JP2536927Y2 - Multiple cone type synchronizer - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a multiple cone type synchronizer.

(Conventional technology) A multi-cone synchronizer such as a double-cone synchronizer and a triple-cone synchronizer is a synchronizer having a large synchronous capacity having a plurality of tapered cone clutches.
A synchronizing device of this type is disclosed in Japanese Patent Application Laid-Open No. 96129 and Japanese Patent Application Laid-Open No. 61-74915.

In this type of synchronizing device, a plurality of synchronizer rings are arranged between a clutch hub and a gear which are mounted on a rotating shaft so as to be relatively rotatable with each other. A plurality of tapered cone clutches are pressed between the spline pieces and are frictionally engaged by sliding of a sleeve spline-fitted to the outer periphery of the clutch hub.

(Problems to be Solved by the Invention) In this type of synchronizing device, it is desirable from the viewpoint of durability that all the tapered cone surfaces constituting each tapered cone clutch are in sliding contact with each other over the entire surface. Due to the above variation, not all of the tapered cone surfaces are in sliding contact with the entire surface, which causes a decrease in durability. Therefore,
An object of the present invention is to enable all the tapered cone surfaces to be in sliding contact with each other over the entire surface.

(Means for Solving the Problems) The present invention relates to a multi-cone type synchronizer of the above-mentioned type, wherein the synchronizer ring includes a synchronizer ring having a tapered cone surface on the inner and outer circumferences. The cone angle on the acute angle side with respect to the axis is set to be larger on the inner peripheral taper cone surface of the synchronizer ring than on the outer peripheral taper cone surface facing the same inner peripheral taper cone surface, and on the outer peripheral taper cone surface of the synchronizer ring facing the same outer peripheral taper cone surface. Set larger than the peripheral taper cone surface, or set smaller than the outer taper cone surface facing the inner taper cone surface on the inner taper cone surface of the synchronizer ring, and the same outer taper cone surface on the outer taper cone surface of the synchronizer ring Is set smaller than the inner peripheral taper cone surface facing the inner surface.

(Operation / Effect of the Invention) In the synchronizer having such a configuration, if the cone angles of the respective tapered cone surfaces are set so as to always satisfy the above-mentioned relationship even in consideration of manufacturing variations, each synchronizer ring exerts a pressing force on the sleeve. Elastically deforms inward and outward of the diameter at the time of frictional engagement, and the angle difference of the cone angle between each tapered cone surface and the tapered cone surface opposed thereto becomes zero. Therefore,
All the tapered cone surfaces are in sliding contact with each other on the entire surface, so that the durability is improved and the occurrence of a synchro failure due to the edge contact and a feeling of two-stepping are prevented.

(Embodiment) Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows a triple-cone synchronizer according to a first embodiment of the present invention. The synchronizer 10 is disposed between a pair of gears 22 and 23 rotatably mounted on the outer periphery of a rotating shaft 21.

The synchronizer 10 includes a pair of synchronization mechanisms 10a and 10b, and the two synchronization mechanisms 10a and 10b are a clutch hub 11, a sleeve 12, a shifting key 13, and a pair of key springs 14.
a, 14b are common components, the first synchro mechanism 10a is a triple cone type synchro mechanism, and the second synchro mechanism 10 is a single cone type synchro mechanism, and are respectively disposed on both sides of the clutch hub 11. ing.
The first and second synchronizing mechanisms 10a and 10b have the first
The present invention is implemented in the synchro mechanism 10a, and the second
Since the synchronization mechanism 10b is a known mechanism, only the first synchronization mechanism 10a will be described below.

The clutch hub 11 constituting the synchronizer 10 is integrally rotatably mounted on the outer periphery of the rotating shaft 21.A sleeve 12 is meshed with an outer spline 11a on the outer periphery by an inner spline 12a. Is slidable in the axial direction. A plurality of notching grooves 11b in the axial direction provided on the outer periphery of the clutch hub 11 are provided with a shifting key 13, and the key 13 is supported by key springs 14a and 14b.
12 are resiliently engaged with the engagement recesses on the inner periphery. On the other hand, a gear spline piece 15 is integrally rotatably mounted on the outer periphery of the boss portion of the gear 22, and the outer ring 16, the middle ring 17, and the inner ring 18 constituting the synchronizer ring are superimposed on each other. It is arranged between the clutch hub 11 and the gear spline piece 15.

The outer ring 16 is, as shown in FIGS. 1 and 2,
An outer spline 16a is provided on the outer circumference, a plurality of first connection grooves 16b are provided, and an inner circumference is provided with a tapered cone surface 16c, and an inward flange 16d is provided with a plurality of second connection grooves 16e. In the outer ring 16, the outer spline 16a is located on the same line as the outer spline 11a of the clutch hub 11, and one end of each shifting key 13 faces each of the first connecting grooves 16b. One end of the key 13 is movable in the axial direction and the circumferential direction by a predetermined amount with respect to the outer ring 16, and in this state, the outer ring 16 is connected to the clutch hub 11 via the shifting key 13.

The middle ring 17 has a tapered cone surface 17 on the outer and inner circumferences.
a, 17b and a plurality of connecting projections 17c,
A first tapered cone clutch is constituted by the tapered cone surface 16c of the ring 16 located on the inner periphery of the outer ring 16, and each projection 17c is provided on the outer periphery of the gear spline piece 15 as shown in FIG. It faces the connecting groove 15a.
A predetermined gap is secured in the circumferential direction between the projection 17c and the connection groove 15a, and the middle ring 17 and the gear spline piece 15 can be relatively rotated slightly larger than 1/2 of each pitch of the spline 12a in the sleeve 12. It is connected to. The outer spline 15b of the gear spline piece 15 is located on the same line as the splines 11a and 16a of the clutch hub 11 and the outer ring 16.

Inner ring 18 has tapered cone surface 18 on outer and inner circumferences
a, 18b and a plurality of connecting projections 18c,
A second taper cone clutch is constituted by the middle ring 17 and the taper cone surface 17b of the middle ring 17 located between the gear spline piece 15 and the gear spline piece.
The third tapered cone clutch is constituted by the 15 tapered cone surfaces 15c. Also, each protrusion 18 of the inner ring 18
c is the second connecting groove 1 of the outer ring 16 as shown in FIG.
We are facing 6e. A predetermined gap is secured in the circumferential direction between the projection 18c and the second connection groove 16e, and the relative rotation between the outer ring 16 and the inner ring 18 is slightly larger than 1/2 of each pitch of the spline 12a in the sleeve 12. It is connected as possible.

Thus, the middle ring 17 and the inner ring 18 of the synchronizer ring of the first synchronization mechanism 10a have tapered cone surfaces (17b, 17a) and (18b, 18a) on the inner and outer circumferences.
The rotation shaft 21 on each tapered cone surface of the outer ring 16, the middle ring 17, the inner ring 18, and the gear spline piece 15 constituting the synchronizer ring
The relationship between the cone angle on the acute angle side with respect to the axis (hereinafter, this cone angle is simply referred to as the cone angle) is as shown in FIG. In the drawing, the relationship between the cone angles of the respective tapered cone surfaces is exaggerated for easy understanding.
Two of the rings 16 to 18, the middle ring 17 and the inner ring 18, each have a tapered cone surface on the inner and outer circumferences, and an outer tapered cone surface 17 a of the middle ring 17.
₁ cone angle theta, the cone angle of the inner peripheral taper cone surface 17b and theta _2, and the cone angle of the outer circumferential taper cone surface 18a of the inner ring 18 theta _3, when the cone angle of the inner circumferential tapered cone surface 18b and theta _4, relationship between the cone angle of the outer peripheral taper cone surface 15c of the cone angle theta ₅ and the gear splines piece 15 of the inner peripheral taper cone surface 16c of the outer ring 16 are set as follows. However, the cone angle difference between the taper cone surfaces facing each other is set as small as possible.

θ ₁ <θ ₅ , θ ₂ <θ ₃ , θ ₄ > θ ₆ Synchronizing device 1 including the first synchro mechanism 10a having such a configuration
At 0, when the sleeve 12 is slid in the first right direction in the drawing, the shifting key 13 first moves in the axial direction integrally with the sleeve 12 to abut the outer ring 16, and the ring 16 is moved in the axial direction. Press. The pressing force in the axial direction is transmitted to the middle ring 17, the inner ring 18, and the gear spline piece 15, and the respective tapered cone clutches are frictionally engaged. For this reason, a friction torque is generated in each tapered cone clutch, and the rings 16 to 18 rotate with each other and are indexed in the circumferential direction. When the sleeve 12 further slides to the right in the figure in this state, the chamfer of the spline 12a of the sleeve 12 comes into contact with the chamfer of the spline 16a of the outer ring 16, and synchronization is started. Is pressed and slid in the axial direction while meshing with the spline 16a, and further, the gear spline piece 15 is pushed and meshed with the spline 15b. Thus, the rotating shaft 21 and the gear 22 are connected via the clutch hub 11 and the sleeve 12 so as to be able to transmit torque.

By the way, in the synchronous device of this type, when the chamfer of the spline 12a of the sleeve 12 is in contact with the chamfer of the spline 15b of the gear spline piece 15, a biting phenomenon occurs in each taper cone clutch.
A shift lock state occurs and the shift operation cannot be performed.
However, in the synchronizing device 10 of the present embodiment, the relative rotation between the outer ring 16 and the inner ring 18 and between the middle ring 17 and the gear spline piece 15 is allowed to be more than 1/2 of each pitch of the spline 12a in the sleeve 12. It has a configuration. Therefore, even if a biting phenomenon occurs in each taper cone clutch as shown below, each ring 16 to 1
8. The relative rotation described above occurs between the gear spline pieces 15, and the occurrence of the shift lock state is prevented, so that a smooth shift operation is achieved.

(1) When a biting phenomenon occurs in the first taper cone clutch between the outer ring 16 and the middle ring 17, the middle ring 17 and the gear spline piece 15 rotate relative to each other.

(2) If a biting phenomenon occurs in the second taper cone clutch between the middle ring 17 and the inner ring 18, the gap between the outer ring 16 and the inner ring 18 and / or the gap between the middle ring 17 and the gear spline piece 15 are relatively large. Rotate.

(3) When a biting phenomenon occurs in the third taper cone clutch between the inner ring 18 and the gear spline piece 15, the outer ring 16 and the inner ring 18 rotate relative to each other.

(4) If the first and third taper cone clutches simultaneously bite between the outer ring 16 and the middle ring 17 and between the inner ring 18 and the gear spline piece 18, the outer ring 16 and the inner ring 18 And, the middle ring 17 and the gear spline piece 15 rotate relative to each other.

(5) If the first and second taper cone clutches between the outer ring 16 and the middle ring 17 and between the middle ring 17 and the inner ring 18 simultaneously bite, the middle ring 17 and the gear spline piece may be used. Relative rotation between 15

(6) If the second and third taper cone clutches simultaneously bite between the middle ring 17 and the inner ring 18 and between the inner ring 18 and the gear spline piece 15, the gap between the outer ring 16 and the inner ring 18. Rotate relative to each other. Thus, in the synchronizer 10, each ring 16
4, the relationship between the cone angles θ _{1 to} θ ₆ of the respective tapered cone surfaces of the gear spline piece 15 is set to θ ₁ <θ ₅ , θ ₂ <θ ₃ , θ ₄ > θ ₆ as clearly shown in FIG. Have been. For this reason, the outer ring 16 pressed by the sleeve 12 pushes the rear end side of the middle ring 17 forward and radially inward to the rear end side in the moving direction, and accordingly the middle ring 17 is inner ring at the front end side. Press the front end side of 18 forward and radially inward. As a result, the rings 17 and 18 are elastically deformed, and the cone angle differences θ ₅ −θ ₁ , θ ₃ −θ ₂ , θ ₄ −θ _{6 of the} respective tapered cone surfaces are obtained.
Is zero, and each tapered cone surface is in sliding contact with the entire surface.

FIG. 5 shows a modification in which the relationship between the cone angles of the respective tapered cone surfaces in the above embodiment is changed. The cone angles θ _{1 to} θ ₆ of the respective tapered cone surfaces in each of the rings 16 to 18 and the gear spline piece 15 in the modification.
Are set as θ ₁ > θ ₅ , θ ₂ > θ ₃ , and θ ₄ <θ ₆ . For this reason, the outer ring 16 pressed by the sleeve 12 presses the front end side of the middle ring 17 forward and radially inward at the front end side in the movement direction, and accordingly the middle ring 17 is inner ring at the rear end side. 18 Press the rear end side forward and radially inward. As a result, each of the rings 17 and 18 is elastically deformed and the cone angle difference θ ₁ −θ ₅ , θ ₂ −θ ₃ , θ
₆ −θ ₄ becomes zero.

FIG. 6 shows a double cone type synchronizer according to a second embodiment of the present invention. The synchronizing device 30 includes a pair of synchronization mechanisms 30a and 30b, and the two synchronization mechanisms 30a and 30b are used.
0b is clutch hub 31, sleeve 32, shifting key 3
3, the pair of key springs 34a and 34b are common components, the first synchronization mechanism 30a is configured as a double cone type synchronization mechanism, and the second synchronization mechanism 30b is configured as a single cone type synchronization mechanism. It is arranged on each side.

In the first synchronizing mechanism 30a, an outer ring 36 and an inner ring 37 constituting a synchronizer ring are disposed between a piece portion 35b rotatably fitted to the clutch hub 31 and the gear spline piece 35, and the outer ring 36 is shifted. A predetermined amount of relative rotation is connected to the clutch hub 31 via a key 33, and an inner ring 37 is connected to the gear spline piece 35 so as to be relatively rotatable by a predetermined amount, and a piece portion 35b of the piece 35 is connected to an outer ring 36. Are rotatably connected to each other by a predetermined amount. These rings 3
6, 37 and the gear spline piece 35, the inner peripheral taper cone surface 36a of the outer ring 36 and the inner ring 37
A first taper cone clutch is formed between the outer peripheral taper cone surfaces 37a of the gear spline piece 35 and the inner peripheral taper cone surface 37b of the inner ring 37.
A second taper cone clutch is formed between 5a and operates in substantially the same manner as the above-mentioned triple cone type synchro mechanism except that two taper cone clutches are frictionally engaged.

The inner ring 37 of the first synchronizing mechanism 30a has an outer tapered cone surface 37a and an inner tapered cone surface 37b. In the inner ring 37, as shown in FIG. The angle θ ₇ is in a relationship of θ ₇ <θ ₉ with the cone angle θ ₉ of the inner peripheral taper cone surface 36a of the outer ring 36, and the cone angle θ ₈ of the inner peripheral taper cone surface 37b is the outer taper cone of the gear spline piece 35. The relationship of θ ₈ <θ ₁₀ is set with respect to the cone angle θ ₁₀ of the surface 35a. Accordingly, the inner ring 37 is elastically deformed in the radial direction by the pressing force of the outer ring 36, so that each cone angle difference becomes zero, and each tapered cone surface comes into sliding contact with the entire surface. The cone angles of the respective tapered cone surfaces are shown in FIG. 8, that is, θ ₇ > θ ₉ , θ ₈ >
It is set in the relationship of theta ₁₀ the same effect.

[Brief description of the drawings]

FIG. 1 is a sectional view of a synchronizer according to a first embodiment of the present invention, FIG. 2 is a front view of an outer ring, FIG. 3 is a front view of a gear spline piece, and FIG. 4 is a cone angle of each tapered cone surface. 5 is a sectional view corresponding to FIG. 4 showing a modification of the cone angle, FIG. 6 is a sectional view of the synchronization device according to the second embodiment, and FIG. 7 is each tapered cone. FIG. 8 is a cross-sectional view corresponding to FIG. 7 showing a modified example of the cone angle, showing a principal part enlarged cross-sectional view showing the cone angle of the surface. Description of reference numerals 10, 30,... Synchronizer, 10a, 30a.
11, 31 ... clutch hub, 12, 32 ... sleeve, 15, 35
…… Gear spline piece, 15c, 35a …… Taper cone surface, 16, 36 …… Outer ring, 16c, 36a …… Taper cone surface, 17 …… Middle ring, 17a, 17b …… Taper cone surface, 18, 37 …… Inner Rings, 18a, 18b, 37a, 37b ...
Tapered cone surface, 21 ... rotating shaft, 22, 23 ... gear.

Claims (1)

(57) [Scope of request for utility model registration] A plurality of synchronizer rings are disposed between a clutch hub and a gear mounted on a rotating shaft so as to be relatively rotatable with each other, and between each of the synchronizer rings and between the synchronizer ring and a spline piece of the gear. In a multi-cone type synchronous device comprising a plurality of tapered cone clutches that are pressed by friction of a sleeve spline-fitted to the outer periphery of the clutch hub and frictionally engaged,
Of the synchronizer rings, the cone angle on the acute angle side with respect to the axis of the rotating shaft in each taper cone surface of the synchronizer ring having a taper cone surface on the inner periphery and the outer periphery is the same inner peripheral taper cone surface on the inner peripheral taper cone surface of the synchronizer ring. The outer peripheral taper cone surface of the synchronizer ring is set to be larger than the inner peripheral taper cone surface of the synchronizer ring, and the inner peripheral taper cone surface of the synchronizer ring is set to be larger than the inner peripheral taper cone surface. A multi-cone type synchronous device characterized in that the outer peripheral taper cone surface of the synchronizer ring is set smaller than the inner peripheral taper cone surface facing the outer peripheral taper cone surface. .