JPS6283560A - Gear train damper device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a damper device that prevents resonance from occurring in a gear train that drives something that experiences severe torque fluctuations, such as a camshaft of an internal combustion engine.

(Prior art and its problems) Generally, in a gear train that drives something with large torque fluctuations such as a camshaft, gear backlash,
Due to the backlash of the bearing, or the complex relationship between the rigidity and inertial mass of each component, resonance may occur at certain rotations, and when this resonance occurs, the drive! Increased PII noise;
In some cases, it even led to destruction.

For this reason, a damper device for the gear train is required to prevent the occurrence of resonance, but conventional damper devices of this type include a single rotating shaft, a main gear fitted to the rotating shaft so as to be able to freely rotate, and the rotating shaft. A plurality of coil springs, whose axes are oriented approximately perpendicular to the radial direction of the gear, are provided at equal intervals in the circumferential direction between the main gear and the driven gear, which is a gear fitted so as to be relatively rotatable. Some gears were constructed in such a way that the force of this spring biased the main gear and the sub gear so as to press them in relative directions.

However, in this conventional device, the magnitude of the damper effect is determined only by the spring load, so if the damper effect is to be increased, the spring diameter must be increased, and the spring may become sagging over time, weakening the damper effect. There are cases.

(Object of the present invention) The present invention was made in view of the above circumstances, and it is possible to obtain a high damper effect without increasing the diameter of the spring, and also to obtain a stable damper effect over a long period of time. To provide a gear train device which is capable of suppressing the occurrence of resonance using independent damper mechanisms when torque is applied in the positive and negative directions with respect to the rotational direction of a shaft, thereby improving the damper function. purpose.
- (Means for solving the problem) In order to achieve the above object, at least one of the gears of a gear train having a driving gear and a driven gear that mesh with each other is rotated integrally with a rotating shaft. The main gear is supported so that it can be rotated, and the sub-gear is supported coaxially with the main gear so that it can rotate relative to the main gear. A positive torque side damper mechanism that prevents the occurrence of resonance when torque is applied in the direction of rotation, and a negative torque side damper mechanism that prevents the occurrence of resonance when torque is applied in the negative direction with respect to the iTI rotation axis rotation direction. side damper mechanisms, and the elastic force of these positive and negative torque side damper mechanisms is applied by hydraulic pressure along a direction perpendicular to the radial direction of the gear, and hydraulic pressure is supplied to the positive and negative torque side damper mechanisms. A supply path is provided at the axis of the rotating shaft, and a check valve for the positive torque side damper mechanism and a check valve for the negative torque side damper mechanism are provided in this supply path, respectively.

(Function) The magnitude of the damper effect is determined by adjusting the hydraulic pressure, which is the source of the elastic force of the damper mechanism. A damper mechanism on the positive torque side suppresses the occurrence of resonance, and a damper mechanism on the negative torque side suppresses resonance when torque acts in the negative direction with respect to the rotation direction of the rotating shaft. This is to eliminate the influence.

(Example) Hereinafter, one embodiment of the present invention will be described based on the drawings.

FIG. 1 is a partially cutaway front view of gear 1 to lane for driving a camshaft equipped with a damper device according to the present invention, and FIG.
The figures are the same side views, and 1 in both figures is an engine body, and this engine body 1 includes a V-shaped cylinder block 3 having a pair of left and right cylinders 2 at the front and rear, a crankcase 4 below the cylinder block 3, and a crankcase 4 below the cylinder block 3. It is composed of a pair of upper front and rear cylinder heads 5 and respective head covers 6 above the cylinder heads.

The engine main body 1 is provided with camshafts (rotating shafts) 7 which are located in each head cover 6 on the upper part and are a pair of front and rear rotating shafts, and also includes a crankshaft 8 in the crankcase 4, which is a crankshaft. Drive gear 9 of shaft 8 and driven gear 1 of each of the cam shirts 1-7
At least two upper and lower idle gears 11a mesh with each other.

They are connected to each other via a gear train 11 consisting of 11b. The rotation of the crankshaft 8 drives the camshaft 7 through one rotation through a gear train 12 consisting of a drive gear 9, a gear train 11, and a driven gear 10. A positive torque side damper mechanism A is provided between the camshaft 7 and the driven gear 10 to prevent resonance from occurring when torque is applied in the positive direction with respect to the rotational direction of the camshaft 7.

That is, the flange member 13 is fixed to the large diameter portion 7a of the camshaft 7. A cylinder member 14 is provided on the upper part of the flange member 13, with its axis oriented perpendicularly to the radial direction of the driven gear 10, as shown in FIGS. 3, 5, and 6. This cylinder member 14 has one end surface open and the other end surface closed with a cap 15, and a plunger 16 is provided inside the cylinder member 14 so as to be freely retractable from the one end surface opening.
This plunger 16 is fitted with a coil spring 17.
is pressed in the protruding direction.

As shown in FIGS. 3 and 4, the cylinder member 14 is fitted onto the large diameter portion 7a of the camshaft 7 in an overlapping state so that it can rotate relatively in the circumferential direction and cannot move in the axial direction. The plunger 16 is fitted into a fitting hole LOa, 1.8a, which is formed in correspondence with the driven gear 10 and the Serashi gear 18, respectively, and the tip surface of the plunger 16 is shaped like an arc at one end edge of the fitting hole 10a of the driven gear 10. It abuts and engages with the engagement surface 10b.

Inside the cylinder member 14 are a communication hole 7b bored in the flange member 13 and an axial center hole 7C of the camshaft 7.
Check valve 1 for positive torque side damper mechanism installed at the inner end of
9 and communicates with the shaft center hole 7C.

The check valve 19 includes a casing 19c having an inlet 19a and an outlet 1.9b, a ball valve body 19d that opens and closes the inlet L9a, and a spring 19e that presses the ball valve body 19d in the valve closing direction. The outlet 19b thereof communicates with the communication hole 7b of the camshaft 7.

The outer end surface of the axial hole 7C of the camshaft 7 is covered with a cap 2.
Blocked by 0. The axial hole 7c of the camshaft 7 has a through hole 21 bored in the peripheral wall on one end side of the camshaft 7 along the radial direction, and an annular groove 22 formed in the outer peripheral surface of the camshaft through which the through hole 21 opens. It communicates with the discharge 1 of a hydraulic pump (not shown) via a passage 23a provided in the bearing part 23.・ A torque is applied in a negative direction with respect to the rotational direction of the camshaft 7 at a position located between the driven gear] O and the servo gear 18 and 180 degrees out of phase with the positive torque side damper mechanism A in the circumferential direction. A negative torque side damper mechanism A' is provided to prevent resonance from occurring when the torque is applied. This negative torque side damper mechanism A' has the same configuration as the positive torque side damper mechanism A, but the direction is opposite, and the component parts corresponding to each component of the positive torque side damper mechanism A in the negative torque side damper mechanism A' are displayed by adding a dash to the number of each component of the positive torque side damper mechanism A. The axial center hole 7C of the camshaft 7 has a check valve 1 on the negative torque side damper mechanism A' side in line with the check valve 19 on the positive torque side damper mechanism A side.
9' is the provision.

This negative torque side check valve 19' includes a casing 19'c having an inlet 19'a and an outlet 19'b, and an inlet 19'.
It consists of a ball valve body 19'd that opens and closes the ball valve body 19'a, and a spring 19'e that presses the ball valve body 19'd in the valve closing direction, and the outlet 19'b of the ball valve body 19'b is connected to the communication hole 7 of the camshaft 7.
' Connected to b.

The positive torque side damper mechanism A and the negative torque side damper mechanism A
' Two damper springs 28a are located on one side between the damper springs 28a,
28b, one damper spring 28c and one spring spring are respectively provided on the other side. Damper spring 28
a to 28c as shown in FIGS. 3, 4 and 7,
The driven gear IO and the flange member 13 are fitted into fitting holes 10e and 13c provided in correspondence with each other.

The damper springs 28a to 28c have their axes perpendicular to the radial direction of the driven gear 10, and have one end attached to one spring seat 30 and the other end attached to the other spring seat. 31, respectively. These spring seats 30, 31 are disposed over both the driven gear 10 and the flange member 13, respectively.

Further, as shown in FIGS. 3, 4, and 8, the activation spring 29 can be fitted into fitting holes 10f and 18d provided in the driven gear 10 and the activation gear 18 so as to correspond to each other. be. The activation spring 29 is arranged with its axis perpendicular to the radial direction of the driven gear 10, and its one end abuts one spring seat 32 and the other end abuts the other spring seat 33. It is locked.

These spring seats 32, 33 are respectively connected to the driven gear 1
0 and Serasigya 18.

Next, the operation of the damper device for a gear train according to the present invention having the above structure will be explained.

The passage 23a, the annular groove 22, the through hole 21, the axial hole 7c,
Hydraulic pressure is introduced into the cylinder member 14 through the check valve 19 and the communication holes 7b, 7c, and 13a in sequence. Therefore, the plunger 16 of the positive torque side damper mechanism A is connected to the coil spring 17.
The spring force and hydraulic pressure force the driven gear 10 to be compressed in a direction perpendicular to the radial direction of the driven gear 10.

Also, in the negative torque side damper mechanism A', there are a passage, an annular groove, a through hole (all not shown), an axial hole 7c, a check valve 19', and communication holes 7'b and 7'c.

introduced into the cylinder member 14' via 13'a,
Plunger 16' is biased in a direction perpendicular to the radial direction of driven gear 10 by the spring force of coil spring 17' and hydraulic pressure.

Furthermore, the damper springs 28a to 28c and the spring spring 29 act in a direction perpendicular to the radial direction of the driven gear 10.

Therefore, the driven gear 10 and the flange member 13, that is, the camshaft 7, are connected to the positive and negative torque side damper mechanisms A and A'.
The driven gear 10 and the activation gear 18 are urged to rotate in the relative direction by the elastic force of the damper springs 28a to 28c.

In this state, when the camshaft 7 rotates via the gear train 12 and torque acts in a positive direction with respect to the rotation direction, in the positive torque side damper mechanism A, the spring force of the coil spring 17 and the hydraulic pressure are Two forces act on the damper springs 28a to 28c, and only the spring force acts on the damper springs 28a to 28c to obtain a damper effect, and even if temporary resonance occurs, the resonance is quickly reduced by the damper effect.

Furthermore, when torque acts in a negative direction with respect to the rotational direction of the camshaft 7, the spring force of the coil spring 17' and the hydraulic pressure act on the negative torque side damper mechanism A', causing the damper springs 28a to 28c to act on the damper mechanism A'. Together with the spring force, a damper effect is obtained, quickly reducing resonance.

Further, the spring force of the spring 29 applies the spring force to the driven gear 10, and the backlash between the driven gear 1o and the idle gear llb meshing therewith is reduced.

Note that the present invention is not limited to the gear train that drives the camshaft of the internal combustion engine described above, but is widely applicable to gear trains that drive engines with severe torque fluctuations.

(Effects of the Invention) As detailed above, the present invention provides a gear train having a driving gear and a driven gear that mesh with each other, at least one of the gears being supported so as to be integrally rotatable around a single rotating shaft. The main gear is composed of a main gear and a sub-gear coaxially supported to be relatively rotatable with the main gear, and a torque is applied between the main gear and the sub-gear and the rotating shaft in a positive direction with respect to the rotational direction of the rotating shaft. There is a positive torque (ill damper mechanism) that prevents the occurrence of resonance when the damper mechanism is applied, and a negative torque side that prevents the occurrence of resonance when the torque acts in the negative direction with respect to the rotational direction of the rotating shaft. A damper mechanism is provided, and elastic force of the positive and negative torque side damper mechanisms is applied by hydraulic pressure along a direction perpendicular to the radial direction of the gear, and hydraulic pressure is supplied to the positive and negative torque side damper mechanisms. The present invention is characterized in that a supply passage is carefully provided on the rotating shaft, and a check valve for the positive torque side damper mechanism and a check valve for the negative torque side damper mechanism are respectively provided in the supply passage.

Therefore, the magnitude of the damper effect can be determined by adjusting the hydraulic pressure, which is the source of the elastic force of the damper mechanism, so the damper effect can be increased without increasing the diameter of the spring, and the elastic force can be adjusted by adjusting the hydraulic pressure. Since the damper effect is obtained in the following manner, it is possible to obtain a stable damper effect over a long period of time.

In particular, the positive torque side damper mechanism suppresses the occurrence of resonance when torque is applied in the positive direction with respect to the rotational direction of the rotating shaft, and the resonance is suppressed when torque is applied in the negative direction with respect to the rotational direction of the rotating shaft. The generation of resonance can be suppressed by the negative torque side damper mechanism, and the damper function can be improved.

Moreover, since the check valves for the positive and negative torque side damper mechanisms are provided at the axis of the rotating shaft, it is possible to eliminate the influence of centrifugal force while having two check valves.

[Brief explanation of drawings]

The drawings show one embodiment of the present invention; FIG. 1 is a partially cutaway front view of a camshaft driving gear train equipped with the damper device of the present invention, FIG. 2 is a side view of the same, and FIG. 3 is a portion of the damper device. 4 is a sectional view taken along line IV-IV in FIG. 3, FIG. 5 is a side view of the flange member, FIG. 6 is a side view of the same, and FIG. 8 is a cross-sectional view taken along the line ■--■ in FIG. 4. FIG. A, A'...damper mechanism, 7...camshaft, 1
0...Driven gear. 85th Melody Map

Claims (1)

[Claims] At least one of the gears of a gear train having a drive side gear and a driven side gear that mesh with each other is supported by a main gear rotatably integrally with a rotating shaft, and a main gear supported coaxially with the main gear so as to be relatively rotatable. a positive torque side damper mechanism that prevents resonance from occurring when torque is applied in a positive direction with respect to the rotational direction of the rotational shaft between the main gear and the subgear and the rotational shaft; and a negative torque side damper mechanism that prevents resonance from occurring when torque acts in the negative direction with respect to the rotational direction of the rotating shaft, and the elastic force of these positive and negative torque side damper mechanisms is controlled by hydraulic pressure. is applied along a direction perpendicular to the radial direction of the gear, and
A supply path for supplying hydraulic pressure to the negative torque side damper mechanism is provided at the axis of the rotating shaft, and a check valve for the positive torque side damper mechanism and a check valve for the negative torque side damper mechanism are provided in this supply path, respectively. A gear train damper device characterized by: