CN202579896U - Interaxle differential of double-axle vehicle - Google Patents
Interaxle differential of double-axle vehicle Download PDFInfo
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- CN202579896U CN202579896U CN 201220241673 CN201220241673U CN202579896U CN 202579896 U CN202579896 U CN 202579896U CN 201220241673 CN201220241673 CN 201220241673 CN 201220241673 U CN201220241673 U CN 201220241673U CN 202579896 U CN202579896 U CN 202579896U
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- thrust bearing
- axle
- annular groove
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- 230000007246 mechanism Effects 0.000 claims description 14
- 238000013461 design Methods 0.000 abstract description 4
- 238000009434 installation Methods 0.000 abstract description 3
- 238000012423 maintenance Methods 0.000 abstract description 3
- 238000005299 abrasion Methods 0.000 abstract 2
- 238000000034 method Methods 0.000 description 8
- 238000012856 packing Methods 0.000 description 7
- 238000005096 rolling process Methods 0.000 description 5
- 238000005461 lubrication Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 238000003756 stirring Methods 0.000 description 2
- TVEXGJYMHHTVKP-UHFFFAOYSA-N 6-oxabicyclo[3.2.1]oct-3-en-7-one Chemical compound C1C2C(=O)OC1C=CC2 TVEXGJYMHHTVKP-UHFFFAOYSA-N 0.000 description 1
- 208000034423 Delivery Diseases 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 210000004513 dentition Anatomy 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000011900 installation process Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 230000036346 tooth eruption Effects 0.000 description 1
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Abstract
The utility model discloses an interaxle differential of a double-axle vehicle, comprising a sliding mesh sleeve, a driving cylindrical gear, a cross axle, a planetary gear, a half axle gear and a driving axle, wherein an axial adjustment component is arranged between the driving cylindrical gear and the driving axle; through the axial adjustment component, a certain axial gap is kept between the driving cylindrical gear and the driving axle so that the end face conical teeth of the driving cylindrical gear, planetary teeth of the planetary gear and half axle teeth of the half axle gear are in proper mesh state; and the axial adjustment component is a one-way thrust bearing. According to the interaxle differential of the double-axle vehicle, a traditional adjustment shin is replaced by the one-way thrust bearing, then the abrasion of the one-way thrust bearing due to sliding friction is eliminated, the abrasion of the driving axle due to rotary friction is eliminated and the function of axial adjustment is also kept, so that the interaxle differential of the double-axle vehicle has the characteristics of being exquisite in design, simple in structure, high in safety, long in service life and convenient in installation and maintenance.
Description
Technical field
The utility model relates to a kind of heavy-duty car drive unit, relates in particular to differential mechanism between a kind of doube bridge vehicle bridge.
Background technique
Mean differential; It is interaxial differential; Be widely used for the heavy-duty car double driving shafts; Like homemade Jiefang brand CA3250P66K2L1TA1 type, this reaches the heavy-duty car that a steyr board ZZ3253N4041C1 type, the northern board ND3251B41J type of running quickly etc. use AC series, 300 serial hub reduction vehicle bridge (jackshaft).As shown in Figure 3; Present normally used interaxial differential; Comprise sliding engaged cover, active cylindrical gears, cross axle, planetary pinion, differential gear and driving shaft (connecting axle promptly); Be provided with axial adjustment pad between said active cylindrical gears and the driving shaft; Said axial adjustment pad makes active cylindrical gears and driving shaft keep certain axial clearance when just adorning, and then makes the end face awl tooth of active cylindrical gears and the semiaxis tooth of planetary planet tooth and differential gear be in the proper engagement state, thereby guarantees the normal operation of each parts of between centers retarder.
But; In service at the between centers retarder; Initiatively cylindrical gears is except receiving and the driven cylindrical gear (not shown) normal delivery of its engagement radially the moment of torsion; Also to receive the axial force of two aspects simultaneously: the one, the axial force that initiatively produces in the semiaxis tooth engagement driving process of the end face of cylindrical gears awl tooth and planetary planet tooth and differential gear, the 2nd, the axial force that initiatively receives in cylindrical gears and the driven cylindrical gear (not shown) engagement process.These two axial forces force initiatively jointly, and cylindrical gears moves after producing axially; Thereby make between axial adjustment end face and the adjustment pad of cylindrical gears initiatively with the Thrust Faces of driving shaft with adjust pad and produce rapid sliding axle to wearing and tearing; And then cylindrical gears and planetary back lash are increased gradually and transmission is not steady; And then cause the bump or shock loads; Particularly in the working environment of high-speed and high-temperature, often causing initiatively, tooth takes place to beat in cylindrical gears, planetary pinion and differential gear.In addition; Because the adjustment pad is unfixing; Be in operation and rotate, initiatively the cylindrical gears force in radial is applied to it, and makes adjustment pad inner edge contact the friction that rotates with the driving shaft outer surfaces; Can form the gauge wear groove in the driving shaft contact position, can preceding driving shaft be twisted off from the adjustment pad when serious.
People are in order to produce axially wearing and tearing with the Thrust Faces of driving shaft with the adjustment pad between the axial adjustment end face that solves cylindrical gears initiatively and the adjustment pad, and adjust the gauge wear problem between pad and driving shaft, have carried out various researchs and trial.
Like " Chongqing University of Technology's journal (physical science) ", the 24th the 12nd phase of volume of December in 2010,52 pages, " the heavy goods vehicles interaxial differential holds and pushes away the packing ring stress analysis ".This article holds to heavy goods vehicles between centers retarder and pushes away the packing ring problem of stress analysis, has calculated the axial force that planet dentition engagement driving is produced.And disclosed, hold and push away the suffered maximum stress 88.81MP of packing ring, and there is tangible edge effect in the intermediate portion stress distribution at 50-60MP, the stress value of contacting point, border is big; Material is that the yield strength that pushes away packing ring of holding that CuSn7Pb7Zn3 casts is 100MP, though can satisfy usage requirement basically, safety coefficient is lower, is merely 1.1, lost efficacy than being easier to, and suggestion uses bigger the holding of yield limit to push away packing ring.
And for example name is called " adjusting shim of vehicle axle differential mechanism ", is disclosed in the CN201368184 patent documentation on December 23rd, 2009.A kind of adjusting shim of vehicle axle differential mechanism is disclosed, this pad upper surface and lower surface be respectively arranged with some dovetail grooves in the radial direction, the dovetail groove of upper surface and the dovetail groove of lower surface are alternately and distribute.The structural design of this adjusting shim of vehicle axle differential mechanism has improved the inner oil lubrication of differential mechanism, has reduced the friction between gear and adjustment pad, has prolonged the working life of component, has reduced the accident rate of vehicle bridge.Though but this technological scheme has oil lubrication preferably; Initiatively between the axial adjustment end face of cylindrical gears and the adjustment pad with the Thrust Faces of driving shaft with adjust pad; And not change of the kinematic relation between adjustment pad and driving shaft, be prone to equally form and axially wear and tear and gauge wear.
Name is called " improved automobile shaft space difference speed system drive mechanism " for another example, is disclosed in the CN102410352A patent documentation on April 11st, 2012.It discloses a kind of improved automobile shaft space difference speed system drive mechanism, and core is end tooth one side at the active cylindrical gears of normally used interaxial differential, has increased an angular contact ball bearing.Adopt this technological scheme; In service at interaxial differential; Axially the adjustment pad can be protected motionless; Basically solve the axial adjustment end face of active cylindrical gears and adjust between the pad and the Thrust Faces of driving shaft and axial wearing and tearing of adjustment pad generation, reach the gauge wear problem between adjustment pad and driving shaft.But be in the proper engagement state for the end face awl tooth that makes the active cylindrical gears and the semiaxis tooth of planetary planet tooth and differential gear, still need and to realize through selecting different thick adjustment pads.
The model utility content
For addressing the above problem, the utility model provides a kind of simple in structure, safe, long service life, mean differential convenient for installation and maintenance.
The utility model is achieved through following technological scheme:
Differential mechanism between a kind of doube bridge vehicle bridge; Comprise sliding engaged cover, active cylindrical gears, cross axle, planetary pinion, differential gear and driving shaft; Be provided with axial adjustment component between said active cylindrical gears and the driving shaft; Said axial adjustment component makes active cylindrical gears and driving shaft keep certain axial clearance; It is characterized in that: said axial adjustment component is an one direction thrust bearing; Said one direction thrust bearing is installed in the end that the is arranged in cylindrical gears initiatively assembling annular groove to the engaging tooth radially inner side, the axial end of the B ring of said one direction thrust bearing and assembling annular groove away from end to the groove bottom of engaging tooth lean on mutually, its radially inner side is gapped with driving shaft, the radial outside that the A of said one direction thrust bearing encircles is gapped with the corresponding diametral surface that assembles annular groove, the radially thrust surface of its axial end and driving shaft leans on mutually.
Adopt the present technique scheme; Because the A of thrust-bearing ring is that static, B ring also is static with respect to the active cylindrical gears with respect to driving shaft; Have between A ring, B ring rolling and retainer thereof relative to driving shaft and initiatively cylindrical gears rotates, thereby the wearing and tearing that endwisely slip of having eliminated axle and adjustment component wear and tear with rotation radially, thereby reduced accident rate; Improve Security, prolonged working life.Simultaneously, also because of assemblies such as one direction thrust bearing B ring, A ring are separable, when installation and maintenance; Can be through selecting the different-thickness of A ring and/or B ring; Make the end face awl tooth of active cylindrical gears and the semiaxis tooth of planetary planet tooth and differential gear be in the proper engagement state, and keep axial clearance corrective action thereby deft design; Simple in structure, more economical.
The further improvement of the utility model, said one direction thrust bearing are single direction thrust ball bearing.
Adopting technique scheme, is more to adapt to high rotating speed because of single direction thrust ball bearing than other one direction thrust bearing.
Further improving again of the utility model, the radial outer side of the B ring of said one direction thrust bearing and assembling annular groove are away from holding to the corresponding diametral surface drive fit of the groove bottom of engaging tooth.
Adopting technique scheme, is that B encircles the assembling annular groove of packing into earlier when assembling; And be tightly fixed, be benchmark with it, rolling element of packing into after can making and retainer thereof and A encircle aligning alignment with it; Thereby guaranteed the normal rotation of thrust-bearing, guaranteed working life.
Further improving again of the utility model; The diameter at the end face engaging tooth mouth place of said assembling annular groove is slightly smaller than the B ring of thrust-bearing and the external diameter of A ring; In when assembling, B ring and A ring are clamp-oned receiving under the condition of axial pressure from the end face engaging tooth mouth of assembling annular groove.
Adopt technique scheme; Because of thrust-bearing B ring, A ring and rolling element and retainer thereof are to separate; In installation process, thrust-bearing B ring, A ring and rolling element and retainer position thereof are limited in the assembling annular groove relatively, thereby make follow-up be sleeved on the driving shaft more convenient; And help B ring, A ring and rolling element and the alignment of retainer aligning thereof, the working life of further guaranteeing thrust-bearing.
Further improving again of the utility model, the end of said sliding engaged cover be provided with to the radially inner side of engaging tooth one direction thrust bearing the A ring hold annular groove.
Adopt technique scheme; Be to bore the semiaxis tooth of tooth and planetary planet tooth and differential gear when being in the proper engagement state because of selecting the A ring and the different-thickness of B ring to adjust the end face of cylindrical gears initiatively; The position of the axial end that leans on mutually with the radially thrust surface of driving shaft that occurs A ring sometimes can surpass the root of the end of cylindrical gears initiatively to engaging tooth; As not the end of sliding engaged cover be provided with to the radially inner side of engaging tooth one direction thrust bearing the A ring hold annular groove; Can make the end of sliding engaged cover be in half engagement to the engagement of engaging tooth, can reduce the intensity at engagement position to the end of engaging tooth and active cylindrical gears.
Description of drawings
Fig. 1 is the structural representation of the utility model;
Fig. 2 is the local enlarged diagram in A place of Fig. 1;
Fig. 3 is the structural representation of traditional interaxial differential.
Wherein: 1-sliding engaged cover, 2-is cylindrical gears initiatively, 3-cross axle, 4-planetary pinion, 5-differential gear, 6-driving shaft; The 7-one direction thrust bearing, 8-end face awl tooth, 9-planet tooth, 10-semiaxis tooth, 11-are held to engaging tooth; 12-assembles annular groove, the 13-B ring, and the 14-A ring, the 15-axial end, 16-is thrust surface radially; The 17-axial end, the 18-groove bottom, 19-holds to engaging tooth, and 20-holds annular groove, and 7A-adjusts pad.
Embodiment
Further describe the technological scheme of the utility model below in conjunction with accompanying drawing.
Like Fig. 1, shown in Figure 2; Differential mechanism between a kind of doube bridge vehicle bridge; Comprise sliding engaged cover 1, active cylindrical gears 2, cross axle 3, planetary pinion 4, differential gear 5 and driving shaft 6; Be provided with axial adjustment component between said active cylindrical gears 2 and the driving shaft 6; Said axial adjustment component makes initiatively, and cylindrical gears 2 keeps certain axial clearance with driving shaft 6; And then make the end face awl tooth 8 of active cylindrical gears 2 be in tight engagement with the planet tooth 9 of planetary pinion 4 and the semiaxis tooth 10 of differential gear 5; It is characterized in that: said axial adjustment component is an one direction thrust bearing 7; Said one direction thrust bearing 7 is installed in the end that the is arranged in cylindrical gears 2 initiatively assembling annular groove 12 to engaging tooth 11 radially inner sides, the axial end 17 of the B ring 13 of said one direction thrust bearing 7 and assembling annular groove 12 away from end to the groove bottom 18 of engaging tooth 11 lean on mutually, its radially inner side is gapped with driving shaft 6, the radial outside of the A ring 14 of said one direction thrust bearing 7 is gapped with the corresponding diametral surface that assembles annular groove 12, the radially thrust surface 16 of its axial end 15 and driving shaft 6 leans on mutually.
Said one direction thrust bearing 7 can be thrust ball bearing and thrust roller bearing, preferably single direction thrust ball bearing.
The radial outer side of the B ring 13 of said one direction thrust bearing 7 and assembling annular groove 12 are away from holding to the corresponding diametral surface drive fit of the groove bottom of engaging tooth 11.
The diameter at 11 mouthfuls of places of end face engaging tooth of said assembling annular groove 12 is slightly smaller than the B ring 13 of thrust-bearing 7 and the external diameter of A ring 14, when assembling, B ring 13 and A ring 14 is clamp-oned for 11 mouthfuls receiving under the condition of axial pressure from the end face engaging tooth of assembling annular groove 12.
The end of said sliding engaged cover 1 be provided with to the radially inner side of engaging tooth 19 one direction thrust bearing 7 A ring 14 hold annular groove 20.
Through test; The active cylindrical gears 2 that adopts former design adjustment pad is installed on the driving shaft; Firmly stir initiatively cylindrical gears 2, can only rotate a week at most, and will adopt the active cylindrical gears 2 of the utility model thrust ball bearing to be installed on the driving shaft; Stir initiatively cylindrical gears 2 with identical power, rotatable at least 10 weeks; Adopt the utility model technological scheme ten surplus a car, trial run more than a year, operation conditions is good.
Claims (5)
1. differential mechanism between a doube bridge vehicle bridge; Comprise sliding engaged cover (1), active cylindrical gears (2), cross axle (3), planetary pinion (4), differential gear (5) and driving shaft (6); Be provided with axial adjustment component between said active cylindrical gears (2) and the driving shaft (6); Said axial adjustment component makes initiatively, and cylindrical gears (2) keeps certain axial clearance with driving shaft (6); It is characterized in that: said axial adjustment component is one direction thrust bearing (7); Said one direction thrust bearing (7) is installed in the end that is arranged in cylindrical gears (2) the initiatively assembling annular groove (12) to engaging tooth (11) radially inner side; The axial end (17) of the B of said one direction thrust bearing (7) ring (13) and assembling annular groove (12) away from end to the groove bottom (18) of engaging tooth (11) lean on mutually, its radially inner side is gapped with driving shaft (6), the radial outside of the A ring (14) of said one direction thrust bearing (7) is gapped with the corresponding diametral surface that assembles annular groove (12), the radially thrust surface (16) of its axial end (15) and driving shaft (6) leans on mutually.
2. differential mechanism between a kind of doube bridge vehicle bridge according to claim 1 is characterized in that: said one direction thrust bearing (7) is a single direction thrust ball bearing.
3. differential mechanism between a kind of doube bridge vehicle bridge according to claim 1 and 2 is characterized in that: the radial outer side of the B ring (13) of said one direction thrust bearing (7) and assembling annular groove (12) are away from holding to the corresponding diametral surface drive fit of the groove bottom of engaging tooth (11).
4. the mean differential of a kind of two bridge cars as claimed in claim 3; It is characterized in that: the diameter at the end face engaging tooth (11) of said assembling annular groove (12) mouthful place is slightly smaller than the B ring (13) of one direction thrust bearing (7) and the external diameter of A ring (14); In when assembling, B ring (13) and A ring (14) mouthful is clamp-oned receiving under the condition of axial pressure from the end face engaging tooth (11) of assembling annular groove (12).
5. differential mechanism between a kind of doube bridge vehicle bridge according to claim 4 is characterized in that: the end of said sliding engaged cover (1) be provided with to the radially inner side of engaging tooth (19) one direction thrust bearing (7) A ring (14) hold annular groove (20).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220241673 CN202579896U (en) | 2012-05-25 | 2012-05-25 | Interaxle differential of double-axle vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220241673 CN202579896U (en) | 2012-05-25 | 2012-05-25 | Interaxle differential of double-axle vehicle |
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| Publication Number | Publication Date |
|---|---|
| CN202579896U true CN202579896U (en) | 2012-12-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220241673 Expired - Lifetime CN202579896U (en) | 2012-05-25 | 2012-05-25 | Interaxle differential of double-axle vehicle |
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| Country | Link |
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| CN (1) | CN202579896U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102705473A (en) * | 2012-05-25 | 2012-10-03 | 陈永康 | Interaxle differential of dual-axle automobile |
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2012
- 2012-05-25 CN CN 201220241673 patent/CN202579896U/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102705473A (en) * | 2012-05-25 | 2012-10-03 | 陈永康 | Interaxle differential of dual-axle automobile |
| CN102705473B (en) * | 2012-05-25 | 2015-05-20 | 陈永康 | Interaxle differential of dual-axle automobile |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20121205 Effective date of abandoning: 20150520 |
|
| RGAV | Abandon patent right to avoid regrant |