CN103511583A - Cylindrical gear type differential mechanism - Google Patents
Cylindrical gear type differential mechanism Download PDFInfo
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- CN103511583A CN103511583A CN201310256913.5A CN201310256913A CN103511583A CN 103511583 A CN103511583 A CN 103511583A CN 201310256913 A CN201310256913 A CN 201310256913A CN 103511583 A CN103511583 A CN 103511583A
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- 230000007306 turnover Effects 0.000 claims description 121
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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
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet 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
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun gears
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Abstract
The invention relates to a cylindrical gear type differential mechanism. According to the cylindrical gear type differential mechanism, one of the output cylindrical gears is provided with a cylindrical gear mesh part having a concave tooth surface on the cross section, and the other output cylindrical gear is provided with a cylindrical gear mesh part having a convex tooth surface on the cross section. The tip circle of the concave tooth surface mesh part is smaller than the root circle of the convex tooth surface mesh part, and an embedment joint area between epicyclic planetary gears is positioned at an axial height of the concave tooth surface mesh part. In addition, the axial length (LEP) of the embedment joint area (EP) of the planetary gears is larger than the axial length (LEW2) of the second output cylindrical gear embedment area (EW2).
Description
Technical field
The present invention relates to spur gear differential, for the driving torque producing by drive system being assigned to the first output cylindrical gears and the second output cylindrical gears, wherein, described spur gear differential has planet carrier, it is with a plurality of turnover planetary pinions along with this planet carrier turnover, and described turnover planetary pinion has formed the first turnover planetary gear set and second week turns planetary gear set.The turnover planetary pinion of described the first turnover planetary gear set is rabbeted at this and the first output cylindrical gears, and second week turns turnover planetary pinion and the second output cylindrical gears interlocking of planetary gear set, in addition, the turnover planetary pinion of first group is also rabbeted interlocking district by planetary pinion with the turnover planetary pinion of second group, thereby make oppositely (gegensinnig) rotation of like this paired turnover planetary pinion of described two turnover planetary gear set, and described two output cylindrical gearss also oppositely connect thus.
Background technique
The known spur gear differential that starts described type from document DE102009032286A1.In described spur gear differential, planetary pinion is on the axial height (Axialniveau) of the first output cylindrical gears interlocking district.This realizes by the following method,, the turnover planetary pinion of described two groups is in its diametrically and is measured as on different big or small standard pitch circles, and on the first output cylindrical gears, realized negative correction of the flank shape (Profilverschiebung), and realized positive correction of the flank shape on the second output cylindrical gears.
Known another spur gear differential that starts described type from document DE102010047143A1.On described sun gear and planet wheel, be provided with the engaging piece of Ke husband of Wei Erte Haber Novi circular arc engagement (Wildhaber/Novikov) type, in described engaging piece, gear has formed the gear teeth with the outer convex side on radial cross section, and other gears chimeric with it have formed the gear teeth with the curved tooth surface on radial cross section.Especially, at GB266, " production of the crown parabola Ke husband of Novi circular tooth gear " (Generation of Crowned Parabolic Novikov gears-Engineering Letter that the people such as 163A and Somer M.Nacy show, 15:, EL1514) in the theoretical foundation of this engaging piece has been described.
Summary of the invention
Task of the present invention is to create a kind of spur gear differential, and described spur gear differential is characterised in that compact structure form, high internal rigid and favourable mechanical movement performance.
According to the present invention, described task solves by spur gear differential, and spur gear differential has:
-be set to for the planet carrier around the turnover of differential mechanism axis,
The-the first output cylindrical gears, described the first output cylindrical gears and differential mechanism axis coaxial arrangement,
The-the second output cylindrical gears, described second exports cylindrical gears equally and differential mechanism axis coaxial arrangement,
-the first group of turnover planetary pinion, described first group of turnover planetary pinion and the first output cylindrical gears are exported cylindrical gears interlocking district (EW1) interlocking by first respectively, and
-the second group of turnover planetary pinion, described second group of turnover planetary pinion and the second output cylindrical gears are exported cylindrical gears interlocking district (EW2) interlocking by second respectively,
-wherein, each turnover planetary pinion of first group is rabbeted district (EP) interlocking with a turnover planetary pinion of second group by planetary pinion respectively,
-wherein, described the first output cylindrical gears has formed a kind of engaging piece, and the flank of tooth of engaging piece indent on radial cross section is crooked,
-wherein, described the second output cylindrical gears has formed a kind of engaging piece, and the flank of tooth of engaging piece is at the upper outside convex bending of radial cross section, and the top circle of the first output cylindrical gears is less than the root circle of the second output cylindrical gears, and
-connect described two turnover planetary gear set each have enough to meet the need planetary planetary pinion interlocking district and extend on the axial height in the first output cylindrical gears interlocking district, and
-the axial length in described planetary pinion interlocking district (EP) is greater than the axial length in the second output cylindrical gears interlocking district (EW2).
Be possible thus in an advantageous manner as follows, that is, be reduced in the planetary load of turnover within the scope of described turnover planetary pinion interlocking district, and be equilibrated at the load in the output cylindrical gears interlocking district on the second output cylindrical gears.On turnover planetary pinion and the engaging piece of realizing on cylindrical gears in output be implemented as the so-called Wei Erte Haber Ke husband of Novi circular arc engaging piece.
By according to the solution of the present invention, the engaging piece maximum load that has reduced to occur in transmission device in given axial arrangement interior volume, and realized thus the optimization to Ke husband of Wei Erte Haber Novi differential mechanism.Now, with respect on the second output cylindrical gears and there is the scheme of identical interlocking sector width between planetary pinion, in identical external loading situation, realized significantly lower tooth root pressure, and in the situation that planetary pinion-planetary Gear Contact is carried out in less extruding.Thus, on planetary pinion, also there is obviously less load, thereby made described planetary pinion can utilize the personal distance improving with respect to conventional construction form to withstand stress.
By according to the solution of the present invention, the load of uneven distribution is all the time compensated, and tooth root pressure at least further reduced in planetary pinion-planetary Gear Contact situation, until described row planetary pinion withstands stress reliably.
The solution of described invention is, the Gear Contact between described planetary pinion is widened, and in order to remain on the Gear Contact on the second output cylindrical gears, wherein, it is constant that the overall width of described differential mechanism keeps.To this, narrow planetary pinion and the if desired sun gear chimeric with it are widened.In order to keep overall width constant, on the contrary the second sun gear is designed thinlyyer, this is because sun gear that is to say that output cylindrical gears suffers significantly lower load.
According to the present invention, described the second sun gear is reducing aspect its width, but does not destroy engagement rule, thereby has obtained in addition the engaging piece that can turn round.The condition of the engaging piece that can turn round for Ke husband of Wei Erte Haber Novi circular arc transmission device is that contact ratio (Sprung ü berdeckung) is greater than 1.It is calculated as follows:
Wherein: b=tooth contact width
β=tilt angle
M=modulus
By formula, can determine tilt angle and the modulus of optimization.The narrowest described tooth contact width utilize described parameter can calculate the narrowest tooth contact width, in the situation that can also meet engagement rule.With this, provided the width ratio of sun gear:
Spur gear differential with Ke husband of Wei Erte Haber Novi circular arc engaging piece according to the present invention is especially suitable as compensation transmission device for car and trailer.
As long as also occur than the lower load of load between planetary pinion in described the first output cylindrical gears interlocking district, so the axial length of the first output cylindrical gears and thus the first axial length of exporting cylindrical gears also can be reduced.Be possible thus as follows, that is, described planetary pinion interlocking district is so constructed, thereby makes respectively to have enough to meet the need planetary pinion to going out surpass first output cylindrical gears in axial epirelief at it in the distolateral region of the second output cylindrical gears.
Described spur gear differential according to the present invention another special aspect according to the present invention is preferably so designed,, described spur gear differential has four planetary pinions pair, the right planetary pinion axis of planetary pinion is each other about differential mechanism axis, and axis symmetrically (that is to say while observing in radial cross section radially) is opposed.The position of the planetary planetary pinion axis of described turnover so determined, thereby makes by each right axis of planetary pinion parallel to each otherly or vertical orientated to limited plane, and in radial cross section, is shown as thus square.By this scheme, be possible as follows, that is, utilize suitable tooth power and substantially tangentially act on the power connection that the tooth power of exporting on cylindrical gears realizes two output cylindrical gearss.Thus, with respect to conventional construction form, especially, in planetary pinion-planetary pinion contacting part, that is to say that right planetary planetary pinion interlocking Qu Zhongye obtains significantly lower tooth root pressure connecting planetary pinion.
By solution according to the present invention, be possible as follows,, by two separately from each other the planetary pinion of diametrically contraposition to maintaining the power of described output cylindrical gears, connect, and reduce thus the contact between planetary pinion, reduce in other words planetary torque, this causes lower pressure.
According to a special aspect of the present invention, described output cylindrical gears is preferably constructed like this, thereby the number of teeth of exporting cylindrical gears can be divided exactly by the right quantity of planetary pinion.Be possible thus as follows, in respective angles (in this case 90 °), around output cylindrical gears, be evenly arranged each planetary pinion pair.Described two output cylindrical gearss that are set to obtain for power have the identical number of teeth.Yet described two planetary pinions or compensation gear have identical with respect to the lower number of teeth of output cylindrical gears equally.
At the velocity ratio i between output cylindrical gears and planetary pinion preferably in the scope 2.5 ± 20%.Preferably, be only designed to have can be by 1 or the number of teeth (prime number) that himself divides exactly for described planetary pinion.In this concrete number of teeth proposing, for output cylindrical gears, be for example 32, and for planetary pinion, be 13.The overall diameter of described planetary pinion envelope circle and the ratio of " length " planetary engaging piece width preferably, in 3 ± 20% scope, have obtained the particularly advantageous ratio of structure space demand and construction weight and differential mechanism transmission device bearing capacity in described ratio situation.
Described according to of the present invention, with the differential mechanism of four Ke husband of Wei Erte Haber Novi circular-arc planet gear mesh, can by the independent assembly that can manufacture inexpensively, be assembled in mode favourable in package technique, and be particularly suitable for producing in enormous quantities.
The particularly preferred embodiment according to the present invention, described spur gear differential is so constructed, thereby the planet axis that makes the first turnover planetary gear set is arranged on the first standard pitch circle, and the planet axis that second week turns planetary gear set is arranged on the second standard pitch circle, and described the first standard pitch circle and the second standard pitch circle have identical diameter substantially.
Described output cylindrical gears is preferably so designed, described output cylindrical gears have just as the number of teeth.Inner in group, turnover planetary pinion is embodied as the assembly that structure is identical, obtains thus in the cost advantage aspect planetary production and the simplification of loading onto in planetary gear set.
As long as be provided with correction of the flank shape in turnover on planetary pinion, this preferably so completes so, that is, the turnover planetary pinion of the first turnover planetary gear set has positive correction of the flank shape, and the turnover planetary pinion that second week turns planetary gear set has negative correction of the flank shape.By described measure, be possible as follows, that is, expand second week and turn the planetary top circle of turnover of planetary gear set with respect to the radial spacing of the top circle of the first output cylindrical gears.
According to particularly preferred embodiment of the present invention, described planet carrier is so designed, thereby makes described planet carrier directly be carried as the actuation gear that imports driving torque and arrange.Described actuation gear may be implemented as firm loop configuration.At this preferably, described actuation gear is so designed, thereby makes described actuation gear form inner opening, and wherein, described inner opening, by so moulding, obtains top circle guide portion thereby make to have enough to meet the need planetary pinion on inner opening wall.In described embodiment, the driving torque being applied on actuation gear is directly passed on turnover planetary pinion as transverse force by a plurality of top circles contact area.The construction machine load of described planet carrier is reduced thus.
Described planet carrier is preferably implemented as sheet material part.Described planet carrier can be assembled into by deep-draw sheet material shell two sheets, cup-shaped or pot shape at this, and described sheet material Ke Cong both sides are placed on actuation gear.To this as an alternative, described planet carrier can also be implemented as turnover housing, and described turnover housing is formed for other attachment regions of actuation gear, or is formed for other districts that driving torque imports.
According to a further aspect in the invention, alternative is delivered to driving torque in planetary pinion flange in above-mentioned contact by top circle, is also possible as follows, that is, each turnover planetary pinion is bearing on planet carrier.Described supporting can or complete by stud structure, described stud structure is configured on turnover planetary pinion, and described stud structure interlocking is in the hole of corresponding planet carrier, (as preferred version) completes by rest pin, described rest pin is anchored in planetary carrier, and extends through turnover planetary pinion.
By described according to the solution of the present invention, be possible as follows, that is, create the spur gear differential be set to axletree transmission device, described spur gear differential is characterised in that short especially axial arrangement length and relative low tooth loads.
Described planetary gear set that be assembled into by four planetary pinions respectively, that act on each output cylindrical gears can realize torque is imported to output cylindrical gears, and without utilize significant radial support power to support output cylindrical gears at this.
Accompanying drawing explanation
Other uniquenesses of the present invention and feature from the description below in conjunction with accompanying drawing, have been provided.Wherein:
Fig. 1 shows the plan view of spur gear differential according to the present invention under part assembled state;
Fig. 2 a shows the perspective view of the cylindrical gears of interlocking each other according to spur gear differential of the present invention;
Fig. 2 b show according to Fig. 2 a according to the axial, cross-sectional view of cylindrical gears of interlocking each other of spur gear differential of the present invention;
Fig. 3 shows according to the plan view of the turnover planet carrier of the spur gear differential transmission device of Fig. 1;
Fig. 4 shows the plan view that drives cylindrical gears according to the spur gear differential combined with transmission of the part assembling of Fig. 1.
Embodiment
Figure 1 illustrates according to spur gear differential of the present invention.Described spur gear differential comprises planet carrier 3, the first output cylindrical gears 1 being provided for around differential mechanism axis X turnover, described the first output cylindrical gears and differential mechanism axis X coaxial arrangement and the second output cylindrical gears 2 that only can be identified on aspect its tooth flange at this, described the second output cylindrical gears equally and differential mechanism axis X coaxial arrangement.Described two output cylindrical gearss 1,2 connect by turnover planetary pinion P1, P2 power.Planet axis XG1, the XG2 of described turnover planetary pinion P1, P2 is parallel to differential mechanism axis X orientation.
Described turnover planetary pinion P1 has formed the parts of first group of G1, and described turnover planetary pinion is respectively by the first output cylindrical gears interlocking district EW1 and the first output cylindrical gears 1 interlocking.Described turnover planetary pinion P2 forms the parts of second group of G2, and described turnover planetary pinion is respectively by the second output cylindrical gears interlocking district EW2 and the second output cylindrical gears 2 interlockings.Each turnover planetary pinion P1 of described first group of G1 rabbets district EP with a turnover planetary pinion P2 of second group of G2 by planetary pinion respectively and rabbets.
Described the first output cylindrical gears 1 so designs, that is, described the first output cylindrical gears forms a kind of engaging piece, and the flank of tooth of this engaging piece indent on radial cross section is crooked, that is to say and on cross section, is spherical.Described the second output cylindrical gears 2 so designs, that is, described the second output cylindrical gears forms a kind of engaging piece, the flank of tooth of this engaging piece is at the upper outside convex bending of radial cross section, wherein, in addition, the top circle of described the first output cylindrical gears 1 is less than the root circle of the second output cylindrical gears 2.Each the planetary pinion interlocking district EP that connects turnover planetary pinion P1, the P2 of described two turnover planetary gear set G1, G2 extends on the axial height of the first output cylindrical gears interlocking district EW1.
Described turnover planetary pinion P1, P2 form respectively planetary pinion to C1, C2, C3, C4.Described planetary pinion is so disposed C1, C2, C3, C4, that is, described planetary pinion is to about differential mechanism axis X diametrically contraposition.That is to say planetary pinion to C1/C3 and planetary pinion to C2/C4 diametrically contraposition.Described planetary pinion is to C1 ... the circumference spacing of C4 is 90 °.
Shown in from accompanying drawing, the turnover planetary pinion P1 of described the first turnover planetary gear set G1 and the first output cylindrical gears 1 interlocking.Described second week turns turnover planetary pinion P2 and the second output cylindrical gears 2 interlockings of planetary gear set G2.
At the interlocking district EP between turnover planetary pinion P1, the P2 of described two turnover planetary gear set G1, G2 in the axial direction and overlapping with the interlocking district EW1 between the first output cylindrical gears 1 at the turnover planetary pinion P1 of the first planetary gear set G1, that is to say and rabbet in the same axial level of district EP in the interlocking district EW1 with the first output cylindrical gears 1.As stated in the beginning, can realize thus the axial length that expands the interlocking district EP between turnover planetary pinion P1, the P2 of described two turnover planetary gear set G1, G2, and the engaging piece load that reduces to have enough to meet the need planetary pinion G1, G2.On the turnover planetary pinion P1 of described first group of G1, in fact can not get around the heeling moment that may be not parallel to the axis of corresponding planetary pinion axis XG1.The heeling moment acting on the turnover planetary pinion P2 of described second group of G2 is reduced with respect to traditional structural type.Obtained generally having high internal rigid, nuzzle intensive mechanical structure in the axial direction.As what further thoroughly discuss below, described spur gear differential is so designed,, axial length that record in the direction of differential mechanism axis X after measured,, planetary pinion interlocking district EP is greater than " length " turnover planetary pinion P2 of second group of G2 and the axial length of the interlocking district EW2 between the second output cylindrical gears 2.
It is upper that the planet axis XG1 of described the first turnover planetary gear set G1 is disposed in the first standard pitch circle T1, and the planet axis XG2 that second week turns planetary gear set G2 is disposed on the second standard pitch circle T2.Described the first standard pitch circle T1 and the second standard pitch circle T2 have identical diameter in shown embodiment herein.The engaging piece geometrical construction of the planetary pinion P2 of described the first output cylindrical gears 1 and second group of G2 is so coordinated each other, that is the top circle KG2 that, second week turns the turnover planetary pinion P2 of planetary gear set G2 do not have and the top circle K1 of the first output cylindrical gears 1 overlapping.
Described output cylindrical gears 1,2 is so designed in described embodiment, that is, described output cylindrical gears has the identical number of teeth.The planetary pinion P2 of described the first output cylindrical gears 1 and second group of G2 forms indent engaging piece according to the engagement of Ke husband of Wei Erte Haber Novi circular arc.The planetary pinion P1 of described the second output cylindrical gears 2 and first group of G1 forms evagination engaging piece according to the engagement of Ke husband of Wei Erte Haber Novi circular arc.Described turnover planetary pinion P1, P2 are from so designing in this, that is, described turnover planetary pinion has the identical number of teeth.
Described planet carrier 3 is so designed, that is, this planet carrier has directly carried to be arranged for and import actuation gear 5(comparison diagram 4 driving torque, that do not express in this accompanying drawing).Described actuation gear 5 may be implemented as firm ring structure.Described planet carrier 3 is embodied as plate forming part in this certainly, and is combined by two sheet material shells, and described sheet material Ke Cong both sides are placed in the ring section of the actuation gear 5 not being shown specifically.Described turnover planetary pinion P1, P2 are bearing in this and complete by rest pin 6G1,6G2, and described rest pin is anchored in planetary carrier 3, and extend through turnover planetary pinion P1, P2, and rotatably support planetary pinion.
Describedly at the spur gear differential shown in this, especially as axletree transmission device, be suitable for many ruts formula automobile.Described spur gear differential is characterised in that short especially axial arrangement length and relative low tooth loads.
Described engaging piece and supporting can so be constructed, that is, it provides sufficient space, to avoid the possible internal pressure based on static overdetermination.Described cylinder engaging piece self is preferably implemented as inclination engaging piece.
In Fig. 2 a, further illustrated according to the gear geometry of spur gear differential of the present invention and interlocking scheme.The turnover planetary pinion P2 of described second group of G2 and the second output cylindrical gears 2 interlockings.Described output cylindrical gears 2 integrally, that is to say single-piece and implements together with wheel hub liner segment 2a.Described wheel hub liner segment 2a has carried interior engaging piece 2b, and for being contained in the insertion section of this wheel drive shaft not shown further.Described the first output cylindrical gears 1 is only being configured with interior engaging piece in the visible wheel hub liner segment of part 1a at this too.Described two output cylindrical gearss 1,2 are produced as formed component, especially extrusion modling part.
" longer " turnover planetary pinion P2 of described second group of G2 is being so designed aspect its axial length, that is, described turnover planetary pinion covers the evagination flank engagement portion of curved tooth surface engaging piece and second driven gear 2 of the first driven gear 1 in the axial direction.Design and layout based on described turnover planetary pinion P2 and the first output cylindrical gears 1, the curved tooth surface engaging piece of the turnover planetary pinion P2 of second group of G2 is not rabbeted with the curved tooth surface engaging piece of the first output cylindrical gears 1.At the power between the turnover planetary pinion P2 of described output cylindrical gears 1 and second group of G2, connect in the situation that first group of G1, be equipped with the first turnover planetary pinion P1(comparison diagram 1 of evagination flank engagement portion) in the middle of be connected.The axial length of the outer convex side cylindrical gears engaging piece of the turnover planetary pinion P1 of described first group of G1 is substantially shorter than the axial length of the curved tooth surface cylindrical gears engaging piece of second group of G2 turnover planetary pinion P2.Each axial length of the outer convex side cylindrical gears engaging piece of described the first turnover planetary pinion P1 is preferably substantially suitable with the axial length of the curved tooth surface cylindrical gears engaging piece of the first output cylindrical gears 1.
Described first group of G1 turnover planetary pinion P1 is so constructed and supports, that is, described turnover planetary pinion can not be rabbeted with the outer convex side cylindrical gears engaging piece of the second output cylindrical gears 2.If desired, the demarcation strip that is provided with perforation or breach can be installed on differential mechanism transmission device, and described demarcation strip covers out the distolateral of the turnover planetary pinion P1 of first group of G1 and the engaging piece of the second output cylindrical gears 2.
In the illustrated embodiment, the number of teeth of described sun gear 1,2 can be by the right quantity of planetary pinion, that is to say that " by 4 " divide exactly.As already implemented, can be achieved as follows thus, that is, the corresponding angle (being 90 ° herein) of take is evenly arranged corresponding planetary pinion opposing connection sun gear 1,2.Described two output cylindrical gearss 1,2 that are set to obtain for power have the identical number of teeth.Described two planetary pinions compensate in other words gear P1, P2 and have equally the identical number of teeth.
At the velocity ratio i between described output cylindrical gears 1,2 and corresponding planetary pinion P1, P2 preferably in the scope 2.5 ± 20%.Described planetary pinion P1, P2 are only designed to have can be by 1 and the number of teeth (prime number) that himself divides exactly.Described is for example " 32 " for sun gear 1,2 in the number of teeth shown in this, and for planetary pinion P1, P2, is " 13 ".The whole diameter of envelope circle of described planetary pinion P2 and the ratio of the engaging piece width B of " length " planetary pinion P2 preferably, in 3 ± 20% scope, have obtained structure space demand and construction weight with respect to the particularly advantageous ratio of the bearing capacity of differential mechanism transmission device in this ratio situation.
The spur gear differential of being illustrated in the structure aspect its cylindrical gears at this is characterised in that, the axial length L EP of described planetary pinion interlocking district EP is greater than the axial length L EW2 of the second output cylindrical gears interlocking district EW2.The coordination of the Length Ratio of described LEP and LEW2 so completes,, engaging piece load is by mutual balance, the interlocking load that its method reduces in planetary pinion interlocking district EP, has enough to meet the need planetary engaging piece by extending distance L EP, and improve interlocking load in interlocking district EW2, turn the engaging piece between planetary pinion P2 at the second output cylindrical gears 2 and second week.The width of arranging the length L EW2 that has obtained the length L EP of described interlocking district EP and rabbeted district EW2 at the cylindrical gears for axle differential mechanism is than the scope at 1.3+/-20%.
In Fig. 2 b, the shortening of the length L EW2 of the prolongation of the length L EP of the interlocking district EP arranging according to the present invention and interlocking district EW2 is further explained.Therefore the evagination flank engagement portion of described the second output cylindrical gears 2 has than the shorter axial length of axial length of planetary pinion P1 first group of G1, that be equipped with equally evagination flank engagement portion.
Figure 3 illustrates planetary carrier.From described accompanying drawing, can see planetary pinion axis XG1,XG2 orientation.Described spur gear differential according to the present invention is so designed,, described spur gear differential has four planetary pinions pair, right planetary pinion axis XG1, the XG2 of planetary pinion each other about differential mechanism axis X-axis line symmetrically (that is to say on radial cross section radially) opposed.The planetary planetary pinion axis XG1,XG2 of described turnover is determined like this at this position,, plane E1, E2, E3, E4 XG1, XG2 being limited by the right corresponding axis of planetary pinion is parallel to each other or is vertical orientated, and therefore as discernible, on radial cross section, be depicted as square.As what implemented above, by described scheme, be possible as follows, that is, utilize the tooth power of suitable tooth power and tangential effect substantially to realize two power connections of exporting cylindrical gearss 1,2.Obtained thus with respect to the significantly lower tooth root pressure of traditional structural type.Described planetary pinion axis XG1, that XG2 is positioned at standard pitch circle T1, T2 is upper, and described standard pitch circle is identical at its diametrically.Described axis is 90 ° to the circumference spacing of XG1, XG2.
Figure 4 illustrates under open mode according to spur gear differential of the present invention.Described planet carrier 3 is produced as double type sheet material part at this, and it has formed the jointing that can not be identified in detail at this.Described jointing forms supporting structure, in described supporting structure, and corresponding two output cylindrical gearss 1,2, its wheel hub liner segment is by radial support in definite saying.Because from planetary pinion being shown to being arranged according to the present invention two driven gears 1,2 to the transverse force of compensation substantially distributes, thus do not produce described supporting structure, significantly, depend on the radial load of load.Although not shown at this, can realize sealed planetary gear carrier 3 and wheel hub liner segment 1a, 2a, and utilize oiling agent to fill the inner space of planet carrier, thereby make described differential mechanism transmission device form the member group of closed continuous lubrication.
The axial restraint of described rest pin 6G1,6G2 completes by cover piece 7 in this embodiment, and described cover piece is installed to the corresponding hole of planet carrier 3 from inside, and overlaps the distolateral of described rest pin 6G1,6G2.Described actuation gear 5 is constructed to the cylindrical gears of engagement, and is contained between two sheet material shells that form planet carrier 3, or is arranged on sheet material shell-side face.
Described output cylindrical gears 1,2 is so designed and arranges, that is, the cylindrical gears engaging piece of output cylindrical gears is in the adjacent position of nuzzling.The tip diameter of described two output cylindrical gearss 1,2 is so different, that is, the tip diameter of the first output cylindrical gears 1 is substantially suitable with the root diameter of the second output cylindrical gears 2.Generally, the engaging piece geometrical construction of described two output cylindrical gearss 1,2 is by coordinated with each other, thereby make cannot be scarfed in the cylindrical gears engaging piece of the first output cylindrical gears 1 with each turnover planetary pinion P2 of the second output cylindrical gears 2 interlockings, yet can on its axial height, be scarfed in the cylindrical gears engaging piece of the first turnover planetary pinion P1.
In spur gear differential according to the present invention, interlocking district EP between turnover planetary pinion P1, the P2 of described two turnover planetary gear set G1, G2 in the axial direction and overlapping with the first interlocking district EW1 exporting between cylindrical gears 1 at the turnover planetary pinion P1 of the first planetary gear set G1, that is to say on the axial height of interlocking district EP cylindrical gears engaging piece in the first output cylindrical gears 1 about differential mechanism axis X, and can not be scarfed in the engaging piece of the first output cylindrical gears 1 at the turnover planetary pinion P2 of this second group of G2.
Turnover planetary pinion P1, the P2 of described two groups G1, G2 rotate backward each other.Described turnover planetary pinion P1, P2 form altogether four independent right, described separately to being so disposed, that is, these are separately to about differential mechanism axis X diametrically contraposition.
In service at described spur gear differential, first the driving moment applying on actuation gear 5 is passed on planet carrier 3.On described planet carrier 3, place rest pin 6G1, the 6G2 of turnover planetary pinion P1, P2.Described turnover planetary pinion P1, P2 has formed two group G1, G2, wherein, the turnover planetary pinion P1 of described first group of G1 and the first output cylindrical gears 1 are rabbeted by Ke husband of Wei Erte Haber Novi circular arc engaging piece, and the turnover planetary pinion P2 of second group of G2 and the second output cylindrical gears 2 are rabbeted by Ke husband of Wei Erte Haber Novi circular arc engaging piece gear, in the described Wei Erte Haber Ke husband of Novi circular arc engaging piece, the first output cylindrical gears 1 has curved tooth surface cylindrical gears engaging piece, and the second output cylindrical gears 2 has outer convex side cylindrical gears engaging piece.Described turnover planetary pinion P1, P2 rabbet by interlocking district EP right in the situation that each other forming respectively planetary pinion.Turnover planetary pinion P1, the P2 of described two groups G1, G2 oppositely connect thus.The tip diameter of the tip diameter of the turnover planetary pinion P2 of the radial position of described axis X G2, second group of G2 and the first output cylindrical gears 1 is so coordinated, that is, only the turnover planetary pinion P1 of first group of G1 is scarfed on the first output cylindrical gears 1.The turnover planetary pinion P1 of described first group of G1 has cylindrical gears engaging piece section, and the axial length of this cylindrical gears engaging piece section is substantially suitable with the axial length of the cylindrical gears engaging piece of the first output cylindrical gears 1.The turnover planetary pinion P2 of described second group has cylindrical gears engaging piece section, and the summation of the first cylindrical gears engaging piece section length of turnover planetary pinion P1 of the axial length of this cylindrical gears engaging piece section and first group of G1 and the axial length of the engaging piece of the second output cylindrical gears 2 is suitable.The turnover planetary pinion P2 of described second group of G2 extends axially thus on the cylindrical gears engaging piece of two driven gears 1,2, and at this, is not scarfed to the first output cylindrical gears 1.
Described two driven gears 1,2 pass through four planetary pinions altogether and, to oppositely, that is to say with velocity ratio " 1 " and connect.The turnover planetary pinion P1 of first group of G1, act in the engaging piece of turnover planetary pinion P2 that whole engaging pieces on the first output cylindrical gears 1 are also scarfed to second group on the axial height of self.Strength ratio based on appearing on the axial height of periphery engaging piece of the first output cylindrical gears 1, has obtained particularly advantageous internal forces balance, and has obtained thus the load of the bearing device of the tooth loads that reduces and turnover planetary pinion P1, P2.
Described turnover planetary pinion P1, P2 and be embodied as inclination engaging piece at Ke husband of the Wei Erte Haber Novi circular arc engaging piece of the driven gear 1,2 of this and described turnover planetary pinion interlocking.The axial length of described planetary pinion interlocking district EP is greater than the axial length of the cylindrical gears engaging piece of the second output cylindrical gears 2.
Claims (10)
1. a spur gear differential, its with:
-planet carrier (3), described planet carrier is arranged for around differential mechanism axis (X) turnover,
The-the first output cylindrical gears (1), described the first output cylindrical gears and differential mechanism axis (X) coaxial arrangement,
The-the second output cylindrical gears (2), described second exports cylindrical gears equally and differential mechanism axis (X) coaxial arrangement,
-the first group (G1) has enough to meet the need planetary pinion (P1), and described first group of turnover planetary pinion rabbeted district (EW1) and described the first output cylindrical gears (1) interlocking by the first output cylindrical gears respectively, and
-the second group (G2) has enough to meet the need planetary pinion (P2), and described second group of turnover planetary pinion rabbeted district (EW2) and described the second output cylindrical gears (2) interlocking by the second output cylindrical gears respectively,
-wherein, each turnover planetary pinion (P1) of described first group (G1) is rabbeted district (EP) interlocking with a turnover planetary pinion (P2) of described second group (G2) by planetary pinion respectively,
-wherein, described the first output cylindrical gears (1) forms engaging piece, and the flank of tooth of engaging piece indent on radial cross section is crooked,
-wherein, described the second output cylindrical gears (2) forms engaging piece, the flank of tooth of engaging piece is at the upper outside convex bending of radial cross section, and the top circle (K1) of described the first output cylindrical gears (1) is less than the root circle of described the second output cylindrical gears (2), and
Extend on the axial height in described the first output cylindrical gears interlocking district (EW1) in the planetary pinion interlocking district (EP) of the turnover planetary pinion (P1, P2) of-these two turnover planetary gear set (G1, G2), and
-the axial length (LEP) in described planetary pinion interlocking district (EP) is greater than the axial length (LEW2) in described the second output cylindrical gears interlocking district (EW2).
2. spur gear differential according to claim 1, it is characterized in that, the ratio of the axial length (LEW2) in the axial length (LEP) in described planetary pinion interlocking district (EP) and described the second output cylindrical gears interlocking district (EW2) is in the scope of 1.3+/-20%.
3. spur gear differential according to claim 1 and 2, it is characterized in that, the axial length (LEW2) of the evagination flank engagement portion of described the second output cylindrical gears (2) is less than the axial length of the curved tooth surface engaging piece of described the first output cylindrical gears (1).
4. according at least one described spur gear differential in claims 1 to 3, it is characterized in that, the length summation of the cylindrical gears engaging piece of the axial length of the turnover planetary pinion (P2) of described second group (G2) and two output cylindrical gearss (1,2) is suitable.
5. according at least one described spur gear differential in claim 1 to 4, it is characterized in that, the planet axis (XG1) of the first turnover planetary gear set (G1) is arranged on the first standard pitch circle (T1), and it is upper that the planet axis (XG2) that second week turns planetary gear set (G2) is arranged in the second standard pitch circle (T2), and described the first standard pitch circle (T1) and described the second standard pitch circle (T2) have identical diameter.
6. according at least one described spur gear differential in claim 1 to 5, it is characterized in that, each turnover planetary pinion (P1) of described first group (G1) is combined into a turnover planetary pinion to (C1, C2, C3, C4) with a turnover planetary pinion (P2) of described second group (G2) respectively, and is altogether provided with four such turnover planetary pinions to (C1, C2, C3, C4).
7. spur gear differential according to claim 6, is characterized in that, every two turnover planetary pinions are to about differential mechanism axis (X) diametrically contraposition.
8. spur gear differential according to claim 7, it is characterized in that, the axis (XG1, XG2) of described turnover planetary pinion (P1, P2) be arranged to make planetary pinion to each axis of (C1, C2, C3, C4) to limiting a plane (E1, E2, E3, E4), and these planes (E1, E2, E3, E4) have been described the square concentric with differential mechanism axis (X) in the radial cross section with respect to differential mechanism axis X.
9. according at least one described spur gear differential in claim 1 to 8, it is characterized in that, the tip diameter (KG2) of the diameter of the standard pitch circle that comprises planet axis (XG1, XG2) (T1, T2), the planetary pinion (P2) of described second group (G2) and the axial length (B) of these planetary pinions (P2) are so coordinated, thus the envelope circular diameter (D) that makes described planetary pinion (P2) with the ratio of the axial length (B) of mentioning in the scope of 3:1+/-20%.
10. according at least one described spur gear differential in claim 1 to 9, it is characterized in that, the number of teeth of described planetary pinion (P1, P2) is prime number, and/or described output cylindrical gears (1,2) has the identical number of teeth.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012210692.8 | 2012-06-25 | ||
| DE201210210692 DE102012210692A1 (en) | 2012-06-25 | 2012-06-25 | Spur gear used as e.g. differential gear for e.g. passenger car, has planetary gear intervention zones whose axial length is made larger than axial length of other output spur gear intervention zones |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103511583A true CN103511583A (en) | 2014-01-15 |
| CN103511583B CN103511583B (en) | 2017-12-26 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310256913.5A Expired - Fee Related CN103511583B (en) | 2012-06-25 | 2013-06-25 | Cylindrical gear type differential mechanism |
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| Country | Link |
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| CN (1) | CN103511583B (en) |
| DE (1) | DE102012210692A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104500687A (en) * | 2014-10-30 | 2015-04-08 | 张惠杰 | Torque guide differential |
| CN105909757A (en) * | 2016-07-08 | 2016-08-31 | 天津天海同步科技有限公司 | Compact type differential |
| WO2017050160A1 (en) * | 2015-09-25 | 2017-03-30 | Byd Company Limited | Differential, power transmission system and vehicle |
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| JP2009150498A (en) * | 2007-12-21 | 2009-07-09 | Jtekt Corp | Differential gear |
| EP2101085A1 (en) * | 2008-03-05 | 2009-09-16 | OMCI S.p.A. Officine Metalmeccaniche Costruzioni Industriali | A mechanical differential |
| CN101611243A (en) * | 2007-01-31 | 2009-12-23 | 谢夫勒两合公司 | Spur-gear differential |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| GB266163A (en) | 1926-04-07 | 1927-02-24 | Wildhaber Ernest | Improvements in or relating to toothed gearing |
| DE102009032286B4 (en) | 2008-12-18 | 2022-01-05 | Schaeffler Technologies AG & Co. KG | Spur gear differential with positive and negative profile shift on the sun gears |
| DE102010047143A1 (en) | 2010-09-30 | 2012-04-05 | Schaeffler Technologies Gmbh & Co. Kg | Planetary gear, planetary differential and gearbox with the planetary differential |
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2012
- 2012-06-25 DE DE201210210692 patent/DE102012210692A1/en not_active Withdrawn
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2013
- 2013-06-25 CN CN201310256913.5A patent/CN103511583B/en not_active Expired - Fee Related
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|---|---|---|---|---|
| DE3419462A1 (en) * | 1984-02-13 | 1985-08-14 | Tractech, Inc., Warren, Mich. | GEARBOX |
| US4677876A (en) * | 1984-02-13 | 1987-07-07 | Tractech, Inc. | Torque-proportioning differential with cylindrical spacer |
| CN101611243A (en) * | 2007-01-31 | 2009-12-23 | 谢夫勒两合公司 | Spur-gear differential |
| JP2009150498A (en) * | 2007-12-21 | 2009-07-09 | Jtekt Corp | Differential gear |
| EP2101085A1 (en) * | 2008-03-05 | 2009-09-16 | OMCI S.p.A. Officine Metalmeccaniche Costruzioni Industriali | A mechanical differential |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104500687A (en) * | 2014-10-30 | 2015-04-08 | 张惠杰 | Torque guide differential |
| CN104500687B (en) * | 2014-10-30 | 2017-05-10 | 张惠杰 | Torque guide differential |
| WO2017050160A1 (en) * | 2015-09-25 | 2017-03-30 | Byd Company Limited | Differential, power transmission system and vehicle |
| US10393249B2 (en) | 2015-09-25 | 2019-08-27 | Byd Company Limited | Differential, power transmission system and vehicle |
| CN105909757A (en) * | 2016-07-08 | 2016-08-31 | 天津天海同步科技有限公司 | Compact type differential |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103511583B (en) | 2017-12-26 |
| DE102012210692A1 (en) | 2014-01-02 |
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