CN109849649A - The transverse drive shaft of the power drive system of motor vehicles including internal combustion engine and speed changer - Google Patents
The transverse drive shaft of the power drive system of motor vehicles including internal combustion engine and speed changer Download PDFInfo
- Publication number
- CN109849649A CN109849649A CN201811427762.4A CN201811427762A CN109849649A CN 109849649 A CN109849649 A CN 109849649A CN 201811427762 A CN201811427762 A CN 201811427762A CN 109849649 A CN109849649 A CN 109849649A
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- China
- Prior art keywords
- drive shaft
- transverse drive
- transverse
- following
- constant velocity
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/22—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of main drive shafting, e.g. cardan shaft
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
The present invention relates to a kind of transverse drive shaft of power drive system (6), which can be connected to the transmission output shaft (4) of driving unit (1) by inner constant velocity joint (5) and be connected to the wheel that can be turned to (9) by outside constant velocity cardan joint (7).The object of the present invention is to provide a kind of transverse drive shafts (6) of type, by the transverse drive shaft, at least reduces and potentially eliminate the radial vibration for introducing wheel suspension or wheel installation part and bodyshell (2) or cause the power of these vibrations.The purpose realizes that transverse drive shaft (6) is characterized in that transverse drive shaft (6) have at least one recess (16) by transverse drive shaft (6).
Description
Technical field
The present invention relates to a kind of transverse drive shaft of power drive system, which can be connected by inner constant velocity joint
It is connected to the transmission output shaft of driving unit, and the wheel that can be turned to is connected to by outside constant velocity cardan joint.
Background technique
Noise reduction is absorbed in the development in vehicle acoustical field at the very start.It is most significantly internal combustion hair first in this respect
Main Noise Sources of the motivation as motor vehicles, and the auxiliary unit that also will have decisive role to overall noise discharge later
As noise source.
It attempts not only to reduce the noise as caused by motor vehicles more and more, also influences in a targeted way or use it
, this is also generally referred to as Noise Design or sound design.Due to recognizing purchase decision of the potential customer when buying vehicle
It is influenced can not be ignored by the noise of internal combustion engine or vehicle, this facilitate this developments.Therefore, the driver of sport car
Prefer the vehicle or engine of the kinetic characteristic of the prominent vehicle of its noise.
Air borne sound source can will be divided into as the noise source on motor vehicles in principle and car body propagates sound source.
Air borne sound source includes the fan noise of such as inlet noise, exhaust outlet noise and radiator, and car body passes
Broadcasting sound source especially includes being attached to the power drive system of bodyshell by engine mount and being also similarly installed at
Rolling tire on bodyshell.
The engine structure for causing it to generate car body propagation acoustical vibration due to impact and alternating force passes through its engine
It is air borne sound that car body is propagated acoustic radiating by surface, and generates actual engine noise in this way.
Most important component with impact and power excitation is crankcase, cylinder block, cylinder cover, crank driver, piston
And valve actuator.These components are exposed under inertia and gas force.
Crankshaft and the driveline components being connected thereto are formed together vibrational system.Here, by becoming on the time
The rotary force of change makes crankshaft carry out whirling vibration, which introduces crankshaft by the connecting rod being hinged on each crankshaft journal.
Here, the whirling vibration of crankshaft is caused to be propagated the noise of acoustic radiating due to car body and be also resulted in since car body propagation sound draws
Enter the noise in bodyshell and internal combustion engine.
Here, when in the case where intrinsic frequency range underexcitation crankshaft, it may appear that high whirling vibration amplitude, this even meeting
Lead to permanent fault.
Because of the high dynamic load being applied on crankshaft by inertia and gas force, manufacturer is required in design internal combustion engine
Most comprehensive feasible (optimizing) mass balance of Shi Shixian.Here, term " mass balance " includes compensating or reducing inertia force
External action all measures.In this respect, the igniting of the rotation of crankshaft, the quantity of cylinder and arrangement and each cylinder is suitable
Sequence is selected as in a manner of realizing optimal mass balance.
The whirling vibration of crankshaft leads to the fluctuation of speed of internal combustion engine and also via timing mechanism or camshaft actuated
Device is transmitted to camshaft, and wherein camshaft itself also constitutes vibrational system and can cause other system (especially valve
Driver) vibration.It is equally possible by the way that vibration is introduced other auxiliary units by bent shaft-driven traction mechanism drive.
In addition, the vibration of crankshaft is introduced in power drive system, can occur via power drive system to speed changer and driving
Axis until vehicle tire to front transfer.
In order to reduce the fluctuation of speed, increase the quality of vibrational system by the way that flywheel is arranged on crankshaft.More due to quality
Greatly, system shows increased inertia.The rotary motion of crankshaft is more evenly.
If overall be fixed to crankshaft in side and be connected to the flywheel design of speed changer by clutch in the other side
For double mass flywheel, then flywheel also has the function of that damper, damper reduce the whirling vibration between clutch and driver.
In order to inhibit the whirling vibration in crankshaft or power drive system, rotary shock absorber, i.e. torsion damping can be provided
Device.Relative motion due to damper block relative to crankshaft, a part of whirling vibration energy are dissipated by friction operation.
Development in terms of engine noise reduction makes the noise section (i.e. real engine noise) of engine continuous
It reduces.Modern motor is commonly provided with the internal combustion engine of very quiet operation, can almost no longer perceive inside the vehicle
To its gimp, or in some cases, gimp is even flooded by such as other noises such as noise, ventilation of rolling wheel
Not yet.
It propagates except sound except through the car body that engine mount introduces, is even more important to acoustics driver comfort
It is by the installation part and suspension of laterally driven axial tire or wheel and thus to the car body propagation sound of bodyshell introducing
Sound.The vibration being introduced on rare occasion via transverse drive shaft can be felt in steering wheel and seat by the driver of motor vehicles
Know.As a result, comfort is affected in particularly disadvantageous mode.Particular problem in this case is with fluid drive
Vibration characteristics or noise characteristic of the internal combustion engine of device in idling mode.
33 18 449 C2 of Germany Patent document DE is related to the above problem, and the present invention is also such.Fig. 1 shows motor-driven
The details of the power drive system of vehicle, the i.e. wheel turned on bodyshell 2 with associated transverse drive shaft 6 together
9 installation part 13,14 and suspension 15.
Describe the driving unit 1 of the motor vehicles with front-wheel drive, which uses rubber bumper 3 as starting
Machine installation part is mounted on chassis 2.In every side lateral arrangement transmission output shaft 4 of driving unit 1, transmission output shaft 4
Transverse drive shaft 6 is connected to by inner constant velocity joint 5.A part of transverse drive shaft 6 is connected by outside constant velocity cardan joint 7
It is connected to spindle nose 8, spindle nose 8 receives and drives the wheel 9 that can be turned to.
Spindle nose 8 rotates in knuckle 10, and knuckle 10 passes through upper ball joint 11 and lower globe joint 12 pivotly
It is mounted on the outer end of two transverse links 13,14.In its inner end, two transverse links 13,14 are fixed to chassis in hinged way
2.Draft hitch 15 is arranged between transverse link 13 and chassis 2.
Inner constant velocity joint 5 is typically designed to three pin-type slip joint 5 comprising three pin-type and bell.Three pin-type connects
First 5 axially displaceable property prevents axial vibration (to introduce transverse drive shaft 6 referring to double-head arrow f) or filter out vibration along axial direction
It is dynamic.
In contrast, the radial vibration of transmission output shaft 4 by inner constant velocity joint 5 unhinderedly (i.e. without
Filter ground) it is introduced into transverse drive shaft 6.These radial vibrations (referring to arrow F) pass through rigid transverse drive shaft 6 from inner constant velocity ten thousand
Outside constant velocity cardan joint 7 to section 5 towards wheel side dynamically transmit and process spindle nose 8, knuckle 10 and transverse link 13,14 into
Enter in chassis 2.Some of them vibration is passed forward to steering wheel and pilot set and is perceived by driver.As a result, comfort
It is affected in particularly disadvantageous mode.
To solve the above-mentioned problems, 33 18 449C2 of patent document DE, which is proposed, is intended to prevent radial vibration from reaching spindle nose
8 measure.In other words, it is had an impact in the transmission path of radial vibration or transmission path.
It is advantageous that including transverse drive shaft 6 and being connected to the component of drive shaft 6 (for example, inner constant velocity is universal
Section 5 three pin members) component give certain Mass Distribution, as a result, be intended to realize two constant velocity cardan joints 5,7 dynamic
It disconnects.
Summary of the invention
Under the background of above content, the object of the present invention is to provide described in a kind of preamble according to claim 1
The transverse drive shaft of power drive system at least reduce by the transverse drive shaft and potentially eliminate that introduce wheel outstanding
The radial vibration of frame or wheel installation part and bodyshell or the power for causing these to vibrate.
The purpose realizes that the drive shaft can be connected by inner constant velocity joint by the transverse drive shaft of power drive system
It is connected to the transmission output shaft of driving unit, and the wheel that can be turned to is connected to by outside constant velocity cardan joint, and wherein
Transverse drive shaft has at least one recess.
According to the present invention, transverse drive shaft has a recess or multiple recesses.
Reduce the flexural rigidity of transverse drive shaft in a targeted way in conjunction with recess.In other words, pass through recess, drive shaft
Become softer in bending, i.e., it is more flexible, and introduce and drive from speed changer (i.e. via transmission output shaft) in radial force
In the case where axis, bigger surrender is generated under a load.Therefore, the lesser drive shaft of rigidity according to the present invention smaller dynamic
Transmitting initially results in the radial force of radial vibration.
The flexural rigidity of transverse drive shaft selects lower, and the radial force transmitted by drive shaft is smaller, which passes through
Outside constant velocity cardan joint introduces wheel and introduces bodyshell by suspension and be passed forward to direction on rare occasion
Disk and pilot set.
It is thereby achieved that the purpose that the present invention is based on, that is, provide a kind of transverse drive shaft, extremely by the transverse drive shaft
It is few to reduce or potentially eliminate the radial vibration of introducing wheel suspension or wheel installation part and bodyshell or cause these vibrations
Power.
Radial vibration especially can be in the automatic transmission with fixation and wherein speed changer is located at the motor-driven of gear " D "
Occur in vehicle.The two sides of speed changer are set and speed changer is connected to the transverse drive shaft of wheel then in driving unit
Upper applied force, the power generate the torque around rolling axis and have vertical or radial force component.
Following embodiments of transverse drive shaft can be advantageous, wherein outside constant velocity cardan joint is ball cage type connector,
Including interior hub and outer hub and multiple balls, these balls are maintained in the retainer between interior hub and outer hub.
The other advantageous embodiments of transverse drive shaft are described below in conjunction with dependent claims.
The following embodiment of transverse drive shaft is advantageous, and wherein at least one recess is completely circumferentially (i.e. over 360 deg.)
Surround transverse drive shaft.In the current situation, at least one recess extends on the entire periphery of transverse drive shaft, specifically encloses
Longitudinal axis around drive shaft extends.
The embodiment particularly provides the manufacture view in drive shaft (especially when combining recess) on such as lathe
Advantage.
Here, the following embodiment of transverse drive shaft is advantageous, and the recess that wherein at least one circumferentially extends completely is
Annular groove.
Annular groove is characterized in that, longitudinal axis rotational symmetry of the groove relative to drive shaft.
In this case, the embodiment of notched bottoms rounded (i.e. no sharp edges and transition part) is advantageous.
In this case, the following embodiment of transverse drive shaft is similarly advantageous, at least one is circumferentially extended completely
Recess there is diameter d and length l, wherein d/D < 0.95 and l/L < 0.1, wherein D indicates the diameter and L of transverse drive shaft
Indicate the length of transverse drive shaft.
D indicates the minimum diameter of the recess at notched bottoms, and D expression combines in transverse drive shaft or the point of positioning recess
The diameter of the transverse drive shaft at place.
Recess according to the present invention relative to the size of corresponding drive shaft has determined notch effects and in individual cases
Under can be very big with difference.
Transverse drive shaft for riding motor vehicles usually has 400 to 800 millimeters of length L.According to the present invention, recessed
Mouth can be up to 40 millimeters or even longer.
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is advantageous: d/D < 0.85.
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is especially advantageous: d/D <
0.75。
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is similarly advantageous: d/D <
0.6。
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is more favorable: d/D≤0.5.
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is advantageous: l/L < 0.05.
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is advantageous: l/L < 0.0375.
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is advantageous: l/L < 0.025.
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is advantageous: l/L < 0.0125.
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is advantageous: l/L <
0.00625。
The following embodiment of transverse drive shaft is advantageous, wherein at least one recess for the drive shaft installed has away from interior
The distance L of side constant velocity cardan joint1With the distance L away from outside constant velocity cardan joint2, wherein L2/L1<0.5。
Above-described embodiment considers following facts: it is particularly advantageous that in wheel side (i.e. as close to outside constant speed ten thousand
Xiang Jie) and thus the area of the king-sized drive shaft of the bending moment caused by the radial force introduced by inner constant velocity joint
Recess is set in domain.
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is advantageous: L2/L1<0.35。
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is advantageous: L2/L1<0.25。
In this case, the embodiment for the transverse drive shaft that wherein following aspect is set up is advantageous: L2/L1< 0.2 or
L2/L1<0.15。
Detailed description of the invention
It will be based on exemplary embodiment below and the present invention will be described in more detail according to Fig. 1 and Fig. 2.In the accompanying drawings:
Fig. 1 is schematically shown according to patent document DE 33 18 449C2 and transverse drive shaft and driving unit one
The installation part and suspension of the wheel turned on bodyshell risen, and
Fig. 2 schematically shows the transverse drive shafts of the power drive system together with outside constant velocity cardan joint and spindle nose
First embodiment.
Specific embodiment
The discussion for having been combined the prior art describes Fig. 1, therefore at this moment with reference to corresponding statement.
Fig. 2 schematically shows the laterally driven of the power drive system with outside constant velocity cardan joint 7 and spindle nose 8 together
The first embodiment of axis 6.Only illustrate the supplementary features relative to Fig. 1, therefore, referring additionally to Fig. 1 and associated description.Identical ginseng
It examines title and has been used for identical component.
In installation site, transverse drive shaft 6 is connected to the transmission output shaft of driving unit by inner constant velocity joint 5
4, and can be set as rotating by transmission output shaft 4.
Drive shaft 6 is connected to the wheel that can be turned to by outside constant velocity cardan joint 7, which is received by spindle nose 8.
In the current situation, outside constant velocity cardan joint 7 is ball cage type connector 7a comprising interior hub 17 and outer hub 18 and more
A ball 19, the multiple ball 19 are maintained in the retainer (not shown) between interior hub 17 and outer hub 18.In present case
Under, outer hub 18 is formed by bell-shaped piece 20, and bell-shaped piece 20 and spindle nose 8 are integrally formed.Interior hub 17 passes through western lattice ring (Seeger-Ring)
21 are fixed against the axial displacement in drive shaft 6.
Transverse drive shaft 6 has recess 16 in wheel side as shown in the figure, and recess 16 is designed as completely in the current situation
The annular groove 16a of circumferentially extending, notched bottoms are rounded off or rounding.
Recess 16 or annular groove 16a have diameter d and length l.D indicates that the diameter of transverse drive shaft 6, L indicate laterally
The length of drive shaft 6.
Recess 16 has the distance L away from inner constant velocity joint 5 (i.e. apart from the inner end of drive shaft 6)1, and away from outside etc.
The distance L of fast universal joint 7 (i.e. apart from the outer end of drive shaft 6)2.It sets up below: L2/L1≈0.25。
Reference signs list
1 driving unit
2 bodyshells, chassis
3 engine mounts, rubber bumper
4 transmission output shafts
5 inner constant velocity joints, three pin-type slip joint
6 transverse drive shafts
7 outside constant velocity cardan joints
7a ball cage type connector
8 spindle noses
9 wheels, the wheel that can be turned to
10 knuckles
11 upper ball joints
12 lower globe joints
Transverse link on 13
14 lower transverse links
15 draft hitch
16 recesses
16a annular groove
Hub in 17
18 outer hubs
19 balls
20 bell-shaped pieces
21 western lattice rings
D recess diameter
The diameter of D transverse drive shaft
L recess length
The length of L transverse drive shaft
L1Distance of the recess away from inner constant velocity joint
L2Distance of the recess away from outside constant velocity cardan joint
Claims (16)
1. a kind of transverse drive shaft of power drive system (6), the drive shaft can be connected to by inner constant velocity joint (5)
The transmission output shaft (4) of driving unit (1) and the wheel (9) that can be turned to is connected to by outside constant velocity cardan joint (7),
It is characterized in that,
The transverse drive shaft (6) has at least one recess (16).
2. transverse drive shaft (6) according to claim 1, which is characterized in that at least one described recess (16) week completely
The transverse drive shaft (6) is surrounded to ground.
3. transverse drive shaft (6) according to claim 2, which is characterized in that at least one recess circumferentially extended completely
It (16) is annular groove (16a).
4. transverse drive shaft (6) according to claim 3, which is characterized in that it is described at least one circumferentially extend completely
Recess (16) has diameter d and length l, wherein d/D < 0.95 and l/L < 0.1, and wherein D indicates the transverse drive shaft (6)
Diameter and L indicate the length of the transverse drive shaft (6).
5. transverse drive shaft (6) according to claim 4, which is characterized in that following to set up: d/D < 0.85.
6. transverse drive shaft (6) according to claim 4 or 5, which is characterized in that following to set up: d/D < 0.75.
7. the transverse drive shaft according to one of claim 4 to 6 (6), which is characterized in that following to set up: d/D < 0.6.
8. the transverse drive shaft according to one of claim 4 to 7 (6), which is characterized in that following to set up: d/D≤0.5.
9. the transverse drive shaft according to one of claim 4 to 8 (6), which is characterized in that following to set up: l/L < 0.05.
10. the transverse drive shaft according to one of claim 4 to 9 (6), which is characterized in that following to set up: l/L <
0.0375。
11. the transverse drive shaft according to one of claim 4 to 10 (6), which is characterized in that following to set up: l/L <
0.025。
12. the transverse drive shaft according to one of claim 4 to 11 (6), which is characterized in that following to set up: l/L <
0.0125。
13. the transverse drive shaft according to one of claim 4 to 12 (6), which is characterized in that following to set up: l/L <
0.00625。
14. the transverse drive shaft according to one of preceding claims (6), which is characterized in that the drive shaft installed
(6) at least one described recess (16) has the distance L away from the inner constant velocity joint (5)1With away from the outside constant speed
The distance L of universal joint (7)2, wherein L2/L1<0.5。
15. transverse drive shaft (6) according to claim 14, which is characterized in that following to set up: L2/L1<0.35。
16. transverse drive shaft (6) according to claim 14 or 15, which is characterized in that following to set up: L2/L1<0.25。
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102017221599.2 | 2017-11-30 | ||
| DE102017221599.2A DE102017221599B4 (en) | 2017-11-30 | 2017-11-30 | Lateral drive shaft with notch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN109849649A true CN109849649A (en) | 2019-06-07 |
Family
ID=66548246
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811427762.4A Pending CN109849649A (en) | 2017-11-30 | 2018-11-27 | The transverse drive shaft of the power drive system of motor vehicles including internal combustion engine and speed changer |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN109849649A (en) |
| DE (1) | DE102017221599B4 (en) |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4068499A (en) | 1976-01-26 | 1978-01-17 | Sharp Everett H | Telescoping universal joints |
| FR2527718A1 (en) | 1982-05-26 | 1983-12-02 | Glaenzer Spicer Sa | TRANSMISSION FOR FILTERING RADIAL VIBRATIONS BETWEEN THE MOTOR SHAFT AND THE WHEEL AXIS |
| CA1285970C (en) * | 1985-12-30 | 1991-07-09 | Danny Dale Brown | Boot restraint for plunging universal joint |
| DE19960963C2 (en) | 1999-12-17 | 2002-03-28 | Daimler Chrysler Ag | Tubular shaft for the transmission of a torque |
-
2017
- 2017-11-30 DE DE102017221599.2A patent/DE102017221599B4/en active Active
-
2018
- 2018-11-27 CN CN201811427762.4A patent/CN109849649A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE102017221599A1 (en) | 2019-06-06 |
| DE102017221599B4 (en) | 2020-06-18 |
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