CN220523217U - Phase adjusting device of noncircular gear continuously variable transmission - Google Patents
Phase adjusting device of noncircular gear continuously variable transmission Download PDFInfo
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- CN220523217U CN220523217U CN202322224977.9U CN202322224977U CN220523217U CN 220523217 U CN220523217 U CN 220523217U CN 202322224977 U CN202322224977 U CN 202322224977U CN 220523217 U CN220523217 U CN 220523217U
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- 238000006073 displacement reaction Methods 0.000 abstract description 2
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- 239000003921 oil Substances 0.000 description 25
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Abstract
The utility model relates to the technical field of continuously variable transmissions, in particular to a phase adjusting device of a non-circular gear continuously variable transmission, which comprises a double-spiral swing hydraulic cylinder, an actuating mechanism and a central differential mechanism; the first central input shaft is respectively connected with the first non-circular driving gear, a cross shaft of the central differential mechanism and an outer hub of the double-spiral swing hydraulic cylinder through splines; the second non-circular driving gear is connected with a left bevel gear of the central differential through a spline; the third non-circular driving gear is connected with a right bevel gear of the central differential through a spline; the right bevel gear of the central differential mechanism is connected with the inner hub of the double-spiral swing hydraulic cylinder. The device replaces the existing double-hydraulic-system planetary row mode by utilizing the mode of adding the differential mechanism and the spiral swing hydraulic cylinder, and associates the phase change among gears with visual component displacement, so that the device is convenient to monitor, simplifies the hydraulic system and is easier to realize accurate control.
Description
Technical Field
The utility model relates to the technical field of continuously variable transmissions, in particular to a phase adjusting device of a non-circular gear continuously variable transmission.
Background
At present, continuously variable transmission refers to a transmission mode capable of realizing continuous change of a transmission ratio between an input shaft and the input shaft in a certain range under external control, and is a development trend of a future transmission. With the continuous and intensive research, non-circular gear type continuously variable transmissions draw great attention because of the advantages of high power, high torque, high efficiency and wide transmission ratio.
The main idea of realizing stepless speed change by using non-circular gears and a differential mechanism is that two non-circular gear pairs with specific transmission ratio functions are specially designed according to specific transmission ratio requirements, the output of two driven wheels are respectively used as two paths of input of the differential mechanism, after superposition, the constant transmission ratio in a certain angle range is realized, the relative positions of the two non-circular gear pairs are changed by a phase adjusting device, the total transmission ratio is further continuously changed, and then a plurality of groups of speed change mechanisms are combined together to sequentially coordinate relay to realize continuous transmission in a 360-degree range.
The Chinese patent discloses a hydraulic phase switching mechanism suitable for a noncircular continuously variable transmission, and the application number is as follows: 202010248561.9, by adopting hydraulic switching and utilizing a planetary gear to enlarge the phase angle of switching, the hydraulic mechanism can be used for adjusting 60 degrees, and the parallel non-circular gear pair phase can be used for adjusting 180 degrees. The disadvantages of this structure are: the method of changing the phase between non-circular gear pairs to realize stepless speed change makes the speed changer speed ratio particularly sensitive to the phase change of the non-circular gears, and the patent needs two sets of hydraulic systems and puts high requirements on the hydraulic systems, so that accurate control is not easy to realize, and particularly under the initial position (phase difference is 0), the smaller fluctuation of the phase can cause the positive and negative change of the speed ratio, and the driving safety is not facilitated.
Disclosure of Invention
In order to effectively solve the problems in the background technology, the utility model provides a phase adjusting device of a non-circular gear continuously variable transmission.
The specific technical scheme is as follows;
a phase adjusting device of a non-circular gear continuously variable transmission comprises a double-spiral swing hydraulic cylinder, an actuating mechanism and a central differential mechanism; wherein,
the double-spiral swing hydraulic cylinder consists of an inner hub, an outer hub, a sliding sleeve and a thrust ball bearing, wherein the sliding sleeve is matched with the outer hub through an external thread, the sliding sleeve is matched with the inner hub through an internal thread, the rotation directions of the internal thread and the external thread are opposite, the thrust ball bearing is sleeved on a first central input shaft and is arranged between the inner hub and the outer hub, and the inner hub is sleeved on the first central input shaft;
the actuating mechanism comprises a left transmission shell, a push-pull disc, a self-locking nut, a clamping ring, an oil cylinder piston disc, an oil cylinder body and an oil cylinder shaft; the oil cylinder body is fixed on the push-pull disc, the oil cylinder shaft penetrates through a round hole in the middle of the push-pull disc, a round hole in the left transmission shell and a round hole in the right transmission shell and is supported on the round hole in the left transmission shell and the round hole in the right transmission shell, the oil cylinder piston disc is fixed on the oil cylinder shaft, a sliding pair is arranged between the oil cylinder piston disc and the inner wall of the oil cylinder body, and the two ends of the oil cylinder shaft are respectively provided with a left oil duct and a right oil duct; the self-locking nut is connected with a sliding sleeve of the double-spiral swing hydraulic cylinder through threads, and a thrust needle bearing is arranged between the self-locking nut and the push-pull disc;
the first central input shaft is respectively connected with the first non-circular driving gear, a cross shaft of the central differential mechanism and an outer hub of the double-spiral swing hydraulic cylinder through splines; the second non-circular driving gear is connected with a left bevel gear of the central differential through a spline; the third non-circular driving gear is connected with a right bevel gear of the central differential through a spline; the right bevel gear of the central differential mechanism is connected with the inner hub of the double-spiral swing hydraulic cylinder.
Preferably, the central differential consists of a left bevel gear, a right bevel gear, four bevel pinions, a cross shaft and a differential case, wherein the four bevel pinions are meshed with the left bevel gear and the right bevel gear; the four bevel pinions are provided with through holes which are respectively matched with the four connecting shafts and the 4 round holes of the differential case which are circumferentially arranged on the cross shaft.
Preferably, the push-pull disc is provided with 3 round holes which are circumferentially arranged, the end part of each round hole is provided with a clamping groove, and each clamping groove is connected with one cylinder body through a clamping ring.
Preferably, the other end of the first central input shaft is connected to the right transmission housing by a tapered roller bearing.
Preferably, the right bevel gear of the central differential is connected with the inner hub of the double-spiral swing hydraulic cylinder through end face teeth at the end.
Preferably, one side of the outer hub is bent inwards and then connected with the first central input shaft through a spline.
Compared with the prior art, the utility model has the beneficial effects that:
the device replaces the existing double-hydraulic-system planetary row mode by utilizing the mode of adding the differential mechanism and the spiral swing hydraulic cylinder, and associates the phase change among gears with visual component displacement, so that the device is convenient to monitor, simplifies the hydraulic system and is easier to realize accurate control.
Drawings
FIG. 1 is a three-dimensional structure of a non-circular gear continuously variable transmission phase adjustment device;
FIG. 2 is a three-dimensional exploded view of the central differential;
FIG. 3 is a three-dimensional explosion structure diagram of a double-helix swing hydraulic cylinder;
FIG. 4 is a three-dimensional exploded view of an actuator;
FIG. 5 is a cross-sectional view of a non-circular gear continuously variable transmission phase adjustment device;
1. double-spiral swing hydraulic cylinder; 11. an inner hub; 12. a sliding sleeve; 13. a thrust ball bearing; 14. an outer hub; 2. an actuator; 21. a left transmission housing; 22. a push-pull disc; 23. a self-locking nut; 24. thrust needle rollers; 25. a bearing right transmission housing; 26. tapered roller bearings; 27. a clasp; 28. a cylinder piston disc; 29. an oil cylinder body; 210. an oil cylinder shaft; 3. a central differential; 31. bevel pinion; 32. a left bevel gear; 33. a cross shaft; 34. a differential case; 35. a right bevel gear; 4. a first non-circular drive gear; 5. a second non-circular drive gear; 6. a third non-circular drive gear; 7. a first central input shaft; 8. and (3) a bearing.
Detailed Description
Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be oriented 90 degrees or at other orientations and the spatially relative descriptors used herein interpreted accordingly.
The following detailed description of the utility model refers to the accompanying drawings and preferred embodiments.
A phase adjusting device of a non-circular gear continuously variable transmission comprises a double-spiral swing hydraulic cylinder 1, an actuating mechanism 2 and a central differential mechanism 3, and is used for adjusting the phase relation among a first non-circular driving gear 4, a second non-circular driving gear 5 and a third non-circular driving gear 6. The non-circular gear stepless speed changer utilizes a phase adjusting device to adjust the phase relation among all non-circular driving gears according to the requirement, thereby achieving the purpose of continuously and steplessly changing the transmission ratio.
The three-dimensional structure of the non-circular gear stepless speed changer phase adjusting device is shown in fig. 1, and comprises a double-spiral swing hydraulic cylinder 1, a group of actuating mechanisms 2 and a central differential mechanism 3, wherein the double-spiral swing hydraulic cylinder is used for adjusting the phase relation among a first non-circular driving gear 4, a second non-circular driving gear 5 and a third non-circular driving gear 6, a first central input shaft 7 plays a role in transmitting power, and a left speed changer shell 21, a right speed changer shell 25 and a bearing 8 mainly play roles in supporting, positioning and the like.
The first central input shaft 7 is respectively connected with the first non-circular driving gear 4, a cross shaft 33 of the central differential 3 and an outer hub 14 of the double-spiral swing hydraulic cylinder 1 through splines; the second non-circular driving gear 5 is connected with a left bevel gear 32 of the central differential 3 through a spline; the third non-circular driving gear 6 is connected with a right bevel gear 35 of the central differential 3 through a spline; the right bevel gear 35 of the central differential 3 is connected with the inner hub 11 of the double-spiral swing hydraulic cylinder 1 through end face teeth at the end part; the self-locking nut 23 of the actuator 2 is connected with the sliding sleeve 12 of the double-spiral swing hydraulic cylinder 1 through threads (the internal connection relation of the phase adjusting device).
As shown in fig. 2, the center differential 3 is composed of a left bevel gear 32, a right bevel gear 35, 4 bevel pinions 31, a cross shaft 33, and a differential case 34, which is an inherent structure of the bevel differential, and the bevel pinions 31 are engaged with the left bevel gear 32 and the right bevel gear 35 by means of bevel gears; the 4 bevel pinions 31 are provided with through holes which are respectively matched with 4 short shafts circumferentially arranged on the cross shaft 33 and 4 round holes of the differential case 34, so as to achieve the purpose of radial limit.
As shown in fig. 3, the double-screw swing hydraulic cylinder is composed of an inner hub 11, an outer hub 14, a sliding sleeve 12 and a thrust ball bearing 13, wherein the sliding sleeve 12 is matched with the outer hub 14 through external threads, and is matched with the inner hub 11 through internal threads, and the rotation directions of the internal threads and the external threads are opposite (right-handed internal screw and left-handed external screw); the thrust ball bearing 13 is sleeved on the first central input shaft 7, is arranged between the inner hub 11 and the outer hub 14, and plays roles of axial limiting and transmitting thrust.
As shown in fig. 4, the actuator 2 is composed of a push-pull disc 22, a self-locking nut 23, a thrust needle bearing 24, a right transmission shell 25, a tapered roller bearing 26, a snap ring 27, an oil cylinder piston disc 28, an oil cylinder body 29 and an oil cylinder shaft 210, wherein 3 circular holes are circumferentially arranged on the push-pull disc 22, and a clamping groove is formed at the end part of each circular hole and connected with the oil cylinder body 29 through the snap ring 27; the cylinder shaft 210 penetrates through the round hole of the push-pull disc 22, the round hole of the left transmission shell 21 and the round hole of the right transmission shell 25, and is supported on the round hole of the left transmission shell 21 and the round hole of the right transmission shell 25, a sliding pair is arranged between the cylinder piston disc 28 and the inner wall of the cylinder body 29, and an oil duct is arranged on the cylinder shaft 210 and is used for feeding and discharging hydraulic oil; the oil cylinder shaft 210 and the oil cylinder piston disc 28 are fixedly connected; the tapered roller bearing 26 mainly plays roles of supporting, force transmission, limiting and the like.
As shown in fig. 5, the cylinder piston disc 28 and the cylinder shaft 210 are fixed, when the left oil passage is filled with oil, the cylinder body 29 moves left to drive the push-pull disc 22 and the sliding sleeve 12 to move left, the sliding sleeve 12 is connected with the inner hub 11 in a spiral pair, and the rotation direction is right rotation, so that the inner hub 11 rotates clockwise (seen from the power input to the output direction) relative to the sliding sleeve 12; since the slide bush 12 is connected to the outer hub 14 by a screw pair and the rotational direction is left-handed, the outer hub 14 rotates counterclockwise (as viewed from the power input to the output) with respect to the slide bush 12. The inner hub 11 is connected with a right bevel gear 35 of the central differential 3 through end face teeth, and the right bevel gear 35 of the central differential 3 is connected with a third non-circular driving gear 6 through a spline; the outer hub 14 is connected to the first central input shaft 7 by a spline, and the first central input shaft 7 is connected to the first non-circular driving gear 4 by a spline, so that the sliding sleeve 12 is shifted left to adjust the phase between the inner hub 11 and the outer hub 14, that is, the phase between the first non-circular driving gear 4 and the third non-circular driving gear 6, that is, the third non-circular driving gear 6 rotates clockwise relative to the first non-circular driving gear 4, and the rotation angle is the sum of the rotation angles of the inner hub 11 and the outer hub 14 relative to the sliding sleeve 12.
According to the working principle of the differential mechanism, the left bevel gear 32 and the right bevel gear 35 coaxially and reversely move relative to the cross shaft 33 at the same speed, the first non-circular driving gear 4 is connected with the first central input shaft 7 through a spline, and the first central input shaft 7 is connected with the cross shaft 33 through a spline; the second non-circular driving gear 5 is connected with the left bevel gear 32 through a spline; the third non-circular driving gear 6 is connected with the right bevel gear 35 through a spline, so that the second non-circular driving gear 5 rotates anticlockwise relative to the first non-circular driving gear 4 when the sliding sleeve 12 moves leftwards, and the rotation angle is consistent with the rotation angle of the third non-circular driving gear 6 relative to the first non-circular driving gear 4.
The same applies when the right oil duct is filled with oil, the sliding sleeve 12 moves right, the third non-circular driving gear 6 rotates anticlockwise relative to the first non-circular driving gear 4, the second non-circular driving gear 5 rotates clockwise relative to the first non-circular driving gear 4, and the relative rotation angles of the third non-circular driving gear and the second non-circular driving gear are consistent.
Other types of differentials besides bevel gear differential can be used for the central differential, and the design of an actuating mechanism and the selection of a bearing can be adjusted, so that the central differential belongs to the protection scope of the patent.
The foregoing is merely a preferred embodiment of the present utility model and it should be noted that modifications and adaptations to those skilled in the art may be made without departing from the principles of the present utility model, which are intended to be comprehended within the scope of the present utility model.
Claims (6)
1. A phase adjusting device of a non-circular gear continuously variable transmission is characterized in that: the hydraulic device comprises a double-spiral swing hydraulic cylinder, an actuating mechanism and a central differential mechanism; wherein,
the double-spiral swing hydraulic cylinder consists of an inner hub, an outer hub, a sliding sleeve and a thrust ball bearing, wherein the sliding sleeve is matched with the outer hub through an external thread, the sliding sleeve is matched with the inner hub through an internal thread, the rotation directions of the internal thread and the external thread are opposite, the thrust ball bearing is sleeved on a first central input shaft and is arranged between the inner hub and the outer hub, and the inner hub is sleeved on the first central input shaft;
the actuating mechanism comprises a left transmission shell, a push-pull disc, a self-locking nut, a clamping ring, an oil cylinder piston disc, an oil cylinder body and an oil cylinder shaft; the oil cylinder body is fixed on the push-pull disc, the oil cylinder shaft penetrates through a round hole in the middle of the push-pull disc, a round hole in the left transmission shell and a round hole in the right transmission shell and is supported on the round hole in the left transmission shell and the round hole in the right transmission shell, the oil cylinder piston disc is fixed on the oil cylinder shaft, a sliding pair is arranged between the oil cylinder piston disc and the inner wall of the oil cylinder body, and the two ends of the oil cylinder shaft are respectively provided with a left oil duct and a right oil duct; the self-locking nut is connected with a sliding sleeve of the double-spiral swing hydraulic cylinder through threads, and a thrust needle bearing is arranged between the self-locking nut and the push-pull disc;
the first central input shaft is respectively connected with the first non-circular driving gear, a cross shaft of the central differential mechanism and an outer hub of the double-spiral swing hydraulic cylinder through splines; the second non-circular driving gear is connected with a left bevel gear of the central differential through a spline; the third non-circular driving gear is connected with a right bevel gear of the central differential through a spline; the right bevel gear of the central differential mechanism is connected with the inner hub of the double-spiral swing hydraulic cylinder.
2. The non-circular gear continuously variable transmission phase adjustment device according to claim 1, wherein the central differential is constituted by a left bevel gear, a right bevel gear, four bevel pinions, a cross shaft and a differential case, the four bevel pinions being engaged with each other; the four bevel pinions are provided with through holes which are respectively matched with the four connecting shafts and the 4 round holes of the differential case which are circumferentially arranged on the cross shaft.
3. The non-circular gear continuously variable transmission phase adjusting device according to claim 1, wherein the push-pull disc is provided with 3 circular holes and is circumferentially arranged, clamping grooves are formed in the end parts of the circular holes, and each clamping groove is connected with one cylinder body through a clamping ring.
4. The non-circular gear continuously variable transmission phase adjustment device according to claim 1, wherein the other end of the first central input shaft is connected with the right transmission housing through a tapered roller bearing.
5. The non-circular gear continuously variable transmission phase adjustment device according to claim 1, wherein the right bevel gear of the central differential is connected with the inner hub of the double helical oscillating hydraulic cylinder through end face teeth of the end portion.
6. The non-circular gear continuously variable transmission phase adjustment device according to claim 1, wherein one side of the outer hub is bent inwards and then connected with the first central input shaft through a spline.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322224977.9U CN220523217U (en) | 2023-08-18 | 2023-08-18 | Phase adjusting device of noncircular gear continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322224977.9U CN220523217U (en) | 2023-08-18 | 2023-08-18 | Phase adjusting device of noncircular gear continuously variable transmission |
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| Publication Number | Publication Date |
|---|---|
| CN220523217U true CN220523217U (en) | 2024-02-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202322224977.9U Active CN220523217U (en) | 2023-08-18 | 2023-08-18 | Phase adjusting device of noncircular gear continuously variable transmission |
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| CN (1) | CN220523217U (en) |
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- 2023-08-18 CN CN202322224977.9U patent/CN220523217U/en active Active
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