• 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:

    公开号:SU1838692A3
    申请号:SU904830558
    申请日:1990-07-11
    公开日:1993-08-30
    发明作者:Yu Cheng；Li Lan
    申请人:Yu Cheng；Li Lan；
    IPC主号:
    专利说明:

    The invention relates to the technology of gears, gears, in particular, to a double internal gear, planetary gear with a small number of teeth raffia.
    ; The aim of the invention is to increase transmission efficiency and reduce power losses in gear bearings, in particular planetary gear transmission of the prior art, as well as] increase transmission power.
    In a planetary gear with a small difference in the number of teeth, the loads on the bearings of the satellite include peripheral force on the pitch circle of the engaged gear pair (the tangential component of the engagement force). According to the invention, peripheral forces directed respectively to the inner and outer rims of the satellite are opposite to each other, only their difference and the radial component of the engagement force act together on the bearings of the satellite, which significantly reduces the load on the latter.
    Therefore, the service life of bearings can be increased from four to tens of times, the power loss in the bearings decreases by two-thirds, and the permissible transmission load increases.
    To reduce the load on the satellite bearings, a relatively small angle a of the profile can be used for a gear pair with an involute tooth profile and a small difference in the number of teeth. In order to expand the limitation of reducing the angle a due to interference, the height coefficient h a of the tooth head can be significantly reduced (usually less than 0.5) and a positive correction of the height of the tooth head can be matched with a difference in the correction factor of zero. Of course, the correction coefficients of both internal and external gear pairs can be zero, and the profile angle a can be reduced to less than 20 ° (to 6 e ), 6 - 14 ° - a particularly important range. With decreasing angle a, the radial component of the engagement force acting on the satellite bearings decreases, the alignment increases, and the engagement efficiency increases. In a planetary gear train, the radial component of the engagement force is the main force acting on the satellite bearings. Therefore, the specified small profile angle is of particular importance.
    If the gear pairs with shortened teeth are helical, their full combination ε τ is equal to the combination of the end part ε ^ plus the combination of the gear part ε β . If it is ensured that the difference X between the correction factor Xg of the inner rim and the correction coefficient Xi of the outer rim of the gear pair is zero or its absolute value is not more than 0.1, the gearing efficiency can usually be increased by decreasing ε ^.
    After decreasing ε ^, ε β of the helical gear increases to ε ν > 1 (usually 1). In some unusual circumstances, when the effect of multiple contact of the teeth of the internal gear pair with a small difference in the number of teeth should be taken into account, it is advisable to make ε Γ > 0.7. This solution can also be used to increase the gearing efficiency of the external gear pair. For an external gear pair, h a can be reduced to less than 0.5 - 0.1 and at the same time ε ^ can be increased (for example, by increasing β and the width of the teeth and decreasing the modulus, etc.) to make ε Γ 1. A detailed analysis of the internal gear pair is as follows: calculation methods ε ^ π g ^ are known. ε ^ can be reduced in the same way as the height coefficient h a of the tooth head in order to avoid possible interference of the profile when the difference in the number of teeth between the inner and outer crowns is very small. Optimum parameters should be selected in the following range:
    | X | <0.1, preferably X = Xg - Xi = 0. Xi> 0, Xr 0; helical pitch angle β = 1 ~ 14 ° (helical wheels) and β = 25 ~ 60 ° (chevron wheels); when the difference in the number of teeth Zd = 1 h a = 0.06 l / 0.2; when Zd = 2 h a = 0.2 ~ 0.35, h a <0.2 is also acceptable; when Zd = 3 or 4 h a usually not more than 0.5; the angle of the profile, as already mentioned, can be reduced, but it is preferable that it is between 14 and 25 °, when the difference in the number of teeth 1.
    After decreasing h a , manufacturing accuracy should be accordingly increased.
    If helical gears are used in both gear pairs of a gear, the helical lines of both gear pairs should have the same direction; or both left, or both right, to compensate for axial forces acting on the bearings of the satellite. If gears with straight teeth are used, the optimum difference in the number of teeth is 4, 5 or 6, h a - 0.35 ~ 0.6, the correction coefficient must correspond to! X | <0.05, preferably X = 0.
    In Figs. 1 and 2, a cross section of a two-crown satellite is shown; in FIG. 3 - gear with a two-crown satellite.
    The gear train contains input 1 and output 2 shafts, a carrier made in the form of an eccentric 3, mounted on it by bearings 4 and 5, a twin-mounted satellite 6 and two central wheels 7 and 8. The satellite 6 has two crowns 9 and 10, a faceplate 11, coaxially put together. The crown 9 is mounted coaxially outside the crown 10 and both are fixed on one side of the faceplate 11.
    The common axis of the crowns 9 and 10 is the axis of the satellite 6. The bolt 12 is designed to connect them. Other connection methods may also be used. One of the crowns can be made intact with the faceplate to simplify manufacturing. If this is possible from the point of view of wheel manufacturing technology, both gears can be made integral with the faceplate.
    flpyrne methods for joining two crowns can be used if they allow
    Get the characteristics of the satellite according to the invention.
    The vertical projections of the tooth width Ϊ β of the two gear rims of the satellite 6 on their common axis should coincide with each other at one point, i.e., the distance between the projections of the width of the teeth of both rims in the axis direction should be zero. £ If the distance is not equal to zero, in a practical production process it should be no more than 3/4 of the minimum Width of the tooth of the satellite 6, preferably (ie more than 1/10. At least the Teeth width of both crowns 9 and 10 of the satellite 6 partially coincides in the radial direction , and their projections onto the common axis coincide (by themselves.
    The ring gears 9 and 10 of the satellite 6 can be made with both external and internal teeth. Crowns with external teeth are preferable to reduce rimming. In the embodiment of FIG. 3 both ring gears 9 and 10 - with external teeth. The central wheel 7 with internal teeth is made integral or mounted with a low-speed output shaft 2. The shaft 2 is mounted on the right housing I3 using low-speed bearings 14 and 15.
    The central wheel 8 with internal teeth is fixed on the left housing 16. The wheel 8 can be made separately and then connected to the housing 16. The eccentric 3 is made integral with the input shaft 1 and mounted in the left housing 16 and the output shaft 2 using high-speed bearings 17 and 18. The transmission includes also oil seals 19 and 20, a mounting bolt 21. It should be noted that the position of the satellite 6 shown in FIG. 3 is the position when it moves to its highest point. The distance between the inner surface of the outer rim 9 of the satellite 6 and the outer surface of the driven central wheel 7, which is meshed with the inner rim 10 of the satellite 6 in the case of the shifted center of the eccentric 3 in the highest position, i.e., the distance b shown in FIG. 3, should be more than double eccentricity a.
    The counterweight and other parts commonly used, but not having special meaning here, are not shown in FIG. 3.
    The gear transmission operates as follows.
    If the eccentric 3 rotates at high speed, it drives the satellite 6, which is meshed with the central wheels 7 and 8. The central wheel 7 drives the output shaft 2 in slow rotation.
    The parameter optimization method in the invention can realize internal engagement with a difference in the number of teeth 1 or 2 when all the restrictive conditions are met to obtain a high engagement efficiency. For example, if you select in one of the gear pairs the profile angle a = 14.5 °, β = & °, the number of teeth of the wheel with external teeth Ζι = 87, the number of teeth of the wheel with internal teeth Z2 = 89, Xh = X 2 = 0, h a = 0.1, tooth width b = 80 mm, module m = 3.5, then according to the well-known calculation method we get = 0.26, = 0.76, ε ν = 1.02. The value of the parameter of the indicator of interference overlap Gs = 0,0172. When used for a planetary gearbox with a reduction number i = 1000, its loss is only 9% of it according to the angular correction method. The gearing efficiency of the gear pair being meshed is approximately 0.9916.
    If there is a pre-reduction stage before a planetary gear with a twin-crown satellite for the formation of a combined transmission, further advantages can be achieved. Their losses in engagement and bearing, as well as hydraulic losses are reduced, strength conditions are improved, therefore, the allowable load increases, temperature increases, vibration and noise are reduced and the volume can be reduced. Since a planetary gear with a small difference in the number of teeth has the advantage of a large output torque acting on its high-speed parts (for example, bearings, etc.) and a planetary gear with a two-crown satellite is usually eccentric, so it is difficult to achieve its dynamic equilibrium. In this case, a decrease in the input speed is quite favorable for increasing the efficiency and improving the transmission quality. A high planetary gear speed coefficient with a small difference in the number of teeth can significantly reduce the contradictions between the crime rate coefficient and volume, strength and efficiency. The optimal gear combination is as follows: the crest consists of a planetary gear with a central wheel with external teeth. The main reduction stage is a planetary gear train with two veins
    Ί new satellite. Good results can be achieved for other planetary gears with a small tooth difference if they are equipped with a pre-reduction stage, in particular a pre-reduction stage consisting of a planetary gear with a central wheel with external teeth.
    权利要求:
    Claims (8)
    [1]
    Claim
    1. A gear transmission containing input and output shafts, a carrier made in the form of an eccentric mounted on it by means of bearings a two-crown satellite, two central wheels, one of which is stationary, the other is driven, forming two external and internal gear pairs with the satellite, characterized in that at least one gear pair has shortened teeth with a head height coefficient of not more than 0.5, the absolute value of the difference of the correction coefficients X is not more than 0.1, preferably zero, the coefficient The nti Xi and X g of the crown correction in a gear pair with shortened teeth are preferably zero, in gear pairs made up of helical gears, two helical gears with internal teeth have an inclination of the same direction, two helical gears with external teeth also have an inclination of the teeth of the same direction, preferably, both gear pairs have shortened teeth.
    [2]
    2. Transmission by π. 1, different from me. that the angle β of the helical line on the pitch circle is / 3 = 1 ° ~ 14 ° when the gear pair with shortened teeth is composed of helical gears, and β = 25 ~ 60 ° 'when the gear pair is composed of chevron gears.
    [3]
    3. The transmission according to claim 1, characterized in that its coefficient of height h of the tooth head is 0.06 - 0.2 with a difference in the number of teeth equal to one, not more than 0.35 with a difference in the number of teeth equal to two, and not more than 0.5 with a tooth difference of three or four.
    [4]
    4. Transfer pop. 1, characterized in that said gear pair is composed of spur gears, the difference in the number of teeth is 4 and 6, the height coefficient h of the tooth head is 0.35 - 0.6, and the absolute value of the difference in the correction coefficients Xi and Xg does not exceed 0. 5.
    [5]
    5. The transmission according to claim 3, which is clear in that its profile angle a is 6 ~ 20 °, more preferably 6 ~ 14 °, and the profile angle a is preferably 14 ~ 25 °, if the difference in the number of teeth in a gear pair with shortened teeth is equal to one.
    [6]
    6. Transmission pop, 1, characterized in that the distance between the inner surface of the outer rim of the satellite and the outer surface of the driven central wheel, designed to interact with the inner rim of the satellite, is chosen at least double eccentricity and eccentric, and the difference in the number of teeth in gear in pairs, preferably no more than four are selected.
    [7]
    7. The transmission according to claim 6, which is clear in that the vertical projections of the width of the teeth of two gear ring gears of the satellite on their common axis are at least partially aligned, both gear ring gears have either external teeth, or both internal teeth, and the distance between the projections of the Central lines of the width of the teeth of these two gear rims on their common axis is preferably zero.
    [8]
    8. The transmission according to claim 6, which is distinguished by the fact that it contains a preliminary reduction stage, which is preferably a planetary gear with a central wheel with external teeth.
    = .. 1..
    Fig.Z
    editor-J— Compiled by G. KuznetsovaTehred M. Morgenthal. Corrector N. Kravtsova
    аказ 2919 Circulation Subscribed
    VNIIIPI of the State Committee for Inventions and Discoveries under the State Committee for Science and Technology of the USSR 113035, Moscow, Zh-35, Raushskaya nab., 4/5
    Production and Publishing Plant Patent, Uzhgorod, Gagarin St. 101
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    同族专利:
    公开号 | 公开日
    DE69017106T2|1995-07-06|
    EP0408314A2|1991-01-16|
    AU5891290A|1991-01-17|
    JP2834286B2|1998-12-09|
    DK0408314T3|1995-06-26|
    PT94652A|1992-02-28|
    BR9003319A|1991-08-27|
    EP0408314B1|1995-02-22|
    AU634253B2|1993-02-18|
    EP0408314A3|1991-05-02|
    CN1031363C|1996-03-20|
    CN1048744A|1991-01-23|
    CA2020820A1|1991-01-12|
    ES2069692T3|1995-05-16|
    HUT54782A|1991-03-28|
    AT118865T|1995-03-15|
    CS343790A2|1991-12-17|
    JPH03117748A|1991-05-20|
    DE69017106D1|1995-03-30|
    HU904164D0|1990-12-28|
    引用文献:
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    WO2006038901A1|2004-10-04|2006-04-13|Lykhovyd Yuriy M|Planetary gear transmission|
    RU2677952C1|2018-03-29|2019-01-22|Виктор Владимирович Становской|Planetary mechanism and planetary transmission based thereon|US2049696A|1935-03-07|1936-08-04|Erhard A M Fliesberg|Transmission gear|
    US2409696A|1943-03-06|1946-10-22|Union Switch & Signal Co|Remote control system|
    CH457295A|1965-07-29|1968-07-31|Centre Electron Horloger|Device for transforming the oscillating movement of an electromechanical watch resonator|
    US3427901A|1966-10-14|1969-02-18|Ernest Wildhaber|Gearing|
    US3451290A|1967-04-03|1969-06-24|Ernest Wildhaber|Gear drive with axially overlapping gears|
    GB1198737A|1967-08-30|1970-07-15|Muneharu Morozumi|Addendum Modified Involute Internal Gearing|
    US4446752A|1981-04-23|1984-05-08|Advanced Energy Concepts '81, Ltd.|Epicycloidal gears and gear tooth arrangement therefor|
    JPS591952U|1982-06-28|1984-01-07|
    ES8700397A1|1985-12-23|1986-10-16|Coop Goizper S|Improvements made to speed reducers|
    CN1009749B|1987-07-18|1990-09-26|湖南省机械研究所|Mixed planetary transmission mechanism and apparatus of involute gears with small tooth difference|JP3280715B2|1992-08-31|2002-05-13|大治郎 中村|Tightening screw|
    KR200208549Y1|1999-04-30|2001-01-15|최병철|Transmitting Unit|
    US6416438B1|1999-04-30|2002-07-09|ByongChol Choi|Transmitting unit|
    GB2384532A|2002-01-25|2003-07-30|Eaton Corp|Arrangement of drive shafts in a change gear transmission|
    ITUB20153713A1|2015-09-17|2017-03-17|Samp Spa Con Unico Socio|EPICYCLOID PRECISION REDUCER|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    CN 89104790|CN1031363C|1989-07-11|1989-07-11|Combined transmission with double-layer gears|
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