• 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:
    A differential mechanism is disclosed including a pair of holdout rings each of which is angularly displaceable to an operable position for maintaining in a disengaged condition an associated overrunning or underrunning clutch member, characterized by the arrangement of the center cam member concentrically within the center driving member, together with the provision of a rotation limiting stop for limiting the extent of rotation of the holdout ring relative to the central driving member when the holdout ring is rotated from an inoperative condition toward an operative condition. In one embodiment, the stop comprises the side wall of a through slot (2e) contained in the inner periphery of the center driving member (2), which stop is engaged by the lateral surface (30e) of an axial projection (30c) of reduced width on the associated holdout ring lug (30b). In a second embodiment, each holdout ring lug (130b) has a generally rectangular configuration, and certain teeth (102m) on the center driving member have stepped teeth with portions of reduced height (102n) that extend radially inwardly between the slots, which reduced tooth portions have lateral surfaces that are engaged by the lugs (130b) to limit the extent of rotational displacement of each holdout ring relative to the central driving member. By providing the stop on the central driving member, a more accurate positioning of the holdout ring in the operative condition is achieved, thereby affording improved quality and reliability of the differential mechanism.
    公开号:SU1223846A3
    申请号:SU833644778
    申请日:1983-09-20
    公开日:1986-04-07
    发明作者:Л.Диссетт Вальтер；Р.Бокс Джеймс
    申请人:Трэктек,Инк (Фирма)；
    IPC主号:
    专利说明:

    2. The mechanism according to claim 1, characterized in that the means for limiting the rotation of the elastic rings are embodied in the form of stops on the projections of the elastic rings that come into contact when the cam sleeve is disconnected from the side surfaces of the grooves of the drive ring.
    3.Mechanism according to claim 1, about tl and - due to the fact that the means
    the rotation restrictions of the elastic rings are made in the form of radial and parallel to the inner surface of the drive ring
    f
    The invention relates to mechanical engineering and in particular can be used to transmit rotation from one driving element to one or two coaxially arranged shafts.
    The aim of the invention is to increase reliability while reducing the cost of manufacture.
    FIG. 1 shows the proposed mechanism, a longitudinal section; in fig. 2 shows a protrusion of an elastic ring; FIG. 3 — fixation of the central cam element; FIG. 4 — cam sleeve, end view; FIG. 5 - elastic ring, end view; in fig. 6 is a section A-A in FIG. in fig. 7 - drive ring, end view; in fig. 8 is a central cam element, end view j in FIG. 9 is a section BB in FIG. eight; in fig. 10 is a variant of the mechanism, an extended section; FIG. 11 - rectangular protrusion of an elastic ring; in fig. 12 - fixing the central cam element; in fig. 13 - cam sleeve, end view; in fig. 14 is an elastic ring, end view i in FIG. 15 is a sectional view BB in FIG. 14j in FIG. 16 - cam sleeve, end view; in fig. 17 - elastic ring, end view; in fig. 18 - section GG in FIG. 17
    The differential mechanism contains a drive ring 1 located between the cam bushings 2 and 3 with slots H (not shown) inside for
    the axes of the stops contacting when the cam sleeve is disconnected with the side surfaces of the rectangular projections of the elastic rings.
    4. The mechanism according to claim 1, about tl and is due to the fact that the length of the stops of the drive ring is equal to the depth of the slots of this element.
    5. The mechanism according to claim 1, characterized in that the cams of the central cam element are made with straight side surfaces.
     .
    five
    0
    sliding axial movement without rotation along the spline sections 5 and 6 of the slotted sleeves 7 and 8, which are connected without rotation by internal key joints 9 and K) with coaxially arranged output shafts 1 and 12, respectively. The cam bushings 2 and 3 are clamped to the ring 1 by springs 13 and 14 to provide a power coupling between the cams 15 and 16 formed on opposite surfaces of the ring 1 and the cams 17 and 18 made on the bushings 2 and 3. Inside the ring 1 there is a concentric a central cam element 19, having at each end a series of equally spaced w, their cams 20 and 21 (Fig. 3), which engage with the corresponding cams 22 and 23 on the cam bushings 2 and 3. The central cam element 19 is held from axial displacement relative to the ring 1 by means of a ring 24 (Fig. 3) located inside the annular grooves in the inner and outer surfaces of the ring 1 and the central cam member 19, respectively. The outer surface 25 of the central cam member 19 is provided with a groove 26 (FIG. 8) for a smaller protrusion 27 (FIG. 7) on the inner surface of the ring 1, thereby limiting the angular displacement of the central cam, of the element 19 relative to the ring.
    Between the ring 1 and the sleeves 2 and 3 there are elastic rings 28 and 29. Each elastic ring has a cut 30 in the axial direction (Fig. 5) defining its C-shaped configuration. The ends of the rings are rotatably mounted inside the respective recesses 31 and 32 of the bodies 2 and 3. The rings 28 and 29 have flanges 33 and 34 radially inwardly located in the corresponding annular grooves 35 and 36 of the recesses 31 and 32, thereby preventing axial displacement of the rings 28 and 29 with respect to sleeves 2 and 3.
    Elastic rings 28 and 29 in the normal state are displaced radially inwards to the state of compression and form a frictional engagement with the inner walls of the recesses 31 and 32. The rings have axially located protrusions 37 circumferentially axially (Fig. 4), which in normal position pass inside the grooves 38, made. on the surface of the ring 1.
    Means are provided to limit the degree of rotational movement of each elastic ring 28 and 29 relative to ring 1 when the corresponding cam sleeve 2 and 3 are in the uncoupling position. The protrusions 37 of the elastic rings have stops 39 extending along the axis. The dimensions of these protrusions are such that when the extreme point 40 enters into engagement with the adjacent end surface of the ring 1, the longitudinal side surface 41 of the stops 39 engages with the adjacent side wall of the corresponding groove, resulting in further rotation of the elastic ring 28 relative to the ring 1.
    The mechanism works as follows.
    In normal operation, the drive ring 1 rotates the output shafts 11 and 12 at the same speed through the cams 15 and T6 of the sleeves 2 and 3 through the splined sections 5 and 6, the sleeves 7 and 8 and the keyed connections 9 and 10.
    When the shaft 11 rotates faster than the shaft 12, due to the interaction between the cams 20 at the central cam element 19 and the corresponding cams 17 at the sleeve 2 ,. this cam sleeve is displaced to the left, overcoming the force of the spring 13. before disengaging it
    five
    0
    five
    0
    five
    0
    five
    0
    five
    The cams 17 of the ring 1. Inwardly directed by the flange 33, the elastic ring 28 also shifts to the left and, as a result of the trenn between this ring and the cam bushing 2, slightly rotates into position (Fig. 2) when the lugs 39 of the projections 37 with their lateral surface 41 interact with the corresponding lateral the wall of the groove 38 and the ring 1, which limits the further rotation of the elastic ring 28 relative to the ring 1.
    In the case of rotation with greater speed of shaft 12, the friction clutch between the elastic ring 28 and cam sleeve 2 causes the center 28 to rotate in the opposite direction relative to the central cam element 19, and when the protrusions 37 are rotated towards the grooves 38, the sleeve 2 is displaced to the right by the action of the spring 13. The output shafts 11 and 12 rotate at the same speed with the drive ring 1. As the output shaft 12 rotates with an increased or reduced speed relative to the shaft 11, the sleeve 3 moves in the same way to the right and holds with the ring in the disengaged state.
    The cams 20 and 21 of the central cam element 19 (Figs. 8 and 9) have straight sides, which simplifies mechanical processing and inspection of these teeth during assembly. Only a small amount of mechanical machining of the groove for the ring 24 is required. The simplified design allows each element to be easily machined while reducing the total cost.
    The entire internal configuration of the drive ring 1 can be drawn with the provision of uniform surfaces used as the base for treating the cams 15 and 16j with torsional force. The improved design allows better control of the distance between the extreme points of the protrusions 37 of the elastic ring 28 relative to the working surface of the driving ring 1, which ensures better contact of the elements of the differential mechanism, and reduce the length of the cams, and hence their processing time.
    The dimensions and position of the cut 30 in the rings 28 and 29 can be very different, since the only
    five
    the function of this cut is to allow the ring to expand when it is inserted into the corresponding groove of the sleeves 2 and 3.
    In the embodiment shown in FIGS. 10-18, the protrusions 37 of the rings 28 and 29 have a rectangular configuration. On the driving ring 1, stops 42 (Fig. 11) are made, which are not aligned in the radial direction with the grooves 38 and are located radially inside the ring 1. The length of each stop 42 in the preferred embodiment is equal to the depth of the grooves 38, The stops 42 have lateral po 238466
    the surfaces 43, which are joined to the longitudinal side surfaces 44 of the protrusions 37, when the corresponding cam sleeve is removed from the clutch and the elastic ring is rotated by friction. When this end surface 45 of the protrusions 37 are in contact with the corresponding surface of the drive ring 1.
    10 Thus, the simplification of a complex structure of elements, ease of manufacture, assembly speed with a reduced number of operations, improved quality, reliability are achieved.
    15 items and reduced cost.
    0,
    39 jff
    J7 V
    F {/ g.2
    fig a
    FIG. five
    /(-TO
    28
    39. 40
    6
    L
    FIG. 7
    nineteen
    fig.Z
    nineteen
    FIG. 9
     / U
    Ft ten
    Fig.P
    gjvtfj
    FIG. one
    223846
     45
    FIG. 15
    Csig.Gb
    Phi1.17
    fi &. 1y
    权利要求:
    Claims (5)
    [1]
    1. DIFFERENTIAL MECHANISM OF BOTTOM DRIVE OF TWO SELF-LOCATED SHAFT, containing a drive ring concentrically located relative to the shafts, a coupling for connecting the drive ring to the shafts, made in the form of spline bushings mounted on the ends of the shafts mounted on them on both sides of the drive ring and to it the cam bushings, the central cam element concentrically located in the drive ring between the cam displacement of the associated cam sleeve, and the cam hub fixation unit is disengaged th position, made in the form of two coaxially arranged between the drive ring and the central cam element of the elastic split rings with protrusions on the side surfaces facing one another, mounted on the cam bushings and the central cam element with the possibility of frictional interaction with it and limited rotation, characterized in that that, in order to increase reliability while reducing the cost of manufacture, on the inner surface of the drive ring are made parallel to its axis grooves, width which exceeds the width of the protrusions of the elastic rings, the latter are located in them when the cam sleeves are turned on and come into contact with the side surface of the drive ring when they are turned off; on the outer surface of the central cam element, means are provided to limit its rotation relative to the drive ring when one of the cam sleeves is disconnected with limited turning capability, providing
    4W
    SU w, 1223846
    [2]
    2. The mechanism by π. 1, characterized in that the means of restricting the rotation of the elastic rings are made in the form of stops on the protrusions of the elastic rings in contact when the cam sleeve is turned off with the side surfaces of the grooves of the drive ring.
    [3]
    3. The mechanism of claim. ^ Characterized in that the means of restricting the rotation of the elastic rings are made in the form of stops located on the inner surface of the drive ring radially and parallel to its axis, which contact when the cam sleeve is disconnected with the lateral surfaces of the rectangular protrusions of the elastic rings.
    [4]
    4. The mechanism according to p. ^ Characterized in that the length of the stops of the driving ring is equal to the depth of the grooves of this element.
    [5]
    5. The mechanism according to claim 1, characterized in that the cams of the central cam element are made with straight lateral surfaces.
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1223846A3|1986-04-07|Differential mechanism for driving two coaxial shafts
    US4424725A|1984-01-10|Locking differential mechanism with improved holdout ring and spring retainer
    SU541445A3|1976-12-30|Differential mechanism
    US4809830A|1989-03-07|Torque transmitting torsional vibration damper device
    US2667087A|1954-01-26|Transfer case differential mechanism
    RU2486391C2|2013-06-27|Support ring of differential
    SU1403994A3|1988-06-15|Differential mechanism for driving pair of axially-located output shafts from input shaft
    US5407041A|1995-04-18|Lock-up device for torque converter
    SU1172448A3|1985-08-07|Differential mechanism
    CA2461597A1|2003-04-10|Locking differential including improved clutch member and adapter sleeve
    US3487903A|1970-01-06|Torque locked spline for clutch
    US4416645A|1983-11-22|Piloted flexible coupling
    EP1053413B1|2009-04-01|Improvements in power sharing gear sets
    SU826974A3|1981-04-30|Frictional clutch
    US2364331A|1944-12-05|Synchronizing transmission
    US6076429A|2000-06-20|Clutch for a differential
    US2369843A|1945-02-20|Synchromesh transmission
    US5179866A|1993-01-19|Transmission gear retainer
    SU947508A1|1982-07-30|Safety clutch
    US2329058A|1943-09-07|Differential mechanism
    US20200025261A1|2020-01-23|Self-contained switchable wedge clutch
    SU1291751A1|1987-02-23|Planetary gearbox synchronizer
    SU1186859A1|1985-10-23|Coupling
    SU1720904A1|1992-03-23|Mechanism of two-speed shaft transmission for tractor power take-off
    SU1418094A1|1988-08-23|Arrangement for engaging vehicle wheel to transmission
    同族专利:
    公开号 | 公开日
    IT1168848B|1987-05-20|
    CA1209374A|1986-08-12|
    IT8367974D0|1983-09-21|
    GB8319714D0|1983-08-24|
    DE3329940A1|1984-11-22|
    JPS59217055A|1984-12-07|
    FR2546255A1|1984-11-23|
    US4557158A|1985-12-10|
    MX159049A|1989-04-13|
    FR2546255B1|1989-05-19|
    AU553959B2|1986-07-31|
    SE8400840L|1984-11-20|
    AU1839683A|1984-11-22|
    SE8400840D0|1984-02-16|
    BR8305364A|1985-03-05|
    GB2140103B|1986-05-29|
    GB2140103A|1984-11-21|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    RU2486391C2|2008-01-29|2013-06-27|Итон Корпорейшн|Support ring of differential|US2638794A|1949-04-13|1953-05-19|Patent Developers Inc|Differential mechanism|
    US2667008A|1950-10-30|1954-01-26|John W Baum|Trolling harness|
    US2667087A|1951-10-10|1954-01-26|Patent Developers Inc|Transfer case differential mechanism|
    GB797870A|1955-12-12|1958-07-09|Patent Developers Inc|Differential mechanism|
    US2830466A|1955-12-12|1958-04-15|Patent Developers Inc|Differential mechanism|
    US3397593A|1966-04-19|1968-08-20|Frederick D. Knoblock|Differential|
    US3451496A|1967-06-07|1969-06-24|Boise Cascade Corp|Plural axle vehicle without transfer case differential mechanism therefor|
    US3791238A|1972-08-04|1974-02-12|Boise Cascade Corp|Differential mechanism of the holdout ring type|
    US4104931A|1976-03-19|1978-08-08|Tomich Michael G|Positive hold differential|
    US4400996A|1980-03-04|1983-08-30|Schou Carl Einar|Positive clutch differential|
    US4424725A|1980-09-19|1984-01-10|Tractech, Inc.|Locking differential mechanism with improved holdout ring and spring retainer|US4644818A|1984-10-29|1987-02-24|Tractech, Inc.|Differential apparatus with side-gear-centered center cam|
    US4745818A|1987-01-30|1988-05-24|Dyneer Corporation|Differential with angularly offset holdout rings|
    US5524509A|1995-01-18|1996-06-11|Titan Wheel International, Inc.|Differential with preload spring means|
    US5590572A|1995-07-28|1997-01-07|Titan Wheel International, Inc.|Locking differential including access windows for C-clip retainers|
    US5671640A|1996-04-30|1997-09-30|Tractech Inc.|Locking differential with pre-load means and C-clip retainers|
    US5901618A|1997-10-31|1999-05-11|Vehicular Technologies, Inc.|Quiet and smooth, positive acting, no-slip differential|
    US6053073A|1999-05-14|2000-04-25|Vehicular Technologies, Inc.|Positive acting differential with multiple pinion pins|
    US6092439A|1999-05-14|2000-07-25|Vehicular Technologies, Inc.|Positive acting differential having chamfered teeth|
    US6053074A|1999-05-14|2000-04-25|Vehicular Technologies, Inc.|Positive acting differential with slotted solid spacer|
    US6047615A|1999-05-14|2000-04-11|Vehicular Technologies, Inc.|Positive acting differential with slotted solid spacer and axle thrust slug|
    US6105465A|1999-05-14|2000-08-22|Vehicular Technologies, Inc.|Positive acting differential with slotted driver|
    US6062105A|1999-05-14|2000-05-16|Vehicular Technologies, Inc.|Positive acting differential with angled coupler groove and mating synchro ring|
    KR20040032431A|2002-10-09|2004-04-17|기아자동차주식회사|No Spin Differential of a Automobile|
    US6826981B1|2003-08-14|2004-12-07|Tractech Inc.|Differential for racing cars|
    US7559390B2|2006-05-01|2009-07-14|American Axle & Manufacturing, Inc.|Electronic all-wheel drive module with overrunning clutch differential|
    US20080242469A1|2007-03-26|2008-10-02|Randy's Ring & Pinion|Lockable differentials|
    US20090107741A1|2007-10-25|2009-04-30|Textron Inc.|Limited Slip Differential For Electric Vehicle|
    US7824296B2|2008-01-31|2010-11-02|Ring And Pinion Service, Inc.|Locking differential having a split-center driver|
    US7946946B2|2008-03-17|2011-05-24|Randy's Ring & Pinion|Preloaded differentials|
    US20100093481A1|2008-10-10|2010-04-15|Randy's Ring & Pinion|Locking differential having improved clutch teeth|
    US8117946B2|2008-10-31|2012-02-21|Ring And Pinion Service, Inc.|Locking differential with shear pin/spring assembly|
    US9587692B2|2015-04-01|2017-03-07|Akebono Brake Industry Co., Ltd|Differential for a parking brake assembly|
    US10788113B2|2016-06-08|2020-09-29|Zhejiang CFMOTO Power Co., Ltd.|Mechanical locking differential|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    US06/496,095|US4557158A|1983-05-19|1983-05-19|Holdout ring construction for differentials|
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