5 will rotate around the axis A1, and the axis A2 will also rotate around the axis A1, but in the opposite direction.

A link mechanism with three intersecting axes is also shown, of which two rotate relative to the third. Also shown is a constant velocity joint using said linkage; wherein the universal joint of equal angular velocities has at least three axes, two of which rotate around the third. This implementation uses the same regulatory system containing the adjusting fork and the adjusting pins of the first implementation, to limit the axis A1 on the homokinetic plane.

12. Twelfth embodiment

In this embodiment, the term "spherical geometry" is explained below and with reference to Fig.16. Fig. 16.1 shows a sphere with a spherical triangle and the corresponding trihedron on it. Referring to Fig. 16.1: the axes 2 and 3 are the diameters of the sphere 1. The sides AD, AO, and AZ of the spherical triangle are cutoff arcs of a large circle of angles D, Z, and O of the trihedron, respectively; and angles A, B, and C are the internal angles of the spherical triangle AD, AO, AZ. Turning to FIG. 16.1: it is obvious that if a spherical triangle AD, AO, AZ is rotated around either radius 4 or radius 5 or diameter 3, then the rotating radii describe the cones in the sphere. As can be seen from Figure 1, it is also obvious that if you change any flat angle of the polyhedral angle D, O or Z, then its cut off arc of the big circle also changes, as does the spherical triangle AD, AO, AZ. Obviously, the rules of spherical geometry apply here.

In the context of the foregoing, the term "spherical geometry" in this implementation means the movement of the components of the hinge in such a way that they describe or form the forms or functions of spherical geometry.

The main objective of this implementation is to provide, firstly, the basis of a universal joint of equal angular velocities with elements mounted between the first shaft of rotation and the second shaft of rotation; in this case, each moving or acting element among the indicated interinstallation elements describes the forms or functions of spherical geometry; and the second objective of the present invention is to provide several specific and novelty variants of a universal joint of equal angular velocities based on spherical geometry.

From the description given below it obviously follows that the execution of hinges of equal angular velocities based on spherical geometry 15, and not on another geometry, provides hinges of reduced size and also hinges that do not have sliding components.

The sixth embodiment described above provided a means of forming the same spherical triangles in each half of the hinge, so that there was a means to ensure that the interconnect element was located on the homokinetic plane of the hinge described there. Said embodiment described a centering means consisting of a shaft having a connecting rod journal at both ends, and also provided for two forks, each of which has a pin mounted on the inner surface; moreover, the continued axis of these connecting rod necks and these pins cut off the geometric center of the specified hinge. For clarity: the hinge according to the sixth embodiment consisted of a modified Hooke hinge having two halves according to FIG. 16.2. The interconnect element is shown in Fig. 16.3 and consists of a disk-shaped element 15 with a hole 17 in the center and two tides 16 attached to it, which are used to connect the two halves of the hinge according to Fig. 16.2 by positioning these tides in the holes 8, 9, 10 and 11 according to FIG. 16.2. Fig. 16.5 shows a shaft 12 with shoulders 13 and connecting rods 18 mounted at both ends, oriented in such a way that the extended axis A6, in the assembled assembly of said connecting rods, intersects the geometric center of the hinge. Fig. 16.4 shows a shaft 12 assembled with a disk-shaped member 15. Fig. 16.6 shows a plug 3 and a plug 4, each of which has a pin 19 and 20 protruding from the inner surface of the forks; however, these pins are oriented so that the continued axis of each pin intersects the geometric center of the hinge in the assembled node. These forks are assembled so that the pins 19 and 20 are on the same side of the hinge, or, in other words, the extended axes of the pins 19 and 20 are not on the same straight line or are not coaxial. Two examples of yet another element 21 according to Fig. 16.7; said element has an opening 22 at both ends, and the length of said element and the angle between said holes are such that in the assembled hinge this first element is at one end on the pin 19 and at the other end on its adjacent pin 18; and the second such element is located on the pin 20 and the second pin 18. The length of each of the elements 21 and the angle between the holes 22 in each element 21 are such that in the assembled hinge and when the axes A1 and A2 are aligned, two identical right-angled spherical triangles with sides G , H, I and J, K, L according to Fig. 16.8 are formed one in each half of the hinge; the right angle is on the axis of the input or output shaft, depending on the specific case. The first element 21 forms side I on the first right-angled spherical triangle, and the second element 21 forms side J on the second right-angled spherical triangle.

16.8A and 16.8B illustrate a hinge according to the above described embodiment. When studying Fig.16.8A and 16.8B in conjunction with the above description, it is obvious that whenever the axes of the input shaft and the output shaft are inclined to each other, then a certain spherical triangle is formed for each possible rotational position and angular position; and it is also obvious that the spherical triangle formed in each half of the hinge due to this design must be identical to the other, so that the plane of rotation of the axis A5 according to Fig. 16.1 and positioned by the tides 16 always halves the angle that appears from time to time between the axes of the input and output shafts.

Although the described hinge and centering tool use spherical geometry to provide centering, all other components that are not the centering tool describe disks or planes centered on the geometric center of the hinge during rotation, and each of these disks can be described by simple planar geometry . From the description below, it will be obvious that it is advisable to modify the hinge of the present invention described above to provide a design in which the components and the relationship between the components describe the forms of spherical geometry rather than planar geometry.

13. The thirteenth embodiment

As can be seen from Fig.16.9 from Fig.16, proposed element 22, which is a disk-shaped element with a hole 32 in the center. The purpose and function of this element is identical to element 15 described above with respect to the twelfth implementation. Element 22 has two rigidly attached pins 23 and 24. Elements 25, 26, 27 and 33 are identically made arc-shaped components centered on the assembly shown in FIG. 16.9; wherein each of the elements 25, 26, 27 and 33 is made with the possibility of free rotation on the pins 23 and 24. The hinge also has two forks, identical to those shown in Fig.16.6; however, one fork is mounted on the pins 28 and 29, the other on the pins 30 and 31. The centering means is similar to the means described in relation to the first hinge, consisting of elements 12, 13, 18, 19, 20 and 21 according to Fig.16.5, 6 and 7. FIG. 16.10 shows the hinge assembly; while the axis of the input shaft and the output shaft are on the same straight line; the image is presented along the axis of the shaft 2 - according to Fig.16.2. In this drawing, only the ends of the plug 3 are visible. During operation of this described hinge, whenever the axes of the input shaft and the output shaft are inclined to each other, a spherical triangle is formed, formed by the cut-off arcs of the trihedron formed by the axes of the pins 23, 28 and 31; and another identical spherical triangle formed by the cut-off arcs of the trihedron formed by the axes of the pins 24, 29 and 30, with the exception that twice at each revolution, when the axis of the pins 28 and 31 are aligned, at this moment a trihedron is not formed on both sides of the hinge. It also clearly follows that during operation of the hinge, pins 28, 29, 30 and 31 describe the arcs of the large circle, and the arc of the large circle is present between the axes of the pins 28 and 31 and also between the axes of the pins 29 and 30. It should be noted that during operation the hinge according to this embodiment, the hinge has four constantly changing spherical triangles - in addition to the mentioned spherical triangles, there are two spherical triangles related to the centering tool described above.

14. Fourteenth embodiment

Another modification using spherical geometry rather than planar geometry is shown in FIG. 16.11 from the drawings of FIG. 16. This modification provides a linkage mechanism identical to that shown in Fig. 16.9, with the exception that elements 27 and 33 are not shown. Referring to Fig. 16.12: two forks are also provided, as in Fig. 16.6, with the exception of that one shoulder on each of the forks is not shown, or is shortened; it should be noted that in order for the pins 19 and 20 to be on the same side of the hinge, it is necessary to extend at least one of the shortened shoulders in order to position the pin 20 or the pin 19, depending on the particular case, in the desired position . In this embodiment, it obviously follows that the action of this hinge is similar to the action of the hinge of the previous description: with the exception that the spherical triangles belonging to the pins 23 and 24 are both rectangular spherical triangles formed between the axis of the pins 23 and 31 and the point at which the arc described by the pin 31, cuts off the arc of the plane of rotation of the pin 23, and an identical triangle is formed on the other side relative to the pins 24, 30 and the arc of the pin 24.

It should be noted that in the hinges according to the last three descriptions, the centering device itself is configured to transmit force through the hinge, and in the hinges described, it takes part of the load. Therefore, it is possible to perform the joint of equal angular velocities exclusively from the centering device provided by the pins 19, 20 together with the elements depicted in Figures 16.5 and 16.7.

Turning to FIG. 16.13: the shaft 12 is rigidly mounted on the surface using a bearing 36 and a corresponding mount. The shafts 37 and 38 are also rigidly attached so that when the angle between their axes can be either fixed or variable, their axes always intersect the center of the shaft 12 and the axis of the two connecting rods 18; and the axis of the pins 19 and 20 also intersect at the same point.

It will be clear to a person skilled in the art that this assembly can be included in a stand-alone support means, for example, in a hollow ball joint from which pipes positioning shafts 37 and 38 extend.

15. Fifteenth embodiment

As can be seen from FIG. 16, another embodiment is provided below. The embodiments described above can be broadly classified as modified Hooke joints, and an implementation that is very different from them is more like a Rzeppa joint. As can be seen from Fig. 16.4, an element is proposed, essentially similar to the element shown in Fig. 16.12, with the exception that the spherical plane of the spherical triangle described by elements 25 is a three-dimensional element 36 of at least the same shape and size; and likewise, on the other side of the hinge, the spherical plane described by element 26 is also a three-dimensional element of at least the same size and shape (regardless of the image in FIG. 16.14 this node is symmetrical). A groove is made in the surface of each three-dimensional element 36 and 37, which describes a large circle, which would be described by pins 30 and 31, if they were present in this embodiment. Also provided are two forks 38 and 39 shown in Fig.16.15; each fork has an elongated and curved shoulder, and each of them has a groove 40 and 41, made in the inner surface of each fork 38 and 39, as a result of which, during operation of the hinge, the ball moves in the grooves by sliding. The assembly of this hinge is similar to the descriptions described above using forks, except that the ball is between the plug 39 and the three-dimensional element 36, and also between the plug 38 and the three-dimensional element 37. According to the latter option: the third and fourth spherical triangles are formed by large circular arcs between the axis of the pin 23 and the center of the ball and between the point at which the path of the ball cuts off the plane of rotation of the pin 23, and similarly on the other side; wherein the first and second spherical triangles are formed by a centering means as described above.

It follows from the foregoing that a potential general characteristic, according to which all moving elements describe spherical geometric trajectories and constructions of the type described here, considers it possible to perform hinges of substantially equal angular velocities without the presence of sliding elements. It also provides the opportunity to reduce all the components that make up the structure to elements of a simple structure; while in all variants of the prior art, hinges of equal angular velocities, which do not perform the functions of spherical geometry, there are sliding components, as well as elements of a very complex structure.

16. The sixteenth embodiment

Fig. 17.1 is a copy of Fig. 16.2: two halves of a modified Hooke joint, well known and referred to in previous embodiments. Turning to FIG. 17.2: the method according to this sixteenth embodiment provides for two forks 3 and 4, each of which has a pin 19 and 20 mounted on the inner arc surface of said forks according to previous embodiments. 17.3 and 17.4 represent elements that are different from the centering tools described or disclosed herein. Fig.17.3 represent a circular annular element, the inner diameter of which exceeds the diameter of the annular element 5 in Fig.17.1. Fig.17.4 shows another circular annular element, the inner diameter of which exceeds the outer diameter of the circular element according to Fig.17.3. Turning to FIG. 17.3: the circular annular element 21 has two tides or trunnions 24 and 25 diametrically opposed to each other, and holes with bearings 22 and 23 to provide or facilitate the installation of the ring 21 on the axis A5 according to FIG. 17.6. Referring to FIG. 17.4: the circular annular element 26 has two diametrically opposite holes with bearings to provide or facilitate the assembly of the annular element 26 with the annular element 21, while the tides or pins 24 and 25 are installed in the bearings 27 and 28, respectively. Also according to FIG. 17.4: the elements 29 and 30 are pins, the axes of which are coaxial with the radii of the annular element 26, and each of these pins is spaced at the same angle from the center of the bearings 27 and 28, respectively. The circular annular elements 21 and 26 are installed according to Fig. 17.5, and their installation with respect to the hinge is shown in Fig. 17.6. The two arc elements shown in Fig. 17.7 have an arc or angle between the holes 32 and 33, equal to the angle between the elements 29 and 19, and also between the elements 30 and 20, when the axes of the shafts 1 and 2 are aligned on one straight line, as a result wherein the first spherical triangle is formed on the first half of the hinge shown in Fig. 17.6, and the second spherical triangle is formed on the second half of the hinge shown in Fig. 17.6; the first spherical triangle is formed by arcs of a large circle between the pin 29 and the pin 19, and the pin 19 and the axis of the shaft 1, and the axis of the shaft 1 and the pin 29. The second spherical triangle is formed by arcs of a large circle between the corresponding points and elements in the second half of the hinge.

It should be noted that the assembly described here effectively performs the same functions as the assembly according to the twelfth embodiment, according to which a shaft with a crank pin at both ends is used to perform the same task as the ring member 27 and the pins 29 and 30 described herein.

The assembly disclosed here provides the ability to use the element shown in FIG. The element shown in Fig. 17.8 is a shaft connected to the center of the hinge either as an input shaft or as an output shaft instead of one of the forks. To facilitate the operation of the centering mechanism described here: the element according to Fig. and in said arcuate slot, a pin 37 is provided that performs the same task as the pin 19 or 20, as the case may be. 17.9 shows a linkage according to an eleventh embodiment. It is obvious that the centering mechanism disclosed here together with the element shown in FIG. 17.8 is applicable, in particular, as a suitable centering means shown in FIG. 17.9. In this embodiment, bearings 22 and 23 are positioned by pins 38 and 39, respectively.

This embodiment is another example of a centering tool that forms a first spherical triangle in the first half of the joint of equal angular velocities, and also forms an identical spherical triangle in the second half of the joint of equal angular velocities, in order to provide or limit the elements of the joint on the homokinetic plane of the joint, while while spherical triangles continuously change, but remain identical to each other during operation of the hinge.

17. Seventeenth embodiment

This embodiment, shown in FIG. 18, is a hybrid of the hinges described above, disclosed in a specific example of the centering mechanism disclosed in the sixteenth embodiment.

As can be seen from Fig. 18, Fig. 18.1 shows a plug 1 with an attached shaft 2 and holes 4 and 5 in the plug. The pin 3 protrudes from the inner arc surface of the plug 1. The axis A1 of the pin 3 intersects the axis A2 of the holes 4 and the axis A3 of the shaft 2. FIG. 18.2 is a circular element 6 having four openings 7, 8, 9 and 10 located at equal intervals on the sides . Fig. 18.3 is another round element 11, the outer diameter of which is less than the inner diameter of the round element 6. The round element 11 has four equally spaced openings 12, 13, 14 and 15 on the sides.

Fig. 18.4 and Fig. 18.5 show a side projection and a horizontal projection, respectively, of a shaft 16 having a through hole 17 and an attached protrusion 18. Two arc elements 19 and 20 are attached to the protrusion 18, and one of them is made only for balance, and the other to provide support for the pin 21. The axis A5 of the pin 21 intersects the axis A4 and A6, which are the axes of the shaft 16 and the holes 17, respectively.

Fig. 18.6 shows a part of the circular elements 22 and 23. The element 22 has a pin 24, which is installed in the hole 25 and rests on the bearing 26, as a result of which the element 22 can rotate on the axis A7.

The element 22 has pins 27 and 28, separated by an equal interval from the axis A7.

Fig. 18.7 shows an arcuate element with two holes 30 and 31; moreover, there are two such elements.

An assembly of various constituent parts is shown in Figs. 18.8, 18.9 and 18.10, which show a cross section of a horizontal projection and a side projection and a side projection, respectively, of an assembled hinge. The element 29 is assembled on the pins 27 and 3, and the second element 29 is mounted on the pins 28 and 21.

Fig. 18.11 shows another view of the hinge assembly, without numbering the components.

Fig. 18.12 shows two spherical triangles formed by the indicated node. The first spherical triangle has sides formed by arcs of a large circle between elements 3, 27 and 24; the second spherical triangle is formed by arcs of a large circle between the elements 21, 28 and 24. It is obvious that when the axes of the elements 2 and 16 are coaxial, then both of these spherical triangles are rectangular spherical triangles; and that during the action of the hinge, whenever the axes A4 and A3 are not aligned, the spherical triangles continuously change, but remain identical to each other, as a result of which the connecting pin 60 between the elements 11, 6 and 23 is limited by continuous rotation on the homokinetic plane of the hinge.

As can be seen from Fig. 18.13: presents a sphere, spherical triangles A, B, C and A, E, D, which are formed with the indicated relationships and with the corresponding hinge elements indicated in brackets.

As an alternative to the elements disclosed and illustrated in Fig. 18.4 and Fig. 18.5: the element 11 has a number of planes and grooves, or slots, cut in an inner circular surface; holes 12 and 13 are not shown. In this embodiment, the shoulder is rigidly attached to the alternative member 11 to position the pin 21 in the same relative position as described above.

18. The eighteenth embodiment

According to Fig. 19.1, this option involves doubling the centering mechanism of equal spherical triangles disclosed in previous embodiments, and which now becomes the scissor mechanism used in the coupling of the first implementation.

19. The nineteenth embodiment

According to Fig. 20, this option has two types - 1) a joint or coupling of equal angular velocities for two shafts that have a fixed angular axial displacement, and 2) a universal joint or coupling of equal angular velocities for connecting two shafts that have a variable angular axial bias. In both cases, the extended axes of the two shafts intersect at some point, and in the second case, the axes can also be coaxial.

As can be seen from Fig. 20.1, a tool is proposed for rigidly positioning at least three pins or pins, separated by an equal radial interval from the central axis and an equal angle from each other, as a result of which all the extended axes of these pins or pins intersect at some point. Fig. 20.1 shows one preferred embodiment of this element; and the illustrated embodiment shows the bottom of a partial spherical concave profile and the top of a partial spherical convex profile; the element has three equally sized shoulders radially emanating from the center of the element; and also provided with three holes - one on each shoulder for the pin to fit into them.

For the purposes of this embodiment, with respect to hinges or couplings for shafts with a fixed angular displacement: provide the two elements shown in Fig. 20.1, while the concave inner surface of the first such element has a radius greater than the convex outer surface of the second such element; moreover, this difference in radii exceeds the radial thickness of the lever element indicated in Fig. 20.2 and described below. Fig. 20.2 shows a curved or partially spherical element having substantially parallel sides and a pin protruding from both ends, as a result of which the extended axes of these pins intersect at some point, which also intersects with a radius that bisects the axis of the two pins and is perpendicular to the inner or concave surface of the specified element. One pin protrudes from the concave side, the second from the convex side. The radius of the outer, or convex, surface is smaller than the concave side of the first, or larger, element indicated in FIG. 1; while the inner or concave surface has a radius larger than the convex surface of the second or smaller version of the element shown in Fig. 20.1.

In this embodiment, with respect to the couplings for shafts with a fixed angular displacement, three variants of the element shown in Fig. 20.1 are provided, each of them having the same dimensions, and each element having an angular distance between the axes of the pins at both ends equal to the fixed angular displacement of the joints them shafts, but in none of the options this angle can exceed the angle of a smaller arc of a large circle between any two holes in the elements shown in Fig. 20.1, minus the angle between the axis of the pin of the curved element, the one indicated in FIG. 20.2, and its nearest adjacent end.

The assembly of these elements is as follows.

1. A pin protruding from the convex side of each of the three variants of the element shown in FIG. 2 is mounted, with the possibility of rotation, in the holes of the concave side of a larger version of the elements shown in FIG. 20.1.

2. A pin protruding from the concave side of the element shown in Fig. 20.2, is mounted, with the possibility of rotation, in the holes of the convex surface of a smaller variant of the element shown in Fig. 20.1.

The said elements and their assembly provide a three-layer assembly in which each of the three element variants shown in FIG. 20.2 connects the holes of a larger version of the element according to FIG. 20.1 with the hole in the smaller embodiment according to FIG. 20.1; and in which the extended axes of each of the pins protruding from each of the three variations of the element of FIG. 20.2, and the extended axes of each of the holes in both variations of the element of FIG. 20.1 intersect at some point. In addition to the indicated node, the arc between the axes of the pins of each of the three variants of the element according to FIG. 2 is located on the arc of a large circle, the center of which is at the intersection of all the axes mentioned above, namely: the extended axes of each of the three holes in the larger version of the element according to FIG. 20.1, and the extended axes of the three holes in a smaller version of the element according to FIG. 20.1; and the extended axes of each of the pins protruding from each of the three element variants according to FIG. 20.2. In addition, the axes of each of the element variations according to FIG. 20.1 also intersect at the same point.

Fig. 20.3 schematically depicts a side projection of a section of the specified node, without perspective. Referring to Fig. 20.3: 1 is a larger version of the element shown in Fig. 20.1; elements 2 and 3 - the first and second variants of the element shown in Fig.20.2; element 6 is a smaller version of the element shown in Fig. 20.1; elements 4, 5, 7 and 8 - pins protruding from elements 2 and 3, as described above, and each of these pins is installed in the hole of either a larger or smaller version of the element shown in Fig. 20.1. Axes A1, A3, A4 and A5 are the extended axes of the pins 7, 4, 8 and 5, respectively; and the axes A2 and A5 are, respectively, the axes of the elements 6 and 1.

The node described above provides a lever system of equal angular velocities, in which: if the axes A2 and A5 have a fixed relationship and element 1 rotates around axis A5, then the link mechanisms between elements 1 and 6 of each of the three element variants shown in Fig. 20.2, two of which are visible in Fig. 20.3, the rotation of the element 6 around the axis A2 will be caused with an angular velocity equal to the angular velocity of rotation of the element 1 around the axis A5; and vice versa - if the element 6 rotates around the axis A2, then these lever mechanisms will cause the rotation of the element 1 around the axis A5 with an angular velocity equal to the speed of rotation of the element 6.

Using the assembly or linkage system described above, it is possible to provide a clutch or joint of equal angular velocities for two shafts having a fixed angular displacement. The node described above is schematically represented in FIG. 20.4; wherein Fig. 20.5 represents the hinge or sleeve in its entirety.

As can be seen from Fig. 20.5, the base 12 is a three-dimensional base having an angle 15 through which it is necessary to transmit power from the first shaft 10 to the second shaft 11. The shaft 10 is rigidly attached to the base 12 with a bearing and mounting means 13, and the shaft 11 similarly, it is rigidly attached to the base 12 by means of a bearing and mounting means 14. Any suitable connecting means is used for rigidly connecting the shaft 10 to the assembly 9, as a result of which the shaft is attached to the element 6 and coaxially with the axis A2 according to FIG. 20.3; and likewise, any suitable fixing means are used for rigidly connecting the shaft 10 to the assembly 9, as a result of which it is attached to the element 1 and coaxial with the axis A5 according to FIG. 20.3. Point B is the intersection point of all the mentioned axes and also the axes of the shafts 10 and 11. This node will transmit power with equal angular velocities from the shaft 10 to the shaft 11.

To provide a universal joint or coupling of equal angular velocities capable of transmitting power between shafts having a variable angular axial displacement, provide, firstly, a node identical to that described above and shown in Fig. 20.3, together with the three subsequent element variants shown in .20.2, and another variant of the element shown in Fig. 20.1, where three more variants of the element according to Fig. 20.2 and another variant of the element according to Fig. 20.1 have a decreasing radius to form another layer, added lower Or more with respect to the central point B Fig.20.3 according to previously described assembly; although the elements have smaller physical dimensions, their angular size is identical to the dimensions of the corresponding elements in the higher layers, as a result of which all axes intersect at some point.

FIG. 20.6 shows an embodiment configured to provide an assembly suitable for inclusion in a hinge or sleeve, and in which the shafts have a variable angular relationship with each other. Element 22 is the third variant of the element according to Fig. 20.1 and has the same angular size as the first two variants of the indicated element, namely: elements 1 and 6. Elements 16 and 17 are the fourth and fifth variants of the element according to Fig. 20.2, and they have the same angular size as the first three options. It should be noted that the third and sixth versions of the element according to Fig.20.2 are not visible and not shown in Fig.20.6. The shaft 23 is rigidly connected to the center of the concave surface of the element 22, and the shaft 24 is rigidly connected to the convex surface of the element 1, as a result of which, in the position of the assembly according to FIG. 20.6, the shafts 23 and 24 are coaxial with each other and also coaxial with the axes of the elements 1 and 22 All axes converge at point B.

In order for this described assembly to function as a universal joint of equal angular velocities, it is necessary to provide a fastener or connection that provides for the angular movement of the axes of the shafts 23 and 24 while limiting the axes of the shafts 23 and 24, as a result of which, whenever the axes of these shafts are misaligned, they will intersect at some point. The assembly described above, shown in Fig. 20.6, is schematically represented in Fig. 20.7, but first refer to Fig. 20.8, which represents important relationships between the shafts disclosed here and the assembly. During operation of the hinge according to this embodiment, it is important that the point B shown in Fig. 20.6 always falls on the axis of the shaft 23, and it is important that the point on the axis of the shaft 24 always falls on a spherical plane whose center is at point B. If the node according to Fig. 20.6 will be performed with sufficient strength and tolerance, it will provide the necessary relationships, or alternatively, limiting means can be provided to create these relationships; and an example of such a limiting mechanism is shown in FIG. 20.9.

As can be seen from Fig. 9, the yoke 25 has a bearing 26 in which the shaft 24 is mounted, as a result of which the shaft 24 can rotate in the bearing 26. The bearing 27 is arranged to receive the shaft 23 therein, as a result of which the shaft 23 can rotate in the bearing 27, but it is rigidly held, and therefore point B, shown as point 10 in FIG. 20.6 and FIG. 20.8, will always be at the intersection of axes A7 and A8. Axis A7 is the axis for bearing 27 in housing 28; and the axis A8, in turn, is the axis for the housing 28.

Obviously, the assembly described here and shown in FIG. 20.6 and bounded in such a way that point B according to FIG. 20.6 is the axis point of all the mentioned axes provides a universal joint of equal angular velocities, in which there are no load-bearing sliding surfaces that are not surfaces rotation and in which all the operating elements transmit torque from the first shaft to the second shaft, which is part of a spherical structure and acting in a spherical system.

A hinge having characteristics inherent in the disclosed structure, and a hinge based on spherical geometry, and a hinge having a structure originally described and illustrated in FIG. 20.3; and a hinge having a structure described and illustrated in FIG. 20.6; and proposed installation tool described in Fig.20.5 and Fig.20.9.

20. Twentieth Embodiment

As can be seen from Fig. 21, this option offers two variants of the assembly described in Fig. 21.3, which is a spherical four-rod linkage mechanism with the extended axes of each of the four axes A1, A2, A3 and A4 in the linkage mechanism passing to a single point and where the arcs between each of the axes form the arcs of a large circle.

Installation means is provided in the center of the double plug 5, as a result of which two variants of the assembly shown in FIG. 21.3 are held in the double plug 5 in conjunction with each other - according to FIG. 21.4. In FIG. 21.4, points P1 and P2 represent the center of the spider elements 1 and 2, respectively; C1 and C2 are large circles of spheres whose center is at points P1 and P2, respectively.

A pin (not shown) extends from the shafts 3 and 4 in such a way that the axis of each pin extends radially from the points P1 and P2, respectively, in the assembled assembly and forms an axis for the axis A3 in each embodiment shown in FIG. 21.3.

Obviously, in this assembly — if means are provided that condition both variants of the assembly of FIG. 21.3 — to move in the same manner as the hinge, the angle between the shaft 1 and the double fork 5 will remain the same as the angle between the shaft 4 and the double fork 5; and the necessary conditions for the joint of equal angular velocities of the double cardan type will be satisfied.

One of the methods that will ensure uniform movement of the two variants of the assembly according to FIG. 21.3 consists in rigidly connecting the first variant of the element 6 to the second variant of the element 6, and in a similar rigid connection of the two variants of the element 7.

One way to rigidly connect each variant of element 6 to each other is to provide a single element according to FIG. 21.5, where the pins 10 and 11 provide the axis of each of the two variants of axis A2, and the hole 12 is axis A1.

Without further explanation, it obviously follows that two variants of the element 7 can be performed as a single component according to Fig.21.5.

21. Twenty-First Embodiment

With reference to FIG. 22, another embodiment of the limiting mechanism of the seventeenth embodiment is described, according to which the spherical triangles formed by this mechanism are identical to each other in the operation of the hinge.

Fig. 22.1 continues the description of the mechanism shown in Fig. 18.12. Fig. 22.2 is a description of the mechanism disclosed in the eighteenth implementation. Fig. 22.3 is a perspective image with a spatial separation of the parts of the hinge of equal angular velocities according to the description of the seventeenth and eighteenth embodiments. FIGS. 22.4, 5 and 6 represent an assembled image of this hinge, wherein the spherical assembly indicated by reference 7 in FIG. 22.3 is a spherical link system substantially disclosed in the eighteenth embodiment.

As can be seen from FIG. , and between the rod 2 and the rod 3, respectively, may differ from each other. This solution provides a means whereby the angles 4 and 5 are continuously substantially identical to each other, as a result of which the two spherical triangles formed by this mechanism remain identical to each other.

According to this embodiment, referring to FIG. 22.7, the mechanism disclosed in FIG. 1 is provided, which also comprises a gear mounted between link 1 and link 2. Link 1 and link 2 have teeth for engagement with gear 3. In this mechanism angles 4 and 5 will always be essentially identical to each other, as a result of which the spherical triangles formed by the mechanism also remain essentially identical to each other.

Therefore, according to the present embodiment, a centering mechanism in accordance with FIG. 22.7 is described, and a constant velocity joint according to FIGS. 22.3, 4, 5 and 6 is provided; while the centering mechanism 7 is replaced by the mechanism disclosed in Fig.22.7.

Summary.

Brief Summary of Embodiments

The first embodiment

A clutch of equal angular velocities, in which the axes of all rotating elements intersect at the intersection of the axes of the input and output shafts. The coupling has an adjusting fork and an adjusting mechanism and is characterized in that the adjusting fork defines an axis of rotation, which bisects the additional angle between the axis of the input shaft and the axis of the output shaft of the coupling.

The regulating mechanism is made in the form of a double scissor assembly, in which all the lever mechanisms have axes radial with respect to the intersection of the axes of the input and output shafts; however, the hinge centers of the control linkages are essentially at the vertices of equal spherical triangles.

Second embodiment

A clutch of equal angular speeds, in which all elements are identical to the elements of the first implementation, with the exception that the control mechanism consists of a gear train in which two link links with gear segments mesh with the central gear; while this node controls the axis of the adjusting fork so that it is on the bisector of the additional angle between the axes of the input and output shafts.

Third Embodiment

An equal-angle clutch in which either the scissor mechanism of the first embodiment or the gear train of the second embodiment adjust the axis of the adjusting fork so that it is on the bisector of the additional angle between the axes of the input and output shafts; while the inner and outer forks are changed from a completely round shape to a partially segmented shape.

Fourth Embodiment

An equal-angle coupling, in which the rotation elements, on which the ends of the input and output shafts rest, are separated by a connecting pipe, and in which the regulating mechanism rests on the connecting pipe, as a result of which the pipe axis is limited by its location on the bisector of the additional angle between the input and output shafts .

Fifth Embodiment

A clutch of equal angular speeds, in which the angle between the input and output shafts can be changed from time to time by a regulating mechanism; however, the specified adjusting mechanism also limits the orientation of the adjusting fork so that its axis of rotation is on the bisector of the additional angle between the input and output shafts. The coupling includes a variable hydraulic displacement device in the form of an inclined disk.

Additional embodiments

One of the options offers a clutch of equal angular speeds, made in the first form, according to which the control mechanism can be performed for a certain fixed angle between the axes of the input shaft and the output shaft using a limited assembly of control elements. Regulatory elements are based on forms of spherical geometry.

In the second form: an expanded assembly of similar regulating elements is made with the possibility of providing a regulating mechanism for a clutch of equal angular speeds, in which the angle between the input and output shafts is variable.

According to yet another embodiment, an equal angular velocity clutch is provided with a control mechanism in the form described in the first preferred embodiment. The original form (disclosed in PR5731) contained one half of the scissor mechanism of the first implementation with a modified double scissor system according to PR5992.

According to another embodiment, a clutch of equal angular speeds is provided, which is implemented by a set of linkage mechanisms to limit the alignment of the axis of rotation of the adjusting fork so that this axis halves the additional angle between the axes of the input and output shafts of the clutch. Regulating lever mechanisms are made in the form of elements that are based on arcs of spherical triangles.

According to another embodiment, a linkage mechanism is disclosed, which is a novelty of the principles of the internal and external fork system or the universal joint system of the type commonly used in double cardan joints. This implementation is in the form of a fork mechanism used in the fourteenth implementation.

Another embodiment discloses a centering mechanism for an equal-angle clutch comprising a system of engaging gears and levers for adjusting the angular relationship between the two halves of the clutch.

Turning to the first embodiment according to FIGS. 1-4, it should be noted that a significant number of characteristics mentioned in the introduction to the description with reference to FIG. 23 are presented in this implementation, such as:

(a) The adjusting fork in conjunction with the scissor mechanism and forming the adjusting mechanism for the universal joint assembly containing the inner and outer fork acts completely symmetrically around the bisector 308 (designated as C in FIG. 4) of the additional angle;

(b) All axes of the control mechanism pass through the center 307 of the clutch (also called the "geometric center");

(c) In another respect, the substantially unlimited linkage between the input and output shafts provided by the universal joint mechanism in the form of an inner fork and an outer fork is limited by a control mechanism in the form of an adjusting fork; in this case, in such a way that the YY axis (indicated in FIG. 1) is on a homokinetic plane.

This description sets forth only certain implementations of the present invention and modifications that are obvious to those skilled in the art that may be practiced within the scope and concept of the present invention.

Claims (71)

1. An equal-angle clutch, in which the regulating mechanism is configured to maintain conditions for equal instantaneous angular-velocity transmission between the input and output shafts, and which comprises an axis of rotation of the input shaft, an axis of rotation of the output shaft, and a control mechanism, essentially a U-shaped output plug an axis having a control pin of the output axis attached to one shoulder of the U-shaped plug of the output axis, wherein the axis of the control pin of the output axis is in a plane formed by the output axis and the axis formed the pins of the U-shaped fork of the output axis, and intersects the geometric center of the coupling, the protrusion of the input axis having a control pin of the input axis, and the axis of the control pin of the input axis is in the plane formed by the input axis and the axis of rotation of the protrusion, and intersects the geometric center of the coupling the mechanism is configured to hold at least parts of the coupling to obtain characteristics of equal angular velocities. 2. The clutch of equal angular velocities according to claim 1, in which all the axes of rotation intersect at a common point, defined as the geometric center of the clutch. 3. The clutch of equal angular velocities according to claim 2, in which the elements of the regulating mechanism are limited in their movement along arcs on large circles of spheres, the center of which is located in the geometric center of the clutch. 4. The clutch of equal angular velocities according to claim 3, in which the axis of rotation of the regulating mechanism is located on the bisector of the additional angle of the input and output axes. 5. The coupling according to claim 4, in which the input axis of rotation ends in a protrusion having an axis of rotation at right angles to the axis of the shaft, while the intersection of the axes coincides with the geometric center of the coupling. 6. The coupling according to claim 5, in which the protrusion is made to rotate around the axis of the first inner fork pair of the pins of the inner fork. 7. The clutch according to claim 6, in which the first inner fork has a second inner fork pair of pins; the first and second pairs of internal fork trunnions form the axis of rotation at right angles to each other and intersect at a point that coincides with the geometric center of the coupling. 8. The coupling according to claim 7, in which each of the trunnions of the first pair of inner fork trunnions of the inner fork is spaced at an equal distance from the geometric center of the coupling. 9. The coupling of claim 8, in which each of these pins of the second pair of internal fork pins of the inner fork is spaced at an equal distance from the geometric center of the coupling. 10. The clutch according to claim 9, in which the axis of the second pair of inner fork trunnions is made to rotate around the axis of the first pair of outer fork trunnions of the outer fork. 11. The clutch of claim 10, in which the outer plug has a second pair of outer fork trunnions; the first and second pairs of external fork trunnions form the axis of rotation, which intersect in the geometric center of the coupling. 12. The clutch according to claim 11, in which each of the pins of the first pair of external fork pins is spaced at an equal distance from the geometric center of the clutch. 13. The coupling according to item 12, in which each of the pins of the second pair of external fork pins is spaced at an equal distance from the geometric center of the clutch. 14. The clutch according to item 13, in which the adjusting fork is essentially U-shaped with the pins of the adjusting fork at its outer ends. 15. The coupling of claim 14, wherein the pins of the adjusting fork are rotatable about an axis of the first outer-fork pair of pins of the outer fork. 16. The coupling according to clause 15, in which each of the pins of the adjusting fork is spaced at an equal distance from the geometric center of the coupling. 17. The coupling according to clause 16, in which the outer fork have a second pair of outer fork trunnions, wherein said first and second pair of outer fork trunnions define rotation axes that intersect at the geometric center of the coupling. 18. The coupling according to 17, in which each of the pins of the first pair of external fork pins of the outer fork is spaced at an equal distance from the geometric center of the coupling. 19. The coupling according to claim 18, wherein each of the pins of the second pair of outer-fork pins of the outer fork is spaced at an equal distance from the geometric center of the coupling. 20. The clutch according to claim 19, in which the output axis of rotation ends in the center of the base, essentially U-shaped plugs of the output axis, having at its outer ends of the journal axes of the output axis; the trunnions of the output axis form an axis at right angles to the axis of the output axis. 21. The coupling according to claim 20, in which the pins of the output axis of the forks of the output axis are rotatable around the axis of the second pair of external fork pins. 22. The coupling according to item 21, in which each of the pins of a pair of pins of the output axis is spaced at an equal distance from the geometric center of the coupling. 23. The coupling according to any one of claims 1 to 22, in which all axes of rotation of the pins and the input and output axes intersect at the geometric center of the coupling. 24. The coupling of claim 23, wherein the adjusting fork has a pivot pin attached to the center of the base of the substantially U-shaped adjusting fork, whereby the axis of the pivot pin is at right angles to the axis of the pivots of the adjusting fork and intersects the geometric center of the clutch . 25. The clutch according to claim 1, in which the specified control pin of the output axis is located at a predetermined angle to the output axis. 26. The clutch according to claim 1, in which the control pin of the input axis is located at a predetermined angle to the input axis. 27. The coupling of claim 26, wherein the angles of the adjusting pin to the input axis and the output axis are equal to each other. 28. The clutch according to item 27, in which the regulatory mechanism is made in the form of a double scissor assembly. 29. The clutch of claim 28, wherein the scissor assembly comprises a first and second scissor link, a first and second scissor link, and articulated shafts of the scissor link. 30. The clutch according to clause 29, in which the first and second scissor links with their centers are pivotally attached to the hinge pin of the adjusting fork. 31. The clutch of claim 30, wherein said scissor links have articulated shafts at their outer ends; wherein the articulated shafts are spaced at an equal distance from the articulated pin of the adjusting fork, while the axes of the articulated shafts intersect in the geometric center of the coupling. 32. The clutch of claim 31, wherein the articulated shafts of the scissor link are pivotally coupled to said first and second scissor wings, whereby the first end of each scissor link is connected to said first scissor link with said control pin of the input shaft and the second end of each scissor link is connected the specified second scissor wings with the specified adjusting pin of the output shaft. 33. The clutch according to any one of claims 1 to 27, in which the control mechanism is made in the form of an engaging gear transmission. 34. The clutch of claim 33, wherein said engaging gear comprises a main support link, a central gear, a first and second connecting link, a first and second link joint shafts. 35. The coupling according to clause 34, in which the main support link at its midpoint is pivotally mounted on the pivot pin of the adjusting fork. 36. The clutch according to clause 35, in which the Central gear wheel is pivotally mounted on the pivot pin of the adjusting fork. 37. The coupling according to clause 36, in which the main support link at its outer ends has a first and second joint shaft. 38. The coupling according to clause 37, in which the axis of the first and second articulated shafts extend radially to the geometric center of the coupling. 39. The clutch of claim 38, wherein in the geometric center, the angles opposite the axes of the first articulated shaft with the articulated pin of the adjusting fork and the second articulated shaft with the pin of the adjusting fork are equal to each other. 40. The clutch of claim 39, wherein the first and second linkages have a tooth segment on the first end of the gear teeth engaged with the central gear when the linkages are pivotally mounted on the articulated shafts of the main support link. 41. The coupling of claim 40, wherein the first and second link arms have trunnions at their second end. 42. The coupling according to paragraph 41, in which the axis of the trunnions of the second end of the first and second lever links extend radially to the geometric center of the coupling. 43. The clutch according to paragraph 42, in which the first and second linkage are identical. 44. The coupling of claim 43, wherein the spherical triangles formed by the hinged centers of the central gear and the first and second ends of the first and second link links are equal to each other. 45. The clutch according to item 44, in which the first link is pivotally connected by a pin of the specified first link with the adjusting pin of the input shaft. 46. The coupling according to item 45, in which the second link is connected by a pin of the second link with the adjusting pin of the output shaft fork. 47. The clutch according to any one of claims 1 to 46, in which the input shaft and output shaft are made interchangeable. 48. The coupling according to any one of paragraphs.30-47, in which all the pivot joints are implemented using deep groove ball bearings. 49. The coupling according to any one of paragraphs.30-47, in which all the pivot joints are implemented using needle roller bearings. 50. The coupling according to any one of claims 1 to 49, in which all the mutual movements of the axes and the regulating mechanism are rotational. 51. A double clutch of equal angular velocities, in which the regulating mechanism is configured to maintain conditions for equal instantaneous transmission of angular velocities between the input and output axes, and which contains the input axis, output axis, input end plug, output end plug, control mechanism, and the plug the input end has a first and second pair of pins of the plugs of the input end, the second pair of pins of the plugs of the input end is pivotally connected to the input end pair of pins of the connecting pipe, and the plug of the output end has a the second and the second pair of pins of the plugs of the output end, the second pair of pins of the plugs of the output end pivotally connected to the output end pair of pins of the connecting pipe. 52. The clutch of claim 51, wherein the input axis terminates in a protrusion of the input axis; wherein the protrusion of the input axis has an axis of rotation at right angles to the input axes; moreover, the intersection of the input axis and the input axis of rotation of the protrusion forms the input geometric center of the coupling. 53. The clutch according to paragraph 52, in which the output axis ends in the protrusion of the output axis; the protrusion of the output axis has an axis of rotation at right angles to the output axes; moreover, the intersection of the output axis and the output axis of rotation of the protrusion determines the output center of the coupling. 54. The coupling of claim 53, wherein the protrusion of the input axis is rotatable about the axis of the first pair of pins of the input end fork in the input end fork. 55. The coupling of claim 53, wherein the protrusion of the output axis is rotatable about the axis of the first pair of pins of the plug of the output end in the plug of the output end. 56. The coupling of claim 55, wherein the second pair of pins of the input end fork forms an axis of rotation at right angles to the axis of the first pair of pins of the input end fork; moreover, the axis of the first and second pairs of pins of the input end fork intersect in the input center of the coupling. 57. The coupling according to clause 56, in which the second pair of pins of the plugs of the output end determines the axis of rotation at right angles to the axis of the first pair of pins of the plugs of the output end; moreover, the axis of the first and second pairs of pins of the plugs of the output end intersect in the output center of the coupling. 58. The coupling according to clause 57, in which the pins of each of the pairs of pins of the input end forks and output end forks are symmetrically located around the input and output centers of the coupling, respectively. 59. The clutch of claim 51, wherein the protrusion of the input axis has a control pin attached to the protrusion of the input axis, whereby the axis of the control pin is in a plane defined by the input axis and the axis of rotation of the protrusion, and intersects the input center of the coupling. 60. The sleeve of claim 51, wherein the protrusion of the output axis has a control pin attached to the protrusion of the output axis, whereby the axis of the control pin is in a plane defined by the output axis and the axis of rotation of the protrusion, and intersects the output center of the coupling. 61. The coupling of claim 60, wherein the axis of each of the adjusting pins is positioned at a predetermined angle to each of the input and output axes; while the angles are equal to each other. 62. The clutch of claim 61, wherein the control mechanism comprises upper and lower transmission units, a pivot shaft of the transmission unit, upper and lower pivot shaft of the unit, upper and lower control linkages. 63. The clutch according to claim 62, wherein the control mechanism is mounted centrally in the connecting pipe and is equally spaced from each of the input and output centers of the clutch. 64. The clutch of claim 63, wherein each of the upper and lower transmission units is pivotally mounted on a pivot shaft; moreover, the axis of the hinge shaft coincides with the central axis of the connecting pipe and intersects the input and output centers of the coupling. 65. The coupling of claim 64, wherein each of the upper and lower transmission units has two articulated shafts, one at each outer end of the units. 66. The coupling of claim 65, wherein the axis of the articulated shafts at the input end of the upper and lower transmission units intersects the input center of the coupling. 67. The coupling of claim 66, wherein the axis of the articulated shafts at the output end of the upper and lower transmission units intersects the output center of the coupling. 68. The clutch of claim 67, wherein each of the articulated shafts at the input end of the upper and lower transmission units is pivotally connected to a control pin of the input axis and each of the articulated shafts at the output end of the upper and lower transmission units is pivotally connected to a control pin of the output axis. 69. The coupling according to any one of paragraphs 51-68, in which all the joints are designed for deep groove ball bearings. 70. The coupling according to any one of paragraphs.51-68, in which all the pivot joints are designed for needle roller bearings. 71. The coupling according to any one of paragraphs.51-70, in which all the mutual movements of the axes and the regulating mechanism are rotational.

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