• 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:
    “DRIVING WHEEL UNIT” A driven wheel unit includes an electric motor coupled to a three-stage, two-speed planetary drive assembly and has a dimensioned width to move between crop rows. A wheel hub is supported on an external surface of a fixed housing by large diameter wheel bearings surrounding both a cavity containing the motor and an adjacent cavity containing the first and second planetary stages. Radially fitted and encircling the two planetary stages are two SAHR disc clutches including pistons engaging the inner and outer surfaces of a compact piston guide member. The third stage planetary carrier defines a cover and is attached to an axially external end of the wheel hub. A third stage ring gear has an external diameter approximately equal to that of the wheel bearings and has an internal diameter fixed to the housing by a flat annular wheel bearing retaining plate, which is fixed to one end of the housing.
    公开号:BR102016005330B1
    申请号:R102016005330-7
    申请日:2016-03-10
    公开日:2020-10-13
    发明作者:Douglas K. Brownell；Eric Vilar；Kyle K. Mckinzie；Reginald M. Bindl
    申请人:Deere & Company；
    IPC主号:
    专利说明:

    Field of the Invention
    [001] The present invention relates to a driven wheel unit including a two-speed planetary gear drive assembly, and more specifically refers to such a driven wheel unit that includes multiple planetary speed reduction stages and is particularly suitable for use on a row crop sprayer or tractor designed to be easily driven between rows of crop having a spacing of about 508 mm (20 inches) without running over the crop. Foundations
    [002] A planetary drive arrangement is often used in a vehicle driven wheel unit to provide high and low operating speeds as well as staggered speed reductions made by directing the power supplied by the drive unit's motors (hydrostatic or electric, for example). example) through multiple stages of planetary gear. Although those familiar with powered wheel units have long appreciated the severe limitations that such designs place, on the available space in which the drive motor and constituent components of the planetary gear arrangements for such wheel units must be located, they will agree whereas these space restrictions are even more severe when wheel units are being used to drive wheels of a row crop tractor intended to be driven between crop rows planted as close as 508 mm (20 inches) to each other, and when the wheel units are powered by an electric motor. In this particular use of a drive unit, it is important for the drive unit to be axially compact, while maintaining the desired torque output and reliability in view of the increasing size of implements being pulled or loaded by the tractor. Therefore, what is needed is a driven wheel unit specially designed for use with a row crop tractor to be driven between crop rows spaced apart by as little as 508 mm (20 inches). summary
    [003] According to a first aspect of the present invention, a driven wheel unit of a row harvest tractor is provided, with the driven wheel unit comprising a two-speed planetary drive assembly including at least two located planetary stages within a fixed housing, with the fixed housing having a cylindrical outer surface on which a main support bearing assembly supporting a rotating wheel hub is mounted, with the drive assembly including radially external and internal friction clutches located radially within of a diameter of the main support bearing assembly and being arranged in a compact manner, radially fitted so as to occupy a minimum of axial width.
    [004] According to a second aspect of the invention, each of the aforementioned internal and external disc clutches is a hydraulically released spring applied friction clutch (SAHR) that includes an annular piston, and a compact and annular piston holder guide member fixed to the fixed housing and having radially external surfaces engaged by the external SAHR friction clutch and having radially internal surfaces engaged by the internal SAHR friction clutch.
    [005] According to a third aspect of the invention, each of the annular friction clutches is L-shaped in cross section, with the legs of the SAHR friction clutch radially external cooperating with annular piston guide and support member to define a first annular cavity for working fluid adapted to selectively receive pressurized fluid to disengage the radially external SAHR friction clutch, and with the radially internal SAHR friction clutch legs cooperating with the annular piston guide and support member to define a second annular cavity for working fluid adapted to selectively receive pressurized fluid to disengage the radially internal SAHR friction clutch.
    [006] According to a fourth aspect of the invention, the internal and external SAHR friction clutches are in an annular arrangement surrounding the entire first planetary stage and surrounding the second stage solar and planetary carrier and with an external clutch disc package being coupled between an outer annular surface of the second stage ring gear and the fixed housing, and with an inner clutch disc package being coupled between an inner annular surface of the second stage ring gear and the outer annular surface of the planetary carrier second stage.
    [007] According to a fifth aspect of the invention, a flat annular retaining plate is releasably attached to an annular end surface facing axially out of the fixed housing and engages and retains first bearing of the main support bearing assembly in place on the housing, the retaining plate having a toothed outside diameter engaged with, and directly fixing, a third stage ring gear to the fixed housing.
    [008] According to a sixth aspect of the present invention, a floating face seal assembly is located on the external cylindrical surface of the fixed housing on an opposite side of the main support bearing assembly in relation to the retainer and, in addition to acting To seal a gap gap existing at an interface between the hub and the fixed housing, the face seal assembly is in request coupling with a second bearing from the main support wheel bearing arrangement and acts to retain the second bearing in the place on the accommodation.
    [009] According to a seventh aspect of the invention, the planetary gear arrangement includes three stages with first, second and third stage solar gears being located in series in relation to end to end with each other along a geometric axis of rotation of the wheel unit and with each solar gear being mounted to rotate one solar gear relative to another.
    [0010] These and other aspects of the invention will become evident from a reading of the description that follows along with the attached drawings. Brief Description of Drawings
    [0011] Fig. 1 is a partial exploded view showing a wheel drive unit constructed in accordance with the principles of the present invention.
    [0012] Fig. 2 is a vertical sectional view taken through the drive wheel unit of Fig. 1.
    [0013] Fig. 3 is a left front perspective view of the drive unit of Fig. 2, but with the tire rim and some transmission components omitted for clarity and with the electric motor and friction disc clutch package external transmission signal shown exploded.
    [0014] Fig. 4 is a front perspective view from the right of drive unit components shown in Fig. 3, but with the electric motor omitted and with the main bearing retaining plate and third stage planetary carrier being included and exploded.
    [0015] Fig. 5 is an enlarged view of a portion of the structure shown in Fig. 4.
    [0016] Fig. 6 is a front perspective view from the left enlarged of the components shown in Fig. 5. Detailed Description
    [0017] With reference now to Figs. 1 and 2, an exemplary embodiment of a drive wheel unit 10 including a fixed housing 12 is shown, with an axially external end section of the housing having a radially external cylindrical surface 14 arranged concentrically with respect to a geometric axis of rotation X An annular wheel hub 16 is supported on the cylindrical surface 14 for rotation about the X axis of rotation by a main wheel support bearing assembly including a pair of axially spaced roller thrust bearings 18.
    [0018] Located in an annular cavity defined by, and extending between, an internal annular wall of the rim 16 and an external annular wall 14 of the fixed housing 12 is a metal annular face seal assembly 20 which, as seen in Fig. 2, is located immediately to the left of the left thrust roller bearing 18. The face seal assembly 20 is positioned against a left surface of the left thrust bearing 18 and maintains an outer track of the latter positioned against a shoulder defined by the inner surface of the wheel hub 16.
    [0019] A wheel rim 22 includes an annular mounting plate, extending radially inward 24 joined at a right angle to an inner surface of the wheel rim 20 and respectively attached to a plurality of radii projected radially outward 26 from the cube 16 by a plurality of fasteners (not shown). A 28 tire is mounted on the rim 20 and has a width W of approximately 425 mm (16.75 inches) that is suitable for moving between rows of agricultural plants, spaced as closely as 508 mm (20 inches) from one another, without running over the plants.
    [0020] The drive wheel unit 10 includes an energized drive assembly 30 located centrally within, and coupled to drive, the hub 16. The drive assembly 30 includes an electric motor 32 and a multi-stage planetary gear arrangement and two speeds 34.
    [0021] Importantly, the drive assembly 30 has a width approximately equal to the width W of the tire 26 so as not to disturb plants grown in rows as the tire 26 travels between the rows of plants.
    [0022] Referring also to Fig. 3, it can be seen that the electric motor 32 includes a substantially cylindrical housing 36 having circular left and right end walls 38 and 40, respectively. An axially external end region of the motor housing 36 is justly received in a cylindrical cavity opening axially inward, 42 formed in the fixed housing 12 in concentric relation with the X axis of rotation and including a right annular end wall 44 , with the right end wall 40 of the motor housing 36 touching the end wall of the cavity 44.
    [0023] The motor 32 has an output shaft 46 arranged along the geometric axis X and rotatably supported within, and projecting to a location to the right of, the end wall of the motor housing 40.
    [0024] Three planetary gear stages comprise the multiple stages of planetary gear arrangement 34 and are spaced axially to the right along the X axis starting at the end wall of the motor housing 40. A first stage solar gear 48 is formed as an integral part of the motor output shaft 46 and is engaged with three first stage planetary gears 50 (the most clearly visible in Figs. 4 and 5) which are in turn engaged with a first ring gear stage 52 having an annular vertical flange 54, with ring gear 52 being held against rotation by a circular pattern of fasteners (not shown) extending through flange 54 and into conjugated threaded holes provided in the right end wall 40 of the motor housing 36. A first stage planetary carrier 56 includes three spindles 58 on which the three planetary gears of the first stage 50 are respec assembled for rotation.
    [0025] An intermediate short shaft 60 has a left end received over a reduced diameter right end of the motor output shaft 46 and can rotate with respect to axis 46. Axis 60 is extremly splined and a left end region of these splines is engaged with a radially internal grooved surface of the first stage carrier 56 so that rotation of the carrier 56 is transferred to the axis 60. Also having a splined connection with the intermediate axis 60 is a second stage solar gear 62, which, as can be seen in Fig. 6, route with planetary carrier 56 and is engaged with four second stage planetary gears 64, which in turn are engaged with a second stage ring gear 66. The second ring gear stage 66 is mounted for rotation in relation to the fixed housing 12, but is adapted to be selectively coupled or fixed to the housing, in the manner described below, to vary the speed of activation of the planetary gear arrangement 34.
    [0026] Referring also to Fig. 4, it can be seen that axially outward movement of ring gear 66 is restricted by a flat annular retaining plate 68 screwed to an outermost outer end surface facing axially outward 70 of the housing fixed 12 by a plurality of mounting screws 72, the retaining plate 68 having a radially external region engaged with an external surface of the axially external main bearing 18 and having a radially internal stepped portion capturing a guide ring 74 between the retaining plate 68 and a shoulder defined by a step formed over an external circumference of the second stage ring gear 66 in an axially external region of the ring gear. Axial movement inward of ring gear 66 is restricted by an annular guide pad or disc 76 loosely sandwiched between a surface axially facing into second stage ring gear 66 and a surface axially facing out of a guide member of annular clutch piston 78. The piston guide member 78 includes an axially inwardly designed annular mounting rib 80 having an axially inwardly facing annular surface engaged with the axially outwardly facing annular surface of an axially projected mounting rib 82 of the fixed housing 12, with the guide member 78 being fixed to the housing spindles 12 by a circular pattern of mounting screws 83 projecting through holes provided in the mounting rib of the guide member 80 and screwed into aligned threaded holes provided in the mounting rib of housing 82.
    [0027] A second stage planetary carrier 84 is provided with spindles 86 on which planetary gears 64 are respectively mounted for rotation. In addition, carrier 84 has an internally toothed axially external portion engaged with an axially internal region of teeth of a third stage solar gear 88 formed as an integral part of a short output shaft having axially internal and external ends respectively supported for rotation at the right end of the intermediate shaft 60 and on a circular end plate or wall defined by a third stage planetary carrier 90 and being secured, by a circular arrangement of screws (not shown) to an annular surface facing axially outward 92 of the hub wheel mounting assembly 16 located radially out of the main bearings 18. The third stage solar gear 88 is engaged with three third stage planetary gears 94, which are respectively mounted for rotation about three spindles 96 of the planetary carrier 90. The planetary gears 94 are geared with a third gear ring gear goodwill 98, with an axially internal region 100 of each of the teeth of the ring gear 98 being modified and respectively engaged with teeth 102 (see Fig. 4) formed on a radially external circumference of the retaining plate 68 in order to prevent relative rotation between ring gear 98 and fixed housing 12.
    [0028] Mounted in housing 12 in relation to the entire planetary first stage and in a location to cooperate with second stage ring gear 66 and carrier 84, hydraulically released radially internal and external disc clutches are fitted by spring (SAHR) 104 and 106, respectively.
    [0029] The external clutch 104 includes an annular disk package 108 located in a large diameter section of an annular cylindrical cavity, with a stepped diameter 110 (see Fig. 6) provided in the spindle housing 12 immediately axially inward, or immediately to the left, from retainer plate 68. Disc pack 108 is located radially out of second stage ring gear 66 and includes first and second sets of interleaved friction plates. The first set of friction plates is fixed against rotation and for this purpose it has an external perimeter including radially projected semicircular tongues, equally spaced from each other and mounted to move axially in complementary shape slits, axially extended 109 provided in a section of large diameter of a stepped cavity 110 of the fixed housing 12. The second set of friction plates is mounted for rotation with the second stage ring gear 66 and for this purpose each has a toothed annular surface, radially internal, engaged for sliding along mating teeth 67 axially formed along an outside diameter of the second stage ring gear 66.
    [0030] As can be seen better in Fig. 6, the external clutch 104 additionally includes an annular external clutch piston 112 which is L-shaped in cross section with a long leg of the L extending axially and having cylindrical surfaces external and inner 114 and 116, respectively, with the outer surface 114 being mounted to slide axially within a smaller diameter section of the stepped diameter cavity 110, and with the inner surface 116 being mounted to slide axially along an outer cylindrical surface 118 of the clutch piston guide member 78. A short leg of the L extends radially inward from the long leg of the L and defines a relatively narrow inner cylindrical surface 120 mounted to slide axially along a radially outer cylindrical surface 122 of the mounting rib 80 of the guide member 78. The piston guide member 78 and piston 112 cooperate to define an annular cavity p for the working fluid 124 which expands and contracts with movement to the left and right of piston 112 respectively, as seen in Fig. 2. A first seal ring 126 is mounted in an annular groove provided on the outer cylindrical surface 116 of the piston guide member 84 and a second seal ring 128 is provided on the inner cylindrical surface 118 of the short leg of the piston L 112. The first and second seal rings 126 and 128 do this to prevent fluid under pressure from leaking to the from the working fluid cavity 124 along the respective interfaces between the inner surface of the piston 116 and the outer surface of the guide member 118 and between the inner surface of the piston 120 and the outer surface of the guide member 122.
    [0031] The outer disk clutch 104, as shown in Fig. 2, is in a disengaged condition in which the fluid pressure in cavity 124 acts against the radially extended leg of the external clutch piston 112 in order to retain the piston for left against the stress of a circular group of spiral compression springs 130 located in an annular cavity for spring 132 formed in the spindle housing 12 adjacent to a left end of the annular external clutch piston 112. In this condition, the first and second interleaved sets of friction plates from disk package 108 are not pressed against each other. Thus, the second stage ring gear 72 is free to rotate at any time when the second stage solar gear 68 is driven. By the supply of fluid under pressure being disconnected from the working fluid cavity 124, the loaded compression springs 130 will extend axially and act to move piston 112 axially outward in order to press the first and second sets of friction plates of the outer annular disk package 108 together, thereby resulting in the second stage ring gear 66 being attached, and prevented from rotating with respect to the spindle housing 12.
    [0032] The inner disc clutch 106 is constructed in a similar manner to the outer disc clutch 104 and includes an annular disc pack 134 located between an inner diameter of the second stage ring gear 66 and an outer annular surface 136 of the carrier second stage planetarium 84. Disc package 134 includes a first set of friction plates interspersed with a second set of friction plates. The first set of friction plates is mounted for rotation with the second stage ring gear 66 and for this purpose each of these plates includes a toothed outside diameter received for sliding axially along mating teeth provided in the inner diameter of the ring gear second stage 66. The second set of friction plates is mounted to rotate with the second stage planetary carrier 84 and for this purpose each of these plates has a toothed outside diameter received to slide axially along a toothed outer annular surface 136 of the second stage planetary carrier 84.
    [0033] As can be seen in Fig. 5, an annular thrust bearing 137 having a flat ring construction has an axially internal portion located on an annular step provided at a radially internal location of the piston guide member 78, the bearing 137 having an axially external face located in addition to an axially internal friction plate of the internal clutch disc package 134.
    [0034] With reference again to Figs. 2, 5 and 6, it can be seen that the internal disc clutch 106 additionally includes an annular clutch piston 138 which is L-shaped in cross section with a long leg of the L extending axially and having cylindrical outer and inner surfaces 140 and 142, respectively, with the outer surface 140 being mounted to slide axially along an inner diameter of the piston guide member 78 and with the inner surface 142 being mounted to slide axially along an outer cylindrical surface of the ring gear. first stage 52. A short leg of the L extends radially outwardly from the long leg of the L and defines a relatively narrow outer cylindrical surface 146 mounted to slide axially along a radially inner cylindrical surface of the mounting rib 80 of the piston guide member 78. Piston guide member 78 and piston 138 cooperate to define an annular cavity for working fluid 148 (F IG. 5) which expands and contracts with movement to the left and right of piston 138, respectively, as seen in Figs. 1 and 5. A first seal ring 150 is mounted in an annular groove provided on an internal cylindrical surface of the piston guide member 78 and a second seal ring 152 is provided on the outer cylindrical surface 146 of the short piston L leg. 138 to prevent fluid under pressure from leaking from the working fluid cavity 148 along the interfaces respectively between the inner surface of the piston 142 and the guide member of the inner surface 142 and between the outer surface of the piston 146 and the inner surface of the mounting rib 80 from guide member 78.
    [0035] The internal disc clutch 106 is shown in a disengaged condition in Fig. 2 in which the clutch piston 138 is retained away to the left from the thrust bearing 137 and against the force of request of a circular group of spiral compression springs 154 located in an annular spring cavity 156 formed partly by an annular portion of the spindle housing wall 44 located radially into the mounting rib 82 and partly by the annular flange 54 of the first stage ring gear 52. In this condition, the first and second interleaved sets of friction plates of the disc pack 134 are not pressed into engagement with each other to establish a drive connection between the second stage planetary carrier 84 and the ring gear. second stage 66. Thus, the second stage ring gear 66 is free to be rotated by the second stage planetary gears 64 at any time the gear Second stage solar 62 is activated. By the supply of fluid under pressure being disconnected from the working fluid cavity 124, the loaded compression springs 130 will extend axially and act to press the inner clutch piston 138 axially outward to make the thrust bearing 137 press the first and second sets of friction plates of the inner annular disk package 134 together in order to establish a drive connection between the second stage planetary carrier 84 and the second stage ring gear 66.
    [0036] Because the clutches 104 and 106 act to selectively couple the second stage ring gear 66 with the fixed housing 12 with all ring gears of the three stages being thus coupled to the fixed housing, the planetary gear arrangement 34 will operate without recirculating power losses as is the case when a ring gear releases the wheels. A related operational benefit of significance is the fact that due to the internal and external clutches 104 and 106 function to rotate on and off the second stage of the three-stage planetary arrangement, as opposed to rotating on and off the first-stage planetary , for example, high clutch and solar speeds will run in the lower range, thus taking advantage of the maximum speed of the electric motor 32.
    [0037] Also of significance is the fact that the inner and outer clutches 104 and 106 are fitted radially and that the piston guide member 78 comprises a sealing part that is common to both clutches to allow complex machining operations to be carried out on this smaller robust part, instead of on two parts or on a large housing.
    [0038] Having described one or more exemplary modalities, it will become evident that several modifications can be made without departing from the scope of the attached claims.
    权利要求:
    Claims (17)
    [0001]
    1. Drive wheel unit (10) for use with a vehicle intended for operation in which a pair of drive wheel units (10) are driven between rows of plants separated from each other by a predetermined distance as narrow as 508 mm (20 inches), with the wheel units (10) including a circular rim (22) carrying a rotating tire (28) around a central axis of rotation and having an axial width that does not exceed the predetermined distance, the unit drive wheel (10) characterized by the fact that it comprises: a fixed housing (12) located along the central axis of rotation and having an external cylindrical surface arrangement configured for, and carrying, a pair of roller thrust bearings (18) in axial alignment with each other along the axis of rotation, the housing (12) additionally including an internal cavity arrangement configured for, and receiving, a drive motor (32) having an e output shaft located along the central axis of rotation and coupled to a first stage of a three-stage, two-speed planetary gear arrangement; a wheel mounting hub (16) being supported for rotation around the outer cylindrical surface of the fixed housing (12) by the pair of roller thrust bearings (18) and the planetary gear arrangement having a third stage planetary carrier ( 90) mounted on the hub (16) and serving as a cover for the hub (16) and for the planetary transmission arrangement; the pair of roller thrust bearings (18) being of a large relative diameter and surrounding the first and second stages of the planetary transmission arrangement; and the drive motor (32) including a housing (36) with an axial distance between an axially internal surface of the housing and an axially external surface of the hub being equal to the axial width of the tire (28).
    [0002]
    2. Drive wheel unit according to claim 1, characterized by the fact that the pair of roller thrust bearings (18) also surrounds radially hydraulically engaged inner and outer disc clutches (106, 104) having respectively packages external and internal disc, with the external disc package being coupled between the fixed housing (12) and an external circumference of a second stage ring gear and being selectively engaged to secure a second stage ring gear to the fixed housing, and with the inner disk package being coupled between an inner circumference of the second stage ring gear and an outer circumference of the first stage planetary carrier and being selectively engaged to secure the second stage ring gear for rotation with the planetary carrier of first stage.
    [0003]
    3. Drive wheel unit according to claim 2, characterized by the fact that each of the internal and external hydraulic disc clutches (106, 104) is a hydraulically released, spring-applied clutch.
    [0004]
    4. Drive wheel unit according to claim 2, characterized in that the hydraulically operable external and internal disc clutches (104, 106) include annular, external and internal hydraulic pistons, respectively; an annular piston guide member (78) being located between the external and internal hydraulic pistons and being fixed to the fixed housing (12); the annular piston guide member (78) including a radially external surface engaged with the external hydraulic piston and acting to guide the external hydraulic piston as it moves axially to selectively engage the outer disk package, and the annular piston guide (78) including a radially internal surface engaged with the internal hydraulic piston and acting to guide the internal hydraulic piston as it moves axially to selectively engage the internal disk package.
    [0005]
    Drive wheel unit according to claim 4, characterized by the fact that the piston guide member (78) has an annular mounting rib (80) at one end defining first regions of radially external and internal surface, and the piston guide member (78) additionally including second regions of radially outer and inner surface respectively staggered radially outward and radially inward from the first regions of radially outer and inner surface, and wherein each of the external and inner includes a first leg axially extended and a second leg radially extended thereby defining an L-shaped cross section, with the first leg of the outer piston having an inner surface extending parallel to, and being in sliding engagement with, a second radially external surface region of the piston guide member (78), and with the second hydraulic piston leg outer having a slidably engaged end with the first radially outer region of the piston guide member (78), whereby an external annular working fluid cavity is formed between the external hydraulic piston and the piston guide member (78 ), and with the first inner piston leg extending parallel to, and in sliding engagement with, the second radially internal surface region of the piston guide member (78) and with the second inner piston leg having a sliding coupling end with the first region radially internal to the piston guide member, whereby an internal annular working fluid cavity is formed between the internal hydraulic piston and the piston guide member (78).
    [0006]
    6. Drive wheel unit according to claim 2, characterized by the fact that the fixed housing (12) has a flat annular end surface axially axial to the outermost; an annular retaining plate (68) being fixed against the flat annular end surface of the housing and extending radially beyond one of the pair of roller thrust bearings (18) in order to hold it in place over the fixed housing (12).
    [0007]
    7. Drive wheel unit according to claim 6, characterized by the fact that the annular retaining plate (68) has a toothed outer perimeter; and a third stage ring gear having an axially internal inner region provided with teeth engaged with those of the retaining plate (68), whereby the third stage ring gear is fixed to the fixed housing (12) by the retaining plate (68) .
    [0008]
    Drive wheel unit according to claim 2, characterized in that the fixed housing (12) has a flat annular end surface axially axial to the outermost; an annular retaining plate (68) being fixed against the flat annular end surface of the housing and extending radially beyond one of the pair of roller thrust bearings (18) in order to hold it in place over the fixed housing (12); and the outer disk package being located immediately axially into the annular retaining plate (68).
    [0009]
    Drive wheel unit according to claim 8, characterized in that the annular retaining plate (68) includes a radially internal annular end region provided with a step defining an annular shoulder arranged in axial opposition to a located shoulder on the second stage ring gear, whereby the retaining plate (68) serves to prevent axial movement out of the outer disk package in relation to the second stage ring gear.
    [0010]
    10. Drive wheel unit according to claim 4, characterized by the fact that the fixed housing (12) has a flat annular end surface axially axial to the outermost; a flat annular retaining plate (68) being fixed against the flat annular surface of the housing and extending radially beyond one of the pair of roller thrust bearings (18) in order to hold it in place over the fixed housing ( 12); and wherein the second stage ring gear is located between, and is axially captured by the piston guide member (78) and the annular retaining plate (68).
    [0011]
    11. Drive wheel unit according to claim 10, characterized in that a third stage ring gear (98) axially overlaps and surrounds a portion of an inner race of the one among the pair of roller thrust bearings (18) and a portion of the second stage solar gear (62), second stage planetary carrier (84) and planetary gears; and the annular retaining plate (68) having a toothed outer periphery engaged with conjugated teeth provided on the third stage ring gear (98) so as to hold it in the fixed housing (12).
    [0012]
    12. Drive wheel unit, characterized by the fact that it comprises: a fixed housing (12); a power unit mounted within an axially internal region of a cavity in the fixed housing (12) and having an output shaft extending axially outwardly along a geometric axis of rotation; a wheel hub (16) including a central opening receiving a cylindrical outer surface of the fixed housing (12) and being mounted for rotation around the geometric axis by first and second roller thrust bearings (18) axially spaced from one another to the along, and having internal tracks fixed to the cylindrical outer surface of the fixed housing (12), and having external tracks located in the central opening of the hub (16), with the inner track of the second roller thrust bearing being located at an outer end extreme axial of the housing (12), and with the hub (16) including a removable cover attached to an axially external surface of the hub (16); a rim (22) carrying a tire (28) and being fixed for rotation with the hub (16), with the tire (28) surrounding the power unit and hub (16) and having a dimension of width approximately equal to a distance between an internal axial surface of the power unit and an axially external surface of the hub (16) which is located axially into the axially external surface of the hub (16); a flat retaining plate (68) being attached to the extreme axially outer end of the housing (12) and being engaged with the inner race of the second roller thrust bearing; a three-stage, two-speed planetary gear arrangement being located in an axially external region of the cavity extending axially from the power unit to, and including, the hub (16), with the hub (16) defining a carrier third stage planetarium (90); the output shaft of the power unit having a first stage solar gear attached to it, a first stage planetary carrier (56) carrying first stage planetary gears meshed with the first stage solar gear and with a first ring gear stage, with the first stage ring gear being fixed to the fixed housing (12); the first stage carrier (56) defining an intermediate axis (60) located along the axis of rotation immediately at an axially external end of the output shaft of the power unit; a second stage solar gear being fixed for rotation with the intermediate shaft (60); a second stage planetary carrier (84) carrying second stage planetary gears meshed with the second stage solar gear and a second stage ring gear, with the second stage planetary gears being located coplanar with the retaining plate (68); an output shaft of the planetary gear arrangement being located immediately axially out of the intermediate shaft (60); a third stage solar gear being mounted for rotation with this output shaft named last; the third stage planetary carrier (90) carrying third stage planetary gears meshed with the third stage solar gear and meshed with a third stage ring gear partially surrounding the inner race of the second roller thrust bearing and circling and being coupled to an external surface of the retaining plate with the third stage ring gear, thus being fixed to the fixed housing (12); and hydraulically operated disc clutches (104, 106) radially operated external and internal having respectively external and internal disk packages located on opposite internal and external sides of the second stage ring gear, with the external disk package being coupled between an annular surface outer of the second stage ring gear and the housing in a location immediately axially into the retaining plate (68), and with the inner disc package being coupled between an inner annular surface of the second stage ring gear and an annular surface first stage carrier (56).
    [0013]
    13. Drive wheel unit according to claim 12, characterized by the fact that it additionally includes an annular piston guide member (78) attached to the fixed housing (12) and including stepped radially external and internal surfaces; the radially external disc clutch including a piston having a stepped inner surface in engagement sealed with, and cooperating with, the stepped radially outer surface of the annular piston guide member (78) so as to define an external pressure fluid cavity for selectively receiving pressurized fluid to perform operation of the external disc clutch (104); and the radially internal disc clutch (106) including an internal clutch piston having a radially staggered external surface in engagement sealed with, and cooperating with the radially staggered internal surface of the guide member (78) in order to define an internal cavity for fluid under pressure to selectively receive pressurized fluid to perform internal disc clutch operation (106).
    [0014]
    14. Drive wheel unit according to claim 13, characterized by the fact that each of the internal and external disc clutches (104, 106) is a hydraulically released disc clutch, applied by spring.
    [0015]
    Drive wheel unit according to claim 13, characterized by the fact that the piston guide member (78) includes an annular mounting rib (80) projecting axially outwardly from the inner disk packages and external; and the annular mounting rib having radially external and internal surfaces respectively defining a portion of the radially external and internal staggered surfaces.
    [0016]
    16. Drive wheel unit according to claim 15, characterized by the fact that each of the internal and external disc clutches (106, 104) is a hydraulically released clutch, applied by spring; the fixed housing (12) having an annular rib (80) projecting axially towards and engaging the annular rib of the piston guide member (78); and the external and internal clutches (104, 106) including radially external and internal annular groups of spiral compression springs located on opposite sides of the annular rib of the fixed housing (12) and being compressed between the fixed housing (12) and the pistons external and internal, whereby the introduction of fluid under pressure in the external cavity will disengage the external clutch (104) and the introduction of fluid under pressure in the internal cavity will disengage the internal clutch (106).
    [0017]
    17. Drive wheel unit according to claim 12, characterized by the fact that the tire (28) of the drive wheel unit has an axial width of between 406.4 and 531.8 mm (16 and 17 inches) and is adapted to move between adjacent crop rows spaced 508 mm (20 inches) apart.
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    同族专利:
    公开号 | 公开日
    BR102016005330A2|2016-10-11|
    US9511661B2|2016-12-06|
    CN105972168A|2016-09-28|
    CN105972168B|2020-04-14|
    DE102016203874A1|2016-09-15|
    US20160263987A1|2016-09-15|
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    法律状态:
    2016-10-11| B03A| Publication of an application: publication of a patent application or of a certificate of addition of invention|
    2020-04-07| B06U| Preliminary requirement: requests with searches performed by other patent offices: suspension of the patent application procedure|
    2020-08-04| B09A| Decision: intention to grant|
    2020-10-13| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 10/03/2016, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    US14/645,776|2015-03-12|
    US14/645,776|US9511661B2|2015-03-12|2015-03-12|Driven wheel unit including an axially compact two-speed planetary gear drive assembly|
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