• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    In the joint, the raceways of the tulip element have the shape of a torus. The ratio of the maximum distance between the axis of the tulip element and the axis of the tori defining the raceways to the radius of said tori is between 1/4 and 3/4. This results in a considerably improved mechanical efficiency and consequently in a reduced opposition to sliding. Application of the joint to automobile vehicle transmissions.
    公开号:SU1075962A3
    申请号:SU802904197
    申请日:1980-04-01
    公开日:1984-02-23
    发明作者:Александр Орэн Мишель
    申请人:Гланзер Списер (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to vehicle transmissions, in particular, to cardan gears and hinges of these gears. A three-hinged hinge of equal angular velocities is known, which contains a crossbar mounted on one of the shafts by means of a cylindrical hub with spikes evenly spaced around its circumference and a fork connected to the other shaft, a sleeve mounted at one end, the cylindrical surface of which has a groove, axially evenly distributed around the arm and circumferential rolling tracks of circular cross-section, and spherical rollers located in the grooves, mounted by means of needle-like rollers on the OF DATA thorns l. A disadvantage of the known hinge is the low efficiency caused by large mechanical losses. Comparative laboratory measurements showed that the hinges with a triangular cross-piece of the described type, with their correct design, lead to the smallest mechanical losses under the action of a rotating torque — these losses are about 5 / 10,000 for an angle of 5 and 2 / 10,000 for a working angle equal to 3 °. And against, the same measurements show that mechanical losses increase rather rapidly with increasing angle. For example, a working angle of 10 ° corresponds to a mechanical loss of 25/10000, counter-slip becomes correspondingly more significant, with the triangular hinge crosspiece loses thus partially its advantage over other types of telescopic connections. The aim of the invention is to increase efficiency. The goal is achieved by the fact that in the hinge grooves are made toroidal, and the ratio of the maximum distance between the longitudinal axis of the fork and the longitudinal axis of the grooves to the radius of the toroidal surface of the latter is in the range of 0.25-0.75. FIG. 1 shows a partial J section along the axis of a classic hinge with a triangular cross; 2, the diagram corresponding to the hinge of FIG. one; in fig. 3 is a section along the axis of the proposed hinge in FIG. 4 is a section A-A in FIG. 3} in FIG. 5 is a diagram corresponding to the hinge of FIG. 3 and 4 / in FIG. g - the same, the second version of the position of the parts of the hinge. The synchronous hinge 1 (Fig. 1) contains a fork 2 and a triple-hub knot (triangular cross) 3 fixed on the pierced end of the transmission shaft 4 with the longitudinal axis Z-Z. Fork 2 has a sleeve 5 with the axis X-X and the groove made inside. From this sleeve there are three protrusions 6, the adjacent longitudinal edges of which are designed in such a way as to determine between two protrusions of a circular section 7 of the circular section, which are equally spaced (equal angles) from one another. The Y-Y axis of each raceway 7 is linear and parallel to axis X-X. Fastening: triangular cross. on shaft 4 it is carried out by means of a cylindrical hub 8 with a groove made inside it. Three sleeves or 9 spikes of circular cross section extend from this hub in the radial direction. On each spike 9 there is a roller 10 with an outer active surface 11 of spherical shape. Between the spike 9 and the roller Yu, a needle bearing 12 is installed, held axially by means of a safety device formed by the respective washers 13 and 14 and a retaining ring 15 which fits into the recess provided at the end of the spike 9. The triangular cross 3 is axially free inside the plug 2. Outside, the plug 2 has a circular shape. The impermeable elastic of the harmony 16 is fixed at one end on the surface of the sleeve 5, surrounds the protrusions 6, then fits into the machined grooves 17 for fastening provided on the shaft 4. The harmonica 16 together with the fork 2 limits the impermeable sheath 18, which delays the lubricant and protects the mechanism. When the angle of the shaft 4 formed by the axis ZZ by the XX axis is small, the axial sliding movement of the triangular cross under the action of the torque is carried out by simple rolling, on the one hand, of the rollers on the spikes by means of the needle bearing and, on the other hand, the spherical surface of the rollers along the raceways forks. Under these conditions, the reciprocating motion of the rollers on their spikes 9, is the result of the rotation of the hinge at an angle, and the general translational motion of all three rollers, resulting from the sliding of the triangular cross, is carried out without significant resistance even with a large value of the transmitted moment rotation FIG. 2 schematically shows the position of the roller 10 when the scarve 1 is operating at a predetermined angle between the axes Z-Z and X-x. Rolling of the roller in the plane P in the preferred direction is prevented by the guide track 7, which causes this roller to move along the Y-Y axis, i.e. at the drift angle oi, formed by the plane P of the roller with the Y – Y axis of the track 7 relative to its natural rolling direction. This demolition corresponds to the lateral sliding of the roller, which is carried out simultaneously on the one hand, by the spherical surface of the roller and by rolling and, on the other hand, rotating the roller relative to its spike 9. As the roller is mounted on a needle bearing, it is assumed that it rotates relative to the spike 9 absolutely free. Consequently, the sliding movement along the track can only be carried out in the plane passing through the thorn axis. If we denote 0 the distance between the center O of the triangular cross and the center 0 (the roller, and we denote r and the distance between the axes X-X and YY, and the expression for the elementary slip is, dn P006-T- ot (P J COS "The hinge (Fig. 3 and 4) differs substantially from hinge 1 (Fig. 1) in only two aspects. First, the central axis YY of each raceway 7 of the fork 2 is an arc, so that these raceways have toroidal shape. The radius R of each torus is much larger than the maximum value of r the distance between the axis X-X and the arc YY. As a result In this design, the free axial sliding of the triangular crossings 3 in the fork is accompanied by the sliding of the rollers on their spikes, regardless of the size of the angle between the pulses of the ZZ and X. X. To ensure this sliding of the rollers relative to their spikes increased compared with the known construction (Fig. 1), the length of the needle bearing 12 exceeds the length of the rollers, which is the second difference between the hinges, In the present embodiment, the accordion 16 is fastened on the cylindrical case; 19, which surrounds the projections b of the fork 2 at the open end after days FIG. 5 schematically shows the position of the roller 10 / when the center O of the triangular cross is in its middle axial position at point 0 of axis X-X, which corresponds to the maximum distance r defined above, as in the case shown in FIG. 3, when the hinge 1 is angled. FIG. 6 shows a similar scheme, corresponding to the displacement h along the axis X-X between points O and 0. Angle 0, formed by the plane P of the roller and the tangent to the trajectory Y, -Y of track 7, is less than the angle α; . With a good approximation, this angle can be expressed by the following relationship:, 4 (e) - (b) .tgccA. (2) The elementary slip corresponding to the increment d ct of the angle oi is given by an expression similar to expression (1) of the form, which has the following form: l, .pd (... d4 -Ht -H) You can see that relation (1) is obtained if to accept R k, which is true, since rectilinear doroyks 7 can be considered as tori with an infinite radius of curvature. For h O (Fig. 5), the ratio of the elementary slip of the proposed hinge to the elementary slip dp of the known (Fig. 1) (Recorded as follows way: iLt- BillM i - ,. n (4) When h t О, when considering a roller with an angle oi and a roller with y The glom ei turns out that only an average value in absolute values of co; the corresponding angles Q vi 62 is significant for slip losses. It can be shown that (if) 4. |. Comparing this ratio with the given ratios (2) and (3), it can be seen that the mechanical losses are of the same magnitude as for hO, i.e., relation (4) is variable. Thus, the mechanical loss is reduced in the ratio 1 - -. In other words, the elementary slip operation and, therefore, the elementary mechanical loss, which is proportional to this work, can be much lower for any angle L when using the proposed hinge 1 (Fig. 3). As a result, the ease of sliding of each roller is achieved when the hinge is at an angle, thereby providing better insulation, for example, the cabins of cars from the engine of the unit, which is a source of vibrations, and less friction sensitivity, which means greater comfort, in particular significant working coal. For example, for a ratio. 1 The resistance will be obtained by placing the roller along its track and then decreases by about 50%, the direct result of which is a very significant gain in terms of freedom of sliding under the influence of the rotating moment and, consequently, convenience. Theoretically, it is possible to distinguish the ratio - up to 1 and, under this condition, the mechanical losses would be practically zero. However, beyond a certain value, the slip resistance does not have any unpleasant effect, but. on the other hand, by increasing the ratio to 1, the possibility of axial sliding of the proposed hinge can be significantly reduced. - That is why, depending on the specific application, taking into account the most common size of the working angle and the axial slip length required for a triangular cross, the ratio will usually be limited to 1/4 to 3/4. Other advantages are achieved by this improvement of the hinges with a triangular cross. In the case where two hinges with a triangular cross each of a known type, shown in FIG. 1 - mounted at the ends of the swinging transmission shaft, the shaft naturally contacts at the end of the stroke with the inside of one of the hinges with a triangular cross-shaped and produces axial thrusts caused by the vibration of moving and driven parts. Conversely, when using one or two hinges 1 (FIG. 3) with annular rolling paths, the rocking shaft tends to self-center relative to the forces, while retaining the free spaces equal to each of these ends. On the other hand, when the centering is triangular the crosses with respect to the axis of the roller 10 approach the center of the triangular cross, and at the same time the distance h increases until it hits the protrusion 20 of the spikes 9, which limit the sliding of the rollers in the direction of the middle. This feature can be advantageous when used for an axial safety lock. Thus, loss of control of the rollers at the ends of the projections of the fork can be avoided without introducing any additional locking devices, and therefore simple. economical way. For this, it is sufficient that the length of the raceways 7 is sufficient so that when the hinge 1 (Fig. 3) is stretched, the rollers 10 rest against the protrusions 20 before reaching the open end of these raceways. In this case, in order to avoid the noisy contact of the rollers with the projections 20 of the triangular cross between each roller and the corresponding protrusion, a spring washer such as a corrugated washer or a disc spring disk, or an elastomer ring can be installed. At this point, a corrugated snap ring can also be installed, which can be inserted after the assembly of the triangular crosspiece within the plug (such a cushioning part is not shown). The invention makes it possible to increase the efficiency of the hinge.
    / 2 A
    9 fO 19
    5
    AA 15 9 20
    1e
    W
    12
    FIG.
    .-...
    FIG. 6
    权利要求:
    Claims (1)
    [1]
    A THREE-SHAPED HINGE OF EQUAL / ANGULAR SPEEDS, comprising a cross mounted on one of the shafts by means of a cylindrical hub with spikes evenly spaced around its circumference and connected to another shaft by a fork mounted with a clearance relative to the cross and having a sleeve at one end, the cylindrical surface of which has three grooves evenly spaced around the circumference in the axial direction and forming raceways of circular cross section, and spherical rollers located in the grooves mounted in the middle stvom needle bearings on said spines, characterized in that, in order to increase efficiency, toroidal grooves formed, and the ratio of the maximum distance between the longitudinal axis and the longitudinal axis of the plug. grooves to the radius of the toroidal surface of the latter is within §, 0.25-0.75.
    FIG. 1
    SU, m 1075962>
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    同族专利:
    公开号 | 公开日
    US4338796A|1982-07-13|
    GB2045397A|1980-10-29|
    GB2045397B|1982-11-24|
    DE3013182A1|1980-10-09|
    JPS6258403B2|1987-12-05|
    IT1128390B|1986-05-28|
    DE3013182C2|1984-04-19|
    FR2453313A1|1980-10-31|
    IT8067521D0|1980-04-03|
    ES8101214A1|1980-12-01|
    BR8002001A|1980-11-25|
    ES490127A0|1980-12-01|
    FR2453313B1|1982-10-29|
    JPS55135230A|1980-10-21|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE7120705U|1971-12-16|Automobiles Peugeot|Universal joint coupling|
    US1834906A|1929-02-27|1931-12-01|Cleveland Steel Products Corp|Universal joint|
    FR1175941A|1957-06-11|1959-04-02|Rech S Ind Soc Et|Constant velocity joint|
    US3125870A|1960-07-04|1964-03-24|Universal joint for transmission of rotational movements |
    US3593541A|1968-04-23|1971-07-20|Toyo Bearing Mfg Co|Constant velocity universal joint|
    FR2050826A6|1969-06-26|1971-04-02|Peugeot & Renault|Universal drive coupling|
    US3818721A|1972-09-15|1974-06-25|Wahlmark Systems|Constant velocity universal drive|
    FR2207554A5|1972-11-17|1974-06-14|Glaenzer Spicer Sa|
    US3877251A|1973-06-15|1975-04-15|Wahlmark Systems|Universal joint system|
    FR2271444B1|1974-05-13|1977-10-28|Glaenzer Spicer Sa|
    FR2286312B1|1974-09-27|1976-12-31|Glaenzer Spicer Sa|
    GB1536885A|1976-04-03|1978-12-29|Rolls Royce Motors Ltd|Constant velocity ratio shaft coupling|
    FR2394711B1|1977-03-04|1981-02-06|Glaenzer Spicer Sa|
    FR2382614B1|1977-03-04|1981-02-06|Glaenzer Spicer Sa|FR2523236B1|1982-03-15|1987-03-20|Glaenzer Spicer Sa|HOMOCINETIC JOINT WITH AXIAL RETAINED TRIPOD|
    FR2525306B1|1982-04-20|1984-06-22|Glaenzer Spicer Sa|
    FR2538057B1|1982-12-16|1985-04-12|Ouest Cie|
    DE3641393C1|1986-12-04|1988-03-17|Daimler Benz Ag|Bellows|
    DE3832002C2|1987-10-01|1991-01-17|Glaenzer Spicer, Poissy, Yvelines, Fr|
    JPH01142511A|1987-11-27|1989-06-05|Mitsubishi Cable Ind Ltd|Method for assembling connector for multi-fiber optical cable|
    DE19819615C2|1998-05-04|2001-03-29|Gkn Loebro Gmbh|Constant velocity sliding joint with disassembly protection|
    US6685572B2|1998-07-22|2004-02-03|Ntn Corporation|Power transmission mechanism|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    FR7908452A|FR2453313B1|1979-04-04|1979-04-04|
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