阅读说明：本技术 一种嵌入式紧凑型高性能同步器、变速器 (Embedded compact high-performance synchronizer and transmission ) 是由 魏小强 张发勇 彭立印 张海涛 田晨 高建敏 汪鹏鹏 李泽 于 2020-06-24 设计创作，主要内容包括：为了解决大扭矩变速器齿轮寿命偏低和用户要求换挡更加轻便的技术问题,本发明提供了一种嵌入式紧凑型高性能同步器、变速器。本发明是在齿轮总成上设置内壁为锥面的环形凸台,将同步器的外摩擦环嵌入到该环形凸台中,从而减小了同步器的轴向安装距,能够在不增大变速器总长度的情况下,增加齿轮的齿宽,提高了齿轮的弯曲疲劳和接触疲劳寿命；本发明将锁止环嵌入齿毂中,进一步减小了同步器的轴向尺寸,从而使得滑动齿套的挂挡行程减小,因而在驾驶室挂挡行程不变的情况下,能够允许变速器摇臂的长度增大,实现大的杠杆比,提高了同步器的换挡能力,降低司机的挂挡力和摘挡力,挂挡更加轻便。(The invention provides an embedded compact high-performance synchronizer and a transmission, aiming at solving the technical problems that the service life of a gear of a large-torque transmission is low and the gear shifting required by a user is more convenient. According to the invention, the annular boss with the conical surface inner wall is arranged on the gear assembly, and the outer friction ring of the synchronizer is embedded into the annular boss, so that the axial installation distance of the synchronizer is reduced, the tooth width of the gear can be increased under the condition of not increasing the total length of the transmission, and the bending fatigue and contact fatigue life of the gear are prolonged; according to the invention, the locking ring is embedded into the gear hub, so that the axial size of the synchronizer is further reduced, and the gear engaging stroke of the sliding gear sleeve is reduced, therefore, under the condition that the gear engaging stroke of a cab is not changed, the length of the rocker arm of the transmission can be allowed to be increased, a large lever ratio is realized, the gear shifting capacity of the synchronizer is improved, the gear engaging force and the gear disengaging force of a driver are reduced, and the gear engaging is more portable.)

1. An embedded compact high performance synchronizer, characterized in that:

the gear hub comprises a first friction ring component, a first locking ring (4) and a gear hub (2) which are sequentially arranged along the axial direction;

the first friction ring assembly comprises a first outer friction ring (6) and a first middle ring (5) which are radially sleeved, the outer conical surface of the first outer friction ring (6) is embedded into the annular boss on the corresponding gear assembly, the first outer friction ring and the inner conical surface of the annular boss form a first friction pair, and the inner conical surface of the first outer friction ring (6) and the outer conical surface of the first middle ring (5) form a second friction pair;

the large end face of the first outer friction ring (6) is matched with the first locking ring (4) through a concave-convex structure, so that synchronous rotation is realized;

the end face of the small end of the first intermediate ring (5) is matched with the corresponding gear through a concave-convex structure, so that synchronous rotation is realized;

lugs (46) protruding outwards in the radial direction are arranged on the circumference of the first locking ring (4) at intervals, a plurality of clamping grooves (21) matched with the lugs (46) are arranged on the gear hub (2) at intervals, and the clamping grooves (21) are matched with the lugs (46) to realize that the first locking ring (4) can only rotate 1/4 circumferential pitches or half tooth pitches relative to the gear hub (2);

a sliding gear sleeve (1) is sleeved on the outer circumference of the gear hub (2), and a steel ball spring packaging type sliding block body (3) is arranged between the sliding gear sleeve (1) and the gear hub (2);

the sliding gear sleeve (1) can axially move along the gear hub (2) and can be axially locked with the first locking ring (4) after axially moving for a certain distance;

the steel ball spring packaging type sliding block body (3) is used for providing certain resistance for the sliding gear sleeve (1) and pushing the first locking ring (4) to axially move when the sliding gear sleeve (1) axially moves.

2. The embedded compact high performance synchronizer of claim 1, wherein:

the device also comprises a second locking ring (9) and a second friction ring assembly;

the structure of the second locking ring (9) is the same as that of the first locking ring (4), and the second locking ring and the first locking ring are symmetrically nested at two ends of the gear hub (2);

the second friction ring assembly and the first friction ring assembly are identical in structure and are symmetrically arranged at two ends of the gear hub (2).

3. The embedded compact high performance synchronizer of claim 1 or 2, characterized in that:

the inner teeth of the sliding gear sleeve (1) comprise a long tooth group and a short tooth group; the long tooth groups and the short tooth groups are uniformly and alternately arranged along the inner circle of the sliding tooth sleeve;

the long tooth group comprises a plurality of standard meshing teeth (11); the standard meshing teeth (11) are used for meshing with the combined gear ring on the corresponding gear; both sides of the standard meshing tooth (11) in the axial direction have first chamfer slopes (111);

the short tooth group comprises a plurality of locking teeth (12); the locking teeth (12) are used for being meshed with the spline locking teeth (42) of the locking ring (4) to lock; the locking tooth (12) is provided with second chamfer inclined planes (121) at two sides in the axial direction;

the gear hub (2) is provided with long spline teeth (25) and short spline teeth (26) which are alternately arranged, and a groove-shaped structure (23) is formed between each short spline tooth (26) and the adjacent long spline tooth (25);

the first locking ring (4) is annular, a plurality of groups of locking tooth groups are arranged on the outer side wall of the circumference of the first locking ring at intervals, and each group of locking tooth groups comprises a plurality of spline locking teeth (42); the tooth side of the spline locking tooth (42) is provided with a slope (421), and the slope (421) is used for being in contact with a second chamfer slope (121) on the locking tooth (12); an abdication gap (41) is formed between every two adjacent locking tooth groups, and the abdication gap (41) can avoid the interference between the first locking ring (4) and the long spline teeth (25) of the gear hub (2); the lug (46) is positioned in the middle of the abdicating notch (41);

the first locking ring (4) is axially nested on the gear hub (2); the spline locking teeth (42) on the first locking ring (4) are positioned in the groove-shaped structure (23); the long spline teeth (25) on the gear hub (2) are positioned in the abdicating notch (41);

the plurality of locking teeth (12) can be divided into two same locking units, a limiting boss (13) is arranged between the two locking units, and the limiting boss (13) is used for limiting the axial movement stroke of the sliding gear sleeve (1);

correspondingly, a first yielding groove (24) is formed after a plurality of teeth are removed from corresponding positions on the gear hub (2), and a second yielding groove (43) is formed after a plurality of spline locking teeth (42) are removed from corresponding positions on the first locking ring (4), so that interference with the limiting boss (13) is avoided.

4. The embedded compact high performance synchronizer of claim 3, wherein:

a tool withdrawal groove (15) is arranged between the adjacent long tooth group and the short tooth group.

5. The embedded compact high performance synchronizer of claim 4, wherein:

an arc structure (14) which is spliced by a large arc or multiple arcs is arranged at the root part of the locking tooth (12) on the inner ring of the sliding tooth sleeve (1).

6. The embedded compact high performance synchronizer of claim 5, wherein:

a plurality of first claws (61)/grooves are arranged on the end surface of the large end of the first outer friction ring (6) along the circumferential direction; a first hole groove (45)/a convex claw matched with the first convex claw (61)/the groove are arranged on the first locking ring (4); the first outer friction ring (6) and the first locking ring (4) can synchronously rotate along the circumferential direction through the matching of the first convex claws (61)/the grooves and the first hole grooves (45)/the convex claws;

a plurality of second claws (51)/grooves are arranged on the end surface of the small end of the first middle ring (5) along the circumferential direction; a second groove (74)/convex claw matched with the second convex claw (51)/groove is arranged on the corresponding gear; the first intermediate ring (5) and the corresponding gear can rotate synchronously along the circumferential direction through the matching of the second convex claw (51)/the groove and the second concave groove (74)/the convex claw.

7. The embedded compact high performance synchronizer of claim 6, wherein:

a first spoon-shaped structure (62) consisting of an arc surface and an inclined surface is processed at the root part of the first convex claw (61);

a second spoon-shaped structure (52) consisting of an arc surface and an inclined surface is processed at the root part of the second convex claw (51);

alternatively, the first and second electrodes may be,

the root parts of the first convex claw (61) and the second convex claw (51) are both processed with sunk groove-shaped structures.

8. The embedded compact high performance synchronizer of claim 1 or 2, characterized in that: lubricating oil grooves are formed in the end face of the small end of the first outer friction ring (6) and the end face of the small end of the first middle ring (5).

9. A transmission comprising a synchronizer and a gear assembly; the method is characterized in that:

the synchronizer is the embedded compact high-performance synchronizer of any one of claims 1-8;

the gear assembly comprises a gear and a combined gear ring; and the gear and the combined gear ring are fixedly connected by adopting integrated forging molding, axial welding or radial welding.

10. The transmission of claim 9, wherein:

the annular boss is arranged at the belly of the gear; or the inner side wall of the combined gear ring; or one part is arranged on the belly part of the gear and the other part is arranged on the inner side wall of the combined gear ring.

Technical Field

The invention relates to an embedded compact high-performance synchronizer and a transmission.

Background

With the development of a high-horsepower high-torque manual transmission, it has become extremely difficult for the conventional synchronizer to achieve a small transmission length by a small mounting distance and a shift stroke, or to increase the bending fatigue and contact fatigue life of the gears by increasing the gear width by reducing the mounting distance of the synchronizer without changing the transmission length.

In addition, the requirement of a user on the portability of gear shifting is higher and higher, a driver requires lighter gear shifting force and gear disengaging force, no impact and no pause and frustration are caused in the gear shifting process, and the driving labor intensity is reduced.

Disclosure of Invention

The invention provides an embedded compact high-performance synchronizer and a transmission adopting the synchronizer, aiming at solving the technical problems that the service life of a gear of a large-torque transmission is low and the shifting required by a user is more convenient.

The technical scheme of the invention is as follows:

an embedded compact high-performance synchronizer is characterized in that:

the gear hub is arranged on the first friction ring component and the second locking ring component;

the first friction ring assembly comprises a first outer friction ring and a first middle ring which are radially sleeved, the outer conical surface of the first outer friction ring is embedded into the annular boss on the corresponding gear assembly, the first outer friction ring and the inner conical surface of the annular boss form a first friction pair, and the inner conical surface of the first outer friction ring and the outer conical surface of the first middle ring form a second friction pair;

the end face of the large end of the first outer friction ring is matched with the first locking ring through a concave-convex structure, so that synchronous rotation is realized;

the end face of the small end of the first intermediate ring is matched with the corresponding gear through a concave-convex structure, so that synchronous rotation is realized;

the circumference of the first locking ring is provided with lugs protruding outwards along the radial direction at intervals, the gear hub is provided with a plurality of clamping grooves at intervals, and the clamping grooves are matched with the lugs to realize that the first locking ring can only rotate 1/4 circumferential pitches or half tooth pitches relative to the gear hub;

a sliding gear sleeve is sleeved on the outer circumference of the gear hub, and a steel ball spring packaging type sliding block body is arranged between the sliding gear sleeve and the gear hub;

the sliding gear sleeve can axially move along the gear hub and can be axially locked with the first locking ring after axially moving for a certain distance;

the steel ball spring packaging type sliding block body is used for providing certain resistance for the sliding gear sleeve when the sliding gear sleeve moves axially and pushing the first locking ring to move axially.

Further, the device also comprises a second locking ring and a second friction ring assembly;

the structure of the second locking ring is the same as that of the first locking ring, and the second locking ring and the first locking ring are symmetrically nested at two ends of the gear hub;

the second friction ring assembly and the first friction ring assembly are identical in structure and are symmetrically arranged at two ends of the gear hub.

Further, the inner teeth of the sliding gear sleeve comprise a long tooth group and a short tooth group; the long tooth groups and the short tooth groups are uniformly and alternately arranged along the inner circle of the sliding tooth sleeve;

the long tooth group comprises a plurality of standard meshing teeth; the standard meshing teeth are used for meshing with the combined gear ring on the corresponding gear; the standard meshing teeth are provided with first chamfer inclined planes at two sides in the axial direction;

the short tooth group comprises a plurality of locking teeth; the locking teeth are used for being meshed with the spline locking teeth of the locking ring to lock; the two sides of the locking tooth in the axial direction are provided with second chamfer inclined planes;

the gear hub is provided with long spline teeth and short spline teeth which are alternately arranged, and a groove-shaped structure is formed between each short spline tooth and the adjacent long spline tooth;

the first locking ring is annular, a plurality of groups of locking tooth groups are arranged on the outer side wall of the circumference of the first locking ring at intervals, and each group of locking tooth groups comprises a plurality of spline locking teeth; the tooth side of the spline locking tooth is provided with an inclined surface which is used for being in contact with a second chamfer inclined surface on the locking tooth; an abdication gap is formed between every two adjacent locking tooth groups, and the abdication gap can avoid the interference between the first locking ring and the long spline teeth of the gear hub; the lug is positioned in the middle of the abdication gap;

the first locking ring is axially nested on the gear hub; the spline locking teeth on the first locking ring are positioned in the groove-shaped structure; the long spline teeth on the gear hub are positioned in the abdicating notch;

the plurality of locking teeth can be divided into two same locking units, and a limiting boss is arranged between the two locking units and used for limiting the axial movement stroke of the sliding gear sleeve;

correspondingly, a first abdicating groove is formed after a plurality of teeth are removed from corresponding positions on the gear hub, and a second abdicating groove is formed after a plurality of spline locking teeth are removed from corresponding positions on the first locking ring, so that interference with the limiting boss is avoided.

Further, a tool withdrawal groove is arranged between the adjacent long tooth group and the short tooth group.

Furthermore, an arc structure formed by splicing a large arc or multiple arcs is arranged at the root part of the locking tooth on the inner ring of the sliding tooth sleeve.

Furthermore, a plurality of first convex claws/grooves are arranged on the end surface of the large end of the first outer friction ring along the circumferential direction; a first hole groove/convex claw matched with the first convex claw/groove is arranged on the first locking ring; the first outer friction ring and the first locking ring can synchronously rotate along the circumferential direction through the matching of the first convex claw/groove and the first hole groove/convex claw;

a plurality of second convex claws/grooves are arranged on the end surface of the small end of the first middle ring along the circumferential direction; a second groove/convex claw matched with the second convex claw/groove is arranged on the corresponding gear; the first intermediate ring and the corresponding gear can rotate synchronously along the circumferential direction through the matching of the second convex claws/grooves and the second grooves/convex claws.

Furthermore, a first spoon-shaped structure consisting of an arc surface and an inclined surface is processed at the root part of the first convex claw;

a second spoon-shaped structure consisting of an arc surface and an inclined surface is processed at the root part of the second convex claw;

alternatively, the first and second electrodes may be,

the root parts of the first convex claw and the second convex claw are both processed with sunk groove structures.

Furthermore, lubricating oil grooves are formed in the end face of the small end of the first outer friction ring and the end face of the small end of the first middle ring.

A transmission comprising a synchronizer and a gear assembly; it is characterized in that:

the synchronizer is the embedded compact high-performance synchronizer;

the gear assembly comprises a gear and a combined gear ring; and the gear and the combined gear ring are fixedly connected by adopting integrated forging molding, axial welding or radial welding.

Further, the annular boss is arranged on the belly of the gear; or the inner side wall of the combined gear ring; or one part is arranged on the belly part of the gear and the other part is arranged on the inner side wall of the combined gear ring.

The invention has the advantages that:

1. in the prior art, a conical surface body is arranged on a combined gear ring, and an inner conical surface of an inner friction ring of a synchronizer is matched with a conical surface body of a pair of combined gear rings to form a pair of friction pairs; the gear assembly is provided with the annular boss with the conical surface on the inner wall, and the outer friction ring of the synchronizer is embedded into the annular boss, so that the axial installation distance of the synchronizer is reduced, the tooth width of the gear can be increased under the condition of not increasing the total length of the transmission, and the bending fatigue and contact fatigue life of the gear are prolonged; the invention reduces the installation distance of the synchronizer, and can reduce the total length of the transmission under the condition of not changing the tooth width of the existing gear.

2. The gear hub is provided with the long spline teeth and the short spline teeth, and a space for accommodating the spline locking teeth on the locking ring can be formed between the long spline teeth and the short spline teeth, so that the locking ring can be embedded into the gear hub, the axial size of the synchronizer is further reduced, the gear engaging stroke of the sliding gear sleeve is reduced, the length of a rocker arm of the transmission can be increased under the condition that the gear engaging stroke of a cab is not changed, a large lever ratio is realized, the gear shifting capacity of the synchronizer is improved, the gear engaging force and the gear disengaging force of a driver are reduced, and the gear engaging is lighter and lighter.

3. According to the invention, the sliding gear sleeve is designed in a long-short gear separation mode, and the long gear does not participate in locking, so that the distance between the end face of the long gear and the end face of the gear ring can be smaller, and the probability of secondary ring shifting impact is reduced.

4. In the traditional scheme, the sliding gear sleeve only has long teeth, not only participates in meshing and engaging but also participates in locking, only one locking angle is provided, the requirements of reliable locking and quick entering and convenient engaging cannot be considered, and only the angle of the locking angle can be selected; the sliding gear sleeve is designed in a long-short gear separation mode, the long gear is used for meshing and engaging, the locking angle on the long gear can be smaller so as to be convenient for entering into the gear quickly, the short gear is used for locking, and the locking angle on the short gear can be larger so as to improve the locking reliability.

5. In the conventional structure, an inner conical surface of an outer friction ring is matched with an outer conical surface of a gear ring frustum to form a friction pair, as shown in fig. 16 (a); the friction pair formed by the outer conical surface of the outer friction ring and the inner conical surface of the annular boss on the gear assembly is shown as (b) in fig. 16; compared with the traditional structure, the friction radius of the synchronizer is generally increased by about the thickness of an outer friction ring frustum, so that the friction torque is increased, the shifting performance of the synchronizer is remarkably optimized, and the synchronization capacity is larger.

6. The traditional combined gear ring is connected with the gear through a spline, so that the radial space of the synchronizer is limited; the invention cancels the spline connection between the gear ring and the gear, and saves the radial space, thereby having light weight, low cost and space saving compared with the traditional synchronizer structure; meanwhile, the rotational inertia and the dragging torque are reduced, and the whole box efficiency is improved.

7. The invention adopts the steel ball spring packaging type sliding block body, and can ensure that the steel ball and the spring cannot be separated from the sliding block body after the synchronizer is shifted, so that the width of a sliding gear sleeve can be smaller, and the smaller mounting distance and the shifting stroke can be realized.

8. Lubricating oil grooves are formed in the small end face of the outer friction ring and the small end face of the middle ring, and lubricating oil firstly enters the end face of the gear and finally enters the space between the conical surfaces of the two friction pairs under the action of centrifugal force, so that the friction conical surfaces are lubricated conveniently, and heat generated in the friction process is taken away.

Drawings

Fig. 1 is a schematic diagram of the structural principle of the present invention.

Fig. 2 is a schematic structural view of the sliding sleeve gear of the present invention.

Fig. 3 is a partially enlarged view of the sliding sleeve according to the present invention.

Fig. 4 is a schematic structural view of the hub gear of the present invention.

Fig. 5 is a schematic view of the locking ring of the present invention.

FIG. 6 is a schematic view of the construction of the outer friction ring of the present invention.

FIG. 7 is a schematic view of the structure of the intermediate ring in the present invention.

FIG. 8 is a schematic view of another structure of the intermediate ring in the present invention.

FIG. 9 is a schematic view of the first and second gear assemblies.

FIG. 10 is a schematic illustration of a friction cone ring lubrication circuit.

FIG. 11 is a schematic view of a precision forging forming structure of a spline integrated with a gear and a bonded ring gear, wherein (a) is a schematic view of a forming structure of a first gear and a first bonded ring gear; (b) the integral forming structure schematic diagram of the second gear and the second combined gear ring is shown.

FIG. 12 is a schematic view of a split axial welding structure of a gear and a bonded gear ring, wherein (a) is a schematic view of a split axial welding structure of a first gear and a first bonded gear ring; (b) is a schematic diagram of a split type axial welding structure of a second gear and a second combined gear ring.

FIG. 13 is a schematic view of a split radial weld configuration of the gear assembly and the bonded ring gear, wherein (a) is a schematic view of a split radial weld configuration of the first gear and the first bonded ring gear; (b) is a schematic diagram of a split type radial welding structure of a second gear and a second combined gear ring.

Fig. 14 is an exploded view of the present invention.

FIG. 15 is a schematic representation of two different placement positions for the annular boss on the gear assembly of the present invention, (a) with a portion of the annular boss on the web of the gear and a portion on the inner sidewall of the mating ring gear; (b) the annular boss is positioned on the inner side wall of the combined gear ring.

FIG. 16 is a schematic diagram of the comparison between the friction radius of the outer friction ring in the conventional structure and the friction radius of the outer friction ring of the present invention, wherein (a) is a schematic diagram of the friction radius of the outer friction ring in the conventional structure, and the inner conical surface of the outer friction ring is matched with the outer conical surface of the gear ring frustum to form a friction pair; (b) the outer conical surface of the outer friction ring is matched with the inner conical surface of the annular boss to form a friction pair.

Description of reference numerals:

1-sliding gear sleeve; 11-standard meshing teeth; 111-a first chamfer bevel; 12-locking teeth; 121-a second chamfer bevel; 13-limiting boss; 14-arc structure; 15-tool withdrawal groove; 16-a spherical groove;

2-a gear hub; 21-card slot; 22-a radial groove; 23-a trough-like structure; 24-a first yielding slot; 25-long spline teeth; 26-short spline teeth;

3-steel ball spring packaging type sliding block body; 31-steel balls; 32-a spring; 33-a slide block;

4-a first locking ring; 41-yielding gap; 42-spline locking teeth; 421-inclined plane; 43-a second abdicating groove; 44-round corners; 45-first bore and groove; 46-a lug;

5-a first intermediate ring; 51-a second lug; 52-a second scoop-like structure; 53-second lubrication groove; 54-sink-trough like structure;

6-a first outer friction ring; 61-a first lug; 62-a first scoop-like structure; 63-a first lubricant sump;

7-a first gear assembly; 71-a first gear; 72-a first bonded ring gear; 721-a first engaging tooth; 73-a first inner conical surface; 74-a second groove;

8-a second gear assembly; 81-a second gear; 82-a second ring gear; 821-a second coupling tooth; 83-a second inner conical surface; 84-a groove;

9-a second locking ring;

101-a second outer friction ring; 102-second intermediate ring.

Detailed Description

The invention is further described below with reference to the accompanying drawings.

As shown in fig. 1 and 14, the embedded compact high-performance synchronizer provided by the present invention is disposed between a first gear assembly 7 and a second gear assembly 8, wherein the first gear assembly 7 is composed of a first gear 71 and a first combined ring gear 72; the second gear assembly 8 is constituted by a second gear 81 and a second ring gear 82.

The embedded compact high-performance synchronizer comprises a first friction ring assembly, a first locking ring 4, a gear hub 2, a second locking ring 9 and a second friction ring assembly which are sequentially arranged along the axial direction; the outer circumference of the gear hub 2 is sleeved with a sliding gear sleeve 1; a steel ball spring packaging type slider body 3 is further arranged between the sliding gear sleeve 1 and the gear hub 2, the steel ball spring packaging type slider body 3 is specifically arranged in a radial groove 22 of the gear hub 2, and the gear hub 2 is structurally shown in fig. 4.

The first friction ring assembly and the second friction ring assembly are identical in structure; the first friction ring assembly comprises a first outer friction ring 6 and a first middle ring 5 which are radially sleeved, and the second friction ring assembly comprises a second outer friction ring 101 and a second middle ring 102 which are radially sleeved; wherein, the outer conical surface of the first outer friction ring 6 and the first inner conical surface 73 of the annular boss on the first gear 71 form a first friction pair, and the inner conical surface of the first outer friction ring 6 and the outer conical surface of the first intermediate ring 5 form a second friction pair; the outer conical surface of the second outer friction ring 101 and the second inner conical surface 83 of the annular boss on the second gear 81 form a third friction pair, and the inner conical surface of the second outer friction ring 101 and the outer conical surface of the second intermediate ring 102 form a fourth friction pair; the conical surface structures of the first inner conical surface 73 and the second inner conical surface 83 of the annular bosses on the first gear 7 and the second gear 8 are shown in FIG. 9; in the synchronization process, the conical surfaces of the first friction pair and the second friction pair work simultaneously to play a friction synchronization role, or the conical surfaces of the third friction pair and the fourth friction pair work simultaneously to play a friction synchronization role.

Friction material may be applied to any one of the conical surfaces forming the first friction pair, for example, friction material may be added to the outer conical surface of the first outer friction ring 6 or friction material may be added to the first inner conical surface 73 of the annular boss of the first gear 71.

Friction material may be applied to any one of the conical surfaces forming the second friction pair, for example, friction material may be added to the inner conical surface of the first outer friction ring 6 or friction material may be added to the outer conical surface of the first intermediate ring 5.

The two ways of increasing the friction material can be combined, that is, the friction material can be increased on both the inner conical surface and the outer conical surface of the first outer friction ring 6, and then the friction material does not need to be increased on the first inner conical surface 73 of the annular boss of the first gear 71 and the outer conical surface of the first intermediate ring 5; alternatively, there is no friction material on both the inner and outer conical surfaces of the first outer friction ring 6, and there is friction material added on both the first inner conical surface 73 of the annular land of the first gear 71 and the outer conical surface of the first intermediate ring 5.

The friction material added can be carbon composite friction material such as bonded carbon fiber and carbon particles, or molybdenum spraying, copper alloy, sintered copper and resin friction material.

The schemes for adding friction materials on the conical surfaces of the third friction pair and the fourth friction pair are respectively the same as those of the first friction pair and the second friction pair, and are not described again.

As shown in fig. 1 and 4, the steel ball spring packaging type slider body 3 comprises a steel ball 31, a spring 32 and a slider 33; the sliding blocks 33 are nested in the radial grooves 22 of the gear hub 2 and cannot move along the radial direction of the gear hub 2 but can move along the axial direction of the gear hub 2; the spring 32 is arranged in the slide block 33, the steel ball 31 and the spring 32 are packaged into a whole, the steel ball 31 cannot be separated out by itself, and the steel ball 31 can freely slide in the spherical groove 16 at the lower end of the sliding gear sleeve 1 and can do telescopic motion along the radial direction.

As shown in fig. 3 and 9, the internal teeth of the sliding gear sleeve 1 have two forms, namely a long tooth group and a short tooth group; the long tooth groups and the short tooth groups are uniformly and alternately arranged along the inner circle of the sliding tooth sleeve; the long teeth set comprises a plurality of standard meshing teeth 11; the normal engagement teeth 11 are used to engage with the first engagement teeth 721 of the first engagement ring gear 72 of the first gear assembly 7 or the second engagement teeth 821 of the second engagement ring gear 82 of the second gear assembly 8 after the synchronizer is put into gear, to transmit power; the standard engaging tooth 11 has first chamfer slopes 111 on both sides in the axial direction. The short tooth group comprises a plurality of locking teeth 12; the locking teeth 12 are used for meshing with the spline locking teeth 42 of the locking ring 4 to lock; the locking tooth 12 has second chamfer inclined planes 121 on two sides in the axial direction, and the second chamfer inclined planes 121 are used for being in contact with the inclined planes 421 on the spline locking teeth 42 of the locking ring 4 so as to enable the locking to be attached tightly in the synchronous speed difference process of the synchronizer, and the locking reliability is improved. The tooth shapes and the locking angle angles of the standard meshing teeth 11 and the locking teeth 12 (two locking angles are provided in the invention, and are respectively determined by the first chamfer inclined plane 111 and the second chamfer inclined plane 121) can be flexibly selected according to the functions required in practice.

In order to facilitate the use of the chamfering machine to process the locking teeth 12 and avoid the interference of the cutter bar of the chamfering machine with the standard meshing teeth 11, a relief groove 15 is arranged between the adjacent long tooth group and the short tooth group, and the relief groove 15 can be formed by removing a plurality of locking teeth 12 on the sliding gear sleeve 1, which are close to the long tooth group, as shown in fig. 2 and 3.

The locking teeth 12 in the short tooth group may be divided into two identical locking units, and a limit boss 13 is provided between the two locking units, the limit boss 13 being configured to contact the first coupling tooth 721 of the first coupling ring gear 72 of the first gear assembly 7 or the second coupling tooth 821 of the second coupling ring gear 82 of the second gear assembly 8; when the sliding gear sleeve 1 axially moves for a certain distance, the limiting boss 13 is contacted with the first combination tooth 721 of the first gear assembly 7 or the second combination tooth 821 of the second gear assembly 8, so that the sliding gear sleeve 1 is limited to continuously axially move, and the function of limiting in-place gear engagement is realized; the limit boss 13 may be an isosceles trapezoid limit boss, a spline tooth-shaped limit boss, a rectangular limit boss, a square limit boss, a semicircular limit boss or a basin-shaped limit boss. Meanwhile, a first abdicating groove 24 (shown in fig. 4) is formed after a plurality of teeth are removed from corresponding positions on the gear hub 2, and a second abdicating groove 43 (shown in fig. 5) is formed after a plurality of spline locking teeth 42 are removed from corresponding positions on the first locking ring 4, so as to avoid interference with the limiting boss 13 on the sliding gear sleeve 1, and thus the sliding gear sleeve 1 can slide axially and smoothly; the number of the limiting lug bosses 13 arranged on the sliding gear sleeve 1, the gear hub 2 and the corresponding tooth removing quantity on the first locking ring 4 can be 3, 4, 5, 6 or more, and the purpose of avoiding interference is achieved.

In order to facilitate the processing of the locking teeth 12, a large arc or three-arc spliced arc-shaped structure 14 is arranged at the root of the locking teeth 12 on the inner ring of the sliding gear sleeve 1, so that the large-diameter milling cutter can be used for processing conveniently.

As shown in fig. 5, the first locking ring 4 is annular, and a plurality of locking tooth sets are arranged on the outer circumferential side wall at intervals, and each locking tooth set includes a plurality of spline locking teeth 42; the tooth side of the spline locking tooth 42 is provided with a slope 421, and the slope 421 is used for connecting with the second chamfer slope 121 on the two sides of the locking tooth 12 of the sliding tooth sleeve 1; an abdicating notch 41 is formed between two adjacent locking tooth groups, and the abdicating notch 41 can avoid the interference between the first locking ring 4 and the spline teeth of the gear hub 2; a fillet 44 (also can be a chamfer angle) is further chamfered at the groove bottom of the abdicating notch 41 so as to avoid interference with the tooth edge of the gear hub 2; in the middle of each abdicating notch 41, a lug 46 is also provided, which is outwardly convex in the radial direction. The second lock ring 9 has the same structure as the first lock ring 4, and the fitting relationship between the second lock ring 9 and the sliding gear sleeve 1 and the gear hub 2 is the same as the fitting relationship between the first lock ring 4 and the sliding gear sleeve 1 and the gear hub 2.

As shown in fig. 4, the gear hub 2 is provided with a plurality of slots 21 at intervals for engaging with the lugs 46 of the first locking ring 4, when the two are engaged, the first locking ring 4 can only rotate 1/4 revolutions or half pitch relative to the gear hub 2, and at this time, when the sliding gear sleeve 1 moves axially along the gear hub 2, the inclined surface 421 of the spline locking tooth 42 of the locking ring 4 can be abutted against the second chamfer inclined surface 121 of the locking tooth 12 of the sliding gear sleeve 1 to lock; the number of the lugs 46 arranged on the locking ring 4 is equal to the number of the slots 21 arranged on the gear hub 2, and can be 3, 4, 5, 6 or more.

In order to nest the first locking ring 4 on the hub 2, the hub 2 has long spline teeth 25 and short spline teeth 26 arranged alternately, and a groove-like structure 23 for accommodating the spline locking teeth 42 on the first locking ring is formed between the short spline teeth 26 and the adjacent long spline teeth 25; after the first lock ring 4 is nested on the gear hub 2, the spline lock teeth 42 are radially nested in the groove-shaped structures 23 on the gear hub 2, and the number of the groove-shaped structures 23 can be 3, 4, 5, 6 or more, as shown in fig. 4.

As shown in fig. 6, a plurality of first claws 61 are arranged on the end surface of the large end of the first outer friction ring 6 along the circumferential direction; as shown in fig. 5, the first locking ring 4 is provided with a first hole 45 (which may be a through hole or a groove) adapted to the first protrusion 61; the first outer friction ring 6 and the first locking ring 4 can rotate synchronously along the circumferential direction through the matching of the first convex claws 61 and the first hole grooves 45; the first claws 61 can be rectangular and kidney-shaped, and the first holes 45 can be rectangular, kidney-shaped, round, runway-shaped, etc.; the number of the first claws 61 is equal to that of the first grooves 45, and may be 3, 4, 5, 6 or more. Or, a groove can be arranged on the small end face of the first outer friction ring 6 along the circumferential direction, a boss matched with the groove on the small end face of the first outer friction ring 6 is arranged on the first locking ring 4, and the first outer friction ring 6 and the first locking ring 4 synchronously rotate along the circumferential direction through the matching of the groove and the boss. The second outer friction ring 101 and the second lock ring 9 achieve the circumferential synchronous rotation in the same manner as the first outer friction ring 6 and the first lock ring 4 achieve the circumferential synchronous rotation.

As shown in fig. 7, a plurality of second claws 51 are arranged on the small end surface of the first intermediate ring 5 along the circumferential direction; as shown in fig. 9, a second groove 74 adapted to the second claw 51 is provided on the first gear 71; the first intermediate ring 5 and the first gear assembly 7 can rotate synchronously along the circumferential direction through the matching of the second convex claws 51 and the second concave grooves 74; the second claws 51 may be rectangular, kidney-shaped, and the second grooves 74 may be rectangular, basin-shaped, kidney-shaped, circular, run-to-run, etc.; the number of the second claws 51 and the second grooves 74 is equal, and may be 3, 4, 5, 6 or more. Alternatively, a plurality of grooves may be circumferentially arranged on the large end surface of the first intermediate ring 5, and corresponding bosses may be provided on the first gear 71, so that the first intermediate ring 5 and the first gear assembly 7 may rotate synchronously in the circumferential direction by the cooperation of the grooves and the bosses. The way of realizing the circumferential synchronous rotation of the second intermediate ring 102 and the second gear assembly 8 is the same as the way of realizing the circumferential synchronous rotation of the first intermediate ring 5 and the first gear assembly 7, namely, the groove 84 is arranged on the second gear assembly 8, and the matched convex claw is arranged on the second intermediate ring 102.

In order to avoid the root of the first claw 61 on the first outer friction ring 6 from breaking, a first spoon-shaped structure 62 formed by an arc surface and an inclined surface is processed at the root of the first claw 61, as shown in fig. 6; similarly, a second spoon-shaped structure 52 formed by a circular arc surface and an inclined surface is processed at the root of the second claw 51 on the first intermediate ring 5, as shown in fig. 7. In other embodiments, the second scoop-like structure 52 can be replaced with a sink-shaped structure 54 as shown in fig. 8, and similarly, the scoop-like structure 62 can be replaced with a sink-shaped structure.

In order to facilitate lubricating the conical surface of the friction pair of the synchronizer and take away heat generated in the friction process, a first lubricating oil groove 63 (shown in fig. 6) is further formed in the small end face of the first outer friction ring 6, and a second lubricating oil groove 53 (shown in fig. 7) is formed in the small end face of the first middle ring 5; the number of the first lubricating oil grooves 63 and the second lubricating oil grooves 53 can be 3, 4, 5, 6 or more, the cross section can be trapezoidal, rectangular, square, U-shaped or V-shaped, and the like, and the arc transition can be added at the root parts; the formed oil circuit lubrication path flows in the arrow direction shown in fig. 10 under the action of the centrifugal force of the rotation of the gear assembly, the transmission gear oil flows radially along the first lubrication oil groove 63 and the second lubrication oil groove 53 from the center to the outer side, is shunted at the small ends of the friction conical surfaces of the first friction pair and the second friction pair, flows in from the small end surfaces of the first friction pair and the second friction pair respectively, flows out from the large end surface, flows out from the end surface at the edge of the gear hub 2 and the end surfaces of the combined gear rings on the first gear assembly 7 and the second gear assembly 8, and finally flows into the bottom of the transmission shell to form a closed-loop lubrication circuit, continuously lubricates the friction conical surface of the synchronizer, takes away the heat generated by friction in the synchronization process, and enables the friction material to work for a long time.

The second outer friction ring 101 is identical in structure to the first outer friction ring 6, and the second intermediate ring 102 is identical in structure to the first intermediate ring 5, and will not be described in detail here.

In the present invention, the first engaging tooth 721 of the first engaging ring gear of the first gear assembly 7 and the second engaging tooth 821 of the second engaging ring gear 82 of the second gear assembly 8 are both external splines, and can be processed by a gear shaping process under the condition of small external diameter of the gear teeth, and at this time, the gear shaping does not interfere with the end face of the gear teeth until the gear shaping is axial, as shown in fig. 9. The combined gear ring and the gear can also adopt an integrated integral structure as shown in fig. 11, and the external spline on the combined gear ring can be processed by a precision forging forming technology. The gear and the combined gear ring can also be welded into a whole by adopting a welding process, and the welding mode can adopt axial welding as shown in figure 12 or radial welding as shown in figure 13. The radial welding can adopt a brazing or electron beam welding mode, and can also adopt a mode of welding before heat treatment or welding after anti-seepage heat treatment before heat treatment.

The working principle and the process of the invention are as follows:

because the first locking ring 4 is nested in the gear hub 2, the first locking ring 4 is driven by the gear hub 2 to rotate synchronously in the circumferential direction; the first friction ring 6 is in concave-convex fit connection with the first locking ring 4, and the first friction ring 6 and the first locking ring 4 rotate synchronously; therefore, the gear hub 2, the first lock ring 4 and the first friction ring 6 rotate synchronously;

the first intermediate ring 5 is in concave-convex fit connection with the first gear assembly 7 and synchronously rotates;

when the sliding gear sleeve 1 is pushed to move leftwards to engage a gear, the spherical groove 16 of the sliding gear sleeve 1 drives the steel ball spring packaging type sliding block body 3 to move axially together, the end face of the steel ball spring packaging type sliding block body 3 is contacted with the end face of the first locking ring 4, the steel ball spring packaging type sliding block body 3 drives the first locking ring 4 to move axially, the first locking ring 4 drives the first intermediate ring 5 to move along the conical surface of the second friction pair, in the moving process of the first locking ring 4 and the first intermediate ring 5, the conical surfaces of the first friction pair and the second friction pair are gradually attached, when no gap exists between the conical surfaces of the first friction pair and the second friction pair, the first friction pair and the second friction pair are both attached, so that the first friction ring 6 drives the first locking ring 4 to rotate under the action of circumferential friction torque generated by the conical surfaces of the friction pairs, when the spline locking teeth 42 of the first locking ring 4 rotate 1/4 for a circumference or a half pitch relative to the gear hub 2, the locking teeth 12 on the sliding gear sleeve 1 which moves axially are attached to the spline locking teeth 42 of the locking ring 4 and are in a locking state, the synchronizer starts to play a synchronization role, the sliding gear sleeve 1, the gear hub 2, the first locking ring 4 and the first outer friction ring 6 are at the same rotating speed, the first gear assembly 7 and the first intermediate ring 5 are at the other rotating speed, the two rotating speeds are finally consistent along with continuous friction of the friction conical surface, and the synchronization process is finished.

Then, under the action of a gear engaging force, the sliding gear sleeve 1 continues to axially move to press down a steel ball of the steel ball spring packaging type slider body 3, the spring of the steel ball spring packaging type slider body 3 is further compressed, the second chamfer inclined plane 121 on the short tooth group of the sliding gear sleeve 1 extrudes the inclined plane 421 of the first locking ring 4 to force the first locking ring 4 to reversely rotate 1/4 for a circle pitch or a half pitch, at the moment, the tooth top of the short tooth group of the sliding gear sleeve 1 corresponds to the tooth space of the spline locking tooth 42 on the first locking ring 4, so that the sliding gear sleeve 1 can continue to axially move, the standard meshing tooth 11 of the sliding gear sleeve 1 is meshed with the combination tooth 721 of the first combination 72 gear ring of the first gear assembly 7 after passing through the steel ball of the slider body 3 and the first locking ring 4, and finally, the movement is stopped after reaching the finger positioning movement, and the gear engaging process is completed.

The principle of pushing the sliding gear sleeve 1 to move axially to the right for gear engagement is the same as the principle of moving leftwards for gear engagement.

It should be noted that in some applications, only one side of the gear is required to be shifted, and in this case, the locking ring and the friction ring assembly on one end of the gear hub 2 may be omitted on the basis of the above-mentioned embodiment, that is, the locking ring and the friction ring assembly are only arranged on one end of the gear hub 2.

In other embodiments, the annular boss which forms the friction pair with the outer conical surface of the outer friction ring may be partially located in the gear web and partially located in the inner side wall of the engaging ring gear, as shown in fig. 15 (a), or may be located only in the inner side wall of the engaging ring gear, as shown in fig. 15 (b).