• 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:
    Gearing mechanism particularly for changing the relative angular position of two parts. A crown or ring gear with internal toothing is pressed from a sheet forming one arm, and a spur gear with external toothing is pressed from a sheet forming a second arm. The connection between the first arm and a hub of the crown gear and between the second arm and the spur gear is accomplished by bridges formed at tooth gaps of a width of at least of one pitch of the toothings. The mechanism can be used with collapsible seats of vehicles, for head rests, for the raising and lowering of windows, in textile machines, childs' vehicles, in furniture, agricultural machines, and the like.
    公开号:SU1450819A1
    申请号:SU837773209
    申请日:1983-11-21
    公开日:1989-01-15
    发明作者:Ян Бабак
    申请人:Азнп Млада Болеслав (Инопредприятие)；
    IPC主号:
    专利说明:

    four
    cl
    about
    00
    (X)
    The invention relates to planetary gears and can be used in the automotive industry, as, for example, in the case of lowering gears; mechanisms of seat backs, armrests and window lowering mechanisms, in mass transport, in the design of road and agricultural machines, trailers in furniture and textile industry, etc.
    Planetary mechanisms are known, in which the crown wheel and the satellite {лит lit are formed from the same workpiece J together with the shoulder and are made by a special precision cutting technology. The transfer of the load from the shoulder of the gear i is accomplished by means of bridges, which form I c along the entire contour of the teeth. The thickness I on the shoulder sheet of this design depends on the size of the bridge and on the required j gear width, I which is limited not only by the strength of the bridge, but also by the need to prevent axial decoupling of the teeth in the case of force transfer. This danger is also relevant, e because the applied technology in the area of the tip of the teeth results in compression of the material, as a result of which the full width of the gearing cannot be used in this area. : Increase in the required gearing gear for the first gear at the point of strength, specified from point i, of the bridge
    This KOHCTpyKujin causes an increase in shoulder thickness I, which, in turn, increases the mass of the mechanism and inexplicably increases its strength. The connection of the gear wheel to the shoulder in a known construction can also consist in the fact that the bridge is reduced to zero and the transfer of the load from the shoulder to the gear wheel is carried out by means of beam-like bearing zones, which arise as a result of a cone-shaped notch in the Tud region, each depression between the teeth As a result, on the other side of the shoulder, a narrow, supporting element of a triangular shape is formed, connecting each tooth with the shoulder. These narrow bearing elements are not advantageous from the point of view of strength, since in addition to the shear load in their root part, there is also a more substantial additional bending load. The requirement for a narrow cavity between the teeth to deepen by itself causes a sharper shape of the tooth profile in its leg with an unfavorable internal angle at the apex with a small radius of curvature, resulting in increased requirements not only for the quality of the material of the extruded product, but also for the manufacture of a pressing tool , thereby reducing its service life (Patent C1) 1A No. 4184714, cl. A 47 C 1/025, 1980).
    The purpose of the invention is to simplify the manufacturing technology of the mechanism by using stamping in the manufacture of gears from one workpiece.
    FIG. 1 shows a shoulder equipped with an internal gear with internal gearing (view P in FIG. 2); in fig. 2 shows section A-A in FIG. one; in fig. 3 - shoulder, equipped with a satellite with external gearing (view W in Fig. 4); in fig. 4 shows a section BB in FIG. 3; in fig. 5 - toothed planetary gear, used as an adjustable seatback hinge, longitudinal section; in fig. 6 is a sectional view BB in FIG. 2; in fig. 7 - section G-Y in FIG. four.
    IG)
    The flat central wheel with internal gearing 14 has a shoulder 1, a stamped hub projecting partially or completely beyond the plane of the shoulder 1 and having no functional purpose. Inside the hub 3, a hole 6 is removed. The hub 3 is connected to the shoulder 1 by means of supporting bridges 5 formed in the places of the enlarged hollows 4 between the teeth. The enlarged cavity 4 between the teeth, created at least in one place of the internal gearing 14 of the central wheel 2, has 13 1 tons of ha at the level of the working height h of the teeth. This width is equal to or bat than the pitch t of the teeth 13, measured at the same diameter. The pitch t is determined by the pitch angle Ч formed by the axes of symmetry from two adjacent teeth in 13, not adjacent to this depression. The axis of symmetry C passes through the center S | central wheel 2 or center S of satellite 8c Enlarged depressions 4 and 11 between the teeth, and demanding the required width of hectares, are formed as a result of excluding one or several teeth 13 on the logically (as in the case of Hecyiwx bridges 5 of the hub 3), axially arched shoulders of carrying bridges 9 with width q must lie under circumferential 15 or internal gear teeth of the p cavities of external gear 14, From the lateral clearance diagram of the trochoid engagement, it follows that the absence of some of the teeth of the external or internal gear Q There is practically no effect on the size of the side clearance, since the load is automatically transmitted by the next pair of teeth. Bearing in mind the specific geometry and configuration of the gear teeth, this does not always have to be the adjacent tooth. To maintain the nature of circular relative rolling motion from a kinematic 2 точки point of view, it is sufficient if at least three teeth are at engagement with a corresponding mutual distance, which is also the limiting condition of using 25 of the invention of the bearing bridge 5 of the hub 3 has a width and . To prevent possible collision with the teeth 13 of the satellite 8, axially removed shoulders, forming a supporting bridge 5, lie above the circumference of the hollows to the internal gear 14 “of the central wheel 2. Given that the internal gear 14 of the central wheel 2 5 is pressed directly in the shoulder 1, I carry; And this bridge 5 is transferred to the hub 3 only partial load. When the rivet gearing 15 of the satellite 8 is attached to the shoulder 1 in order to avoid a possible collision with the teeth 13 of the central wheel 2.
    FIG. Figure 4 shows the shoulder 7 with negative bridges when the depth of punching of the satellite 8 in the shoulder 7 exceeds the thickness of the shoulder 7. This version of the satellite 8 with external gearing is possible only in favorable cases from the point of view of strength, since unlike the supporting bridges 5 The hubs 3 bearing bridges 9 transfer the entire load to the shoulder 7. Increasing the carrying capacity of the bridges 9 can in many cases be achieved by adding another bridge 9, which is sufficient, due to the nature of the load and the relatively large cross-section of the supporting bodies. The bearing bridges 5 and 9 of the hub 3 and satellite 8 are correspondingly placed symmetrically along the contour of the gear wheels, especially in the version with negative bridges,
    权利要求:
    Claims (3)
    [1]
    Invention Formula
    1 A gear mechanism mainly for a seat with an adjustable back, containing interacting gears, one of which is flat.
     J, Cl JX llJfc i-TJ Jl, .1.J -fc- «-« - ---
    in the holes 12 further protection- 40 "" central wheel with internal
    A concentric fit sheet for eccentricity, which also conveys the same type of load as supporting bridges 5, can significantly reduce the thickness of arm 1 and use the minimum number of enlarged cavities 4 between the teeth and supporting bridges 5.
    FIG. 3 and 4, the arm 7 is shown equipped with a satellite 8 with external gearing 15. The satellite 8 is also partially or, as shown in the drawing, completely protrudes beyond the plane of the arm 7 and has an opening 10 in its middle part. The arm 7 is connected to the satellite 8 is by means of non-bridge 9, created in places with enlarged cavities 11 between the teeth. Ana-clutch, another satellite with external engagement, each of which is formed from a single piece in conjunction with the sides having a leash that limits the center distance of the gearwheel core by the amount of eccentricity, so as to simplify the manufacturing technology mechanism, at least one of the wheels has at least one cavity in the number of teeth, whose width in the working height zone is equal to or greater than the tooth pitch measured at the same diameter and is determined by the angular step limited with no symmetry E x abutment teeth to the cavity, and in place of depressions are formed between the teeth of bearing bridges.
    50
    Logically (as in the case of Hecyiwx bridges 5 of the hub 3), the axially arched shoulders of the supporting bridges 9 having width q should lie under the circumference K p of the depressions of the outer teeth K p of the depressions of the external gearing 15 of the satellite 8 to avoid a possible collision with the teeth 13 central wheel 2.
    FIG. 4 shows the shoulder 7 with negative bridges, when the depth of punching of the satellite 8 in the shoulder 7 exceeds the thickness of the shoulder 7. This version of the satellites 8 with external gearing is possible only in favorable cases from the point of view of strength, since in contrast to the supporting bridges 5 hub 3 bearing bridges 9 transmit to shoulder 7 the entire load. Increasing the bearing capacity of the bridges 9 can in many cases be achieved by adding another bridge 9, which is sufficient due to the nature of the load and a relatively large section of the carrying arms. The bearing bridges 5 and 9 of the hub 3 and the satellite 8, respectively, are arranged symmetrically along the contour of the gear wheels, especially in the version with negative bridges,
    Invention Formula
    1 A gear mechanism mainly for a seat with an adjustable backrest, containing interacting gears, one of which is a "" central wheel with an internal
    gearing, another satellite with external gearing, each of which is formed from one part together with sides having a lead, limiting the center distance of the middle of gear wheels by the amount of eccentricity, characterized in that, in order to simplify the manufacturing technology of the mechanism, at least one of the wheels has at least one cavity in the teeth row, the width of which in the working height zone is equal to or greater than the tooth pitch measured at the same diameter and determined by the angular step bounded by the axes the symmetry is not adjacent to the trough of the teeth, and the bearing bridges are formed in the place of the trough between the teeth.
    [2]
    2. The mechanism of pop. 1, characterized in that the supporting bridge of the central wheel is formed by an axially curved shoulder lying above the circumference of the depressions of the teeth of the central wheel.
    [3]
    3. The mechanism according to p, I, O tl and h a-y i and with the fact that the supporting bridge of the satellite is formed by an axially curved shoulder, lying under the circumference of the satellite's teeth.
    qjus.l
    eight
    15
    eleven
    but
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1450819A1|1989-01-15|Gear mechanism ,particularly, for seat with adjustable back
    US4668013A|1987-05-26|Hinge structure for seat with adjustable backrest
    US4882943A|1989-11-28|Backlash-free reducing mechanism, particularly usable for setting various parts of a seat of an automobile vehicle
    US4302047A|1981-11-24|Hinge mount for seats having adjustable backrest
    EP2278190B1|2013-01-23|Deformation crown gear speed reduction mechanism
    EP1663702B1|2009-10-28|Angular position adjusting mechanism
    US7585248B2|2009-09-08|Hinge mounting for an adjustment device of a motor vehicle seat
    US4275924A|1981-06-30|Hinge mount having a wobble gear adjuster for a tiltable seat back of a motor vehicle seat
    CN103775601A|2014-05-07|Differential transmission device
    JP2008545927A|2008-12-18|Crown gear and differential device with crown gear
    EP2115326A1|2009-11-11|Spur gear differential
    KR200485637Y1|2018-02-02|Load rating optimised bevel gear toothing
    US5531504A|1996-07-02|Articulated armature for seats with adjustable backs, in particular for motor vehicles
    JPH05272597A|1993-10-19|Epicyclic gear train planet carrier
    DE102011087579A1|2013-06-06|Spur gear differential for use in drive train of e.g. motor vehicle, has sun wheels, and rotational torque-transferring connection formed between inner surface of axial drive wheel and radial peripheral surface of planetary carrier
    GB1575340A|1980-09-17|Pulleys and gear wheels
    GB2049027A|1980-12-17|Hinge arrangement
    AU603661B2|1990-11-22|Reinforced double toothing planet wheel for a micrometric articulation used more especially in vehicle seats
    DE102012213398A1|2014-02-06|spur gear
    US20070234536A1|2007-10-11|Casing for a hinge attachment of a car seat and method for its manufacturing
    US3960400A|1976-06-01|Lightweight railway wheel
    US5704870A|1998-01-06|Angular adjustment mechanisms
    US1730184A|1929-10-01|Differential gear
    US5496225A|1996-03-05|Vehicle seat articulations
    US10605346B2|2020-03-31|Deceleration device
    同族专利:
    公开号 | 公开日
    GB2132261A|1984-07-04|
    JPS59140936A|1984-08-13|
    IT8323881D0|1983-11-24|
    DE3342495A1|1984-05-30|
    FR2536816B1|1986-05-23|
    GB2132261B|1986-07-23|
    ES285018U|1985-06-16|
    CS231432B1|1984-11-19|
    FR2536816A1|1984-06-01|
    US4570510A|1986-02-18|
    IT1169466B|1987-05-27|
    BR8306416A|1984-06-26|
    GB8330653D0|1983-12-29|
    ES285018Y|1986-04-01|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    GB575110A|1944-02-28|1946-02-04|W E Sykes Ltd|Improvements in and relating to gearing for producing step by step motion applicableto gear cutting or similar machines|
    GB1180848A|1951-01-28|1970-02-11|Fritz Keiper|Hinge Fittings for Seats with Adjustable Backrests.|
    NL92285C|1951-12-11|
    US2888833A|1954-09-21|1959-06-02|John Deere Plow Company|Counter drive|
    FR1569654A|1968-01-25|1969-06-06|
    US3673891A|1970-09-14|1972-07-04|Ferro Mfg Corp|Reclining seat adjuster|
    CS151290B1|1971-05-26|1973-09-17|
    DE7417259U|1973-07-05|1976-01-29|Bus Bodies Ltd., Port Elizabeth, Kapland |ROTATING DEVICE FOR REGULATING THE RELATIVE ANGLE POSITION OF TWO ORGANS|
    ZA745939B|1974-09-18|1976-01-28|Bus Bodies Sa Ltd|Controlling rotary mechanisms|
    DE2609607C3|1976-03-09|1984-02-02|Keiper Automobiltechnik Gmbh & Co Kg, 5630 Remscheid, De|
    FR2383633B1|1977-03-15|1980-04-30|Faure Bertrand|
    SU650847A1|1977-06-20|1979-03-05|Предприятие П/Я Г-4695|Vehicle door window raiser|
    DE2734568A1|1977-07-30|1979-02-08|Keiper Automobiltechnik Gmbh|ARTICULATED FITTING FOR SEATS WITH ADJUSTABLE BACKREST, IN PARTICULAR MOTOR VEHICLE SEATS|
    DE2834492C2|1978-08-07|1994-07-28|Keiper Automobiltechnik Gmbh & Co Kg, 5630 Remscheid, De|
    DE2918252A1|1979-05-05|1980-11-20|Rentrop Hubbert & Wagner|JOINT FITTING FOR SEATS WITH ADJUSTABLE BACKREST, IN PARTICULAR MOTOR VEHICLE SEATS|
    DE3013304C2|1980-04-05|1983-05-11|Keiper Automobiltechnik Gmbh & Co Kg, 5630 Remscheid|Adjusting device for seats and windows, in particular for motor vehicles|
    DE3118896C2|1981-05-13|1984-09-06|Keiper Automobiltechnik Gmbh & Co Kg, 5630 Remscheid|Swivel joint, especially for seats with adjustable backrests|
    DK425182A|1981-10-07|1983-04-08|Lcp Steel Prod|TILT BRACKET|
    US4469375A|1981-11-25|1984-09-04|Keiper U.S.A., Inc.|Taumel hinge recliner|JPH0266366A|1988-08-31|1990-03-06|Ikeda Bussan Co Ltd|Gear structure|
    GB2229510B|1989-02-16|1993-10-20|Hoover Universal|Seat recliner mechanism|
    US4914330A|1989-03-09|1990-04-03|Michel Pierrat|Low speed brushless electric motor|
    DE4034843C2|1990-11-02|1997-04-17|Keiper Recaro Gmbh Co|Backrest adjustment fitting for vehicle seats, in particular motor vehicle seats|
    DE4117497C2|1991-05-28|1997-01-16|Johnson Controls Naue Engineer|Adjustment fitting for seats with reclining backrest, especially for motor vehicle seats|
    JP3228694B2|1997-03-14|2001-11-12|株式会社東郷製作所|Hinge structure|
    US7229132B2|2002-09-27|2007-06-12|Meeker R & D, Inc.|Foldable booster car seat|
    JP4120542B2|2003-09-10|2008-07-16|アイシン精機株式会社|Angular position adjustment mechanism|
    TWI249482B|2003-09-10|2006-02-21|Aisin Seiki|Angular position adjusting mechanism|
    JP4107249B2|2004-02-17|2008-06-25|アイシン精機株式会社|Angle adjustment mechanism|
    JP4029847B2|2004-02-17|2008-01-09|アイシン精機株式会社|Angular position adjustment mechanism|
    GB0710548D0|2006-06-30|2007-07-11|Meeker R & D Inc|Juvenile convertible car seat|
    ITMI20060266U1|2006-07-21|2008-01-22|Giuseppe Tornaghi|HINGE WITH MORE POSITIONS FOR BACKRESTS, ARMRESTS AND MOVEMENTS IN GENERAL OF SOFAS AND BEDS.|
    DE202009016813U1|2009-12-11|2011-04-21|Brose Fahrzeugteile Gmbh & Co. Kg, Hallstadt|Drive device for a display element of a motor vehicle|
    DE102011051988A1|2011-07-20|2013-01-24|C. Rob. Hammerstein Gmbh & Co. Kg|Fitting for an adjusting device of a motor vehicle seat and method for its production|
    DE102012105575A1|2012-06-26|2014-01-02|C. Rob. Hammerstein Gmbh & Co. Kg|storage unit|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    CS846882A|CS231432B1|1982-11-25|1982-11-25|Planet mechanism|
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