CN103174814A - Transmission system - Google Patents
Transmission system Download PDFInfo
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- CN103174814A CN103174814A CN2011104616042A CN201110461604A CN103174814A CN 103174814 A CN103174814 A CN 103174814A CN 2011104616042 A CN2011104616042 A CN 2011104616042A CN 201110461604 A CN201110461604 A CN 201110461604A CN 103174814 A CN103174814 A CN 103174814A
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- Prior art keywords
- gear
- semiaxis
- transmission system
- planetary carrier
- integrally formed
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 79
- 239000003638 chemical reducing agent Substances 0.000 abstract 2
- 238000013459 approach Methods 0.000 abstract 1
- 238000012986 modification Methods 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
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Abstract
The invention discloses a transmission system which comprises a differential planet gear mechanism and a speed reducer, wherein the differential planet gear mechanism comprises a first solar gear, a first half shaft integrated with the first solar gear, a second solar gear, a second half shaft integrated with the second solar gear, a plurality of planet gears meshed with the first solar gear and the second solar gear at the same time and a rotatable planet gear rack, wherein the planet gear rack can support a plurality of plant gears in a rotatable mode. The speed reducer is connected between the first half shaft and the second half shaft to enable the rotation direction of the first half shaft and the rotation direction of the second half shaft to be opposite and enable speed ratio of the second half shaft to the first half shaft to satisfy the equation n2/n1=1+-(2/i), and i represents transmission ratio of the transmission system. According to the transmission system, when the transmission ratio approaches 1, large transmission ratio can be obtained, the structure is simplified, size is reduced, efficiency is improved and cost is reduced.
Description
Technical field
The present invention relates to a kind of transmission system, especially the transmission system of big speed ratio.
Background technique
In the transmission systems such as retarder (or speed changer), gear is the most basic driving parts.The velocity ratio of pinion unit (also claiming rotating ratio) depends on gear ratio.When velocity ratio was very large, the rotating speed of small gear was very high, so the tooth of small gear is easy to fatigue fracture.For fear of this situation, in the prior art, usually big speed ratio is assigned to some levels, make every one-level power train have suitable velocity ratio.But this Multi-stage transmission has caused the volume of transmission system large, complex structure, and cost is high, and transmission efficiency is low.
Summary of the invention
The problem that causes in order to solve prior art big speed ratio transmission system Multi-stage transmission according to a first aspect of the invention, provides a kind of transmission system, and it comprises differential planet gear mechanism and retarder.Described differential planet gear mechanism comprises: the first sun gear, with integrally formed the first semiaxis of described the first sun gear, secondary sun wheel, with integrally formed the second semiaxis of described secondary sun wheel, mesh a plurality of planetary pinions of described the first sun gear and described secondary sun wheel and the planetary carrier that can rotate, the described a plurality of planetary pinions of described planetary carrier rotatably support simultaneously.Described retarder is connected between described the first semiaxis and described the second semiaxis, makes the direction of rotation of described the first semiaxis and described the second semiaxis, and makes the ratio n of the rotating speed of described the second semiaxis and described the first semiaxis
2/ n
1=1 ± (2/i), wherein, n
1Be the rotating speed of described the first semiaxis, n
2Be the rotating speed of described the second semiaxis, i is the velocity ratio of described transmission system, i=n
1/ n
H, n
HIt is the rotating speed of described planetary carrier.
According to a second aspect of the invention, provide a kind of transmission system, it comprises differential planet gear mechanism and accelerator.Described differential planet gear mechanism comprises: the first sun gear, with integrally formed the first semiaxis of described the first sun gear, secondary sun wheel, with integrally formed the second semiaxis of described secondary sun wheel, mesh a plurality of planetary pinions of described the first sun gear and described secondary sun wheel, the planetary carrier that can rotate, the described a plurality of planetary pinions of described planetary carrier rotatably support simultaneously.Described retarder is connected between described the first semiaxis and described planetary carrier, makes the sense of rotation of described the first semiaxis and described planetary carrier identical, and makes the ratio n of the rotating speed of described planetary carrier and described the first semiaxis
H/ n
1=[1 ± (1/i)]/2, wherein, n
1Be the rotating speed of described the first semiaxis, n
HBe the rotating speed of described planetary carrier, i is the velocity ratio of described transmission system, i=n
1/ n
2, n
2Rotating speed for described the second semiaxis.
Drive train according to the present invention during near 1 (a first aspect of the present invention) or near 2 (a second aspect of the present invention), can obtain big speed ratio when the velocity ratio of retarder; Simultaneously need stepped transmission unlike the big speed ratio transmission system of using in prior art, thereby in the problem of small gear fatigue fracture, simplify the structure under can avoiding the big speed ratio situation, reduced volume, improved efficient, and reduced cost.
Description of drawings
Fig. 1 is the schematic diagram according to the transmission system of one embodiment of the present invention, and wherein differential planet transmission mechanism illustrates in the sectional view mode.
Fig. 2 is the schematic diagram according to the transmission system of another embodiment of the present invention, and wherein differential planet transmission mechanism illustrates in the sectional view mode.
Embodiment
Referring to accompanying drawing 1 and Fig. 2, drive train according to the present invention comprises differential planet transmission mechanism 7 and retarder 8.
Differential planet transmission mechanism 7 is a kind of binary gear drives, and an one typical example is differential mechanism.Structural representation as a kind of differential mechanism of differential planet transmission mechanism has been shown in Fig. 1 and Fig. 2.
Differential mechanism 7 comprises the first semiaxis 71, the second semiaxis 72 and housing 77.The first angular wheel 73 that differential mechanism 7 also comprises and the first semiaxis 71 is integrally formed, and integrally formed the second angular wheel 74 of the second semiaxis 72, between first, second angular wheel 73,74 and simultaneously and a plurality of planetary pinions 75 of this two angular wheels engagements and the planetary carrier 76 that supports these planetary pinions 75.Housing 77 surrounds above-mentioned member and integrally formed with planetary carrier 76.
In this application, " integrally formed " both comprised that two above structures were situations of the different piece on same single component, also comprised after two above structures form separately being installed together the situation as single component in the course of the work.
In the present invention, " housing " is not to be necessary, and it can be the part of planetary carrier 76.In this sense, description hereinafter, all can be considered as the description to planetary carrier 76 for the description of housing.
Retarder 8 can be any type well known by persons skilled in the art, and its velocity ratio can be fixed, and can be also variable (being speed changer); Can be gear drive type, can be also worm-gear endless-screw type.As described below, in the present invention, the velocity ratio of retarder 8 is very little, for example near 1 or 2, so the structure of retarder 8 can be very simple, and can effectively avoid in prior art the fatigue problem of the small gear gear teeth in the big speed ratio situation.
In a kind of embodiment shown in Figure 1, retarder 8 is connected between the first semiaxis 71 and the second semiaxis 72.Retarder 8 comprises and integrally formed the first gear 81 of the first semiaxis 71 and second gear 82 integrally formed with the second semiaxis 72.Retarder 8 also comprises three gear 83 and four gear 84 integrally formed with same rotating shaft 86, and wherein, the 3rd gear 83 and the first gear 81 are by idle pulley 85 engagements, so the 3rd gear 83 has identical sense of rotation with the first gear 81; And the 4th gear 84 and the second gear 82 engagements, therefore the 4th gear 84 has opposite sense of rotation with the second gear 82.So, have opposite sense of rotation between the first semiaxis 71 and the second semiaxis 72.
In transmission system shown in Figure 1, the first semiaxis 71 is as the input end of transmission system, and housing 77 (or planetary carrier 76) is as the output terminal of transmission system.Should be appreciated that, structurally essence is not different with the second semiaxis for the first semiaxis, therefore, both can exchange, and can be as input end.Can be by form gear 78 on housing 77, the rotation of housing 77 is exported to other power train.
When the first semiaxis 71 under from the motivational drive outside transmission system with rotation speed n
1During rotation, the first semiaxis 71 drives the second semiaxis 72 through retarder 8 and rotates, and the rotating speed of the second semiaxis 72 is n
2If the rotating speed of planetary carrier 76 (or housing 77) is n
H, according to the velocity ratio formula of differential planet transmission mechanism, when the direction of rotation of the first semiaxis 71 and the second semiaxis 72, have:
| n
1-n
2|=2n
H(formula 1)
n
1, n
2, n
HBe scalar.
If the velocity ratio of drive train according to the present invention shown in Figure 1 is i, i=n
1/ n
HIf the velocity ratio of retarder 8 is k, k=n
1/ n
2With i, k substitution formula 1, can obtain:
K=1/[1 ± (2/i)] or n
2/ n
1=1 ± (2/i) (formula 2)
Perhaps
I=2/|1 one (1/k) | (formula 3)
Can be found out by formula 2 and 3, in order to obtain large drive system than i, only need make the velocity ratio of retarder 8 near 1.
When the rotating speed of the first semiaxis 71 and the second semiaxis 72 very near the time, namely the velocity ratio k of retarder 8 near 1 o'clock, can obtain the velocity ratio i of very large transmission system.For example, when k=1.01, drive system is approximately 200 than i; When k=1.001, drive system is approximately 2000 than i; When k=1.0001, drive system is approximately 20000 than i.
Velocity ratio k can easily obtain with conventional design method near 1 retarder 8, and the number of teeth of each gear in retarder 8 is approached, thereby has avoided in the prior art problem of the gear teeth fatigue fracture of small gear in the big speed ratio situation.
In addition, different from transmission systems such as retarders of the prior art, even can having in theory, transmission system of the present invention can compare i by infinitely-great drive system, but, structure is almost constant, still keep simple, need not prior art and must be divided into a plurality of gear stages like that, the problem that transmission efficiency descends also so not can occur as prior art.Therefore, transmission system of the present invention is particularly suitable for being applied in the occasion of big speed ratio.
In the embodiment shown in fig. 1, the first gear 81 and the 3rd gear 83 are by idle pulley 85 engagements.Mode as an alternative, the first gear 81 and the 3rd gear 83 can directly mesh, and the second gear 82 and the 4th gear 84 mesh by idle pulley.It will be understood by those skilled in the art that the purpose that increases idle pulley 85 is to make the first semiaxis 71 and the second semiaxis 72 to have opposite sense of rotation.
In the embodiment shown in fig. 1, although with the first or second semiaxis as input end,, should be appreciated that, also can be with the rotating shaft 86 of retarder 8 input end as transmission system.In this case, rotating shaft 86 receives from the outer power of transmission system and rotates, thereby drives the first semiaxis and the rotation of the second semiaxis, and making both, the ratio of rotating speed is velocity ratio k.
In addition, in the above-mentioned description of doing with reference to Fig. 1, transmission system is a kind of retarder that is particularly suitable for big speed ratio.But, should be appreciated that, if with planetary carrier or housing as input end, and with one in the first semiaxis, the second semiaxis, rotating shaft 86 as output terminal, so, transmission system of the present invention becomes a kind of speed increaser that is particularly suitable for big speed ratio.
Fig. 2 shows the transmission system according to another embodiment of the present invention.In transmission system shown in Figure 2, the first semiaxis 71 is the input end of transmission system, and the second semiaxis 72 is the output terminal of transmission system.Retarder 9 is connected between the first semiaxis 71 and housing 77 (perhaps planetary carrier 76).Retarder 9 comprises and integrally formed the first gear 91 of the first semiaxis 71 and second gear 92 integrally formed with housing 77.Retarder 8 also comprises three gear 93 and four gear 94 integrally formed with same rotating shaft 96, wherein, and the 3rd gear 93 and the first gear 91 engagements, the 4th gear 94 and the second gear 92 engagements.
Utilize between retarder shown in Figure 29, the first semiaxis 71 and housing 77 and have identical sense of rotation.But the invention is not restricted to this, the first semiaxis 71 and housing 77 can have opposite sense of rotation.
Be similar to the symbolism of employing embodiment illustrated in fig. 1, the rotating speed of establishing the first semiaxis 71 is n
1, the rotating speed of the second semiaxis 72 is n
2, the rotating speed of housing 77 (or planetary carrier 76) is n
H, the drive system of transmission system shown in Figure 2 is than being i, i=n
1/ n
2, the velocity ratio of retarder 9 is k, k=n
1/ n
HWith above-mentioned relation substitution formula 1, can obtain:
K=2/[1 ± (1/i)] or n
H/ n
1=[1 ± (1/i)]/2 (formula 4)
Perhaps
I=1/|1-(2/k) | (formula 5)
Can be found out by formula 4 and 5, in order to obtain large drive system than i, only need make the velocity ratio k of retarder 9 near 2.
During very near 2 times of the rotating speeds of housing 77 (or planetary carrier 76), namely the velocity ratio k of retarder 9 near 2 o'clock, can obtain the velocity ratio i of very large transmission system when the rotating speed of the first semiaxis 71.For example, when k=2.01, drive system is approximately 200 than i; When k=2.001, drive system is approximately 2000 than i; When k=2.0001, drive system is approximately 20000 than i.
Velocity ratio k can easily obtain with conventional design method near 2 retarder 9, by velocity ratio k is distributed between the first/the 3rd gear and the second/the 4th gear, the number of teeth of the pitch wheel in retarder 9 is approached, thereby avoided in the prior art problem of the gear teeth fatigue fracture of small gear in the big speed ratio situation.Even making one group of gear ratio in the first/the 3rd gear and the second/the 4th gear is 2, is also the allowed band of fatigue design, the gear teeth fatigue fracture phenomenon of small gear in the big speed ratio situation can not appear in prior art.
Even can having in theory, transmission system of the present invention can compare i by infinitely-great drive system, but structure is almost constant, still keeps simple, need not prior art and must be divided into a plurality of gear stages like that, the problem that transmission efficiency descends also so not can occur as prior art.Therefore, transmission system of the present invention is particularly suitable for being applied in the occasion of big speed ratio.
Although in the embodiment shown in Figure 2, the first semiaxis 71 is input ends, and the second semiaxis 72 is output terminals, but, should be appreciated that, in two semiaxis, any one is all as input end, another is as output terminal, as long as retarder is connected between input end semiaxis and planetary carrier.
Mode as an alternative also can be with the rotating shaft 96 of retarder 9 input end as transmission system.In this case, rotating shaft 96 receives from the outer power of transmission system and rotates, thereby drives the first semiaxis (perhaps the second semiaxis) and housing (perhaps planetary carrier) rotation, and making both, the ratio of rotating speed is velocity ratio k.
In addition, in the above-mentioned description of doing with reference to Fig. 2, transmission system is a kind of retarder that is particularly suitable for big speed ratio.But, should be appreciated that, if with above-mentioned output terminal for example the second semiaxis as input end, and with one in the first semiaxis, housing (or planetary carrier), rotating shaft as output terminal, so, transmission system of the present invention becomes a kind of speed increaser that is particularly suitable for big speed ratio.
Protection scope of the present invention only is defined by the claims.Have benefited from instruction of the present invention, those skilled in the art can make various modification, modification or replacement to the present invention as the case may be in the situation that do not exceed protection domain of the present invention, and these modification, modification or replacement fall into protection scope of the present invention.
Claims (13)
1. a transmission system, is characterized in that, comprises differential planet gear mechanism and retarder, and described differential planet gear mechanism comprises:
The first sun gear,
First semiaxis integrally formed with described the first sun gear,
Secondary sun wheel,
Second semiaxis integrally formed with described secondary sun wheel,
A plurality of planetary pinions, described a plurality of planetary pinions mesh described the first sun gear and described secondary sun wheel simultaneously,
The planetary carrier that can rotate, the described a plurality of planetary pinions of described planetary carrier rotatably support,
Described retarder is connected between described the first semiaxis and described the second semiaxis, makes the direction of rotation of described the first semiaxis and described the second semiaxis, and makes the ratio n of the rotating speed of described the second semiaxis and described the first semiaxis
2/ n
1=1 ± (2/i), wherein, n
1Be the rotating speed of described the first semiaxis, n
2Be the rotating speed of described the second semiaxis, i is the velocity ratio of described transmission system, i=n
1/ n
H, n
HIt is the rotating speed of described planetary carrier.
2. transmission system as claimed in claim 1, is characterized in that, described retarder comprises:
The first gear, described the first gear and described the first semiaxis are integrally formed,
The second gear, described the second gear and described the second semiaxis are integrally formed,
Idle pulley,
The 3rd gear, described the 3rd gear makes described the 3rd gear and described the first gear have identical sense of rotation by described idle pulley and described the first gear engagement,
The 4th gear, described and described the second gear engagement,
Wherein, described the 3rd gear and described the 4th gear and same rotating shaft are integrally formed.
3. transmission system as claimed in claim 1, is characterized in that, described retarder comprises:
The first gear, described the first gear and described the first semiaxis are integrally formed,
The second gear, described the second gear and described the second semiaxis are integrally formed,
The 3rd gear, described the 3rd gear and described the first gear engagement,
Idle pulley,
The 4th gear, described the 4th gear makes described the 4th gear and described the second gear have identical sense of rotation by described idle pulley and described the second gear engagement,
Wherein, described the 3rd gear and described the 4th gear and same rotating shaft are integrally formed.
4. transmission system as claimed in claim 2 or claim 3, is characterized in that, an input end as described transmission system in described the first semiaxis, described the second semiaxis and described rotating shaft, and described planetary carrier is as the output terminal of described transmission system.
5. transmission system as claimed in claim 2 or claim 3, is characterized in that, described planetary carrier is as the input end of described transmission system, an output terminal as described transmission system in described the first semiaxis, described the second semiaxis and described rotating shaft.
6. transmission system as claimed in claim 1, is characterized in that, described retarder is speed changer.
7. transmission system as claimed in claim 1, is characterized in that, described differential planet gear mechanism is differential mechanism.
8. a transmission system, is characterized in that, it comprises differential planet gear mechanism and accelerator, and described differential planet gear mechanism comprises:
The first sun gear,
First semiaxis integrally formed with described the first sun gear,
Secondary sun wheel,
Second semiaxis integrally formed with described secondary sun wheel,
A plurality of planetary pinions, described a plurality of planetary pinions mesh described the first sun gear and described secondary sun wheel simultaneously,
The planetary carrier that can rotate, the described a plurality of planetary pinions of described planetary carrier rotatably support,
Described retarder is connected between described the first semiaxis and described planetary carrier, makes the sense of rotation of described the first semiaxis and described planetary carrier identical, and makes the ratio n of the rotating speed of described planetary carrier and described the first semiaxis
H/ n
1=[1 ± (1/i)]/2, wherein, n
1Be the rotating speed of described the first semiaxis, n
HBe the rotating speed of described planetary carrier, i is the velocity ratio of described transmission system, i=n
1/ n
2, n
2Rotating speed for described the second semiaxis.
9. transmission system as claimed in claim 8, is characterized in that, described retarder comprises:
The first gear, described the first gear and described the first semiaxis are integrally formed,
The second gear, described the second gear and described planetary carrier are integrally formed,
The 3rd gear, described the 3rd gear and described the first gear engagement,
The 4th gear, described the 4th gear and described the second gear engagement,
Wherein, described the 3rd gear and described the 4th gear and same rotating shaft are integrally formed.
10. transmission system as claimed in claim 9, is characterized in that, an input end as described transmission system in described the first semiaxis, described planetary carrier and described rotating shaft, and described the second rotating shaft is as the output terminal of described transmission system.
11. transmission system as claimed in claim 9 is characterized in that, described the second rotating shaft is as the input end of described transmission system, an output terminal as described transmission system in described the first semiaxis, described planetary carrier and described rotating shaft.
12. transmission system as claimed in claim 8 is characterized in that, described retarder is speed changer.
13. transmission system as claimed in claim 8 is characterized in that, described differential planet gear mechanism is differential mechanism.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011104616042A CN103174814A (en) | 2011-12-26 | 2011-12-26 | Transmission system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011104616042A CN103174814A (en) | 2011-12-26 | 2011-12-26 | Transmission system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103174814A true CN103174814A (en) | 2013-06-26 |
Family
ID=48634877
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011104616042A Pending CN103174814A (en) | 2011-12-26 | 2011-12-26 | Transmission system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103174814A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103303116A (en) * | 2013-06-27 | 2013-09-18 | 中国北方车辆研究所 | Single-motor power-split coupled transmission system |
| CN103603934A (en) * | 2013-08-20 | 2014-02-26 | 曾江华 | Stepless speed change mechanism |
| CN107630980A (en) * | 2017-11-06 | 2018-01-26 | 安徽理工大学 | A kind of new differential speed reducer |
| CN108397532A (en) * | 2018-02-23 | 2018-08-14 | 高则行 | Booster engine and the wind-driven generator for including this booster engine |
| CN109163065A (en) * | 2018-09-26 | 2019-01-08 | 吉林大学 | A kind of decoupling wheel hem retarding mechanism suitable for distributed electric drive automobile |
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| US20040102275A1 (en) * | 2002-11-21 | 2004-05-27 | Jyotsnamoy Chakraborty | Axle assembly |
| CN101020410A (en) * | 2007-02-02 | 2007-08-22 | 吉林大学 | Power coupler for mixed power automobile |
| US20100234162A1 (en) * | 2009-01-16 | 2010-09-16 | Gm Global Technology Operations, Inc. | Torque distributing drive mechanism for motorized vehicles |
| CN202468899U (en) * | 2011-12-26 | 2012-10-03 | 高则行 | Transmission system |
-
2011
- 2011-12-26 CN CN2011104616042A patent/CN103174814A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2115426U (en) * | 1991-02-04 | 1992-09-09 | 齐征宇 | Combined two-cylinder power transmission system |
| US20040102275A1 (en) * | 2002-11-21 | 2004-05-27 | Jyotsnamoy Chakraborty | Axle assembly |
| CN101020410A (en) * | 2007-02-02 | 2007-08-22 | 吉林大学 | Power coupler for mixed power automobile |
| US20100234162A1 (en) * | 2009-01-16 | 2010-09-16 | Gm Global Technology Operations, Inc. | Torque distributing drive mechanism for motorized vehicles |
| CN202468899U (en) * | 2011-12-26 | 2012-10-03 | 高则行 | Transmission system |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103303116A (en) * | 2013-06-27 | 2013-09-18 | 中国北方车辆研究所 | Single-motor power-split coupled transmission system |
| CN103303116B (en) * | 2013-06-27 | 2018-03-30 | 中国北方车辆研究所 | Single power of motor shunting coupling speed change system |
| CN103603934A (en) * | 2013-08-20 | 2014-02-26 | 曾江华 | Stepless speed change mechanism |
| CN103603934B (en) * | 2013-08-20 | 2016-06-29 | 曾江华 | A kind of stepless speed changing mechanism |
| CN107630980A (en) * | 2017-11-06 | 2018-01-26 | 安徽理工大学 | A kind of new differential speed reducer |
| CN108397532A (en) * | 2018-02-23 | 2018-08-14 | 高则行 | Booster engine and the wind-driven generator for including this booster engine |
| CN109163065A (en) * | 2018-09-26 | 2019-01-08 | 吉林大学 | A kind of decoupling wheel hem retarding mechanism suitable for distributed electric drive automobile |
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