CN105042017A - Meshing type automobile differential mechanism - Google Patents
Meshing type automobile differential mechanism Download PDFInfo
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- CN105042017A CN105042017A CN201510232000.9A CN201510232000A CN105042017A CN 105042017 A CN105042017 A CN 105042017A CN 201510232000 A CN201510232000 A CN 201510232000A CN 105042017 A CN105042017 A CN 105042017A
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- planetary
- wheel shaft
- absorbing ring
- planet wheel
- bar
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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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
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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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/24—Arrangements for suppressing or influencing the differential action, e.g. locking devices using positive clutches or brakes
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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
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
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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
- F16H57/00—General details of gearing
- F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0479—Gears or bearings on planet carriers
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0482—Gearings with gears having orbital motion
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0493—Gearings with spur or bevel gears
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
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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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H2048/204—Control of arrangements for suppressing differential actions
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The invention relates to an automobile differential mechanism. The meshing type automobile differential mechanism comprises a planet carrier, half shaft gears, planet gears and a driven gear. The planet gears are connected with the planet carrier together through a planet wheel shaft. The planet carrier is connected with a fixed connecting plate. The fixed connecting plate is provided with first connecting teeth. The half shaft gears is penetrated by a push rod. The push rod is connected with a driven drive block and a movable connecting plate. The movable connecting plate is provided with second connecting teeth. The planet wheel shaft is provided with a sliding rod. The sliding rod is connected with a driving drive block in a sliding manner. The fixed connecting plate and the movable connecting plate are located outside the area defined by the two half shaft gears and the planet gears. The driving drive block and the driven drive block are located inside the area defined by the two half shaft gears and the planet gears. The automobile differential mechanism has the beneficial effect that when the differential speed of two half shafts is larger than the set value, the two half shafts can synchronously rotate, and solves the problem that according to an existing differential mechanism, when an automobile is driven on a poor road, the passing capability can be seriously affected.
Description
Technical field
The present invention relates to automobile differential, particularly relate to a kind of engagement type automobile differential.
Background technique
Differential mechanism is that one can make rotary motion reach two axles from an axle, and makes the differential attachment that the latter can rotate with different rotating speeds each other.Chinese Patent Application No. 2011800533570, publication date be August 21 in 2013 day, be called the automobile differential namely disclosing an existing structure in the patent document of " locking differential electrically triggered ", automobile differential comprises planetary wheel carrier and is positioned at two differential gears of planetary wheel carrier.During use, the left and right semiaxis (when for being then antero posterior axis during center differential) of automobile stretches into through semiaxis mounting hole after in planetary wheel carrier and links together with two differential gears correspondingly, is driven and rotate by differential gear.In using process, need to inject lubricant oil to lubricate differential mechanism with life-saving.
Existing difference device has the following disadvantages: when automobile travels on bad road, can have a strong impact on passing capacity.Such as when a driving wheel of automobile is absorbed in muddy road surface, although another driving wheel is in good road surface, automobile often can not advance (being commonly called as skidding).Trackslip in driving wheel original place now on muddy road surface, the but transfixion of the wheel in good road surface.This is because wheel on muddy road surface and the adhesion between road surface less, the moment of reaction less to semiaxis effect can only be taken turns by this in road surface, therefore to distribute to this torque taken turns also less for differential mechanism, although the adhesion between another driving wheel and good road surface is larger, but because of the feature of mean allocation torque, make this driving wheel also can only assign to the torque with slipping drive wheel equivalent, so that driving force is not enough to overcome running resistance, automobile can not advance, and power then consumes on slipping drive wheel.Now open the throttle and automobile not only can not be made to advance, waste fuel oil on the contrary, accelerate component wear, especially make tire wear aggravate.
Summary of the invention
The invention provides the engagement type automobile differential that can make two semiaxis synchronous axial system when a kind of differential when two semiaxis is greater than setting value, solve existing differential mechanism can have a strong impact on passing capacity problem when automobile travels on bad road.
Above technical problem is solved by following technical proposal: a kind of engagement type automobile differential, comprise the differential gear that planetary wheel carrier and two are arranged at planetary wheel carrier two ends, the driven gear that described planetary wheel carrier is connected with planetary pinion and drives planetary wheel carrier to rotate, described planetary pinion meshes together with described differential gear, described planetary pinion is linked together with planetary wheel carrier by planet wheel shaft, described planetary wheel carrier is connected with determines connecting plate, described determine connecting plate be provided with some first connect tooth, push rod is equipped with slidably in described differential gear, described push rod is connected with driven driving block and the plate that is dynamically connected, the described plate that is dynamically connected is provided with the second connection tooth that can mesh together with described first connection tooth, the side face of described planet wheel shaft is provided with slide bar, described slide bar slidably connects the active drive block that the centrifugal force slip produced when being rotated by described planet wheel shaft removes to drive described driven driving block, describedly determine connecting plate and the plate that is dynamically connected is positioned at outside the region that described two differential gears and planetary pinion surround, described active drive block and driven driving block are positioned at the region that described two differential gears and planetary pinion surround.In using process, when producing skidding, speed difference between two semiaxis can cause the rotating speed of planet wheel shaft larger, the centrifugal force produced when planet wheel shaft rotates makes active drive block skid off along slide bar and drive driven driving block, driven driving block to be dynamically connected plate and make the second connection tooth and first be connected tooth to mesh together by push rod, thus realize two semiaxis and be fixed together and synchronous axial system, after synchronous axial system, planet wheel shaft can not rotate, now determine connecting plate can lose centrifugal force and make now active drive block can lose centrifugal force and separate with driven driving block.Make the first connection tooth be connected tooth with second can not mesh together, folding folding like this and realize the speed discrepancy of two differential gears being controlled in setting range to improve the passing capacity (also namely preventing skidding) of automobile.
As preferably, oil-filling mechanism is provided with in described planetary pinion, described oil-filling mechanism comprises oil outlet, gas supplementing opening, sealing head, sealing head is driven to seal up the first spring of oil outlet, cylinder body and slipper seal are connected to the piston of cylinder body, described cylinder body is divided into air cavity and oil pocket by described piston, described piston is provided with the one-way valve opened towards air cavity, described piston is linked together with described sealing head by connecting rod, described oil outlet is connected with described oil pocket by oil duct, described gas supplementing opening is connected with described air cavity by air flue, described oil outlet is arranged at described planetary tooth top, the distance that described sealing head stretches out described planetary tooth top is greater than the tooth top gap between described planetary pinion and differential gear.During use, lubricant oil is loaded onto in oil pocket, planetary gear rotation is driven when planet wheel shaft rotates, when planetary gear rotation meshes together to the tooth being provided with oil outlet with differential gear, planetary teeth groove drives in sealing head indentation gear, is also moved towards oil pocket by connecting rod driven plunger and drive lubricant oil in oil pocket to flow to oil outlet through oil duct and flow to fueling cavity thus realize the lubrication to gear when Stamping Steel Ribbon inside contracts while making the first spring energy-storage; When sealing head staggers with teeth groove, oil outlet is sealed in nose heave Xinmi City of effect lower seal of the first spring, the proceduredriven piston of sealing head movement moves towards air cavity, now because the pressure in the part outflow of the oil in oil pocket, event oil pocket is less than the pressure of air cavity, one-way valve is opened and to make in replenish air to oil pocket and to reclaim in oil suction chamber by unnecessary having in fueling cavity, make next time piston press oil pocket time lubricant oil can reliably flow out.Achieve self oiling.Can overcome and can produce splash phenomena when lubricating in prior art and the deficiency causing lubrication effect to decline.
As preferably, described planetary wheel carrier is shell construction, and described planetary wheel carrier and differential gear surround Seal cage, is filled with inert gas in described Seal cage, and the air pressure in described Seal cage is greater than a standard atmospheric pressure.In time the heat loss produced during planetary gear rotation can be fallen, prevent temperature from rising too high and affecting the friction effect of connecting plate.
As preferably, described planetary pinion has a pair, described a pair planetary pinion is linked together with described planetary wheel carrier by same described planet wheel shaft, circular interior bar is equipped with rotationally in described planet wheel shaft, the outer circumferential face of described interior bar is provided with the first friction layer, the internal surface of described planet wheel shaft is provided with the second friction layer, together with described interior bar and planet wheel shaft to be connected to the second friction layer by described first friction layer.When two planetary rotating speeds inconsistent and cause planet wheel shaft to produce distortion time, planet wheel shaft can produce relative to interior bar and rotate, during rotation, external friction layer and the second friction layer produce friction energy-absorbing and eliminate torque force, thus play the effect of the distortion resistance improving planet wheel shaft.
As preferably, described interior bar comprises left bar and right bar, the left end of described left bar is linked together with described planet wheel shaft by left energy-absorbing spring, the right side of described left bar is provided with some the first commutating tooths along the distribution of left bar circumference, the right-hand member of described right bar is linked together with described planet wheel shaft by right energy-absorbing spring, the left side of described right bar is provided with some the second commutating tooths along the distribution of right bar circumference, and described first commutating tooth and the second commutating tooth mesh together.When driving interior bar also to produce distortion when planet wheel shaft distortion, right bar and left bar can be driven circumferentially to separate under the effect of the first commutating tooth and the second commutating tooth, energy-absorbing camber of spring and energy-absorbing time separately, can be caused.Further by planet wheel shaft distortion resistance.
As preferably, between described planet wheel shaft and interior bar, be filled with rubbing agent.When in using process, the first friction layer and the second friction layer produce wearing and tearing and cause friction energy-absorbing effect to decline, rubbing agent can be filled between the first friction layer and the second friction layer and make the friction energy-absorbing effect that the first friction layer and the second friction layer still keep good, thus solves frictional force and decline and the abutting power that can not adjust easily between the first friction layer and the second friction layer and adjust the problem of frictional force.
As preferably, described active drive block is provided with cushion pad, and described cushion pad is loop configuration, and the driving part of described active drive block is in the region that described cushion pad surrounds.Effectively can prevent active drive block and driven driving block from closing up in process and produce excessive impact and cause damage and vibration greatly.
As preferably, the first absorbing ring that described cushion pad is provided with vacuum breaker passage and extends along cushion pad bearing of trend, the second absorbing ring extended along cushion pad bearing of trend is provided with in described first absorbing ring, adsorption tank is formed between described first absorbing ring and the second absorbing ring, described dust-absorbing groove is all connected by the space outerpace of described vacuum breaker passage with the first absorbing ring with both inner spaces of the second absorbing ring, the flat segments that the tangent direction along described planet pin extends is provided with in described vacuum breaker passage, be provided with the centrifugal force produced when being rotated by described planet wheel shaft in described flat segments to move and the plug blocking described vacuum breaker passage and the valve opening spring that plug is opened.Dynamic to determine when connecting plate closes up except normal frictional force is fixed, also extrude the first absorbing ring and the second absorbing ring simultaneously, make all to form negative pressure in the inner space of the first absorbing ring and adsorption tank, also namely carry out adsorbing together with the second absorbing ring by the first absorbing ring and be fixed.When vibrated or instant impact and make the first absorbing ring absorption place produce moment partial disengagement time, under the effect of the second absorbing ring, after instant impact disappears, the first absorbing ring again can recover and adsorb, make absorbing ring be subject to moment impact and produce local instantaneously disconnect time can not produce obscission, and namely the slippage of adsorption force littlely can still keep good suction-operated, good reliability when therefore fixing, is not easy between connecting plate to skid separately.Anti-vibration ability when connecting plate is close together and reliability can be improved.Sucker can vacuum breaker automatically in time when connecting plate needs separately for this technological scheme, thus can not interfere the normal differential action of differential mechanism.
As preferably, be provided with the some elastomeric connector strip the first absorbing ring and the second absorbing ring linked together in described adsorption tank, described elastomeric connector strip distributes along the first absorbing ring bearing of trend.When the first absorbing ring and the second absorbing ring all adsorb upper, elastomeric connector strip is elongated and energy storage, this energy produces the trend impelling the first absorbing ring to move towards absorbate, make when the first absorbing ring produce disconnect instantaneously time, accelerate the first absorbing ring and return to adsorbed state.Also namely reduce further the possibility that when receiving moment impact, connecting plate separates, also namely improve anti-moment impact ability when connecting plate is close together in other words.
As preferably, the absorption end of described second absorbing ring stretches out the absorption end of described first absorbing ring.Better reliability during absorption.
The present invention has following advantage: the speed discrepancy of two differential gears can be limited in setting difference range, and when causing planetary pinion rotating speed too fast when exceeding setting value, two semiaxis can synchronous axial system, improve automobile passing capacity and can anti-slip; Be dynamically connected plate and the plate that is dynamically connected is positioned at the region that two differential gears and planetary pinion surround, and structural compactness is good.
Accompanying drawing explanation
Fig. 1 is the structural representation of the embodiment of the present invention one.
Fig. 2 is the schematic diagram of the embodiment of the present invention two.
Fig. 3 is the front elevational schematic of the plate that is dynamically connected in the embodiment of the present invention three.
Fig. 4 is C-C cross-sectional schematic of Fig. 3.
Fig. 5 is the close-up schematic view at the D place of Fig. 4.
Fig. 6 is planetary pinion in the embodiment of the present invention four and differential gear schematic diagram when meshing together.
Fig. 7 is the close-up schematic view at the A place of Fig. 6.
Fig. 8 is the close-up schematic view at the B place of Fig. 6.
Fig. 9 is the schematic diagram that the real the present invention of the present invention executes the planet wheel shaft in example five.
In figure: planetary wheel carrier 1, driven gear 2, determine connecting plate 3, first connects tooth 31, be dynamically connected plate 4, second connects tooth 41, planet wheel shaft 5, interior bar 51, left bar 511, right bar 512, external friction layer 513, first commutating tooth 514, second commutating tooth 515, interior friction layer 52, left energy-absorbing spring 53, right energy-absorbing spring 54, slide bar 55, sliding sleeve 56, active drive block 57, the drive portion 571 of active drive block, planetary pinion 6, tooth top 61, differential gear 7, axle journal 71, internal spline 72, sealing cover 73, driveshaft 74, driven driving block 75, the drive portion 751 of driven driving block, Returnning spring 76, oil-filling mechanism 8, oil outlet 81, gas supplementing opening 82, sealing head 83, first spring 84, cylinder body 85, air cavity 851, oil pocket 852, piston 86, one-way valve 861, connecting rod 862, oil duct 87, air flue 88, cushion pad 9, first absorbing ring 91, the absorption end 911 of the first absorbing ring, second absorbing ring 92, the absorption end 921 of the second absorbing ring, adsorption tank 93, elastomeric connector strip 94, vacuum breaker passage 95, flat segments 951, plug 96, valve opening spring 97, sealing head stretches out the distance L1 of planetary tooth top, tooth top gap L2 between planetary pinion and differential gear, the region S1 that two differential gears and planetary pinion surround, Seal cage S2.
Embodiment
Below in conjunction with accompanying drawing and embodiment, the present invention is further illustrated.
Embodiment one, and see Fig. 1, a kind of engagement type automobile differential, comprises planetary wheel carrier 1.Planetary wheel carrier 1 is shell construction.The two ends, left and right of planetary wheel carrier 1 are respectively rotatably connected to a differential gear 7.Differential gear 7 is provided with axle journal 71.Differential gear 7 is rotationally connected with planetary wheel carrier 1 by axle journal 71.Axle journal 71 is tubular structure.Internal spline 72 is provided with in axle journal 71.Planetary wheel carrier 1 be externally connected to driven gear 2.Driven gear 2 is gear ring.Planetary wheel carrier 1 is also rotatably connected to planet wheel shaft 5.The two ends of planet wheel shaft 5 are respectively connected with a planetary pinion 6.Planetary pinion 6 meshes together with two differential gears 7 all simultaneously.Planetary wheel carrier 1 is also connected with determines connecting plate 3.Determine connecting plate 3 to be positioned at outside the region S1 that two differential gears and planetary pinion surround.Determine connecting plate 3 for loop configuration.Determine connecting plate 3 and be provided with some first connection teeth 31.First connects the circumference distribution radial extension of tooth 31 along semiaxis.Slide in axle journal 71 and be equipped with driveshaft 74.One end of driveshaft 74 is connected with the plate 4 that is dynamically connected.The plate 4 that is dynamically connected is positioned at outside the region S1 that two differential gears and planetary pinion surround.The plate 4 that is dynamically connected is provided with some second and connects tooth 41.Second connects the circumference distribution radial extension of tooth 41 along semiaxis.The other end of driveshaft 74 is connected with driven driving block 75.Driven driving block 75 is positioned at the region S1 that two differential gears and planetary pinion surround.Driven driving block 75 looping in two semiaxis 7.Planetary wheel carrier 1 is also provided with the plate 4 and determine the Returnning spring 76 that connecting plate 3 separates of making to be dynamically connected.Planet wheel shaft 51 is provided with some slide bars 55.Slide bar 55 distributes along the circumference of planet wheel shaft 5.Slide bar 55 extends (realize to better utilize centrifugal force skidding off, slide bar 55 extends then best results along the tangent direction of planet wheel shaft 5) along the radial direction of planet wheel shaft 5.Slide bar 55 is arranged with sliding sleeve 56.Sliding sleeve 56 is connected with active drive block 57.Active drive block 57 is positioned at the region S1 that two differential gears and planetary pinion surround.The drive portion 571 of active drive block is sphere.The curvature of the drive portion 571 of active drive block is identical with the curvature of the drive portion 751 of driven driving block.
During use, two semiaxis (for left and right semiaxis or antero posterior axis) are stretched in axle journal 71 and are meshed together with internal spline 72 and link together with the present invention.Driving gear on power input shaft meshes together with driven gear 2 and drives planetary wheel carrier 1 one axle journal 71 for axle rotation, and planetary wheel carrier 1 pulls differential gear 7 with axle journal 71 for axle rotates by planetary pinion 6.Differential gear 7 drives two semiaxis to rotate, when two differential gears produce rotating speeds inconsistent time, planetary pinion 6 also carries out oneself with planet wheel shaft 5 for axle while revolving round the sun then realizes differential.When differential be greater than setting value namely skid time, the centrifugal force produced when planet wheel shaft 5 rotates makes active drive block 57 extrude driven driving block 75, driven driving block 75 makes the second connection tooth 41 be connected tooth 31 with first towards determining connecting plate 3 to move to mesh together by driveshaft 74 plate 4 that is dynamically connected, thus realizes holding together two differential gears 7 tightly (i.e. synchronous axial system), skidding can not being produced.Skid after eliminating, planet wheel shaft 5 rotating speed decline active drive block 57 is subject to centrifugal force decline, the result declined is that active drive block 57 drives the power of driven driving block 75 inadequate, the plate 4 that is dynamically connected under the effect of Returnning spring 76 makes the second connection tooth 41 be connected tooth 31 with first away from determining connecting plate 3 to depart from, and differential mechanism recovers normal differential action.
Embodiment two, and the difference with embodiment one is:
See Fig. 2, the inner of axle journal 71 is provided with sealing cover 73.Planetary wheel carrier 1 and differential gear 7 surround Seal cage S2.Inert gas is filled with in Seal cage S2.Air pressure in Seal cage S2 is greater than a standard atmospheric pressure.Seal cage S2 is also filled with lubricant oil.
Embodiment three, and the difference with embodiment two is:
See Fig. 3, active drive block 57 is provided with cushion pad 9.Cushion pad 9 is loop configuration.The drive portion 571 of active drive block is positioned at the region that cushion pad 9 surrounds.Cushion pad 9 is provided with the first absorbing ring 91.First absorbing ring 91 extends along cushion pad 9 bearing of trend.The second absorbing ring 92 is provided with in first absorbing ring 91.Second absorbing ring 92 extends along cushion pad bearing of trend.Two annular adsorption tanks 93 are formed between first absorbing ring 91 and the second absorbing ring 92.Article two, adsorption tank 93 is positioned at the both sides of the second absorbing ring 92 width direction.Some elastomeric connector strip 94 are together provided with in adsorption tank 93.First absorbing ring 91 and the second absorbing ring 92 link together by elastomeric connector strip 94.Elastomeric connector strip 94 distributes along the first absorbing ring 91 bearing of trend.
See Fig. 4, cushion pad 9 is provided with vacuum breaker passage 95.Adsorption tank 93 is all connected, is specially disjunctor in sleeve pipe 56 by the space outerpace of vacuum breaker passage 95 with the first absorbing ring 91 with both inner spaces of the second absorbing ring 92.The gas of discharging during such absorption can play the plate 4 and determine the effect that connecting plate closes of accelerating to be dynamically connected.
Flat segments 951 is provided with in vacuum breaker passage 95.Flat segments 951 extends along the tangent direction of planet pin 5.Plug 96 is provided with in vacuum breaker passage 95.Plug 96 is positioned at flat segments 951.The absorption end 921 of the second absorbing ring stretches out the absorption end 911 of the first absorbing ring.The absorption end 911 of the first absorbing ring exceeds the first connection tooth 42.
See Fig. 5, in vacuum breaker passage 95, be also provided with valve opening spring 97.Valve opening spring 97 does not block vacuum breaker passage 95 for making plug 96.Elastomeric connector strip 94 and the first absorbing ring 91 link together in the mode of integrative-structure.Elastomeric connector strip 94 and the second absorbing ring 92 link together in the mode of integrative-structure.
In using process, active drive block 57 under the influence of centrifugal force with driven driving block 75(see Fig. 1) be connected to together, the first absorbing ring 91 and the second absorbing ring 92 first adsorb driven driving block 75 and play and alleviate impact force and the effect of effect of reinforcing the connection.The elastic force that centrifugal force overcomes valve opening spring 97 makes plug 96 can remain on the state closing vacuum breaker passage 95.When centrifugal force declines and needs differential mechanism to recover normal state, valve opening spring 97 overcomes centrifugal force and plug 96 is opened, thus makes adsorption force not affect the normal separation of active drive block 57 and driven driving block.
Embodiment four, and the difference with embodiment three is:
See Fig. 6, in planetary pinion 6, be provided with oil-filling mechanism 8.The number of oil-filling mechanism 8 is equal with the number of teeth of planetary pinion 6.
See Fig. 7, oil-filling mechanism 8 comprises oil outlet 81, gas supplementing opening 82, sealing head 83, first spring 84, cylinder body 85 and piston 86.The oil outlet 81 of same oil-filling mechanism and gas supplementing opening 82 are arranged on the tooth top 61 of the same tooth of planetary pinion 6, the tooth top of same tooth only arranges oil outlet and the gas supplementing opening of an oil-filling mechanism, and namely in the present embodiment, the tooth of oil-filling mechanism and planetary pinion 6 is arranged correspondingly.Sealing head 83 and the first spring 84 are arranged in oil outlet 81, stretch out tooth top 61 at the effect lower seal head 83 of the first spring 84 and seal up oil outlet.The distance L1 that sealing head stretches out planetary tooth top is greater than tooth top gap L2(between planetary pinion and differential gear see Fig. 8).Cylinder body 85 is formed in planetary pinion 6 in the mode of integrative-structure, is the chamber in planetary pinion 6.Piston 86 slipper seal is connected to cylinder body 85.Cylinder body 85 is divided into air cavity 851 and oil pocket 852 by piston 86.Piston 86 is provided with the one-way valve 861 opened towards air cavity 851.Piston 86 is linked together with sealing head 83 by connecting rod 862.Connecting rod 862 links together with slipper seal between planetary pinion 6, and oil outlet 81 is disconnected with air cavity 851.Oil outlet 81 is connected with oil pocket 852 by oil duct 87.Gas supplementing opening 82 is connected with air cavity 851 by air flue 88.Oil duct 87 and air flue 88 are all be formed in planetary pinion 6 in the mode of integrative-structure, are the hole in planetary pinion 6.
The process of the present invention's lubrication is:
See Fig. 6 and Fig. 8, in the process that planetary pinion 6 rotates, bottom surface crush seal 83 contraction in planetary pinion 6 of the teeth groove of differential gear 7, sealing head 83 shrinks and oil outlet 81 is opened and makes the first spring 84 energy storage.
See Fig. 7, also moved towards oil pocket 852 by connecting rod 862 driven plunger 86 when sealing head 83 shrinks, the pressure increase in oil pocket 852 is closed by one-way valve 861 and lubricant oil in oil pocket 852 flows to oil outlet 81 through oil duct 87 and flows out from oil outlet 81 and realize lubrication.
When differential gear loses the squeezing action to sealing head 83, move outside the effect lower seal head 83 of the first spring 84 and oil outlet 81 is sealed up, moved towards air cavity 851 by connecting rod 862 driven plunger 86 when sealing head 83 stretches out, pressure drop in oil pocket 852 and pressure increase in air cavity 851, one-way valve 861 is opened, oil unnecessary in air and fueling cavity 56 is through gas supplementing opening 82, air flue 88 and one-way valve 861 and flow to oil pocket 852, the air pressure that pressure in oil pocket 852 can be maintained in same gear exterior is equal, so that lubricant oil can squeeze out by piston 86 when oil pocket 852 moves next time.
Therefore do not need in the present embodiment to add lubricant oil in planetary wheel carrier, achieve the good reliability when dry-type working of connecting plate, friction adhesive.
Embodiment five, and the difference with embodiment four is:
See Fig. 9, in planet wheel shaft 5, be equipped with circular interior bar 51.Interior bar 51 is tubular structure.The internal surface of planet wheel shaft 5 is provided with interior friction layer 52.Interior bar 51 comprises left bar 511 and right bar 512.The outer circumferential face of left bar 511 and right bar 512 is all provided with external friction layer 513.External friction layer 513 is covered with interior bar 51 along the circumference of interior bar 51.The left end of left bar 511 is linked together with planet wheel shaft 5 by left energy-absorbing spring 53.The right side of left bar 511 is provided with some the first commutating tooths 514 along the distribution of left bar circumference.The right-hand member of right bar 512 is linked together with planet wheel shaft 5 by right energy-absorbing spring 54.The left side of right bar 512 is provided with some the second commutating tooths 515 along the distribution of right bar circumference.First commutating tooth 514 and the second commutating tooth 515 mesh together.Be rotatably connected together with planet wheel shaft 5 together with left bar 511 and right bar 512 to be also all connected to interior friction layer 52 by external friction layer 513.Liquid rubbing agent is filled with in planet wheel shaft 5.
When planet wheel shaft 5 produces distortion, planet wheel shaft 5 can produce relative rotation relative to interior bar 51, and movement process China and foreign countries' friction layer 513 and interior friction layer 52 rub and consume energy and play the effect stoping twisting.If the moment of torsion of planet wheel shaft 5 and result in interior bar 51 also together produce twisting time, now left bar 511 and right bar 512 can separate vertically under the leading role of the first commutating tooth 514 and the second commutating tooth 515, separation process not only can make external friction layer 513 produce friction and energy-absorbing with interior friction layer 52, left energy-absorbing spring 53 and right energy-absorbing spring 54 can also be impelled to be out of shape and energy-absorbing, play energy-absorbing and prevent from reversing the effect produced, thus realizing the distortion resistance improving planet wheel shaft.And right energy-absorbing spring 54 and left energy-absorbing spring 53 can also play the effect of repairing planet wheel shaft 5.
Claims (10)
1. an engagement type automobile differential, comprise the differential gear that planetary wheel carrier and two are arranged at planetary wheel carrier two ends, the driven gear that described planetary wheel carrier is connected with planetary pinion and drives planetary wheel carrier to rotate, described planetary pinion meshes together with described differential gear, described planetary pinion is linked together with planetary wheel carrier by planet wheel shaft, it is characterized in that, described planetary wheel carrier is connected with determines connecting plate, described determine connecting plate be provided with some first connect tooth, push rod is equipped with slidably in described differential gear, described push rod is connected with driven driving block and the plate that is dynamically connected, the described plate that is dynamically connected is provided with the second connection tooth that can mesh together with described first connection tooth, the side face of described planet wheel shaft is provided with slide bar, described slide bar slidably connects the active drive block that the centrifugal force slip produced when being rotated by described planet wheel shaft removes to drive described driven driving block, describedly determine connecting plate and the plate that is dynamically connected is positioned at outside the region that described two differential gears and planetary pinion surround, described active drive block and driven driving block are positioned at the region that described two differential gears and planetary pinion surround.
2. engagement type automobile differential according to claim 1, it is characterized in that, oil-filling mechanism is provided with in described planetary pinion, described oil-filling mechanism comprises oil outlet, gas supplementing opening, sealing head, sealing head is driven to seal up the first spring of oil outlet, cylinder body and slipper seal are connected to the piston of cylinder body, described cylinder body is divided into air cavity and oil pocket by described piston, described piston is provided with the one-way valve opened towards air cavity, described piston is linked together with described sealing head by connecting rod, described oil outlet is connected with described oil pocket by oil duct, described gas supplementing opening is connected with described air cavity by air flue, described oil outlet is arranged at described planetary tooth top, the distance that described sealing head stretches out described planetary tooth top is greater than the tooth top gap between described planetary pinion and differential gear.
3. engagement type automobile differential according to claim 1 and 2, it is characterized in that, described planetary wheel carrier is shell construction, and described planetary wheel carrier and differential gear surround Seal cage, be filled with inert gas in described Seal cage, the air pressure in described Seal cage is greater than a standard atmospheric pressure.
4. engagement type automobile differential according to claim 1 and 2, it is characterized in that, described planetary pinion has a pair, described a pair planetary pinion is linked together with described planetary wheel carrier by same described planet wheel shaft, circular interior bar is equipped with rotationally in described planet wheel shaft, the outer circumferential face of described interior bar is provided with the first friction layer, and the internal surface of described planet wheel shaft is provided with the second friction layer, together with described interior bar and planet wheel shaft to be connected to the second friction layer by described first friction layer.
5. engagement type automobile differential according to claim 4, it is characterized in that, described interior bar comprises left bar and right bar, the left end of described left bar is linked together with described planet wheel shaft by left energy-absorbing spring, the right side of described left bar is provided with some the first commutating tooths along the distribution of left bar circumference, the right-hand member of described right bar is linked together with described planet wheel shaft by right energy-absorbing spring, the left side of described right bar is provided with some the second commutating tooths along the distribution of right bar circumference, and described first commutating tooth and the second commutating tooth mesh together.
6. engagement type automobile differential according to claim 4, is characterized in that, is filled with rubbing agent between described planet wheel shaft and interior bar.
7. engagement type automobile differential according to claim 1 and 2, is characterized in that, described active drive block is provided with cushion pad, and described cushion pad is loop configuration, and the driving part of described active drive block is in the region that described cushion pad surrounds.
8. engagement type automobile differential according to claim 7, it is characterized in that, the first absorbing ring that described cushion pad is provided with vacuum breaker passage and extends along cushion pad bearing of trend, the second absorbing ring extended along cushion pad bearing of trend is provided with in described first absorbing ring, adsorption tank is formed between described first absorbing ring and the second absorbing ring, described dust-absorbing groove is all connected by the space outerpace of described vacuum breaker passage with the first absorbing ring with both inner spaces of the second absorbing ring, the flat segments that the tangent direction along described planet pin extends is provided with in described vacuum breaker passage, be provided with the centrifugal force produced when being rotated by described planet wheel shaft in described flat segments to move and the plug blocking described vacuum breaker passage and the valve opening spring that plug is opened.
9. engagement type automobile differential according to claim 8, is characterized in that, is provided with the some elastomeric connector strip the first absorbing ring and the second absorbing ring linked together in described adsorption tank, and described elastomeric connector strip distributes along the first absorbing ring bearing of trend.
10. engagement type automobile differential according to claim 8, is characterized in that, the absorption end of described second absorbing ring stretches out the absorption end of described first absorbing ring.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711026867.4A CN107795657A (en) | 2015-05-09 | 2015-05-09 | Engagement type automobile differential |
| CN201510232000.9A CN105042017B (en) | 2015-05-09 | 2015-05-09 | Engagement type automobile differential |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201510232000.9A CN105042017B (en) | 2015-05-09 | 2015-05-09 | Engagement type automobile differential |
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| CN201711026867.4A Division CN107795657A (en) | 2015-05-09 | 2015-05-09 | Engagement type automobile differential |
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| CN105042017A true CN105042017A (en) | 2015-11-11 |
| CN105042017B CN105042017B (en) | 2017-11-07 |
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| CN201711026867.4A Pending CN107795657A (en) | 2015-05-09 | 2015-05-09 | Engagement type automobile differential |
| CN201510232000.9A Active CN105042017B (en) | 2015-05-09 | 2015-05-09 | Engagement type automobile differential |
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| CN201711026867.4A Pending CN107795657A (en) | 2015-05-09 | 2015-05-09 | Engagement type automobile differential |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109442023A (en) * | 2018-12-17 | 2019-03-08 | 玉环县格黎特汽车配件厂 | A kind of integral cold forging angular wheel shaft |
| CN118492445A (en) * | 2024-06-19 | 2024-08-16 | 马鞍山市铔冠重工机械有限公司 | Steel plate drilling equipment for mold production |
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| CN118492445B (en) * | 2024-06-19 | 2024-10-11 | 马鞍山市铔冠重工机械有限公司 | Steel plate drilling equipment for mold production |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105042017B (en) | 2017-11-07 |
| CN107795657A (en) | 2018-03-13 |
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Effective date of registration: 20180326 Address after: 245300 Jixi County Hongxing Industrial Park, Xuancheng, Anhui Patentee after: Jixi County Huiyang Axles Co., Ltd. Address before: 324100 Zhejiang city of Quzhou province Fonglin Town, Jiangshan City tree village duck step No. 11 Patentee before: JIANGSHAN XIANJIN ELECTROMECHANICAL TECHNOLOGY SERVICE CO., LTD. |