CN108488345B - Three-branch non-circular gear stepless speed change transmission device - Google Patents

Three-branch non-circular gear stepless speed change transmission device Download PDF

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Publication number
CN108488345B
CN108488345B CN201810445654.3A CN201810445654A CN108488345B CN 108488345 B CN108488345 B CN 108488345B CN 201810445654 A CN201810445654 A CN 201810445654A CN 108488345 B CN108488345 B CN 108488345B
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China
Prior art keywords
gear
shaft
circular
cylindrical
driven gear
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CN201810445654.3A
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CN108488345A (en
Inventor
贵新成
李红勋
贾楠
牛善田
赵重年
李心宇
冯晓梅
李立顺
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Army Military Transportation University
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Army Military Transportation University
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Classifications

    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/24—Friction clutches with axially-movable clutching members with conical friction surfaces cone clutches
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft

Abstract

The invention discloses a three-branch non-circular gear stepless speed change transmission device which comprises a phase regulator (100), a cam mechanism (1), a non-circular gear shared input and output transmission mechanism and three groups of non-circular gear branch transmission mechanisms which are connected together in a linkage mode. The three-branch non-circular gear stepless speed change transmission device disclosed by the invention can simply and reliably enable the non-circular gear speed change mechanism to realize continuous transmission within a full-angle 360 DEG range, has good transmission performance, is favorable for wide popularization and application, and has great production practice significance.

Description

Three-branch non-circular gear stepless speed change transmission device
Technical Field
The invention relates to the technical field of mechanical transmission, in particular to a three-branch non-circular gear stepless speed change transmission device.
Background
Currently, continuously variable transmission refers to a transmission mode capable of realizing continuous change of a transmission ratio between an input shaft and an output shaft in a certain range under external control, and is a development trend of a future transmission. With the continuous and deep research, the non-circular gear stepless speed change mechanism has the advantages of high power, high torque, high efficiency and wide transmission ratio, and is widely paid attention to.
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 the two non-circular gear pairs is used as two paths of input of the differential mechanism, the transmission ratio is constant in a certain angle range after being overlapped by the differential mechanism, the relative positions of the two non-circular gear pairs are changed by a phase adjusting device, the total transmission ratio is 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.
It should be noted that, the non-circular gear is also called a special gear, and is a gear with an indexing curved surface not being a rotating curved surface, and after the gear pair (gear pair) is formed by the non-circular gear and another gear, in the meshing process, the instantaneous angular velocity ratio of the non-circular gear is changed according to a certain set motion rule.
However, there is no technology that can simply and reliably allow a non-circular gear shifting mechanism to achieve a continuous transmission in the 360 range.
Disclosure of Invention
In view of the above, the invention aims to provide a three-branch non-circular gear stepless speed change transmission device which can simply and reliably enable a non-circular gear speed change mechanism to realize continuous transmission within a full-angle 360 DEG range, has good transmission performance, is beneficial to wide popularization and application, and has great production and practical significance.
The invention provides a three-branch non-circular gear stepless speed change transmission device which is characterized by comprising a phase regulator, a cam mechanism, a non-circular gear shared input and output transmission mechanism and three groups of non-circular gear branch transmission mechanisms which are connected together in a linkage mode.
Wherein, non-circular gear sharing input output drive mechanism includes: a first input shaft, a second input shaft, a first non-circular driving gear, a second non-circular driving gear as a common input transmission portion, and a first cylindrical driven gear, a second cylindrical driven gear, a first cylindrical gear shaft, a second cylindrical gear shaft, a differential mechanism, and a main output shaft as a common output transmission portion;
a first input shaft which is horizontally distributed is fixedly arranged on the left side of the first non-circular driving gear;
a second input shaft is transversely arranged in the second non-circular driving gear in a penetrating way;
a first cylindrical gear shaft is fixedly arranged on the right side of the first cylindrical driven gear;
and a second cylindrical gear shaft is transversely arranged in the first cylindrical gear shaft, and the second cylindrical gear shaft transversely penetrates through the second cylindrical driven gear.
The differential mechanism is a double-internal-meshing gear mechanism and specifically comprises a gear ring, wherein a planet carrier and a sun gear are arranged in the gear ring, and the planet carrier is positioned at the outer side of the sun gear;
the inner side of the planet carrier is meshed with the outer side of the sun gear;
the outer side of the first cylindrical gear shaft is in key connection with the inner side of the annular gear of the differential mechanism;
the outer side of the second cylindrical gear shaft is in key connection with the inner side of the planet carrier in the differential mechanism;
the outer side of the right end of the sun gear in the differential mechanism is in key connection with the inner side of the main output shaft.
The first input shaft and the first non-circular driving gear are of an integrated structure;
the right end outer side of the second input shaft is in key connection with the inner side of the second non-circular driving gear;
the right side of the second cylindrical gear shaft penetrates through the first cylindrical gear shaft, and a bearing is arranged between the outer surface of the right end of the second cylindrical gear shaft and the inner side wall of the first cylindrical gear shaft.
Wherein each set of said non-circular gear branch drives comprises: a first non-circular driven gear, a first cylindrical driving gear, a conical clutch, a second non-circular driven gear and a second cylindrical driving gear, wherein
The first non-circular driven gear is meshed with the first non-circular driving gear;
the first cylindrical driving gear is meshed with the first cylindrical driven gear;
a middle supporting shaft which is horizontally distributed is transversely arranged in the first cylindrical driving gear in a penetrating manner;
the left end of the middle supporting shaft transversely penetrates through the inside of a first middle shaft, the outer side of the left end of the middle supporting shaft is in key connection with the inner side of the first middle shaft, and the left end of the middle supporting shaft and the inner side of the first middle shaft are relatively fixed;
the second non-circular driven gear is meshed with the second non-circular driving gear;
the second cylindrical driving gear is meshed with the second cylindrical driven gear;
the right end of the intermediate support shaft transversely penetrates through the inside of a second intermediate shaft, and a bearing is arranged between the outer side of the right end of the intermediate support shaft and the inner side of the second intermediate shaft, and the two shafts can rotate relatively.
The inner side of the first non-circular driven gear is fixedly connected with the first intermediate shaft through the conical clutch;
the middle support shaft and the first cylindrical driving gear are of an integrated structure, and the first cylindrical driven gear and the first cylindrical gear shaft are of an integrated structure;
the inner side of the second non-circular driven gear is fixedly connected with the second intermediate shaft through the conical clutch.
Wherein the phase adjuster comprises a stator and a rotor, wherein:
the stator is connected with the first input shaft through a key;
the rotor is connected with the second input shaft through a key.
Wherein, the toper clutch includes two manipulation pieces, two interior axle sleeves, two outer cone disks and two return springs, wherein:
the two control blocks, the two inner sleeves, the two outer conical discs and the two return springs penetrate through the middle supporting shaft;
the outer sides of the left end and the right end of the middle supporting shaft are respectively provided with the first middle shaft and the second middle shaft;
the outer walls of the first intermediate shaft and the second intermediate shaft are respectively provided with one inner shaft sleeve; two control blocks are symmetrically arranged between the two inner sleeves;
one ends of the two control blocks, which are opposite, are respectively contacted with the cam mechanism;
the outer walls of one ends of the two inner shaft sleeves, which are opposite, are respectively sleeved with one outer conical disc;
the outer walls of the opposite ends of the first intermediate shaft and the second intermediate shaft are respectively provided with a return spring;
the inner sleeve is in axial contact with the return spring;
a bearing is arranged between the first intermediate shaft and the second intermediate shaft and the inner sleeve respectively;
the inner rings of the two bearings are fixedly connected with the first intermediate shaft and the second intermediate shaft respectively, and the outer rings of the two bearings are fixedly connected with the two inner sleeves respectively;
the bearing is in axial contact with the control block, namely the inner sleeve is in axial contact with the control block through the bearing;
the two outer conical discs are respectively connected with the first non-circular driven gear and the second non-circular driven gear in a key manner;
the inner side of the first non-circular driven gear is in key connection with the outer side of an outer conical disc arranged at the left end of the conical clutch.
The cam mechanism comprises a cam mechanism main body, and a cam driving piece is pivoted at the center of the cam mechanism main body;
the cam mechanism main body is provided with three grooves at equal intervals along the circumferential direction, and openings are formed in the inner side and the outer side of each groove;
a conical driven member is arranged in each slot, and a diaphragm spring is fixedly arranged on the outer side of each conical driven member;
a roller is arranged on the inner side of each conical driven member;
each roller is in contact with the cam driver.
The cam driving piece is provided with a round driving piece body, and the round driving piece body is provided with a bulge;
the central angle corresponding to the bulge is 130 degrees;
the cam driving piece is connected with the second input shaft through a key;
and one opposite ends of the two control blocks are respectively in axial contact with the left side and the right side of the conical driven piece in the cam mechanism.
Compared with the prior art, the technical scheme provided by the invention provides the three-branch non-circular gear stepless speed change transmission device, which can simply and reliably enable the non-circular gear speed change mechanism to realize continuous transmission within a full-angle 360-degree range, has good transmission performance, is beneficial to wide popularization and application, and has great production practical significance.
Drawings
FIG. 1 is a schematic perspective view of a three-branch non-circular gear continuously variable transmission device provided by the invention;
FIG. 2 is a schematic perspective view showing the connection state of a non-circular gear shared input/output transmission mechanism and three groups of non-circular gear branch transmission mechanisms in a three-branch non-circular gear continuously variable transmission device provided by the invention;
FIG. 3 is a schematic view of a three-dimensional exploded structure between any one group of non-circular gear shifting mechanism and cam mechanism in a three-branch non-circular gear continuously variable transmission device provided by the invention, wherein a phase regulator is omitted;
FIG. 4 is a cross-sectional view of a three-branch non-circular gear continuously variable transmission provided by the invention when any one of the non-circular gear speed change mechanisms and the cam mechanism are mutually matched;
FIG. 5 is a schematic perspective view of a phase adjuster in a three-branch non-circular gear continuously variable transmission device according to the present invention;
FIG. 6 is a schematic diagram of a three-dimensional exploded view of a phase adjuster in a three-branch non-circular gear continuously variable transmission device according to the present invention;
FIG. 7 is a schematic perspective view of a phase adjuster, a first input shaft and a second input shaft in a three-branch non-circular gear continuously variable transmission device according to the present invention;
FIG. 8 is a cross-sectional view of a three-branch non-circular gear continuously variable transmission provided by the invention, wherein any one group of non-circular gear shifting mechanisms are provided with a conical clutch which is mutually connected with an intermediate support shaft and a first intermediate shaft;
FIG. 9 is a schematic perspective exploded view of a conical clutch of any one of the non-circular gear speed changing mechanisms in the three-branch non-circular gear stepless speed changing transmission device provided by the invention;
FIG. 10 is a schematic view of a cam mechanism in a three-branch non-circular gear continuously variable transmission provided by the present invention;
FIG. 11 is a schematic diagram of a power transmission path of any one set of non-circular gear shifting mechanism in a three-branch non-circular gear continuously variable transmission device provided by the invention;
FIG. 12 is a graphical representation of the reciprocal gear ratio of an embodiment of a three-branch non-circular gear continuously variable transmission provided by the present invention with a common parameter phase difference of 0;
FIG. 13 is an image of the reciprocal gear ratio of a specific embodiment of a three-branch non-circular gear continuously variable transmission provided by the present invention when the phase difference of certain parameters is 0;
FIG. 14 is an image of the reciprocal gear ratio of a specific embodiment of a three-branch non-circular gear continuously variable transmission provided by the present invention with a specific parameter phase difference of-130;
FIG. 15 is an image of the reciprocal gear ratio of a specific embodiment of a three-branch non-circular gear continuously variable transmission provided by the present invention when the phase difference of a particular parameter is-130;
FIG. 16 is a graphical representation of the overall ratio of an embodiment of a three-branch non-circular gear continuously variable transmission with different phase differences for certain parameters, provided by the present invention;
in the figure, 1 is a cam mechanism; 2 is a second cylindrical gear shaft;
3 is a first non-circular drive gear; 4 is a first non-circular driven gear;
31 is a first input shaft; 41 an intermediate support shaft; 5 is a first cylindrical gear shaft;
40 is a first cylindrical drive gear; 30 is a first cylindrical driven gear;
700 is a differential mechanism, 6 is a sun gear; 7 is a planet carrier; 9 is a gear ring;
8 is a main output shaft; 10 is a clutch; 42 is a first intermediate shaft; a 111 second intermediate shaft;
11 is a second non-circular driven gear; 110 is a second cylindrical drive gear;
12 is a second non-circular drive gear; 120 is a second cylindrical driven gear; 121 is a second input shaft;
1001 is a diaphragm spring; 1002 is a cam driving member; 1003 roller; 1004 a conical follower;
101 is a manipulation block; 102 is an inner hub; 103 is an outer cone; 104 is a return spring;
10100 is a stator, 10200 is a rotor, 1020 is a bearing, 10021 is a driving member body, 10022 is a protrusion, and 800 is a housing.
Detailed Description
In order to better understand the aspects of the present invention, the present invention will be described in further detail with reference to the drawings and embodiments.
Referring to fig. 1 to 11, the present invention provides a three-branch non-circular gear continuously variable transmission device, which can simply and reliably enable a non-circular gear speed change mechanism to realize continuous transmission within 360 ° range, and has good transmission performance, and specifically includes: a phase adjuster 100, a cam mechanism 1, a non-circular gear common input-output transmission mechanism and three groups of non-circular gear branch transmission mechanisms which are connected together in linkage.
In a specific implementation of the present invention, the non-circular gear shared input/output transmission mechanism includes: the first input shaft 31, the second input shaft 121, the first non-circular driving gear 3, the second non-circular driving gear 12 as common input transmission portions, and the first cylindrical driven gear 30, the second cylindrical driven gear 120, the first cylindrical gear shaft 5, the second cylindrical gear shaft 2, the differential mechanism 700, and the main output shaft 8 as common output transmission portions;
a first input shaft 31 which is horizontally distributed is fixedly arranged on the left side of the first non-circular driving gear 3;
a second input shaft 121 is transversely and penetratingly arranged in the second non-circular driving gear 12;
a first cylindrical gear shaft 5 is fixedly arranged on the right side of the first cylindrical driven gear 30;
a second cylindrical gear shaft 2 is transversely arranged in the first cylindrical gear shaft 5, and the second cylindrical gear shaft 2 transversely penetrates through the second cylindrical driven gear 120.
In the present invention, in a specific implementation, the differential mechanism 700 is a double-ring gear mechanism, and specifically includes a ring gear 9, a planet carrier 7 and a sun gear 6 are disposed in the ring gear 9, and the planet carrier 7 is located at the outer side of the sun gear 6;
the inner side of the planet carrier 7 and the outer side of the sun gear 6 are meshed with each other;
the outer side of the first cylindrical gear shaft 5 is in key connection with the inner side of the annular gear 9 (serving as a first input element) of the differential mechanism 700;
a key connection is formed between the outer side of the second cylindrical gear shaft 2 and the inner side (serving as a second input element) of the planet carrier 7 in the differential mechanism 700;
in particular, the outer side of the right end of the sun gear 6 (as an output element) in the differential mechanism 700 is in key connection with the inner side of the main output shaft 8, so that the same-speed rotation is maintained.
In particular, the differential mechanism can be a bevel gear differential mechanism, a traditional planetary gear mechanism or a double-internal-meshing planetary gear mechanism. A double ring planetary gear mechanism is shown in fig. 4.
In particular, the first input shaft 31 and the first non-circular driving gear 3 are integrally formed.
In particular, the outer side of the right end of the second input shaft 121 and the inner side of the second non-circular driving gear 12 are connected by a key.
In the present invention, the right side of the second cylindrical gear shaft 2 penetrates through the first cylindrical gear shaft 5, and a bearing is installed between the outer surface of the right end of the second cylindrical gear shaft 2 and the inner side wall of the first cylindrical gear shaft 5, so that the second cylindrical gear shaft can rotate relatively. In the present invention, each group of non-circular gear branch transmission mechanisms is theoretically only operated by 120 °, but in order to maintain the power continuity, there should be a certain angle overlapping, and the actual angle of each group of non-circular gear branch transmission mechanisms should be greater than 120 °.
It should be noted that continuously variable transmission means transmission in which any gear ratio in a transmission range can be continuously obtained.
For the present invention, each set of said non-circular gear branch transmissions comprises: a first non-circular driven gear 4, a first cylindrical driving gear 40, a cone clutch 10, a second non-circular driven gear 11 and a second cylindrical driving gear 110, wherein:
the first non-circular driven gear 4 is meshed with the first non-circular driving gear 3 (specifically through gear teeth on the outer sides of the first non-circular driven gear and the first non-circular driving gear) to form a first non-circular gear pair;
the first cylindrical driving gear 40 is meshed with the first cylindrical driven gear 30 (specifically, through gear teeth on the outer sides of the first cylindrical driving gear and the first cylindrical driven gear) to form a first cylindrical gear pair;
a middle supporting shaft 41 horizontally distributed is transversely arranged in the first cylindrical driving gear 40 in a penetrating manner;
the left end of the intermediate support shaft 41 transversely penetrates through the inside of a first intermediate shaft 42, and the outer side of the left end of the intermediate support shaft 41 is in key connection with the inner side of the first intermediate shaft 42, so that the left end and the inner side of the first intermediate shaft are relatively fixed;
the second non-circular driven gear 11 is meshed with the second non-circular driving gear 12 (specifically, through gear teeth on the outer sides of the second non-circular driven gear and the second non-circular driving gear), and the second non-circular driven gear and the second non-circular driving gear form a second non-circular gear pair;
the second cylindrical driving gear 110 is meshed with the second cylindrical driven gear 120 (specifically, through gear teeth on the outer sides of the two), and the two form a second cylindrical gear pair;
the right end of the intermediate support shaft 41 transversely penetrates through the inside of a second intermediate shaft 111, and a bearing is arranged between the outer side of the right end of the intermediate support shaft 41 and the inner side of the second intermediate shaft 111, and the two shafts can rotate relatively;
in particular, the first non-circular gear pair, the second non-circular gear pair, the first spur gear pair, the second spur gear pair, the cone clutch 10 and a differential mechanism 700 are located in a hollow housing 800.
In particular, the inner side of the first non-circular driven gear 4 is fixedly connected (i.e., fixedly connected) with the first intermediate shaft 42 through the conical clutch 10.
In particular, the intermediate support shaft 41 and the first cylindrical driving gear 40 are integrally formed, and the first cylindrical driven gear 30 and the first cylindrical gear shaft 5 are integrally formed.
In particular, the inner side of the second non-circular driven gear 11 is fixedly connected (i.e. fixedly connected) with the second intermediate shaft 111 through the conical clutch 10.
In particular, the second intermediate shaft 11 and the second cylindrical driving gear 110 are integrally formed, and the second cylindrical driven gear 120 and the second cylindrical gear shaft 2 are integrally formed.
In a specific implementation of the present invention, referring to fig. 4, 5 and 6, the phase adjuster 100 includes: stator 10100 and rotor 10200, wherein:
the stator 10100 is in key connection with the first input shaft 31, and the stator 10100 and the first input shaft are fixed relatively and rotate at the same rotation speed;
the rotor 10200 is connected with the second input shaft 121 by a key, and the rotor 10200 and the second input shaft are fixed relatively and rotate at the same rotation speed;
the phase regulator (100) is connected with a common input transmission part in the non-circular gear common input-output transmission mechanism and is used for controlling and changing the relative positions (namely phases) of the first non-circular gear pair and the second non-circular gear pair so as to realize speed ratio transmission.
It should be noted that, the rotor 10200 adopts a dynamic balance structure, under the adjustment of an external swinging cylinder or a screw mechanism (i.e., an external driving device), the rotor 10200 can rotate relative to the stator 10100, the rotation angle range is-130 ° to +130°, that is, the rotor rotates to drive the second input shaft 121 to rotate simultaneously, so as to adjust the phase position of the first non-circular driving gear 3 fixedly connected to the first input shaft 31, thereby changing the phases of the first non-circular gear pair and the second non-circular gear pair, and realizing the transmission of a speed ratio.
In particular implementations of the invention, in each set of the non-circular gear branch transmissions, the cone clutch 10 includes: two steering blocks 101, two inner sleeves 102, two outer cones 103 and two return springs 104, wherein:
the two control blocks 101, the two inner sleeves 102, the two outer conical disks 103 and the two return springs 104 penetrate through the middle support shaft 41;
the first intermediate shaft 42 and the second intermediate shaft 111 are respectively arranged on the outer sides of the left end and the right end of the intermediate support shaft 41;
the outer walls of the first intermediate shaft 42 and the second intermediate shaft 111 are respectively provided with one of the inner sleeves 102. Two control blocks 101 are symmetrically arranged between the two inner sleeves 102;
one end of each of the two control blocks 101, which is opposite to each other, is in contact with the cam mechanism 1;
the outer walls of the opposite ends (namely, the far ends) of the two inner sleeves 102 are respectively sleeved with one outer conical disc 103;
the outer walls of the opposite ends (i.e. the far ends) of the first intermediate shaft 42 and the second intermediate shaft 111 are respectively provided with a return spring 104;
the inner sleeve 102 is in axial contact with the return spring 104;
a bearing 1020 is also respectively arranged between the first intermediate shaft 42 and the second intermediate shaft 111 and the inner sleeve 102;
the inner rings of the two bearings 1020 are fixedly connected with the first intermediate shaft 42 and the second intermediate shaft 111 respectively, and the outer rings of the two bearings 1020 are fixedly connected with the two inner sleeves 102 respectively;
the bearing 1020 is in axial contact with the control block 101, namely, the inner shaft sleeve 102 is in axial contact with the control block 101 through the bearing 1020;
in particular implementation, the two outer conical discs 103 are respectively connected with the first non-circular driven gear 4 and the second non-circular driven gear 11 by keys, so as to realize the rotation at the same rotation speed.
In particular implementation, the inner side of the first non-circular driven gear 4 is connected with the outer side of the outer conical disc 103 at the left end of the conical clutch 10 by a key, and the two are relatively fixed.
In a specific implementation of the present invention, the cam mechanism 1 includes: a cam mechanism main body 1005, wherein a cam driving member 1002 is pivoted at the center of the cam mechanism main body 1005 (i.e. the cam driving member 1002 can rotate by 360 °);
the cam mechanism main body 1005 is provided with three slots 1006 (i.e. the three slots 1006 are spaced 120 °) at equal intervals along the circumferential direction, and each slot 1006 is open at both inner and outer sides;
a cone follower 1004 is arranged in each slot 1006, and a diaphragm spring 1001 is fixedly arranged outside each slot 1006 on the cone follower 1004;
a roller 1003 is arranged on the inner side of each conical driven member 1004;
each roller 1003 is in contact with the cam driver 1002;
the cam mechanism main body 1005 is provided with a first through hole 1007 and a second through hole 1008.
For the present invention, it should be noted that, the cam mechanism 1 is respectively connected to a set of non-circular gear branch transmission mechanisms correspondingly, and is used for controlling the three sets of non-circular gear branch transmission mechanisms to sequentially cooperate with the non-circular gear sharing input/output transmission mechanism to perform power transmission, so as to realize continuous transmission within a full-angle 360 ° range, that is, complete continuous conversion of 360 ° power flow through continuous coordination relay.
In the present invention, the first through hole 1007 and the second through hole serve as weight reduction functions.
In particular, the cam driving member 1002 has a circular driving member body 10021, and a protrusion 10022 (specifically, integrally formed) is disposed on the circular driving member body 10021;
the central angle corresponding to the protrusion 10022 is 130 °.
In particular, the cam driving member 1002 and the second input shaft 121 are fixedly connected (i.e. keyed) by a spline, and rotate at the same rotation speed.
In particular, opposite ends of the two manipulating blocks 101 are respectively in axial contact with the left and right sides of the tapered follower 1004 in the cam mechanism 1.
In the present invention, the roller 1003 is in contact with the tapered follower 1004, and the cam follower 1004 is in contact with the diaphragm spring 1001. Therefore, when the cam mechanism driving member 1002 contacts with a certain set of rollers 1003 within the range of 130 ° of the convex center angle, the roller 1003 can push the conical driven member 1004 to move radially outwards, the diaphragm spring 1001 is compressed, and under the action of the conical driven member 1004, the engagement of the conical clutch 10 in the set of non-circular gear branch transmission mechanisms can be realized, so that the power transmission of the set of non-circular gear branch transmission mechanisms can be realized.
When the rest part of the cam mechanism driving member 1002 (namely, the part with the central angle of 230 degrees outside the bulge) is in contact with the roller 1003, under the action of the elastic force of the diaphragm spring 1001, the conical driven member 1004 and the roller 1003 fall back to the initial positions, meanwhile, in the 230 degrees range, the cam mechanism driving member 1002 sequentially passes through the other two rollers 1003 to sequentially control the other two conical driven members 1004 to move outwards along the radial direction, so that the cam mechanism driving member 1002 can sequentially act on the other two groups of non-circular gear branch transmission mechanisms, and the power transmission of the other two groups of non-circular gear branch transmission mechanisms is sequentially realized.
Therefore, as can be seen from the above technical solution, according to the present invention, with the cooperation of the cam mechanism 1 and the cone clutch 10, for three sets of non-circular gear branch transmission mechanisms, each time the cam driving member 1002 rotates one revolution, the three sets of non-circular gear branch transmission mechanisms can be controlled in sequence to perform coordination relay under the cooperation of the non-circular gear sharing input/output transmission mechanism, so as to realize power transmission within 360 °.
Furthermore, it should be noted that, in the present invention, when the tapered follower 1004 in the cam mechanism 1 moves radially outwards, the operating blocks 101 on both sides are pushed to move axially, so as to push the inner sleeve 102 to move axially, and compress the return spring 104, at this time, the friction surfaces of the inner sleeve 102 and the outer cone disc 103 contact each other and are pressed under the action of the axial thrust, the inner sleeve 102 and the outer cone disc 103 are relatively fixed and rotate at the same rotation speed, and at the same time, in view of the fact that the two outer cone discs 103 are respectively connected with the first non-circular driven gear 4 and the second non-circular driven gear 11 by a key, and the first intermediate shaft 42 and the second intermediate shaft 111 are respectively connected with the inner sleeve 102 fixedly, the connection between the first non-circular driven gear 4 and the first intermediate shaft 42 and the connection between the second non-circular driven gear 11 and the second intermediate shaft 111 can be further realized for the present invention.
Meanwhile, when the tapered follower 1004 in the cam mechanism 1 falls back radially, the separation of the inner sleeve 102 and the outer cone 103 is achieved under the elastic force of the return spring 104, i.e., the power transmission between the first non-circular driven gear 4 and the first intermediate shaft 42 and the power transmission between the second non-circular driven gear 11 and the second intermediate shaft 111 are cut off.
For the present invention, as shown in fig. 11, for the non-circular gear common input-output transmission mechanism, the power input by the external driving device is divided into two paths through the phase adjuster 100, input to two input elements of the first input shaft 31 and the second input shaft 121, respectively, and then output at a constant transmission ratio through the output element of the main output shaft 8. The specific power transmission route is shown in fig. 11.
For the present invention, in a specific embodiment, the input rotation speed may be set to n in An output rotation speed of n out The number of teeth of the driving wheel and the driven wheel of the first non-circular gear pair is z respectively 3 、z 4 Reciprocal transmission ratio is omega 4 The number of teeth of the driving wheel and the driven wheel of the second non-circular gear pair is z respectively 12 、z 11 Reciprocal transmission ratio is omega 11 A first circleThe number of teeth of the driving wheel and the driven wheel of the column gear pair is z 'respectively' 4 、z′ 3 The number of teeth of the main and driven wheels of the second cylindrical gear pair is z 'respectively' 11 、z′ 12 The rotating speed of the planet carrier of the differential mechanism is n H The rotation speed of the sun wheel is n S The rotation speed of the gear ring is n R Then n 3 ＝n 12 ＝n i ，n S ＝n out . The characteristic parameter value of the double-internal-meshing planetary differential mechanism is k, and the motion characteristic equation n of the double-internal-meshing planetary differential mechanism s +(k-1)n H -kn R =0, obtainable:
i.e.
As shown in fig. 12, r 4 And r 11 Average, ω, of reciprocal transmission ratios of the first and second non-circular gear pairs, respectively 4 And omega 11 Is linearly changed within the range of 0-260 degrees, s 4 Sum s 11 The reciprocal transmission ratio image linear segment amplitude values of the first non-circular gear pair and the second non-circular gear pair are respectively:
in order to make the non-circular gear pitch curve cover continuous and the pole diameter not too small, r is usually taken 4 ＝r 11 To avoid sharp points in the pitch curve of the non-circular gear, the non-linear segment adopts a sine-cosine curve. When the phase difference of the initial position is 0 DEG, the constant total transmission ratio is provided in the range of 0 DEG to 260 DEGDenoted as i 0 In particular, taking t= 0,130 °,260 °, then
Thus, the first and second light sources are connected,
let ω be 4 Relative omega 11 Left shift is negative, right shift is positive, and-130 is less than or equal to t 4 -t 11 130 or less
Therefore, the total gear ratio range of the mechanical continuously variable transmission is
In the embodiment of the invention, the forward gear in the transmission ratio range is 1-10, and the reverse gear is-5 to-10, so that:
because the unknown quantity is five, but the equation is only three, the characteristic parameter values k and omega of the double internal meshing planetary differential mechanism are generally given firstly 11 Amplitude s of linear segment 11 The specific combination of the mechanism characteristics and the non-circular gear pair pitch curve shape. In this example, k=1.6, s is taken 11 =0.4, thenThe reciprocal transmission ratio of the two non-circular gears at the phase difference of 0 ° and the limit phase difference is shown in fig. 12 to 15. The effective total gear ratio change curves at different phase differences are shown in fig. 16. In fig. 12 to 16, W4 is the first non-circular driven gear 4Curve of reciprocal of gear ratio of circular gear 4; w11 is a plot of the reciprocal of the second non-circular driven gear ratio.
In summary, compared with the prior art, the three-branch non-circular gear stepless speed change transmission device provided by the invention can simply and reliably enable the non-circular gear speed change mechanism to realize continuous transmission within a full-angle 360 DEG range, has good transmission performance, is beneficial to wide popularization and application, and has great production and practical significance.
The foregoing is merely a preferred embodiment of the present invention 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 invention, which are intended to be comprehended within the scope of the present invention.

Claims (4)

1. The three-branch non-circular gear stepless speed change transmission device is characterized by comprising a phase regulator (100), a cam mechanism (1), a non-circular gear shared input and output transmission mechanism and three groups of non-circular gear branch transmission mechanisms which are connected together in a linkage manner;
the non-circular gear sharing input and output transmission mechanism comprises: a first input shaft (31), a second input shaft (121), a first non-circular driving gear (3), a second non-circular driving gear (12) as a common input transmission section, and a first cylindrical driven gear (30), a second cylindrical driven gear (120), a first cylindrical gear shaft (5), a second cylindrical gear shaft (2), a differential mechanism (700), and a main output shaft (8) as a common output transmission section;
a first input shaft (31) which is horizontally distributed is fixedly arranged on the left side of the first non-circular driving gear (3);
a second input shaft (121) is transversely arranged in the second non-circular driving gear (12) in a penetrating manner;
a first cylindrical gear shaft (5) is fixedly arranged on the right side of the first cylindrical driven gear (30);
a second cylindrical gear shaft (2) is transversely arranged in the first cylindrical gear shaft (5), and the second cylindrical gear shaft (2) transversely penetrates through the second cylindrical driven gear (120);
each set of said non-circular gear branch drives comprising: a first non-circular driven gear (4), a first cylindrical driving gear (40), a conical clutch (10), a second non-circular driven gear (11) and a second cylindrical driving gear (110), wherein
The first non-circular driven gear (4) is meshed with the first non-circular driving gear (3);
the first cylindrical driving gear (40) is meshed with the first cylindrical driven gear (30);
a middle supporting shaft (41) which is horizontally distributed is transversely arranged in the first cylindrical driving gear (40) in a penetrating manner;
the left end of the middle supporting shaft (41) transversely penetrates through the inside of a first middle shaft (42), the outer side of the left end of the middle supporting shaft (41) is in key connection with the inner side of the first middle shaft (42), and the left end of the middle supporting shaft and the inner side of the first middle shaft are relatively fixed;
the second non-circular driven gear (11) is meshed with the second non-circular driving gear (12);
the second cylindrical driving gear (110) is meshed with the second cylindrical driven gear (120);
the right end of the middle supporting shaft (41) transversely penetrates through the inside of a second middle shaft (111), a bearing is arranged between the outer side of the right end of the middle supporting shaft (41) and the inner side of the second middle shaft (111), and the two bearings can rotate relatively;
the phase adjuster (100) comprises a stator (10100) and a rotor (10200), wherein:
the stator (10100) is in key connection with the first input shaft (31);
the rotor (10200) is connected with the second input shaft (121) in a key way;
the cone clutch (10) comprises two actuating blocks (101), two inner sleeves (102), two outer cone discs (103) and two return springs (104), wherein:
the two control blocks (101), the two inner sleeves (102), the two outer conical discs (103) and the two return springs (104) penetrate through the middle support shaft (41);
the outer sides of the left end and the right end of the middle supporting shaft (41) are respectively provided with a first middle shaft (42) and a second middle shaft (111);
the outer walls of the first intermediate shaft (42) and the second intermediate shaft (111) are respectively provided with an inner shaft sleeve (102);
two control blocks (101) are symmetrically arranged between the two inner sleeves (102);
one ends of the two control blocks (101) opposite to each other are respectively contacted with the cam mechanism (1);
the outer walls of one ends of the two inner sleeves (102) which are opposite to each other are respectively sleeved with one outer conical disc (103);
the outer walls of one ends of the first intermediate shaft (42) and the second intermediate shaft (111) which are opposite to each other are respectively provided with a return spring (104);
the inner sleeve (102) is in axial contact with the return spring (104);
a bearing (1020) is arranged between the first intermediate shaft (42) and the second intermediate shaft (111) and the inner shaft sleeve (102) respectively;
the inner rings of the two bearings (1020) are fixedly connected with the first intermediate shaft (42) and the second intermediate shaft (111) respectively, and the outer rings of the two bearings (1020) are fixedly connected with the two inner sleeves (102) respectively;
the bearing (1020) is in axial contact with the control block (101), namely the inner shaft sleeve (102) is in axial contact with the control block (101) through the bearing (1020);
the two outer conical discs (103) are respectively connected with the first non-circular driven gear (4) and the second non-circular driven gear (11) in a key way;
the inner side of the first non-circular driven gear (4) is in key connection with the outer side of an outer conical disc (103) arranged at the left end of the conical clutch (10);
the cam mechanism (1) comprises a cam mechanism main body (1005), wherein a cam driving piece (1002) is pivoted at the center position of the cam mechanism main body (1005);
the cam mechanism main body (1005) is provided with three grooves (1006) at equal intervals along the circumferential direction, and each groove (1006) is provided with openings at the inner side and the outer side;
a conical driven member (1004) is arranged in each slot (1006), and a diaphragm spring (1001) is fixedly arranged on the outer side of each conical driven member (1004) in each slot (1006);
a roller (1003) is arranged on the inner side of each conical driven member (1004);
each roller (1003) is in contact with the cam driver (1002);
the cam driving piece (1002) is provided with a circular driving piece body (10021), and a bulge (10022) is arranged on the circular driving piece body (10021);
the central angle corresponding to the bulge (10022) is 130 degrees;
the cam driving piece (1002) is connected with the second input shaft (121) in a key way;
one ends of the two control blocks (101) which are opposite to each other are respectively in axial contact with the left side and the right side of a conical follower (1004) in the cam mechanism (1).
2. The three-branch non-circular gear continuously variable transmission device according to claim 1, wherein the differential mechanism (700) is a double-internal-gear mechanism, the differential mechanism (700) specifically comprises a gear ring (9), a planet carrier (7) and a sun gear (6) are arranged in the gear ring (9), and the planet carrier (7) is positioned on the outer side of the sun gear (6);
the inner side of the planet carrier (7) is meshed with the outer side of the sun gear (6);
the outer side of the first cylindrical gear shaft (5) is in key connection with the inner side of an inner gear ring (9) of the differential mechanism (700);
the outer side of the second cylindrical gear shaft (2) is in key connection with the inner side of a planet carrier (7) in the differential mechanism (700);
the outer side of the right end of the sun gear (6) in the differential mechanism (700) is in key connection with the inner side of the main output shaft (8).
3. The three-branch non-circular gear continuously variable transmission device according to claim 1, wherein the first input shaft (31) and the first non-circular driving gear (3) are of an integrally formed structure;
the outer side of the right end of the second input shaft (121) is in key connection with the inner side of the second non-circular driving gear (12);
the right side of the second cylindrical gear shaft (2) penetrates through the first cylindrical gear shaft (5), and a bearing is arranged between the outer surface of the right end of the second cylindrical gear shaft (2) and the inner side wall of the first cylindrical gear shaft (5).
4. The three-branch non-circular gear continuously variable transmission according to claim 1, characterized in that the inner side of the first non-circular driven gear (4) is fixedly connected with the first intermediate shaft (42) through the conical clutch (10);
the middle support shaft (41) and the first cylindrical driving gear (40) are of an integrated structure, and the first cylindrical driven gear (30) and the first cylindrical gear shaft (5) are of an integrated structure;
the inner side of the second non-circular driven gear (11) is fixedly connected with the second intermediate shaft (111) through the conical clutch (10).
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Publication number Priority date Publication date Assignee Title
EP0797025A1 (en) * 1996-03-21 1997-09-24 LANDINI SpA Under-load change-speed gear unit with double clutch
CN1651808A (en) * 2004-02-02 2005-08-10 杨斌彬 Uninterruptible power gear speed variator
JP2006046424A (en) * 2004-08-02 2006-02-16 Toyota Motor Corp Gear type continuously variable transmission
JP2006057679A (en) * 2004-08-18 2006-03-02 Toyota Motor Corp Gear shift mechanism using non-circular gear
JP2010181004A (en) * 2009-02-09 2010-08-19 Isuzu Motors Ltd Transmission
CN201827305U (en) * 2010-09-30 2011-05-11 湖北汽车工业学院 Sectional continuous stepless speed-change transmission system device
CN102146989A (en) * 2010-09-30 2011-08-10 湖北汽车工业学院 Sectionally continuous variable-speed drive system device
DE102014200240A1 (en) * 2014-01-09 2015-07-09 Schaeffler Technologies AG & Co. KG Gear device with Rampenzahnradpaarung and vehicle with the transmission device
CN208605580U (en) * 2018-05-11 2019-03-15 中国人民解放军陆军军事交通学院 A kind of novel three branches non-circular gear infinitely variable speed transmission

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0797025A1 (en) * 1996-03-21 1997-09-24 LANDINI SpA Under-load change-speed gear unit with double clutch
CN1651808A (en) * 2004-02-02 2005-08-10 杨斌彬 Uninterruptible power gear speed variator
JP2006046424A (en) * 2004-08-02 2006-02-16 Toyota Motor Corp Gear type continuously variable transmission
JP2006057679A (en) * 2004-08-18 2006-03-02 Toyota Motor Corp Gear shift mechanism using non-circular gear
JP2010181004A (en) * 2009-02-09 2010-08-19 Isuzu Motors Ltd Transmission
CN201827305U (en) * 2010-09-30 2011-05-11 湖北汽车工业学院 Sectional continuous stepless speed-change transmission system device
CN102146989A (en) * 2010-09-30 2011-08-10 湖北汽车工业学院 Sectionally continuous variable-speed drive system device
DE102014200240A1 (en) * 2014-01-09 2015-07-09 Schaeffler Technologies AG & Co. KG Gear device with Rampenzahnradpaarung and vehicle with the transmission device
CN208605580U (en) * 2018-05-11 2019-03-15 中国人民解放军陆军军事交通学院 A kind of novel three branches non-circular gear infinitely variable speed transmission

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