CN108458069A - A kind of big damping automatic tensioner of variation rigidity - Google Patents
A kind of big damping automatic tensioner of variation rigidity Download PDFInfo
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- CN108458069A CN108458069A CN201810277510.1A CN201810277510A CN108458069A CN 108458069 A CN108458069 A CN 108458069A CN 201810277510 A CN201810277510 A CN 201810277510A CN 108458069 A CN108458069 A CN 108458069A
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- torsionspring
- shell
- damping
- damping unit
- tensioner
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- 238000013016 damping Methods 0.000 title claims abstract description 157
- 230000002441 reversible effect Effects 0.000 claims abstract description 13
- 238000005096 rolling process Methods 0.000 claims abstract description 9
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- 239000002184 metal Substances 0.000 claims description 11
- 229910052751 metal Inorganic materials 0.000 claims description 11
- 239000000463 material Substances 0.000 claims description 3
- 239000013013 elastic material Substances 0.000 claims description 2
- 238000001125 extrusion Methods 0.000 claims description 2
- 239000011295 pitch Substances 0.000 description 13
- 230000009471 action Effects 0.000 description 7
- 238000005299 abrasion Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 239000000243 solution Substances 0.000 description 5
- 238000001746 injection moulding Methods 0.000 description 4
- 230000033001 locomotion Effects 0.000 description 4
- 230000007246 mechanism Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000001154 acute effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000001629 suppression Effects 0.000 description 2
- 230000009885 systemic effect Effects 0.000 description 2
- 229910000851 Alloy steel Inorganic materials 0.000 description 1
- 229910000881 Cu alloy Inorganic materials 0.000 description 1
- 241000167880 Hirundinidae Species 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000005097 cold rolling Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000002360 explosive Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Classifications
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
- F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
- F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
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- 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
- F16H2007/081—Torsion springs
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Abstract
The invention discloses a kind of big damping automatic tensioners of variation rigidity, including tensioner arm, shell, first damping unit, second damping unit, torsionspring, tensioning wheel, mandrel, rolling bearing, wear-resistant plastic bushing, the shell is fixed on engine body, the mandrel is fixed on shell, the tensioner arm is pivotally installed on through wear-resistant plastic bushing on mandrel, the belt wheel is installed on the one end of tensioner arm far from mandrel through rolling bearing, shell vessel is provided in the shell, the torsionspring is arranged in shell vessel and the tensioner arm spring base of the other end and tensioner arm abuts against, first damping unit and the second damping unit are oppositely disposed at shell vessel top, one end of first damping unit is abutted against with tensioner arm, the reverse arm of the other end and torsionspring abuts against.The present invention can provide bigger frictional dampings；The torque for providing bigger when belt tension fluctuates larger by changing rigidity avoids the noise that skids and generate.
Description
Technical field
The present invention relates to transmission system field, especially a kind of big damping automatic tensioner of variation rigidity, the auto-tensioning
Device is designed for automobile engine front end accessory drive system.
Background technology
For the automatic tensioner of automobile engine front end accessory system, main purpose is to make belt in transmission system
Tension is appropriate, compensation belt variation and decaying caused by tension or abrasion caused by engine speed fluctuations due to being tensioned
The swing of arm allows system normally effectively to work to avoid belt slippage, noise and vibration.
A kind of traction drive mechanism with vibration damper is disclosed in patent CN201080012969, in the mechanism
The vibration damper of setting can be acted with the vibration damper in the vibration damping when tensioner arm is rotated by spring effect
Normal pressure between device and shell.But the mechanism generates frictional damping due to only leaning on spring outer diameter to change, on the one hand to part
Dimensional accuracy and installation accuracy it is more demanding, between spring and vibration damper excessive gap can cause damp very little, rise
Less than the effect of decaying accessory system vibration；And gap is too small, then can cause to act between vibration damper and shell just
Pressure is excessive, and to which at stretcher service life initial stage, stretcher damping is bigger than normal, damping abrasion aggravation may be led to the later stage
Cause damping is rapid to decline and a series of NVH problems caused by damping piece rapid wear.
A kind of high-damping automatic tensioner, the high-damping of the automatic tensioner are disclosed in patent CN201420445047
Essentially from two aspects, spring and tensioner arm act on the resultant force of damping piece and so-called due to squeezing caused by outside spring
The power of pressure drag damping member, the normal pressure that the two power generate between damping piece outer surface and shell turn in tensioner arm relative to shell
Frictional damping is generated when dynamic.The actual situation is that spring, during torsion, the variation of spring outer diameter is non-uniform.More
Specifically, apart from the position of first and last gib head about a quarter circle, spring will produce maximum outer diameter variation.Therefore, the patent
The damping piece region of about a quarter circle and spring effect is only set, can not effectively increase due to spring radial dilatation and generate
Frictional damping.Second Problem is, described with the damping piece of the spring outer diameter zone of action and for being closed in tensioner arm and spring
The damping piece that damping is generated under force effect is integrated, and integrated design in this way can limit produced by changing due to spring outer diameter
Damping.It is preferred that should partially due to spring outer diameter variation and the damping that generates should can be freely along inner walls diameter
To directionally independent movement so that the part damping piece is more uniformly bonded shell, make abrasion evenly, to damping piece wearability
It can be more preferably.
In addition, with the increase of automatic tensioner usage time, the damping of automatic tensioner can reduce, and damping reduces meeting
The reduced capability for causing automatic tensioner attenuation factor to vibrate.It is decreased in frontal attachments system condition acute variation
Underdamping is with an equal amount of system vibration of decaying, therefore system fluctuation aggravates, and tensioner arm pivot angle increases.Big tensioner arm pendulum
Angle causes damping piece abrasion aggravation, damping therefore faster to reduce, and system response is worse, forms a vicious circle.Meanwhile it being tensioned
Arm pivot angle acute variation may lead to problems such as abnormal sound, tensioner arm hit limited block and stretcher premature failure.
Invention content
After overcoming current automatic tensioner damping less than normal and too fast and damping vibration attenuation of decaying
Problem caused by system response variation, provides a kind of automatic tensioner, possesses big damping, after damping vibration attenuation, according to
So it is able to maintain that smaller tensioner arm pivot angle so that system can maintain system to stablize in the service life of entire stretcher, protect
Card frontal attachments system possesses good NVH performances and the longer service life of stretcher.
In order to solve the above technical problems, the technical solution adopted by the present invention is：
A kind of big damping automatic tensioner of variation rigidity, including：Tensioner arm, shell, the first damping unit of arc, arc second damp
Device, torsionspring, tensioning wheel, mandrel, rolling bearing, wear-resistant plastic bushing, shell are fixed on engine body through two bolts
On, the mandrel is fixed on shell, and the tensioner arm is pivotally installed on through wear-resistant plastic bushing on mandrel, institute
Belt wheel is stated through the rolling bearing one end far from mandrel that is installed on tensioner arm, the formation of two level ladder blind hole is provided in the shell
Shell vessel, the torsionspring is arranged in the shell vessel and the tensioner arm spring base of the other end and tensioner arm offsets
It connects, first damping unit and the second damping unit are oppositely disposed at shell vessel top, first damping unit
One end is abutted against with tensioner arm, and the reverse arm of the other end and torsionspring abuts against, another reverse arm of the torsionspring with
Shell abuts against, and second damping unit is drivingly connected with tensioner arm and its inner wall fits with torsionspring outer ring, described
Torsionspring is gradually contacted by part outer ring with inner walls during windup-degree changes changes the torsionspring
Torsion stiffness.
The torque that torsionspring described in this programme generates passes to tensioner arm, first damping through the first damping unit
The normal pressure generation first that device generates extruding inner walls under the collective effect of tensioner arm and torsionspring reaction force rubs
Wipe damping；Second damping unit shape-ordinatedly follows tensioner arm to rotate together, while the damping unit inner wall and torsion
Spring outer ring be bonded, torsionspring load when can generate due to spring outer diameter increase caused by between the second damping unit and shell
Normal pressure, which generates the second frictional damping when tensioner arm rotates；The torsionspring is turned round during torsion
Turning rigidity can change with windup-degree.
Further, first damping unit is arc-shaped, and curved angle is 120 °~180 °, including retainer and the
One damping unit, the first damping unit integrated injection molding is on the outside of the first retainer, and by both being respectively arranged at
And it is connected in spaced the first dovetail shaped cooperation.
Further, first retainer is made of rigid material, one abutted against with the reverse arm of torsionspring
Plane is processed at end, and the one end abutted against with the tensioner arm is arranged to convex globoidal, the corresponding setting on tensioner arm with it is described
The matched cancave cambered surface of convex globoidal, the inner wall of first retainer are provided with the first damping unit spring base, and described first
Damping unit spring base and tensioner arm spring base are both provided with the curved surface to match with the helix angle of torsionspring.The two shape
Ordinatedly so that first damping unit can be rotated around the male-female engagement face to mend under the action of tensioner arm and torsionspring
Repay the frictional dissipation of first damping unit.
Further, second damping unit is arc-shaped, and curved angle is 90~240 °, including pressure bearing shell and the
Two damping units, the second damping unit integrated injection molding on the outside of pressure bearing shell, and by both being respectively arranged at and
It is connected in spaced the second dovetail shaped cooperation, the inner wall of the pressure bearing shell fits with the torsionspring outer ring.
Further, the pressure bearing shell is made of elastic material, and when the torsionspring reverses, outer diameter becomes larger, described
Extruding force the second damping unit is transferred uniformly into after pressure bearing shell extrusion to be in contact with shell.
Further, the inner wall of the pressure bearing shell radially be equipped with a boss, the tensioner arm be equipped with it is described convex
The sliding slot that platform is slidably matched, the boss, sliding slot and torsionspring limit second damping unit and are only capable of along the core jointly
The radial direction of axis moves.
Further, the vessel bottom surface of the shell vessel is equipped with the helical curve to match with the helix angle of torsionspring
Face, the lowermost end of the spiral camber are provided with the block for abutting torsionspring reverse arm, the shell of the lower part of the housing
Inner wall is equipped with the pattern draft of certain angle, when certain angle is reversed in the direction that torsionspring loads on edge, outside torsionspring
Circle is contacted with inner walls；When torsionspring continues load, inner walls limitation and the inner walls contact site of the shell
The torsionspring outer diameter divided continues to increase, the antitorque disabler of part torsionspring, and torsionspring number of active coils is reduced, rigidity
Change, stretcher realizes variation rigidity function.
Further, the inner walls for being provided with the pattern draft are circular cone plane, to mandrel axis direction evagination
Curved surface or to far from the mandrel axis direction convex curved surface；The central diameters equal pitch helical springs such as the torsionspring use,
Become central diameter helical spring, variable-pitch screw spring or becomes central diameter variable-pitch screw spring.Above-mentioned three kinds of features are set alone or in combination
It sets, it can be achieved that more automatic tensioner stiffness variation rules.
Further, antifriction metal (AFM) bushing is further fixedly arranged between the inner walls and the torsionspring.It is described
Antifriction metal (AFM) bushing has splendid wearability, and more stable variation rigidity function can be provided for automatic tensioner.
Further, the antifriction metal (AFM) sleeve is provided with several card slots, the vessel bottom surface in a certain interval
It is correspondingly provided with several matched with the card slot and limits the buckle that the anti-wearing liner is moved relative to shell.
Compared with prior art, the beneficial effects of the invention are as follows：Can be system by the way that the independent damping unit of two-stage is arranged
The damping of bigger is provided；Can the damping unit of self-movement keep the power being distributed on damping unit more equal in systemic effect
Even, also evenly, automatic tensioner service life improves for damping piece abrasion；The sphere of action for the second damping unit being rationally arranged
Preferably camber of spring can be utilized to generate frictional damping；The torsionspring that rigidity can be changed with windup-degree can be in belt tension wave
The torque of bigger is provided when dynamic larger, the braking of suppression system prevents tensioner arm from hitting limited block, maintains band section constant tension,
The noise that skids and generate is avoided, stretcher service life is improved.
Description of the drawings
Fig. 1 is the explosive view of the embodiment of the present invention.
Fig. 2 is the vertical view of the embodiment of the present invention.
Fig. 3 is present invention sectional view along A-A shown in Fig. 2.
Fig. 4 is the stereogram of tensioner arm of the embodiment of the present invention.
Fig. 5 is the stereogram of the first damping unit of the embodiment of the present invention.
Fig. 6 is the stereogram of the second damping unit of the embodiment of the present invention.
Damping unit stress diagram when the work of the embodiment of the present invention of the positions Fig. 7.
Fig. 8 is the vertical view of shell of the embodiment of the present invention.
Fig. 9 is the stereogram of anti-wearing liner of the embodiment of the present invention.
Figure 10 embodiment of the present invention etc. central diameters equal pitch helical spring show with the assembly of three kinds of different shape inner walls 13
It is intended to.
Figure 11 is torsionspring stiffness variation schematic diagram when using different shape inner walls 13 in Figure 10.
Figure 12 is a kind of inner walls 13 assembling schematic diagram of the present invention using the helical spring and shape of pitches.
Torsionspring stiffness variation schematic diagram in Figure 13 Figure 12.
In figure：10- shells；11- is buckled；12- blocks；13- inner walls；14- vessels bottom surface；15- shell vessels；20-
Antifriction metal (AFM) bushing；21- card slots；30- torsionsprings；The second damping units of 40-；41- pressure bearing shells；The second damping units of 42-；
The second dovetail shapeds of 43- coordinate；44- boss；The first damping units of 50-；51- retainers；The first damping units of 52-；The first swallows of 53-
Shape of tail coordinates；54- spring bearing surfaces；55- convex globoidals；56- the first damping unit spring bases；60- tensioner arms；61- tensioner arm bullets
Spring abutment；62 cancave cambered surfaces；63- sliding slots；70- wear-resistant plastic bushings；80- mandrels；90- rolling bearings；100- belt wheels.
Specific implementation mode
To more fully understand the present invention, the embodiment of the present invention is described in further details below in conjunction with the accompanying drawings.
As shown in Figure 1,2 and 3, the big damping automatic tensioner of a kind of variation rigidity, including：Tensioner arm 60, shell 10, arc
One damping unit 50, the second damping unit of arc 40, antifriction metal (AFM) bushing 20, torsionspring 30, tensioning wheel 100, mandrel 80, rolling
Dynamic bearing 90, wear-resistant plastic bushing 70, the shell 10 are fixed on through two bolts on engine body when mounted, the mandrel
80 are fixed in an interference fit on shell 10, and the tensioner arm 60 is pivotally pacified through wear-resistant plastic bushing 70
Loaded on mandrel 80, the belt wheel 100 is installed on the one end of the tensioner arm 60 far from the mandrel 80 through rolling bearing 90.Institute
The shell vessel 15 that the formation of two level ladder blind hole is provided in shell 10 is stated, the torsionspring 30 is arranged in the shell vessel
In 15 and the tensioner arm spring base 61 of the other end and tensioner arm 60 abuts against, first damping unit, 50 and second damping unit
40 are oppositely disposed at 15 top of shell vessel, and one end and the tensioner arm 60 of first damping unit 50 offset
It connecing, the reverse arm of the other end and torsionspring 30 abuts against, and another reverse arm and the shell 10 of the torsionspring 30 abut against,
Second damping unit 40 is drivingly connected with the tensioner arm 60 and its inner wall fits with 30 outer ring of torsionspring, the torsion
Turn spring 30 and gradually contacts the change torsion bullet with inner walls 13 by part outer ring during windup-degree changes
The torsion stiffness of spring 30.
The torsionspring 30 is set to generate torsion, the torsion by the first damping unit 50 when the tensioner arm 60 rotates
The torque that spring 30 generates passes to tensioner arm 60 through the first damping unit 50, and first damping unit 50 is in 60 He of tensioner arm
The normal pressure for squeezing shell 10 is generated under the collective effect of torsionspring 30, which generates first when tensioner arm 60 rotates
Frictional damping；Second damping unit 40 shape-ordinatedly follows tensioner arm 60 to rotate together, while the damping unit 40
Inner wall is bonded with 30 outer ring of torsionspring, and the torsionspring 30 can be generated when loading since spring outer diameter increases caused second
Normal pressure between damping unit 40 and shell 10, the normal pressure generate the second frictional damping when tensioner arm 60 rotates；It is described
Torsion stiffness during torsion of torsionspring 30 can change with windup-degree.
As shown in Fig. 4,5 and 6, first damping unit 50 is arc-shaped, and curved angle is 120 °, by retainer 51
It is constituted with the first damping unit 52,52 integrated injection molding of the first damping unit passes through difference in 51 outside of retainer
It is set to the two and is connected in spaced the first dovetail shaped cooperation 53.
First retainer 51 is made of hard alloy steel, and the one end abutted against with the reverse arm of torsionspring 30 adds
For work at plane 54, the one end abutted against with the tensioner arm 60 is arranged to the convex globoidal 55 toward evagination, corresponding in tensioner arm 60
The corresponding cancave cambered surface 62 toward indent is set, and the two shape-ordinatedly makes first damping unit in tensioner arm 60 and torsion
It can be rotated around the male-female engagement face to compensate the frictional dissipation of first damping unit 52 under the action of spring.Described first protects
The inner wall for holding frame 51 is provided with the first damping unit spring base 56, the first damping unit spring base 56 and tensioner arm spring
Seat 61 is both provided with the curved surface to match with the helix angle of torsionspring 30.
Second damping unit 40 is arc-shaped, and curved angle is 170 °, is damped by pressure bearing shell 41 and second single
Member 42 is constituted, and 42 integrated injection molding of the second damping unit is in the outside of pressure bearing shell 41, and by both being respectively arranged at
And be connected in spaced the second dovetail shaped cooperation 43, inner wall and 30 outer ring of the torsionspring of the pressure bearing shell 41
It fits.The pressure bearing shell 41 is made of cold rolling steel disc, and the outer diameter in load of the torsionspring 30 becomes larger, and squeezes and reverses
Extruding force is delivered evenly to the second resistance after 41 compressive deformation of pressure bearing shell by the pressure bearing shell 41 of 30 outer diameter contact of spring
On Buddhist nun's unit 42 and 10 contact surface of shell.It is additionally provided with a boss 44 on second damping unit 40, is set on the tensioner arm 60
There are a sliding slot 63, the boss 44, sliding slot 63 and torsionspring 30 to limit second damping unit 40 jointly and be only capable of along described
The radial direction of mandrel 80 moves.
After automatic tensioner 1 assembles, the spring bearing surface of 30 one end of torsionspring and first damping unit 50
54 abut against, and the other end of spring and the block 12 of the shell 10 abut against.The other end of second damping unit 50 and tensioning
Arm convex globoidal 62 abuts against.The first lap of torsionspring 30 is located at the damping dress of spring base 61 and first of the tensioner arm successively
On the spring base 56 set.The tensioner arm spring base 61 and the first damping unit spring base 56 are all the song with helix angle
Face, helix angle are equal with the helix angle of torsionspring 30.Due to the boss 44 of second damping unit 40 and described
63 shape of the sliding slot cooperation of tight arm, the torsionspring 30 and the cooperation of tensioner arm spring base 61 also limit the second damping unit
40 along mandrel 70 axial movement.
Damping unit stress diagram when being illustrated in figure 7 present invention work, the resistance that automatic tensioner generates at work
Buddhist nun is mainly derived from the first damping unit 50 and the second damping unit 40.When load, the tensioner arm 60 is rotated around mandrel 80, will
Power Fa passes to torsionspring 30 by the first damping unit 50, and torsionspring 30 is made to load, and stores energy.At the same time, institute
It states torsionspring 30 and acts on a reaction force Fb to the first damping unit 50, under the action of power Fa and Fb, first damping
Device 50 bears a bonding force radially.Under the force action, the first damping unit 40 squeezes shell 10, generates distribution
Normal pressure T1 in 52 outside of the first damping unit.Meanwhile torsionspring 30 is during the loading process, 30 outer diameter meeting of torsionspring
Become larger.Outer ring of the retainer 51 of the pressure bearing shell 41 of second damping unit 40 and the first damping unit 50 all with torsionspring 30
Contact, therefore 41 inner wall of pressure bearing shell can be made by torsionspring due to 30 radial deformation of torsionspring during the loading process
30 extruding force N1,51 inner wall of the retainer is by 30 extruding force N2 of torsionspring.The former, which will produce, is distributed in the second damping list
The normal pressure T2 in 42 outside of member, the latter can make the normal pressure T1 for being distributed in 52 outside of the first damping unit increase.When described
When tight arm 60 is with 10 relative motion of shell, normal pressure T1 and T2 will produce the frictional resistance opposite with 60 direction of motion of tensioner arm,
It is respectively defined as the first frictional damping and the second frictional damping.
As shown in Fig. 8,9 and 10, the vessel bottom surface 14 of the shell vessel 15 is equipped with the helix angle with torsionspring 30
The spiral camber to match, the lowermost end of the spiral camber are provided with the block 12 for abutting 30 reverse arm of torsionspring,
The inner walls 13 of 10 lower part of the shell are equipped with the pattern draft α of certain angle, when torsionspring 30 is along the direction of load
When reversing certain angle, 30 outer ring of torsionspring is contacted with inner walls 13；When torsionspring 30 continues load, the shell
10 limitation of inner walls 13 and 30 outer diameter of torsionspring of 13 contact portion of inner walls continue to increase, the part torsionspring
30 antitorque disablers, 30 number of active coils of torsionspring are reduced, and stiffness change, stretcher realizes variation rigidity function.
Specifically, an antifriction metal (AFM) bushing 20 can be added between the inner walls 13 and the torsionspring 30, it is described
Antifriction metal (AFM) bushing 20 has splendid wearability, and material is copper alloy, and more stable variation rigidity can be provided for automatic tensioner
Function.
20 bottom of antifriction metal (AFM) bushing is arranged in a certain interval there are four card slot 21, and the vessel bottom surface 14 corresponds to
There are four the buckle 11 for limiting the anti-wearing liner 20 and being moved relative to shell is matched with the card slot 21 for ground setting.
Usually, the inner walls 13 for being provided with the pattern draft are circular cone plane, to mandrel axis direction evagination
Curved surface or to far from the mandrel axis direction convex curved surface；The torsionspring 30 such as can be used at the central diameters equal pitch spiral bullet
Spring becomes central diameter helical spring, variable-pitch screw spring or becomes central diameter variable-pitch screw spring.Above-mentioned inner walls of different shapes
13 and different types of torsionspring can be arranged alone or in combination, to realize more automatic tensioner stiffness variation rules.
As shown in Figure 10, the torsionspring 30 such as can be used at the central diameters equal pitch helical spring, and it is oblique to be provided with the draft
The inner walls 13 of degree can obtain different spring rate change curves, b has indicated setting by designing different shapes
The inner walls 13 for stating pattern draft are circular cone plane, and a indicates that the inner walls 13 for being provided with the pattern draft are to mandrel
The curved surface of axis direction evagination, c indicate that the inner walls 13 for being provided with the pattern draft are to far from the mandrel axis side
To the curved surface of convex.Show that the rigidity of three kinds of 13 structures of inner walls in Figure 10 changes with 30 torsion angle of torsionspring in Figure 11
Relationship.As can be seen, Ko is the stiffness curve of conventional automatic tensioner, it can be seen that spring rate is certain value.And this reality
The automatic tensioner for applying tri- kinds of 13 structures of inner walls of a, b, c in example is tensioned when torsionspring 30 is loaded into certain angle
Arm 60 is torqued into certain angle θ0When, the spring rate Kt becomes larger, and the case where stiffness variation can be with the change of pattern draft α
Change and changes.
As shown in Fig. 12, torsionspring 30 is the helical spring using pitches on the basis of b structures in Fig. 10.It is attached
In figure, the pitch of torsionspring 30 gradually increases since that one end close to vessel bottom surface 14.Correspondingly, as shown in figure 13,
The torsionspring stiffness K d of pitches structure d torsionspring stiffness Ks compared with prior art0, it is loaded into centainly in torsionspring 30
When angle, i.e., tensioner arm 60 is torqued into certain angle θ0When, spring rate Kt becomes larger；And compared with the structure b in Figure 10, torsion
The spring structure of 30 pitches of spring, stiffness variation also can be different from the stiffness variation of pattern draft α structures is only changed.
Similarly, antifriction metal (AFM) bushing 20 can also be increased in above-mentioned a, b, c, d structure.
Compared with prior art, the beneficial effects of the invention are as follows：Can be system by the way that the independent damping unit of two-stage is arranged
The damping of bigger is provided；Can the damping unit of self-movement keep the power being distributed on damping unit more equal in systemic effect
Even, also evenly, automatic tensioner service life improves for damping piece abrasion；The sphere of action for the second damping unit being rationally arranged
Preferably camber of spring can be utilized to generate frictional damping；The torsionspring 30 that rigidity can be changed with windup-degree can be in belt tension
The torque of bigger is provided when fluctuating larger, the braking of suppression system prevents tensioner arm 60 from hitting limited block, maintains band section tension permanent
It is fixed, the noise that skids and generate is avoided, stretcher service life is improved.
The above is enumerating for specific embodiments of the present invention, for the equipment and structure of wherein not detailed description, is answered
When being interpreted as that the existing common apparatus in this field and universal method is taken to be practiced.
The above embodiment of the present invention is only to illustrate that technical solution of the present invention is used simultaneously, only the row of technical solution of the present invention
It lifts, the technical solution and its protection domain being not intended to restrict the invention.Using equivalent technologies mean, equivalent apparatus etc. to this hair
The improvement of technical solution disclosed in bright claims and specification is considered to be without departing from claims of the present invention
And the range disclosed in specification.
Claims (10)
1. a kind of big damping automatic tensioner of variation rigidity, including：Tensioner arm, shell, the first damping unit of arc, arc second hinder
Buddhist nun's device, torsionspring, tensioning wheel, mandrel, rolling bearing, wear-resistant plastic bushing, shell are fixed on engine machine through two bolts
On body, the mandrel is fixed on shell, and the tensioner arm is pivotally installed on through wear-resistant plastic bushing on mandrel,
The belt wheel is installed on the one end of tensioner arm far from mandrel through rolling bearing, it is characterised in that：It is provided with two level in the shell
The shell vessel that ladder blind hole is formed, the torsionspring is arranged in the shell vessel and the tensioning of the other end and tensioner arm
Arm spring base abuts against, and first damping unit and the second damping unit are oppositely disposed at shell vessel top, and described
One end of one damping unit is abutted against with tensioner arm, and the reverse arm of the other end and torsionspring abuts against, the torsionspring
Another reverse arm is abutted against with shell, second damping unit and tensioner arm drive connection and its inner wall and torsionspring outer ring
It fits, the torsionspring is gradually contacted by part outer ring with inner walls during windup-degree changes changes institute
State the torsion stiffness of torsionspring.
2. the big damping automatic tensioner of a kind of variation rigidity according to claim 1, it is characterised in that：The first damping dress
It sets and is arc-shaped, curved angle is 120 °~180 °, including retainer and the first damping unit, the first damping unit one
It is molded on the outside of the first retainer, and is connected by being respectively arranged at the two and coordinating in the first spaced dovetail shaped
It connects.
3. the big damping automatic tensioner of a kind of variation rigidity according to claim 2, it is characterised in that：First retainer
It is made of rigid material, plane is processed into the one end abutted against with the reverse arm of torsionspring, is abutted against with the tensioner arm
One end be arranged to convex globoidal, the corresponding setting on tensioner arm and the matched cancave cambered surface of the convex globoidal, described first protects
The inner wall for holding frame is provided with the first damping unit spring base, and the first damping unit spring base and tensioner arm spring base are all provided with
It is equipped with the curved surface to match with the helix angle of torsionspring.
4. the big damping automatic tensioner of a kind of variation rigidity according to claim 1, it is characterised in that：The second damping dress
It sets and is arc-shaped, curved angle is 90~240 °, including pressure bearing shell and the second damping unit, the second damping unit one
It is molded on the outside of pressure bearing shell, and is connected by being respectively arranged at the two and coordinating in the second spaced dovetail shaped
It connects, the inner wall of the pressure bearing shell fits with the torsionspring outer ring.
5. the big damping automatic tensioner of a kind of variation rigidity according to claim 4, it is characterised in that：The pressure bearing shell by
Elastic material is made, and when the torsionspring reverses, outer diameter becomes larger, after the pressure bearing shell extrusion that extruding force is equal
The second damping unit is transferred to evenly to be in contact with shell.
6. the big damping automatic tensioner of a kind of variation rigidity according to claim 5, it is characterised in that：The pressure bearing shell
Inner wall is radially equipped with a boss, and the tensioner arm is equipped with the sliding slot that is slidably matched with the boss, the boss, sliding slot and
Torsionspring limits second damping unit and is only capable of moving along the radial direction of the mandrel jointly.
7. the big damping automatic tensioner of a kind of variation rigidity according to claim 1, it is characterised in that：The shell vessel
Vessel bottom surface is equipped with the spiral camber to match with the helix angle of torsionspring, and the lowermost end setting of the spiral camber is useful
In the block for abutting torsionspring reverse arm, the inner walls of the lower part of the housing are equipped with the pattern draft of certain angle, work as torsion
Turn spring when reversing certain angle along the direction of load, torsionspring outer ring is contacted with inner walls；When torsionspring continues
When load, the inner walls limitation of the shell and the torsionspring outer diameter of inner walls contact portion continue to increase, the part
The antitorque disabler of torsionspring, torsionspring number of active coils are reduced, and stiffness change, stretcher realizes variation rigidity function.
8. the big damping automatic tensioner of a kind of variation rigidity according to claim 7, it is characterised in that：It is provided with the draft
The inner walls of gradient are circular cone plane, to the curved surface of mandrel axis direction evagination or to far from the mandrel axis direction convex
Curved surface；The central diameters equal pitch helical springs such as the torsionspring use become central diameter helical spring, variable-pitch screw spring or change
Central diameter variable-pitch screw spring.
9. the big damping automatic tensioner of a kind of variation rigidity according to claim 7, it is characterised in that：The inner walls with
Antifriction metal (AFM) bushing is further fixedly arranged between the torsionspring.
10. the big damping automatic tensioner of a kind of variation rigidity according to claim 9, it is characterised in that：The antifriction metal (AFM)
Sleeve is provided with several card slots in a certain interval, and the vessel bottom surface is correspondingly provided with several and card slot and matches
It closes and limits the buckle that the anti-wearing liner is moved relative to shell.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810277510.1A CN108458069A (en) | 2018-03-31 | 2018-03-31 | A kind of big damping automatic tensioner of variation rigidity |
| PCT/CN2018/113225 WO2019184342A1 (en) | 2018-03-31 | 2018-10-31 | Variable-stiffness and high-damping automatic tensioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810277510.1A CN108458069A (en) | 2018-03-31 | 2018-03-31 | A kind of big damping automatic tensioner of variation rigidity |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108458069A true CN108458069A (en) | 2018-08-28 |
Family
ID=63238302
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810277510.1A Pending CN108458069A (en) | 2018-03-31 | 2018-03-31 | A kind of big damping automatic tensioner of variation rigidity |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN108458069A (en) |
| WO (1) | WO2019184342A1 (en) |
Cited By (6)
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| CN109060336A (en) * | 2018-08-31 | 2018-12-21 | 华南理工大学 | A kind of Z-type Automatic Wedge Belt Tensioner test device |
| WO2019184342A1 (en) * | 2018-03-31 | 2019-10-03 | 华南理工大学 | Variable-stiffness and high-damping automatic tensioner |
| CN111120598A (en) * | 2018-11-01 | 2020-05-08 | 上海汽车集团股份有限公司 | Engine and belt tensioner thereof |
| CN111207192A (en) * | 2019-09-30 | 2020-05-29 | 宁波丰茂远东橡胶有限公司 | Automatic tensioner with circular damping sleeve |
| CN112611493A (en) * | 2020-12-07 | 2021-04-06 | 潍柴动力股份有限公司 | Tensioner load calibration device and system and engine front end gear train |
| CN112682449A (en) * | 2019-10-18 | 2021-04-20 | 长城汽车股份有限公司 | Elastic element mounting plug and mounting plug assembly |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115135906A (en) | 2020-01-08 | 2022-09-30 | 盖茨公司 | Adjustable damping mechanism for tensioner device |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2019184342A1 (en) | 2019-10-03 |
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