CN112253702A - A stepless speed change mechanism - Google Patents
A stepless speed change mechanism Download PDFInfo
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- CN112253702A CN112253702A CN202010961549.2A CN202010961549A CN112253702A CN 112253702 A CN112253702 A CN 112253702A CN 202010961549 A CN202010961549 A CN 202010961549A CN 112253702 A CN112253702 A CN 112253702A
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
本发明公开了一种无级变速机构，属于变速器技术领域。所述无级变速机构包括输入轴、第一外齿轮、第二外齿轮、第一机构、第二机构、第三机构、第四机构、输出轴和调速机构；输入轴分别与第一外齿轮和第一机构连接；第一机构与第四机构连接；第一外齿轮与第二外齿轮啮合；第二外齿轮与第三机构连接；第二机构与第三机构连接；第一机构与第二机构连接；第三机构与第四机构连接；输出轴与第四机构连接；调速机构分别与第二机构和第三机构连接。本发明通过齿轮、第一机构、第二机构、第三机构、第四机构和调速机构之间的配合实现了输出端无级变速，并且能够实现空挡和倒挡，具有结构简单可靠、制造成本低、维修方便、调速范围广及适用工况广泛等优点。
The invention discloses a stepless transmission mechanism, which belongs to the technical field of transmissions. The continuously variable speed change mechanism includes an input shaft, a first external gear, a second external gear, a first mechanism, a second mechanism, a third mechanism, a fourth mechanism, an output shaft and a speed regulating mechanism; the input shaft is respectively connected with the first external gear. The gear is connected with the first mechanism; the first mechanism is connected with the fourth mechanism; the first external gear is meshed with the second external gear; the second external gear is connected with the third mechanism; the second mechanism is connected with the third mechanism; The second mechanism is connected; the third mechanism is connected with the fourth mechanism; the output shaft is connected with the fourth mechanism; the speed regulating mechanism is respectively connected with the second mechanism and the third mechanism. The invention realizes the stepless speed change at the output end through the cooperation among the gears, the first mechanism, the second mechanism, the third mechanism, the fourth mechanism and the speed regulating mechanism, and can realize the neutral gear and the reverse gear. It has the advantages of low cost, convenient maintenance, wide speed regulation range and wide range of applicable working conditions.
Description
Technical Field
The invention relates to the technical field of transmissions, in particular to a stepless speed change mechanism.
Background
With the higher and higher requirements of the society on environmental protection, the electric vehicle technology becomes the mainstream research direction of each large vehicle enterprise. The working characteristics of the motor are constant torque at low speed and reduced torque at high speed, so that the torque and the vehicle speed are adjusted only by adjusting the rotating speed of the motor, the motor needs to give consideration to the climbing capability and the highest speed of the vehicle, and the motor is high in energy consumption and low in efficiency. The existing automatic gear used for the electric vehicle still belongs to step speed change, and only realizes automatic gear shifting through electric control, and has the defects of complex structure, high manufacturing cost and difficult maintenance of a speed change mechanism.
Disclosure of Invention
In order to solve the problems of complex structure, high manufacturing cost and difficult maintenance of the existing speed change mechanism, the invention provides a stepless speed change mechanism, which comprises an input shaft, a first external gear, a second external gear, a first mechanism, a second mechanism, a third mechanism, a fourth mechanism, an output shaft, a speed regulation mechanism and a connecting shaft; the input shaft is respectively connected with the first external gear and the first mechanism; the first mechanism is connected with the fourth mechanism; the first external gear is meshed with the second external gear; the second external gear is connected with a third mechanism; the second mechanism is connected with the third mechanism; the first mechanism is connected with the second mechanism; the third mechanism is connected with the fourth mechanism; the output shaft is connected with the fourth mechanism; the speed regulating mechanism is respectively connected with the second mechanism and the third mechanism.
The stepless speed change mechanism provided by the invention realizes stepless speed change of the output end through mutual matching of the gear, the first mechanism, the second mechanism, the third mechanism, the fourth mechanism and the speed regulation mechanism, can realize neutral gear and reverse gear, and has the advantages of simple and reliable structure, low manufacturing cost, convenience in maintenance, wide speed regulation range, wide applicable working condition and the like.
Drawings
Fig. 1 is a schematic structural view of a continuously variable transmission mechanism provided in embodiment 1;
fig. 2 is a schematic cross-sectional structure diagram of the first mechanism provided in this embodiment 1;
fig. 3 is a schematic cross-sectional structure diagram of a fourth mechanism provided in this embodiment 1;
fig. 4 is a schematic cross-sectional structure diagram of a second mechanism provided in this embodiment 1;
fig. 5 is a schematic cross-sectional structure view of a third mechanism provided in this embodiment 1;
fig. 6 is a schematic structural view of the continuously variable transmission mechanism provided in embodiment 2;
fig. 7 is a schematic view of the output rotation speed increase of the continuously variable transmission mechanism of the embodiment 1;
fig. 8 is a schematic view of the reduction in the output rotation speed of the continuously variable transmission mechanism of the embodiment 1;
fig. 9 is a schematic view of the continuously variable transmission mechanism of the embodiment 1 in which the output rotation speed is 0;
fig. 10 is a schematic diagram of the output reverse rotation (reverse) of the continuously variable transmission mechanism of the embodiment 1;
fig. 11 is a schematic diagram of the relationship between the input and output speeds of the continuously variable transmission mechanism and the speed control mechanism according to embodiment 1.
Detailed Description
The technical solution of the present invention is further described below with reference to the accompanying drawings and examples.
Example 1
Referring to fig. 1, the present embodiment provides a continuously variable transmission mechanism including an input shaft 1, an external gear 2, an external gear 3, a first mechanism 11, a second mechanism 12, a third mechanism 13, a fourth mechanism 14, an output shaft 4, and a speed adjusting mechanism 5. Wherein, the input shaft 1 is respectively connected with the external gear 2 and the first mechanism 11; the first mechanism 11 is connected with the fourth mechanism 14; the external gear 2 meshes with the external gear 3; the external gear 3 is connected with a third mechanism 13; the second mechanism 12 is connected with the third mechanism 13; the first mechanism 11 is connected with the second mechanism 12; the third mechanism 13 is connected with the fourth mechanism 14; the output shaft 4 is connected with the fourth mechanism 14; the governor mechanism 5 is connected to the second mechanism 12 and the third mechanism 13, respectively.
Referring to fig. 1 and 2, the first mechanism 11 of the present embodiment includes a sun gear 1103, a planetary gear 1105, a planetary carrier 1104, a ring gear 1102, and a gear 1101; the input shaft 1 passes through the gear 1101 and the sun gear 1103 and then is connected with the planet carrier 1104; the sun gear 1103 meshes with the planet gears 1105; the ring gear 1102 is provided with internal teeth, and the planet gears 1105 are meshed with the internal teeth of the ring gear 1102; the planet carrier 1104 is connected with the planet wheels 1105; gear 1101 is connected to sun gear 1103. The number of planets 1105 may be determined by design requirements, such as 3, 4, or 5. The sun gear 1103 and the gear 1101 can be connected in a variety of ways, such as: the sun gear 1103 is connected to the gear 1101 by a connecting rod, or the sun gear 1103 and the gear 1101 form an integrated structural member, and the implementation manner of connecting the sun gear 1103 and the gear 1101 is not particularly limited in this embodiment. In practical application, a first bearing is mounted at the center of the gear 1101 and the sun gear 1103, and the input shaft 1 passes through the first bearing and then is connected with the planet carrier 1104; the first bearing enables the rotation of the input shaft 1 to be independent of the rotation of the gear 1101 and the sun gear 1103, i.e., the rotation of the input shaft 1 does not drive the rotation of the gear 1101 and the sun gear 1103.
Referring to fig. 1 to 3, the fourth mechanism 14 of the present embodiment includes a sun gear 1404, planet gears 1403, a planet carrier 1402, and an annulus 1401; sun gear 1404 is connected to ring gear 1102; sun gear 1404 meshes with planet gears 1403; the ring gear 1401 is provided with internal teeth and external teeth, and the planet wheel 1403 is meshed with the internal teeth of the ring gear 1401; the carrier 1402 is connected to the planetary gear 1403 and the output shaft 4, respectively. The number of planets 1403 may be determined by design requirements, such as 3, 4, or 5. The output shaft 4 and the planet carrier 1402 can be connected in various ways, for example: the planet carrier 1402 and the output shaft 4 are connected by a connecting member, or the planet carrier 1402 and the output shaft 4 form an integrated structural member, and the embodiment does not specifically limit the implementation manner of connecting the planet carrier 1402 and the output shaft 4.
Referring to fig. 1, 2, and 4, the second mechanism 12 of the present embodiment includes a sun gear 1204, planet gears 1203, a planet carrier 1205, a ring gear 1202, and a gear 1201; the sun gear 1204 meshes with the planet gears 1203; the gear ring 1202 is provided with internal teeth, and the gear ring 1202 is fixed externally; the planet gears 1203 mesh with the internal teeth of the ring gear 1202; the carrier 1205 is connected to the gear 1201, and the gear 1201 meshes with the gear 1101. The number of planets 1203 may be determined according to design requirements, for example 3, 4 or 5. The planet carrier 1205 and the gear 1201 can be connected in various ways, for example: planet carrier 1205 is connected with gear 1201 through the connecting rod, or planet carrier 1205 constitutes the integrated structure with gear 1201, and this embodiment does not specifically restrict the realization that planet carrier 1205 is connected with gear 1201.
Referring to fig. 1, 3 to 5, the third mechanism 13 of the present embodiment includes a sun gear 1304, a planetary gear 1303, a planetary carrier 1302, and a ring gear 1301; sun gear 1304 meshes with planet gears 1303; the ring gear 1301 is provided with internal and external teeth; the planet gears 1303 mesh with the internal teeth of the ring gear 1301; the external teeth of the ring gear 1301 mesh with the external teeth of the ring gear 1401. The number of planets 1303 may be determined by design requirements, e.g., 3, 4, or 5.
Referring to fig. 1, 4 and 5, the continuously variable transmission mechanism of the present embodiment further includes a connecting shaft 6, and the external gear 3 is connected to the third mechanism 13 through the connecting shaft 6, specifically: one end of the connecting shaft 6 is connected with the external gear 3, and the other end of the connecting shaft 6 passes through the gear 1201, the sun gear 1204 and the sun gear 1304 and then is connected with the planet carrier 1302. In practical application, a second bearing is mounted at the center of the sun gear 1204 and the sun gear 1304, and the connecting shaft 6 passes through the second bearing and then is connected with the planet carrier 1302; the second bearing enables the rotation of the connecting shaft 6 to be independent of the rotation of the sun gear 1204 and the sun gear 1304, i.e., the rotation of the connecting shaft 6 does not drive the rotation of the sun gear 1204 and the sun gear 1304.
Referring to fig. 1, 4 and 5, the speed adjusting mechanism 5 is fixedly connected to the sun gear 1204 and the sun gear 1304, and the implementation manner of the fixed connection is not particularly limited in this embodiment as long as the speed adjusting mechanism 5 can synchronously operate with the sun gear 1204 and the sun gear 1304. In practice, the governor mechanism 5 may be acted upon by an external control unit, which may be a generator, a motor, a hydraulic device, etc.
Example 2
Referring to fig. 1, 4 to 6, the present embodiment provides a continuously variable transmission mechanism that differs from embodiment 1 in that: in the embodiment, the sun gear (1204) and the sun gear (1304) in embodiment 1 are combined into an integrated structural member (7), that is, the sun gear (1204) and the sun gear (1304) are combined into one structural member (7) instead of two separate structural members, so that the second mechanism (12) is connected with the third mechanism (13) through one structural member (7); correspondingly, the speed regulating mechanism (5) is respectively connected with the second mechanism (12) and the third mechanism (13) through a structural member (7); one end of the connecting shaft (6) is connected with the external gear (3), and the other end of the connecting shaft (6) penetrates through the gear (1201) and the structural part (7) and then is connected with the planet carrier (1302). In practical application, the speed regulating mechanism (5) is fixedly connected with the structural part (7); a third bearing is installed in the center of the structural part (7), and the connecting shaft (6) penetrates through the third bearing and then is connected with the planet carrier (1302). In addition, other structural features of this embodiment are the same as those of embodiment 1, and are not described again in this embodiment.
Since the operating principle of embodiment 1 is the same as that of embodiment 2, the operating principle of the continuously variable transmission mechanism of the present embodiment will be described below by taking embodiment 1 as an example only. For the sake of simplicity and explanation of the operation principle of the continuously variable transmission mechanism of the present embodiment, the parameters are set as follows: setting omegaInput deviceSince the input shaft 1, the external gear 2, and the carrier 1104 are integrally connected to each other, the rotation speed of the input shaft 1, the external gear 2, and the carrier 1104 are all the same, and therefore ω is set1＝ωInput device＝ωOuter gear 2＝ωPlanet carrier 1104(ii) a Similarly, the speed regulating mechanism 5 is fixedly connected with the sun gear 1204 and the sun gear 1304, the rotating speed of the speed regulating mechanism 5 is the same as the rotating speeds of the sun gear 1204 and the sun gear 1304, and ω is set8＝ωSpeed regulating mechanism 5＝ωSun gear 1204＝ωSun gear 1304. The first mechanism 11, the second mechanism 12, the third mechanism 13, and the fourth mechanism 14 have the same pitch circle diameter of the sun gear, the same pitch circle diameter of the planetary gear, and the same pitch circle diameter of the ring gear, the same pitch circle diameter of the external gear 2 and the external gear 3, the same pitch circle diameter of the gear 1101 and the gear 1201, and the same pitch circle diameter of the external teeth of the ring gear 1301 and the external teeth of the ring gear 1401. Since the external gears 2 and 3 mesh with each other, the rotational speeds of the input shaft 1, the carrier 1104, and the carrier 1302 are all the same, and ω is set6＝ω1＝ωInput device. Since the gear 1101 and the gear 1201 mesh with each other, the rotational speeds of the sun gear 1103 and the carrier 1205 are the same, and ω is set2＝ωGear 1101＝ωGear 1201. Since the rotation speeds of the ring gear 1102 and the sun gear 1404 are the same, ω is set3＝ωRing gear 1102＝ωSun gear 1404. Since the ring gear 1401 and the ring gear 1301 are meshed with each other, the rotation speeds of the ring gear 1401 and the ring gear 1301 are the same, and ω is set4＝ω7＝ωRing gear 1401＝ωGear ring 1301。
According to the transmission principle of the planetary gear system, when the rotation speed of any two components of the sun gear, the planet carrier and the ring gear is the same, the rotation speed of the other component is also the same, and at the moment, three components of the planetary gear system are relatively static, and the transmission ratio is 1. Accordingly, the continuously variable transmission mechanism according to the present embodiment operates as follows:
working condition 1: the fourth mechanism 14 has a transmission ratio of 1 and the output speed increases.
Referring to fig. 7, when the gear ratio of the fourth mechanism 14 is 1, ω is4＝ω3. Due to omega4＝ω7Thus ω3＝ω7This means that the rotational speed of the ring gear 1102 is the same as the rotational speed of the ring gear 1301, while the rotational speed of the planet carrier 1104 is always the same as the rotational speed of the planet carrier 1302, i.e. ω is1＝ω6Therefore, the rotational speed of the sun gear 1103 and the rotational speed of the sun gear 1304 are also always the same, i.e., ω2＝ω8(ii) a Due to omega2＝ω9Thus ω8＝ω9,ω8Is the rotational speed, ω, of the sun gear 12049The rotational speed of the planet carrier 1205; omega10The rotational speed of ring gear 1202 is 0 because ring gear 1202 is fixedly connected externally, and ω is obtained8＝ω9＝ω 100. In which the second mechanism 12 is completely stationary and the fourth mechanism 14 may be equivalently a through-shaft, ω3＝ω4＝ω5，ω5The rotational speed of the output shaft 4. The rotation speed of the planet carrier 1104 is the input rotation speed, and the rotation speed omega of the sun gear 110320, ring gear 1102 rotation speed ω3Is the output speed, which is greater than the input speed.
Working condition 2: when the gear ratio of the first mechanism 11 is 1, the output rotation speed is reduced.
Referring to fig. 8, when the gear ratio of the first mechanism 11 is 1, ω is1＝ω2＝ω3. And due to omega1＝ω6，ω2＝ω9Thus ω9＝ω6This means that the planet carrier 1205 and the planet carrier 1302 rotate at the same speed, and the sun 1204 and the sun 1304 both rotate at ω8Therefore, the rotation speed of the ring gear 1202 is the same as the rotation speed of the ring gear 1301 by ω10＝ω 70, and ω is4＝ω7Thus ω 40. Omega in this operating mode1＝ω2＝ω3The first mechanism 11 may be equivalent to a through shaft. The sun gear 1404, the ring gear 1401, and the carrier 1402 are coupled to each other at the input rotational speed, 0, and ω, respectively5Is the output speed, which is lower than the input speed.
Working condition 3: neutral, output speed is 0.
Referring to FIG. 9, following condition 2, the rotational speed ω of sun gear 13048Continuously increasing the rotational speed ω of the ring gear 14017Starting from 0 to invert. Sun gear 1204 speed ω8Increasing the rotation speed omega of the planet carrier 1205 with the ring gear 1202 fixed all the time9And (4) increasing. Sun gear 1103 rotation speed ω2＝ω9Increasing the rotational speed ω of the planet carrier 11041Invariant (omega)1Input speed), the speed ω of the ring gear 1102 is then3And decreases. Sun gear 1404 speed ω3Reducing the rotational speed ω of the ring gear 1301 and the ring gear 14014＝ω7Reverse rotation when ω3And ω4When in a certain proportion, the rotation speed omega of the planet carrier 14025The output speed is 0.
Working condition 4: reverse gear
Referring to FIG. 10, following condition 3, sun gear 1304 rotates at a speed ω8Continuing to increase, the speed ω at which the ring gear 1301 reverses direction7And also increases. Sun gear 1204 speed ω8Increasing the number of revolutions omega of the planet carrier 1205 with the ring gear 1202 fixed all the time9The increase continues. Sun gear 1103 rotation speed ω2＝ω9Increasing the rotational speed ω of the planet carrier 11041Invariant (omega)1Input speed), ring gear 1102 rotatesω3The decrease continues. Sun gear 1404 speed ω3Continuing to decrease, the ring gear 1401 reverses the rotational speed ω4＝ω7When the rotation speed of the planet carrier 1402 increases continuously, the rotation speed ω5The reverse rotation is started from 0, that is, the output rotation speed is started to reverse.
As shown in fig. 11, in the continuously variable transmission mechanism of the present embodiment, the output rotational speed and the rotational speed of the governor mechanism correspond to time while the input rotational speed is kept constant; when the output rotating speed is changed from high to low, the rotating speed of the speed regulating mechanism is changed from low to high; when the rotating speed of the speed regulating mechanism is increased to the set rotating speed, the output rotating speed is 0; when the speed regulating mechanism continues to rise to exceed the set rotating speed, the output rotating speed changes direction.
The stepless speed change mechanism provided by the embodiment of the invention has the following advantages:
1. the stepless speed change mechanism provided by the embodiment of the invention has 4 working conditions of speed increasing, speed reducing, neutral gear and reverse gear, and the four working conditions can be smoothly and continuously transited.
2. The stepless speed change mechanism provided by the embodiment of the invention has the advantages of simple speed regulation, no power interruption in the speed regulation process and quiet and stable operation.
3. The stepless speed change mechanism provided by the embodiment of the invention has the advantages that the continuous change of the output rotating speed can be realized under the condition that the rotating speed of the input end of the stepless speed change mechanism is kept constant, so that the power source of the input end can always work in a high-efficiency working interval, and the transmission efficiency is high.
4. When the stepless speed change mechanism works in a neutral gear, the power source at the input end can run in a high-efficiency interval or stop completely; if the input end power source still operates in a high-efficiency interval during neutral gear, no power delay exists during acceleration, and the acceleration speed is high.
5. When the stepless speed change mechanism works in reverse gear, the reverse rotation of the power source at the input end is not needed, a mechanical gear shifting device is not needed, the reverse rotation of the output end can be realized only by giving a reverse gear signal and enabling the rotating speed of the speed regulating mechanism to exceed the set rotating speed, and the stepless speed change mechanism is simple and convenient to operate and quick in response.
6. The stepless speed change mechanism provided by the embodiment of the invention does not need a clutch, a hydraulic device and the like, and has the advantages of simple and reliable structure, low manufacturing cost and very convenient maintenance.
7. The stepless speed change mechanism provided by the embodiment of the invention can realize speed increase and speed reduction, and has the advantages of wide speed regulation range and wide application working condition.
The above-mentioned embodiments are intended to illustrate the objects, technical solutions and advantages of the present invention in further detail, and it should be understood that the above-mentioned embodiments are only exemplary embodiments of the present invention, and are not intended to limit the present invention, and any modifications, equivalents, improvements and the like made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (14)
1. A continuously variable transmission mechanism is characterized by comprising an input shaft (1), an external gear (2), an external gear (3), a first mechanism (11), a second mechanism (12), a third mechanism (13), a fourth mechanism (14), an output shaft (4) and a speed regulating mechanism (5); the input shaft (1) is respectively connected with the external gear (2) and the first mechanism (11); the first mechanism (11) is connected with the fourth mechanism (14); the external gear (2) is meshed with the external gear (3); the external gear (3) is connected with a third mechanism (13); the second mechanism (12) is connected with the third mechanism (13); the first mechanism (11) is connected with the second mechanism (12); the third mechanism (13) is connected with the fourth mechanism (14); the output shaft (4) is connected with a fourth mechanism (14); the speed regulating mechanism (5) is respectively connected with the second mechanism (12) and the third mechanism (13).
2. Continuously variable transmission according to claim 1, wherein the first mechanism (11) comprises a sun gear (1103), planet gears (1105), a planet carrier (1104), a ring gear (1102) and a gear (1101); the input shaft (1) passes through the gear (1101) and the sun gear (1103) and then is connected with the planet carrier (1104); the sun gear (1103) is meshed with the planet gear (1105); the gear ring (1102) is provided with internal teeth, and the planet gear (1105) is meshed with the internal teeth of the gear ring (1102); the planet carrier (1104) is connected with the planet wheel (1105); the gear (1101) is connected to the sun gear (1103).
3. Continuously variable transmission according to claim 2, characterized in that the fourth mechanism 14 comprises a sun gear (1404), planet gears (1403), a planet carrier (1402) and a ring gear (1401); the sun gear (1404) is connected with the gear ring (1102); a sun gear (1404) meshes with the planet gears (1403); the gear ring (1401) is provided with internal teeth and external teeth, and the planet gear (1403) is meshed with the internal teeth of the gear ring (1401); the planet carrier (1402) is connected to the planet gear (1403) and the output shaft (4), respectively.
4. Continuously variable transmission according to claim 3, characterized in that the second mechanism (12) comprises a sun gear (1204), planet gears (1203), a planet carrier (1205), a ring gear (1202) and a gearwheel (1201); the sun wheel (1204) is meshed with the planet wheel (1203); the gear ring (1202) is provided with internal teeth, and the gear ring (1202) is fixed outside; the planet gear (1203) is meshed with the internal teeth of the gear ring (1202); the planet carrier (1205) is connected with the gear (1201), and the gear (1201) is meshed with the gear (1101).
5. Continuously variable transmission according to claim 4, characterized in that the third mechanism (13) comprises a sun gear (1304), planet gears (1303), a planet carrier (1302) and a ring gear (1301); the sun wheel (1304) is meshed with the planet wheel (1303); the gear ring (1301) is provided with internal teeth and external teeth; the planet gears (1303) are meshed with the inner teeth of the gear ring (1301); the external teeth of the ring gear (1301) mesh with the external teeth of the ring gear (1401).
6. The continuously variable transmission mechanism according to claim 5, further comprising a connecting shaft (6), wherein the external gear (3) is connected to the third mechanism (13) through the connecting shaft (6).
7. Continuously variable transmission according to claim 6, characterized in that the centers of the gear (1101) and the sun gear (1103) are each fitted with a first bearing through which the input shaft (1) is connected to the planet carrier (1104).
8. Continuously variable transmission according to claim 7, wherein the sun gear (1103) is connected to the gear wheel (1101) by a connecting rod, or the sun gear (1103) and the gear wheel (1101) constitute an integrated structural member; the planet carrier (1402) is connected with the output shaft (4) through a connecting piece, or the planet carrier (1402) and the output shaft (4) form an integrated structural piece; the planet carrier (1205) is connected with the gear (1201) through a connecting rod, or the planet carrier (1205) and the gear (1201) form an integrated structural member.
9. Continuously variable transmission according to claim 8, wherein the governor mechanism (5) is fixedly connected to the sun wheel (1204) and the sun wheel (1304), respectively; one end of the connecting shaft (6) is connected with the external gear (3), and the other end of the connecting shaft (6) penetrates through the gear (1201), the sun gear (1204) and the sun gear (1304) and then is connected with the planet carrier (1302).
10. Continuously variable transmission according to claim 9, characterized in that the sun wheel (1204) and the sun wheel (1304) are each centrally fitted with a second bearing through which the connecting shaft (6) passes and is connected to the planet carrier (1302).
11. Continuously variable transmission according to claim 8, wherein the sun wheel (1204) and the sun wheel (1304) form an integrated structural element (7), and the second mechanism (12) is connected to the third mechanism (13) via the structural element (7); the speed regulating mechanism (5) is respectively connected with the second mechanism (12) and the third mechanism (13) through a structural member (7).
12. Continuously variable transmission according to claim 11, wherein the speed regulating mechanism (5) is fixedly connected to the structural member (7); one end of the connecting shaft (6) is connected with the external gear (3), and the other end of the connecting shaft (6) penetrates through the gear (1201) and the structural part (7) and then is connected with the planet carrier (1302).
13. Continuously variable transmission according to claim 12, characterized in that a third bearing is centrally mounted on the structural part (7), through which third bearing the connecting shaft (6) is connected to the planet carrier (1302).
14. Continuously variable transmission according to claim 1, wherein the governor mechanism (5) is acted upon by an external control unit.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2020109534866 | 2020-09-11 | ||
| CN202010953486 | 2020-09-11 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112253702A true CN112253702A (en) | 2021-01-22 |
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| CN113685513A (en) * | 2021-09-23 | 2021-11-23 | 清驰汽车江苏有限公司 | Stepless speed change mechanism and speed change method thereof |
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| DE102012213224A1 (en) * | 2012-07-27 | 2014-01-30 | Zf Friedrichshafen Ag | Gear box e.g. dual clutch transmission for working machine, has input element of planetary gear set that is decoupled with output branch with variable speed, such that mechanical power branch is interlocked with planetary gear set |
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| CN203254956U (en) * | 2013-01-29 | 2013-10-30 | 同济大学 | Continuously variable electronic hybrid power system |
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| CN107763155A (en) * | 2016-08-16 | 2018-03-06 | 钟跃荣 | A kind of the mechanical stepless speed changes method and stepless speed changing mechanism of double-planet mechanism composition |
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| CN113685513A (en) * | 2021-09-23 | 2021-11-23 | 清驰汽车江苏有限公司 | Stepless speed change mechanism and speed change method thereof |
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| CN214036723U (en) | 2021-08-24 |
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Application publication date: 20210122 |