WO2020068532A1 - Tendeur de courroie doté d'un amortisseur qui agit sur deux brins de courroie - Google Patents

Tendeur de courroie doté d'un amortisseur qui agit sur deux brins de courroie Download PDF

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Publication number
WO2020068532A1
WO2020068532A1 PCT/US2019/051834 US2019051834W WO2020068532A1 WO 2020068532 A1 WO2020068532 A1 WO 2020068532A1 US 2019051834 W US2019051834 W US 2019051834W WO 2020068532 A1 WO2020068532 A1 WO 2020068532A1
Authority
WO
WIPO (PCT)
Prior art keywords
tensioner
damper
base
pulley
axis
Prior art date
Application number
PCT/US2019/051834
Other languages
English (en)
Inventor
Mark M. Wigsten
Dale N. SMITH
Brian SCOTTI
Jason Moss
Original Assignee
Borgwarner Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Borgwarner Inc. filed Critical Borgwarner Inc.
Publication of WO2020068532A1 publication Critical patent/WO2020068532A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/0829—Means for varying tension of belts, ropes, or chains with vibration damping means
    • F16H7/0834—Means for varying tension of belts, ropes, or chains with vibration damping means of the viscous friction type, e.g. viscous fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1209—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means
    • F16H7/1227—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means of the viscous friction type, e.g. viscous fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1254—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
    • F16H7/1281—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0812—Fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0865—Pulleys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0874—Two or more finally actuated members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0893—Circular path
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0897—External to internal direction

Definitions

  • the present disclosure relates to a belt tensioner with a damper that acts on two belt strands.
  • the present disclosure provides a tensioner for tensioning two strands of a belt around an accessory pulley.
  • the tensioner includes a base assembly, an arm member, first and second tensioner pulleys, a tensioning spring and a damper.
  • the base assembly has a base structure and a bearing that permits the base structure to pivot about a drive axis.
  • the arm member is movably mounted to the base assembly.
  • the first tensioner pulley is coupled to the base structure for rotation about a first tensioner pulley axis that is parallel to the drive axis.
  • the second tensioner pulley coupled to the arm member for rotation about a second tensioner pulley axis that is parallel to the drive axis.
  • the tensioning spring is disposed in a load path between the base assembly and the arm member.
  • the tensioning spring biases the second tensioner pulley toward the first tensioner pulley in a manner that is configured to tension the belt.
  • the damper is coupled to the base assembly and the arm member and damps motion of the arm member when the arm member moves relative to the base assembly in a first direction that moves the second tensioner pulley away from the first tensioner pulley.
  • the present disclosure provides a tensioner for tensioning a belt around an accessory pulley.
  • the tensioner includes a base, first and second tensioning pulleys, first and second shafts, an arm assembly, a belt tensioning spring and a damper.
  • the first tensioning pulley is mounted to the base for rotation about a first axis.
  • the first shaft is mounted to the base and extends transverse to the first axis.
  • the second shaft is mounted to the base and extends parallel to the first shaft.
  • the arm assembly is slidably mounted to the first and second shafts.
  • the second tensioning pulley is mounted to the arm assembly for rotation about a second axis that is parallel to the first axis.
  • the belt tensioning spring is disposed in a load path between the base and the arm assembly.
  • the belt tensioning spring biases the arm assembly in a first direction relative to the base that moves the second axis toward the first axis.
  • the damper is coupled to the base and the arm assembly and resists translating movement of the arm assembly on the first and second shafts in a second direction that is opposite the first direction.
  • the present disclosure provides a tensioner for tensioning a belt around an accessory pulley that is driven about a drive axis.
  • the tensioner includes a base, first and second tensioning pulleys, an arm assembly, a belt tensioning spring and a damper.
  • the first tensioning pulley is mounted to the base for rotation about a first axis that is parallel to the driven axis.
  • the arm assembly is mounted to the base for pivoting motion about the driven axis.
  • the second tensioning pulley is mounted to the arm assembly for rotation about a second axis that is parallel to the driven axis.
  • the belt tensioning spring is disposed in a load path between the base and the arm assembly and biases the arm assembly in a first rotational direction about the driven axis relative to the base that moves the second axis toward the first axis.
  • the damper is coupled to the base and the arm assembly and resists pivoting of the arm assembly relative to the base in a manner that would move the second tensioning pulley away from the first tensioning pulley.
  • Figure 1 is a perspective view of a first tensioner constructed in accordance with the teachings of the present disclosure, the tensioner being shown in operative association with a front engine accessory drive of an internal combustion engine;
  • Figure 2 is a perspective view of a portion of the front engine accessory drive illustrated in Figure 1 , the view illustrating the first tensioner and an accessory in more detail;
  • Figure 3 is an exploded perspective view of the first tensioner
  • Figure 4 is a front elevation view of the first tensioner and the accessory shown in Figure 2;
  • Figure 5 is a left side elevation view first tensioner and the accessory shown in Figure 2;
  • Figure 6 is a section view taken along the line 6-6 of Figure 5;
  • Figure 6A is an enlarged portion of Figure 6, the view illustrating a damper in more detail
  • Figure 7 is a section view taken along the line 7-7 of Figure 5;
  • Figure 8 is a perspective view of a second tensioner constructed in accordance with the teachings of the present disclosure, the view depicting the second tensioner in operative association with a motor-generator;
  • Figure 9 is a front exploded perspective view of the second tensioner shown in Figure 8.
  • Figure 10 is a rear exploded perspective view of the second tensioner shown in Figure 8.
  • Figure 11 is a rear perspective view of the second tensioner shown in Figure 8.
  • Figure 12 is a section view taken along the line 12-12 of Figure 11.
  • an exemplary belt tensioner constructed in accordance with the teachings of the present disclosure is generally indicated by reference numeral 10.
  • the belt tensioner 10 is shown in operative association with an accessory pulley 12 as part of a front engine accessory drive 14 on an internal combustion engine 16.
  • the front engine accessory drive 14 includes a belt 20, a crankshaft pulley 22, which is coupled to a crankshaft (not specifically shown) for rotation therewith, and a plurality of accessory pulleys 12 and 24, which are drivingly coupled to a rotary engine accessories, such as a motor-generator 26 and a power steering pump 28, respectively.
  • belt tensioner 10 can be employed in various other types of belt drive systems and as such, it will be understood that the teachings of the present disclosure are not limited to the particular belt drive system that is shown in the drawings and described herein, or even more generally to front engine accessory drives.
  • the belt tensioner 10 can include a base assembly 30, an arm assembly 32, and a first tensioner pulley 34, a second tensioner pulley 36, a tensioning spring 38 and a damper 40.
  • the base assembly 30 can include a mount 44, a base structure 46 and a bearing 48.
  • the mount 44 can define a mount aperture 50 and can be fixedly coupled to an appropriate structure, such as the internal combustion engine 16 (Fig. 1 ) or to one of the driven accessories, such as the motor-generator 26.
  • the mount 44 is an annular structure that is fixedly coupled to a housing 54 of the motor-generator 26 and disposed concentrically around the accessory pulley 12.
  • the accessory pulley 12 is mounted to a shaft 56 of the motor- generator 26 for rotation therewith about a drive axis 58.
  • the base structure 46 can define a base aperture 60, which can be disposed about the drive axis 58 and configured to receive the shaft 56 of the motor-generator 26 there through, a first tensioner pulley hub 62, a pair of first shaft mounts 64, a pair of second shaft mounts 66 and a first spring mount 67.
  • the first tensioner pulley hub 62 can define a first tensioner pulley axis 68 that is disposed parallel to the drive axis 58.
  • the first shaft mounts 64 are configured to support a first shaft 70 such that the first shaft 70 is transverse to the drive axis 58 and the first tensioner pulley axis 68.
  • the first shaft 70 can be retained to the first shaft mounts 64 in any desired manner.
  • retaining ring grooves 72 are formed into the ends of the first shaft 70, the first shaft 70 is assembled to the base structure 46 such that the opposite ends of the first shaft 70 extend from the first shaft mounts 64, and external snap or retaining rings 74 are fitted into each of the retaining ring grooves 72.
  • the second shaft mounts 66 are configured to support a second shaft 78 such that the second shaft 78 is parallel to the first shaft 70.
  • the second shaft 78 can be retained to the second shaft mounts 66 in any desired manner.
  • retaining ring grooves 80 are formed into the ends of the second shaft 78, the second shaft 78 is assembled to the base structure 46 such that the opposite ends of the second shaft 78 extend from the second shaft mounts 66, and external snap or retaining rings 82 are fitted into each of the retaining ring grooves 80.
  • the first spring mount 67 can extend from one of the first shaft mounts 64 and can comprise a flange that defines an abutting face 86 and a through-hole 88.
  • the bearing 48 is disposed between the mount 44 and the base structure 46 and permits pivoting movement of the base structure 46 about the drive axis 58 relative to the rotary accessory (i.e., the housing 54 of the motor-generator 26 in the example provided).
  • the bearing 48 can be any type of bearing, such as a bearing with bearing elements (not shown) that are disposed between a pair of races (not shown) that are mounted to the mount 44 and the base structure 46.
  • the bearing 48 could comprise concentric elements, which are similar to bushings but which are unitarily and integrally formed with the mount 44 and the base structure 46, and a suitable material, such as a coating or plating, that is applied to one or both of the elements on the mount 44 and base structure 46 to control friction there between.
  • the bearing 48 comprises first and second bearing members 90a, 90b and a thrust plate 92.
  • the first and second bearing members 90a, 90b are annular structures that are non-rotatably coupled to opposite axial sides of the mount 44 and have a bearing face 94 that faces away from the mount 44.
  • each of the first and second bearing members 90a, 90b has a plurality of tabs 96 that are received into a respective notch 98 formed in the mount 44 to inhibit relative rotation between the mount 44 and the each of the first and second bearing members 90a, 90b.
  • the thrust plate 92 is an annular structure that is received in an annular recess (not shown) in the mount 44 and abutted against the bearing face 94 of the first bearing member 90a.
  • the base structure 46 is abutted against the bearing face 94 of the second bearing member 90b and secured to the thrust plate 92, for example via a plurality of threaded fasteners (not shown) that are received through an annular shoulder 1000 on the base structure 46 that is received through the mount aperture 50 in the mount 44 and threadably engaged to threaded holes 102 formed in the thrust plate 92.
  • the thrust plate 92 and the base structure 46 cooperate to sandwich the first and second bearing members 90a, 90b to the opposite axial sides of the mount 44 so that the base structure 46 is mounted to the mount 44 in a manner that inhibits relative axial movement there between along the drive axis 58 but permits pivoting movement of the base structure 46 relative to the mount 44 about the drive axis 58.
  • the arm assembly 32 includes a second pulley hub 110, which defines a second tensioner pulley axis 112 that is parallel the drive axis 58 and the first tensioner pulley axis 68, and is movably mounted to the base assembly 30 so that the second tensioner pulley axis 112 can be moved to change the spacing between the first and second tensioner pulley axes 68 and 112.
  • the arm assembly 32 can be pivotally mounted to the base assembly 30, such as to the mount 44 or to the base structure 46.
  • the arm assembly 32 is slidably mounted on the first and second shafts 70 and 78 includes an arm member 120, a hub structure 122, a first bushing set 124 and a second bushing set 126.
  • the arm member 120 can be a stamping or a weldment that can have an arm 130, a hub mount 132, which can be disposed on a first end of the arm 130, a first shaft mount 134, which can be disposed on a second, opposite end of the arm 130 and a second spring mount 136.
  • the hub structure 122 can be mounted to the hub mount 132 and can define the second pulley hub 110 and a second shaft mount 138.
  • the first bushing set 124 comprises an outer bushing 140, which is received into the first shaft mount 134 on the arm member 120, and a pair of first inner bushings 142 that are received into the opposite ends of the outer bushing 140 and receive the first shaft 70 there through.
  • the second bushing set 126 includes a pair of second inner bushings 150 and a retaining clip 152. Each of the second inner bushings 150 is received into a shaft aperture 156 formed through the second shaft mount 138.
  • the retaining clip 152 is disposed around the second inner bushings 150 (so as to abut the opposite axial ends of the second inner bushings 150 and to span across the second shaft mount 138) and the second shaft 78 is received through the retaining clip 152, as well as the second inner bushings 150 and the second shaft mount 138.
  • the second spring mount 136 can define an abutting face 158 (Fig. 6) and a through-hole 160 (Fig. 6).
  • the first tensioner pulley 34 is coupled to the base structure 46 for rotation about the first tensioner pulley axis 68.
  • the first tensioner pulley 34 is secured to a bearing 164, the bearing 164 is received on the first tensioner pulley hub 62 and a threaded fastener 166 is received through the bearing 164 and fixedly couples the bearing 164 to the first tensioner pulley hub 62.
  • the second tensioner pulley 36 is coupled to the arm member 120 for rotation about the second tensioner pulley axis 112.
  • the second tensioner pulley 36 can be secured to a bearing 170, the bearing 170 can be received on the second pulley hub 110 of the hub structure 122, and a threaded fastener 172 can be received through the hub mount 132 on the arm member 120 and threadably engage the second pulley hub 110 to fixedly secure the second pulley hub 110 to the hub mount 132 such that the second tensioner pulley 36 is disposed between the arm member 120 and the hub structure 122.
  • the tensioning spring 38 is disposed in a load path between the base assembly 30 and the arm member 120 and biases the second tensioner pulley 36 toward the first tensioner pulley 34 in a manner that is configured to tension the belt 20 ( Figure 1 ) about the accessory pulley 12.
  • the tensioning spring 38 can be any type of spring, such as torsion spring or an extension spring, but in the example provided is a compression spring that is received coaxially about the damper 40.
  • the damper 40 can be coupled to the base assembly 30 and the arm assembly 32 and is configured to damp motion of the arm member 120 relative to the base assembly 30.
  • the damper 40 is a“one-way” damper that is configured to damp motion of the arm member 120 relative to the base assembly 30 that would tend to drive the second tensioner pulley 36 away from the first tensioner pulley 34.
  • the damper 40 can be mounted to the first and second spring mounts 67 and 136.
  • the tensioning spring 38 can urge the second tensioner pulley 36 toward the first tensioner pulley 34.
  • the tensioning spring 38 urges the first and second spring mounts 67 and 136 apart from one another to thereby translate the arm assembly 32 along the first and second shafts 70 and 78.
  • the damper 40 can be any type of damper, such as a fluid damper.
  • the damper 40 is a hydraulic damper having a damper housing 180, a rod 182, a valve 184 and a compensation piston 186.
  • the damper housing 180 can comprise a first housing member 190, a second housing member 192, an internal snap ring 194 and a seal 196.
  • the first housing member 190 comprises a tubular body 200, an end cap 202 and a threaded member 204.
  • the tubular body 200 defines a first cylinder portion 210 and a first coupling portion 212.
  • the first cylinder portion 210 extends from a first side of the end cap 202 and has a first circumferentially extending wall surface 214.
  • the first coupling portion 212 is coupled to an end of the first cylinder portion 210 that is opposite the end cap 202 and defines a snap ring groove 216, an internally threaded segment 218, and an annular seal surface 220.
  • the internal snap ring 194 is received into the snap ring groove 216.
  • the second housing member 192 defines a second cylinder portion 224, a second coupling portion 226, a vent passage 228 and a rod mount 230.
  • the second cylinder portion 224 can be formed in a first axial end of the second housing member 192 and can define a second circumferentially extending wall surface 234.
  • the second coupling portion 226 can include a male threaded segment 236 and a seal groove 238.
  • the male threaded segment 236 can be disposed on the first axial end of the second cylinder portion 224 and can include male threads that are configured to engage female threads in the internally threaded segment 218.
  • the seal groove 238 can extend around the circumference of the second cylinder portion 224 and can be configured to receive the seal 196 therein.
  • the vent passage 228 can comprise one or more apertures that can be formed radially through a wall of the second cylinder portion 224 to permit venting of an interior space within the second cylinder portion 224 to the atmosphere.
  • the rod mount 230 can be formed in a second end of the second housing member 192 that is opposite the first axial end and can include a bushing aperture 240, a counterbore 242 and a snap ring groove 244.
  • the bushing aperture 240 extends through the second axial end of the second housing member 192 and intersects the interior of the second cylinder portion 224.
  • the counterbore 242 and the snap ring groove 244 are formed concentric with the bushing aperture 240.
  • a flanged bushing 250 is inserted into the second axial end of the second housing member 192 and has a bushing body 252, which is received in the bushing aperture 240, and a flange 254 that extends radially from an axial end of the bushing body 252 and is received into the counterbore 242.
  • An internal snap ring 256 is received into the snap ring groove 244 and secures the flange 254 of the bushing 252 in the counterbore 242.
  • the seal 196 is received into the seal groove 238 in the second coupling portion 226, the second coupling portion 226 is received into the first coupling portion 212 and the male threaded segment 236 is threadably engaged to the internally threaded segment 218 to secure the first and second housing members 190 and 192 to one another. Threading of the male threaded segment 236 into the internally threaded segment 218 draws the seal 196 into sealing engagement with the annular seal surface 220. If desired, the first end of the second housing member 192 can be driven into abutment with the internal snap ring 194.
  • the rod 182 can have first and second rod ends 270 and 272, respectively, and a rod body 274 that can be disposed between the first and second rod ends 270 and 272.
  • the rod body 274 can be received through the rod mount 230 and into both the interior of the second cylinder portion 224 and the interior of the first cylinder portion 210.
  • the first rod end 270 can define a valve mount 280 having a mount flange 282, a valve coupling segment 284, and a mount body 286 that is disposed axially between the mount flange 282 and the valve coupling segment 284.
  • the mount flange 282 can be disposed adjacent to an axial end of the rod body 274 and can form a shoulder or flange that extends radially outwardly from the mount body 286.
  • the valve coupling segment 284 is formed with a plurality of male threads 290 in the example provided, but it will be appreciated that the valve coupling segment 284 could be formed with a plurality of female threads or could consist of a head or other shape that would be similar to the head of a bolt or rivet.
  • the second rod end 272 defines a male threaded segment 292.
  • the valve 184 can include a valve body 300 and a valve element 302 that is movably coupled to the valve body 300.
  • the valve body 300 can define a first fluid passage 310 that extends through the valve body 300 and a valve seat 312 that can intersect an axial end of the first fluid passage 310.
  • the valve body 300 can be received onto the mount body 286 and abutted against the mount flange 282.
  • a washer 316 can be received onto the mount body 286 on a side of the valve body 300 that is opposite the mount flange 282 and a nut 318 can be threadably engaged to the male threads 290 of the valve coupling segment 284 to fixedly retain the valve body 300 to the first rod end 270 of the rod 182.
  • the valve body 300 can sealingly engage the rod 182 and the first circumferentially extending wall surface 214 of the first cylinder portion 210.
  • the valve element 302 can be coupled to the valve body 300 for movement between a first position, in which the valve element 302 is abutted against the valve seat 312 to thereby inhibit fluid flow through first fluid passage 310 in a first direction, and a second position in which the valve element 302 is spaced apart from the valve seat 312 to thereby permit fluid flow through the first fluid passage 310.
  • three valve elements 302 are received into respective valve seats 312 and each of the valve elements 302 comprises a spherical ball that is disposed between a respective one of the valve seats 312 in the valve body 300 and the washer 318.
  • one or more small diameter orifices can be employed to permit metered/controlled fluid flow through the valve body 300.
  • the small diameter orifice(s) can be formed via drilling (e.g., laser drilling).
  • the small diameter orifice(s) can permit dampened movement between the arm and the base when the valve element 302 is abutted against the valve seat 312.
  • the compensation piston 186 can be slidably received in the second cylinder portion 224 and slidably received on the rod body 274. Seals 320 disposed on the compensation piston 186 can form a seal between the compensation piston 186 and the second circumferentially extending wall surface 234, as well as a seal between the compensation piston 186 and the rod body 274.
  • the compensation spring 322 can bias the compensation piston 186 axially away from the rod mount 230. Contact between the compensation piston 186 and the internal snap ring 194 can limit axial movement of the compensation piston 186 away from the rod mount 230.
  • first and second fluid chambers 350 and 352 can be filled with a suitable fluid, which may or may not be a compressible fluid.
  • the first and second fluid chambers 350 and 352 are filled with a suitable incompressible fluid, such as a light oil.
  • a fill aperture 356 can be formed through the first end cap 202 in the first housing member 190 and a suitable plug 358 can be fitted to the fill aperture 356 after the first and second fluid chambers 350 and 352 have been suitably filled.
  • the damper 40 is coupled to the base assembly 30 and the arm member 120 and is configured to damp motion of the arm member 120 when the arm member moves relative to the base assembly 30 in a first direction that moves the second tensioner pulley 36 away from the first tensioner pulley 34.
  • the threaded member 204 that extends from the end cap 202 on the first housing member 190 of the damper housing is received through the through-hole 88 in the first spring mount 67, and the male threaded segment 292 of the second rod end 272 of the rod 182 can be received through the through-hole 160 in the second spring mount 136.
  • Nuts 364 and 366 can be threadably engaged to the threaded member 204 and to the male threaded segment 292 to fixedly couple the damper housing 180 to the base structure 46 and to couple the rod 182 to the arm member 120.
  • the end cap 202 is abutted directly against the abutting face 86 of the first spring mount 67.
  • the tensioning spring 38 can be received about the damper housing 180 and can have a first axial end, which can abut the end cap 202 on the damper housing 180, and a second axial end that can abut a spring seat 370 that is threadably coupled to the rod 182 at a location between the second end of the damper housing 180 and the abutting face 158 of the second spring mount 136. It will be appreciated that the spring seat 370 and the nut 366 cooperate with the male threaded segment 292 to generate a clamp load that fixedly couples the rod 182 to the arm member 120.
  • the tensioning spring 38 of the tensioner 10 urges the second tensioner pulley 36 toward the first tensioner pulley 34 to apply a tensioning force to the belt 20.
  • the force exerted by the tensioner 10 onto the belt 20 causes the base structure 46 to pivot about the drive axis 58 so that the base structure 46 is disposed in a neutral or centered position.
  • the second tensioner pulley 36 is located as close to the first tensioner pulley 34 as is possible. Any rotation of the base structure 46 from the neutral position will tend to drive the second tensioner pulley 36 away from the first tensioner pulley 34, thereby further separating the first and second tensioner pulleys 34 and 36 from one another.
  • the damper 40 is employed to damp movement of the second tensioner pulley 36 when it is moved away from the first tensioner pulley 34 to thereby prevent relatively rapid pivoting movement of portions of the tensioner 10 about the drive axis 58. More specifically, and with additional reference to Figure 6A, reaction forces transmitted from the second tensioner pulley 36 to the arm assembly 32 would tend to move the arm assembly 32 toward the first spring mount 67 on the base structure 46. Because the second rod end 272 of the rod 182 is fixed to the arm member 120, this movement of the arm assembly 32 would cause corresponding motion of both the rod 182 (i.e., to retract into the damper housing 180) and the valve 184.
  • Movement of the valve 184 in this direction drives the valve element 302 into the valve seat 312, which closes the first fluid passage 310 in the valve body 300 to thereby prevent fluid from migrating from the first fluid chamber 350 into the second fluid chamber 352, either entirely or at a rate that is sufficient to permit relatively rapid acceleration of the arm member 120) so that the valve 184 cannot move (or move rapidly) toward the end cap 202. Consequently, the rod 182 cannot retract (further) into the damper housing 180, which thereby inhibits or resists movement of the arm member 120 in a direction that would move the second tensioner pulley 36 away from the first tensioner pulley 34.
  • the belt 20 could stretch over its anticipated life and that the arm member 120 (and the second tensioner pulley 36 therewith) can be moved toward the first tensioner pulley 34 by the tensioning spring 38 to accommodate the increased length of the (stretched) belt 20. Since the rod 182 is coupled to the arm member 120 for movement therewith, movement of the arm member 120 (and the second tensioner pulley 36) toward the first tensioner pulley 34 will cause corresponding motion of the rod 182, which draws the rod 182 out from the damper housing 180. Because the valve 184 is fixed to the rod 182, withdrawing motion of the rod 182 causes an increase in the volume of the first fluid chamber 350 and a reduction in the volume of the second fluid chamber 352.
  • the increase in the volume of the first fluid chamber 350 is not equivalent to the reduction in the volume of the second fluid chamber 352 due to the volume of the rod 182 in the second fluid chamber 352.
  • the volume of the rod 182 is equal to the cross-sectional area of the portion of the rod body 274 that exits the second fluid chamber 352 multiplied by the length of the rod body 274 that has exited the second fluid chamber 352, which is the distance over which the valve 184 is translated. Consequently, withdrawal of the rod 182 would ordinarily require that fluid from a reservoir be drawn into the first fluid chamber 350 to compensate for the volume of the rod 182 and maintain the first fluid chamber 350 in a filled condition. In the example provided, however, compensation for the volume of the rod 182 is provided by reducing the volume of the second fluid chamber 352 by an appropriate amount.
  • the compensation spring 322 biases the compensation piston 186 toward the valve 184 to develop fluid pressure in the second fluid chamber 352. Movement of the compensation piston 186 toward the valve 184 ceases when the force acting on the compensation piston 186 due to the pressure in the second fluid chamber 352 is balanced with the force that is applied by the compensation spring 322 to the compensation piston 186.
  • the rod 182 is withdrawn from the damper housing 180, compensation for the volume of the rod 182 is provided by movement of the compensation piston 186 toward the valve 184 due to the force exerted by the compensation spring 322 on the compensation piston 186.
  • the tensioner 10 is robust and damps movement of the arm member 120/second tensioner pulley 36 in a direction away from the first tensioner pulley 34 throughout the relatively large range of movement of the second tensioner pulley 36 without the need to couple the first fluid chamber 350 to an external reservoir. Pivoting motion of the tensioner 10 about the drive axis 58 that would be caused by rapid changes in the magnitude and/or direction of the torque supplied to or by the motor-generator 26 is thereby damped or attenuated.
  • the tensioner 10a can include a base assembly 30a, an arm assembly 32a, and the first tensioner pulley 34, the second tensioner pulley 36, the tensioning spring 38 and the damper 40.
  • the base assembly 30a includes a base structure 46a and a bearing 48a.
  • the base structure 46a can define a base aperture 60a, which can be disposed concentrically about the drive axis 58 and configured to receive a hub member (not shown) of a motor-generator (not shown) there through, a first tensioner pulley hub 62a, which defines the first tensioner pulley axis 68, and a first spring mount 67a, which defines first a yoke mount aperture 400.
  • the bearing 48a can be any type of bearing that can support the base structure 46a for rotation on the hub member of the motor-generator.
  • the bearing 48a is a bushing having a bushing body 404 and a bushing flange 406.
  • the bushing body 404 has an annular shape and is received radially between the hub member of the motor-generator and the inside surface of the base aperture 60a.
  • a notch 408 is formed in the base aperture 60a and a keying member 410 that is coupled to and extends radially outwardly from the bushing body 404 is received into the notch 408 to inhibit relative rotation between the bushing body 404 and the base structure 46a.
  • the bushing flange 406 extends radially outwardly from the bushing body 404 and serves as a thrust washer that is located axially between the base structure 46a and a shoulder (not shown) on the motor-generator.
  • the arm assembly 32a includes an arm member 120a, a thrust bearing 412 and an arm bearing 414.
  • the arm member 120a can define an arm aperture 420, which can be disposed concentrically about the drive axis 58 and configured to receive the hub member of the motor-generator there through, a second pulley hub 110a, which defines the second tensioner pulley axis 112, and a second spring mount 136a, which defines a second yoke mount aperture 422.
  • the thrust bearing 412 is an annular structure that is received over the hub member of the motor- generator and abutted against both the base structure 46a and the arm member 120a.
  • the arm bearing 414 can be any type of bearing that can support the arm member 120a for rotation on the hub member of the motor-generator.
  • the arm bearing 414 is a bushing having a bushing body 426 and a bushing flange 428.
  • the bushing body 426 has an annular shape and is received radially between the hub member of the motor-generator and the inside surface of the arm aperture 420.
  • a notch 430 is formed in the arm aperture 420 and a keying member 432 that is coupled to and extends radially outwardly from the bushing body 426 is received into the notch 430 to inhibit relative rotation between the bushing body 426 and the arm member 120a.
  • the bushing flange 428 extends radially outwardly from the bushing body 426 and serves as a thrust washer that is disposed between the arm member 120a (i.e., on a side of the arm member 120a opposite the thrust bearing 412) and a fastener set 440 that secures the tensioner 10a to the hub member of the motor-generator.
  • the fastener set 440 includes a second thrust bearing 442, a spacer 444, a wave spring 446 and a nut 448 that are received on the hub member.
  • the nut 448 is tightened to threads (not shown) on the hub member to secure the tensioner 10a to the motor-generator, as well as to preload the several thrust bearings 406, 412 and 428.
  • the first tensioner pulley 34 and the second tensioner pulley 36 are mounted to the first and second pulley hubs 62a and 110a, respectively, and are rotatable about the first and second tensioner pulley axes 68 and 112, respectively.
  • a first yoke 450 can be threaded to the threaded member 204 of the damper housing 180, while a second yoke 452 can be threaded to the male threaded segment 292 of the second rod end 272 of the rod 182.
  • an anti-rotation means such as jam nuts, crimps, deformation or adhesives, may be employed to inhibit rotation of the first and second yokes 450 and 452 relative to the damper housing 180 and the rod 182, respectively.
  • the first yoke 450 can include a pair of ears 460 that can be fitted about the first spring mount 67a and a pin or rivet 462 can be received through holes 464 in the ears 460 and the first yoke mount aperture 400 in the first spring mount 67a.
  • the second yoke 452 can include a pair of ears 470 that are fitted about the second spring mount 136a and a pin or rivet 472 can be received through holes 474 in the ears 470 and the second yoke mount aperture 422 in the second spring mount 136a. Accordingly, the damper housing 180 and rod 182 are pivotally coupled to the base structure 46a and the arm member 120a, respectively.
  • the tensioning spring 38 is disposed between the end cap 202 on the damper housing 180 and the spring seat 370a that is disposed on the rod 182.
  • the spring seat 370a in this example is slidably received on the rod 182.
  • the shaft (not shown) of the motor-generator is disposed concentrically within the hub member of the motor-generator, the accessory pulley (not shown) is coupled to the shaft for rotation therewith, and a belt (not shown) is fitted to a belt drive system (not shown) that includes the tensioner 10a and the motor-generator such that the belt wraps around the first and second tensioner pulleys 34 and 36 and the accessory pulley in a manner that is similar to that which is shown in Figure 1.
  • the tensioning spring 38 will urge first and second spring mounts 67a and 136a on the base structure 46a and the arm member 120a, respectively, apart from one another, causing the base structure 46a and the arm member 120a to pivot about the hub member of the motor-generator in a manner that tends to pivot the first and second tensioner pulleys 34 and 36 toward from one another.
  • the damper 40 can resist relative pivoting movement between the base structure 46a and the arm member 120a in a manner that tends to pivot the first and second tensioner pulleys 34 and 36 away from one another (i.e., in a direction that would tend to reduce tension in the belt).
  • damper 40 has been described in the various embodiments above as being a “one-way” damper that resists movement between the base structure 46, 46a and the arm member 120, 120a that tends to move the first and second tensioner pulleys 34 and 36 away from one another, it will be appreciated that the damper 40 could be configured as a “two-way” damper that resists movement between the base structure 46, 46a and the arm member 120, 120a that tends to move the first and second pulleys 34 and 36 away from one another and that tends to move the first and second pulleys 34 and 36 toward one another.
  • the valve 184 (Fig.
  • damper 40 can employ small diameter orifices to dampen movement between the arm member 120 and the base structure 46 in both directions.
  • the damper 40 has been described and illustrated as being a linear damper, it will be appreciated that the damper 40 could be configured differently.
  • the damper 40 could be constructed in a manner that is described in U.S. Patent No. 4,615,096, which is incorporated by reference as if fully set forth in detail herein, and can be integrated into the tensioner to provide damping of the arm member 120, 120a relative to the base structure 46, 46a in a rotary manner.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

Un tendeur comprend un ensemble de base, un élément bras monté mobile sur l'ensemble de base, des première et seconde poulies montées sur l'ensemble de base et l'élément bras, respectivement, un ressort de tension et un amortisseur. L'ensemble base comporte une structure de base et un palier qui permettent à la structure de base de pivoter autour d'un axe d'entraînement. Le ressort de tension est disposé dans une voie de charge entre l'ensemble de base et l'élément bras et sollicite la seconde poulie vers la première poulie de façon à tendre une courroie. L'amortisseur est accouplé à l'ensemble de base et à l'élément bras et amortit le mouvement de l'élément bras lorsque ce dernier se déplace par rapport à l'ensemble de base.
PCT/US2019/051834 2018-09-25 2019-09-19 Tendeur de courroie doté d'un amortisseur qui agit sur deux brins de courroie WO2020068532A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201862736103P 2018-09-25 2018-09-25
US62/736,103 2018-09-25

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WO2020068532A1 true WO2020068532A1 (fr) 2020-04-02

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010276152A (ja) * 2009-05-29 2010-12-09 Ntn Corp オートテンショナ
JP2016191365A (ja) * 2015-03-31 2016-11-10 スズキ株式会社 内燃機関のベルト張力調整装置
US20170175857A1 (en) * 2012-12-26 2017-06-22 Litens Automotive Partnership Orbital tensioner assembly
US20180066733A1 (en) * 2015-04-02 2018-03-08 Litens Automotive Partnership Accessory drive tensioner with improved arrangement of tensioner arm and biasing member
CN207213061U (zh) * 2017-08-25 2018-04-10 华南理工大学 一种发动机前端附件液压式自动张紧器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010276152A (ja) * 2009-05-29 2010-12-09 Ntn Corp オートテンショナ
US20170175857A1 (en) * 2012-12-26 2017-06-22 Litens Automotive Partnership Orbital tensioner assembly
JP2016191365A (ja) * 2015-03-31 2016-11-10 スズキ株式会社 内燃機関のベルト張力調整装置
US20180066733A1 (en) * 2015-04-02 2018-03-08 Litens Automotive Partnership Accessory drive tensioner with improved arrangement of tensioner arm and biasing member
CN207213061U (zh) * 2017-08-25 2018-04-10 华南理工大学 一种发动机前端附件液压式自动张紧器

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