Planetary gearing

258453 2

The invention relates to a planet gear with at least one planetary wheel, driven by the eccentric, and with at least one central wheel. The planetary wheel may be arranged inside or outside the central wheel. In order to achieve the shape of the two wheels, one of them is arranged with a closed rolling cycloid and a second roller ring. The shot thus occurs between the internal epicycloid profile and the outer ring of the rollers or between the inner crown and the external hypocyclide profile. The number of outer ring rollers or the number of curve sections of the outer hypocyclid profile is one greater than the number of curve segments of the internal epicycloid profile or the number of inner ring wings.

The term cycloid closed loop curve of these types of gears can be explained in relation to Figure 3 which represents one of the possibilities of kinematic creation of an equidistant short epicycloid.

After a solid base circle Kj with the center of the Mas with a radius and rolls without the slipping of an angular velocity and b of the rolling circle K2 with the center B and the radius b. The guide a + b = r the center B of the rolling circle Kj moves around the center M of the basic circle K ^ The point C inside the rolling circle K2, which lies on the line e with the center B of the rolling circle K2, describes the abbreviated epicycloid ZE. To the abbreviated epicycloid ZE we can construct a double-edged EK whose creational point Q lies on a normal abbreviated epicycloid ZE that passes through the tangent point A of the basic circle K1 and the rolling circle K2> Normal n strengthens the guider r the transfer angle y, the guider r forms with the x-axis the angle aa with the center line B of the rolling circle K2 and forming the point C of the abbreviated epicycloid ZE angle b. The crevice point Q of the equidistant EC has a constant distance Z from the creation point C of the epicycloid ZE and describes a circle K3 whose center lies at the forming point C of the epicycloid ZE and moves around the normal pole N at normal n. The a / b = α / β = z ratio, where £ is an integer. From the illustration in Fig. 3, for the equidistant EC, in the rectangular coordinates, the following expressions can be derived: x = r.cos and + e.cos (/? + <* · + Q.cos (y + β) y = r.sin a + e .sin (y + a) where the coordinates of the cycloid code are the center of the B roller of the rolling circle K2 the distance between the center B of the rolling circle K2 and the forming point C of the abbreviated epicycloid ZE or eccentricity where £ is an integer. From the illustration in Fig. 3, for the equidistant EC, in the rectangular coordinates, the following expressions can be derived: x = r.cos and + e.cos (/? + <* · + Q.cos (y + β) y = r.sin a + e .sin (y + a) where the coordinates of the cycloid code are the center of the B roller of the rolling circle K2 the distance between the center B of the rolling circle K2 and the forming point C of the abbreviated epicycloid ZE or eccentricity where £ is an integer. From the illustration in Fig. 3, for the equidistant EC, in the rectangular coordinates, the following expressions can be derived: x = r.cos and + e.cos (/? + <* · + Q.cos (y + β) y = r.sin a + e .sin (y + a) where the coordinates of the cycloid code are the center of the B roller of the rolling circle K2 the distance between the center B of the rolling circle K2 and the forming point C of the abbreviated epicycloid ZE or eccentricity

the distance C of the shortened epicycloid ZE and the forming point Q of the equidistant EC

angle of rotation střed center B angle between the driver ra rails e the angle between the driver ra standard n

For angles, the relation y = arctg applies

The upper sign applies to epicycloid (Fig. 3), while the lower sign applies to the hypooycloid generated by rolling the rolling circle K2 along the inner circumference of the base circle Kj ,. From this mathematical description, the three parameters r, e ac [. In the left hand side, the corresponding epicycloid ZE and its ecvividant EK are shown on the left-hand side, while on the right hand side, for the same roll of rollers, the hypocycloidase is plotted by its equidistant. The base circles have a radius a, a 'and center M, the rolling circles K2 have a radius, b' and center B, B ', both cycloids have the center M', the cylinders 15 have the center C, C 'and the rim is 0. The eccentricity OM = e or the handle is equally long and parallel to the BC and B'C7 Segments The angular velocity / S induced at the center of the roller ring or in the O joint through the eyelet produces at the center of the M cycloid a velocity vector having the same direction as the tee F , equal to the torque applied, divided. The curved disc which is supported by a fixed roller ring is rotated about its center M in the direction of the yoke or, if desired, oh'a. Power transmission can only take place perpendicular to the touching walls. However, the normal cycloid must pass through the touch point A, A 'of the rolling circle K2 and the solid base circle K1. The lines CA, C'A 'therefore form these normals and their extension is intersecting in the instant N, N' pole. induced at the center of the roll of the rollers or in the joint O through the ring e produces in the center M a cycloid velocity vector having the same direction as the tangent F equal to the applied torque divided by e. Thus, the curve disk which is supported by the fixed roller ring is rotated around its center M in the direction of the egg or, oh'a. Power transmission can only take place perpendicular to the touching walls. However, the normal cycloid must pass through the touch point A, A 'of the rolling circle K2 and the solid base circle K1. The lines CA, C'A 'therefore form these normals and their extension is intersecting in the instant N, N' pole. induced at the center of the roll of the rollers or in the joint O through the ring e produces in the center M a cycloid velocity vector having the same direction as the tangent F equal to the applied torque divided by e. Thus, the curve disk which is supported by the fixed roller ring is rotated around its center M in the direction of the egg or, oh'a. Power transmission can only take place perpendicular to the touching walls. However, the normal cycloid must pass through the touch point A, A 'of the rolling circle K2 and the solid base circle K1. The lines CA, C'A 'therefore form these normals and their extension is intersecting in the instant N, N' pole. rotated about its center M in the direction of the or, respectively, oh'a. Power transmission can only take place perpendicular to the touching walls. However, the normal cycloid must pass through the touch point A, A 'of the rolling circle K2 and the solid base circle K1. The lines CA, C'A 'therefore form these normals and their extension is intersecting in the instant N, N' pole. rotated about its center M in the direction of the or, respectively, oh'a. Power transmission can only take place perpendicular to the touching walls. However, the normal cycloid must pass through the touch point A, A 'of the rolling circle K2 and the solid base circle K1. The lines CA, C'A 'therefore form these normals and their extension is intersecting in the instant N, N' pole.

Since the rolls 15 of the ring have centers C, C 'and their radii are equal to the constant distances q CQ and q' = C 'S', the Q, Q 'points must simultaneously pass through these normals. Referring to Fig. 3, there is a single roller 15 on which a broken circle is indicated. The bodies Q are both the EC-equidistant EC loosening points, i.e. the cycloid disc, and the body touch of this disc with the wings of the wreath 15 and determine, for each of the described types of kinetics two curves. This fact that cycloid ring contacting points describe the cycloid is not present in the art. In the following, the equivistant will be referred to as the cycloid abbreviated as the rolling cycloid as the rolling cycloid, and the intended equivistant to the truncated cycloid assigned to the ring points of the wound rolls is referred to as the reference cycloid.

Accordingly, in the case of translocation with epicycloids, cycling cyclodextrins in the internally or externally related cycloid. In the mathematical assessment of gears, provided that factors such as manufacturing tolerances, flexibility and thermal expansion are not taken into account, these two curves, i.e. the rolling cycloid and the reference cycloid, and therefore their parameters, are identical. The parameters of the retractable cycloids are therefore unsuitable for forming the rolling cycloid to be used by the practical gear. This has so far been aided by the empirical correction of the rolling cycloid that a rolling cycloid has been made smaller than the reference epicycloid, increased relative to the reference hypocycloid, which was then picked up in the region of the vertices and waves of the waves, as described by the German pat. Nos. 464 992 and 459 025.

These corrections have the following shortcomings in the gear train: The bearing position on the cycloid profile is due to the deflected and / of the curved part of the curve during one turn of the eccentric on only one or two outer rollers, which is caused by the fact that the individual curve segments do not have the same distances of the outer cylinders in the circumferential direction. Therefore, a small part of the entire curve must be transmitted by the whole force.

Irregular run and occurrence of oscillations, especially at higher speeds, caused by the fact that the instantaneous 258453 4 poles of the rolling cycloid and the cycloid relatives deviate from the momentum kinematically from its motion pole with the radius ez and from its solid polodium with the radius e (z + 1) IN. Bumps after passing through the S-peak when engaging the curve section with the roller.

Large lateral clearance that can not be determined in advance.

The invention overcomes these drawbacks and its object is a planetary gear with at least one planet wheel driven by an eccentric and with at least one central wheel where the jaws are engaged by means of a closed rolling cycloid on one wheel and the rollers on the second wheel and the touching points of the rolling cyclone rollers describe the reference cyclode , where both cycloids are given by the formula x = r.cos and + e.cos (β + a) + q.cos (y + a) y = r sin a + e.sin (β + a) (y + a) where x, y is the line and the ordinate of the point in the rectangular coordinate system r = a + b the sum of the radius of the base circle and the radius b of the rolling circle

Kj and hence the center of the B of the rolling circle Kj is eccentricity, equal to the distance of the center B of the rolling circle K2 and forming,

point C of the abbreviated epicycloid ZE q the constant distance forming the point C of the abbreviated epicycloid ZE and forming the

point Q equidistant EC at normal nk both curves ZE, EC and angle clamped by axis xa and center of bearing guide B of the rolling circle K2 passing through the beginning M and point A of the basic circle with the rolling circle Kj fj the angle of decay of the forming point C abbreviated epicycloids γ transmission angle, clamped normal to the guide B of the center B of the rolling circle K2 <

The object of the invention is that the value of the rolling cyclone parameter 3 is greater than the reference cycloid, and the r-value for the epicycloid-type rolling cycling r is greater than that for the cyclocyclide rolling cyclone, rather than for the reference cycloid. This shape of the rolling cycloid with respect to the reference cycloid, which is manifested by the alignment and elongation of the side of the curve, results in a very considerable increase in the length of the engagement, which can be several times the size of the existing one. In the course of the practice, shortly after the position of the apex there is a soft engagement between the curve section and the opposing roller, which continues the next course of rotation almost along the side of the curve between the top and the bottom. This even dispatch indicates that almost half of all rollers are in engagement with the respective sides of the curve and the transfer load. The trajectory of the shot is extended, that a plurality of hips engage the corresponding knobs in the touch regions slightly displaced from one curve segment to the other; can also be explained by the thoughtful projection of all the contact areas of each of the simultaneously engaging vines on one side of the curve, as shown in Figures 5 and 6. Of course, there is a certain clearance between the rollers and the curve sections that come into engagement, and the ratios given in the load transfer angular lateral clearance. 5 258453 and said load-carrying ratios become angular lateral play after rotation. 5 258453 and said load-carrying ratios become angular lateral play after rotation. 5 258453

The considerable increase in the track of the engagement compared to the state of the art leads to the fact that the gear of the same velocity can transmit substantially higher torques or, that the gear for the same purpose may be smaller. Practical experiments have shown that the path of engagement can be increased by five times the previous value and the gear according to the invention can therefore be proportionally smaller.

The cyclonic gear runs the more calmly and generally the better the equilibrium of the instant poles of both cycloids. Immediate poles of known gears are relatively close together, but they deviate from prescribed orbits. Although the instant poles of the two cycloids are greater than the conventional gears, the lateral clearance is eliminated in practice and, in this position, they circulate along a circular stationary half-point. Even from this point of view, it is obvious that the gears run substantially more evenly and calmly.

The determination of the parameters according to the invention further allows the continuous rolling of individual rollers not loaded into the loaded state, so that there are practically no shocks that occur upstream of the peak. This also contributes to a quieter run and longer life span.

In addition, it is worth highlighting the very significant reduction in friction losses which far exceeds the reduction achieved by the use of cycloid gears, which themselves have relatively low losses.

The lateral clearance, which always exists, can be referred to as the angular lateral play δ or the longitudinal axial play Au between the rollers and their points of contact on the curve disk.

Therefore, the aforementioned relationship between the parameters q, r can be mathematically expressed by this possibility of mutual rotation of the planetary wheel with the central wheel, i.e. the length lateral clearance Au as the function of the angle 0 according to the following relation: A1 - Aq - Ar.cosysins where

Au is the longitudinal lateral clearance

Aq is the difference of q values

Ar is the difference of the values ​​of the parameter ra arctg l / m - + Sco4 '

According to a further feature of the invention, the rolling cycloid may have a greater value than a reference cycloid. This in particular can compensate for clearance in the bearings and the elastic deformation of the shaft.

According to a further preferred embodiment, when determining the values ​​of the parameters raq, the difference between the values ​​of the parameter r and the difference between the values ​​of the parameter 3 and the rolling cycloidy is in the ratio (yr ^ 2-1): (1 - "Vmax"), where the reduction ratio m = e / b.

Another preferred embodiment of the planetary gear according to the invention consists in reducing the angular clearance δ, which is given by the relation d = (1 + 1 / z). (arccos Zm / arccos / -m ^ /), where m is the ratio of the reduction of the reference cycloid am ^ is the ratio of the reduction of the rolling cycloid az = a / 258453 6

2 is a cross-sectional view taken along line II-II in FIG. 1; FIG. 1 is a cross-sectional view taken along line II-II; FIG. Fig. 4 shows the epicycloid epithelium roll on the left side with hypocycloid on the right, Fig. 5 epicycloid flanks with parameters r, q modified opto-retractable cycloid, Fig. 6 equal sides of the curves as Fig. 5 after overcoming the lateral clearance and Fig. Figures 7 and 8 diagram showing the relationship:

Aq - Ar.cosgΔη = 'Yig-

According to FIGS. 1 and 2, two eccentric rolling paths 8, 8 of eccentricity e = OM and e = OM 'are arranged on the shaft J1, housed in the ball bearing 2 in the two-part housing 5 and the ball bearing 3, in the shaft 180 °. In the rolling bearings 9, 10 the curves 13, 14 with the closed cycloid profile 11, 12 are mounted on the rollers 7, j. The closed cylindrical profiles 11, 12 are rolling over the outer cylinders 15 mounted on the pins 16 which are mounted concentrically around the center axis 0 Of the housing 4, 5. In the curved discs 13, 14, a bore 17, 18 is arranged concentrically with respect to their MM, M'-M 'axis. The inner rollers 20 are mounted on the pins 19 fixed in the shaft flange 21, around the centerline 0-0. The shaft is mounted in the bottom part of the cabinet by means of ball bearings 2, 23.

Depending on the purpose of the gear, one or two of the parts 1, 6, 4, 5 can be driven.

The construction of the gears as such is known and is used with cycloidal discs of conventional dimensions. However, in Figure 2, a common half-pole N for rollers of one half-circle is indicated by what can be achieved by dimensioning the ra parameters 3 of the invention. As indicated, the instantaneous poles of the two cycloids coincide after the lateral clearance and together they run along the circular solid half-field.

Fig. 3 and 4 have been described in the introduction to the explanation of the basic concepts.

Figure 5 shows a number of epicycloid hips corresponding to Figure 3. The full circle of the extended cycloid has the parameters e, 3 and forms the geometric point of the points of contact of the roller wound with the associated rolling cycloid in the kits: all the contact bodies are projected on a single flank . Further, a broken line is represented by a cycloid flank corroborated in a known manner, which can be expressed as a reduction of the values ​​of the parameters rj, q2 compared to the parameters r, 3 of the reference cycloid. The relevant reference signs have index 2. It is obvious that the profilebok is strongly curved and steeper. The third curve marked dotted is the hip profile according to the invention, the designation of which has index 1. Each of the cycloids is marked with some striking points; common center M, vertices S, S2, S1, depressions T, T2, T1, centers B, B2, B1 of the rolling circles forming points C, C2, truncated cycloid,

Fig. 6 shows the flank profiles of FIG. 5 after the passage of the lateral play, as illustrated by the approximation of the point M by the angle δ. It is to be understood that, in the epicycloid sphincter used, the flank profile of the reference cycloid is assigned to the roller collar and remains in the plane of xy in a shape and position. Both hip profiles apply to two different curve discs, which have a certain clearance due to the necessary manufacturing tolerances and engage the reference cyclone only after the lateral clearance has passed. As shown in connection with FIG. 5, the downstream cyclodeid, indicated by the dashed line, is formed in a conventional manner and the other, indicated by a dotted line, is according to the invention.