CN210889963U - Zero-backlash phase adjuster structure - Google Patents

Abstract

The utility model provides a zero backlash phase regulator structure, including casing, back shaft and driving gear, the back shaft includes center pin, elastic element and eccentric cover, and the center pin forms the swing joint structure of relative rotation with the casing, and the eccentric cover forms the swing joint structure of relative rotation with the driving gear, and elastic element sets up between center pin and eccentric cover, and eccentric cover and center pin form the relative rotation structure; the first outer circle and the second outer circle on the central shaft form an eccentric structure with the eccentricity of e1, the outer circle of the eccentric sleeve on the eccentric sleeve and the inner hole of the eccentric sleeve form an eccentric structure with the eccentricity of e2, the shell and the driving gear form an eccentric structure with the eccentricity of e, and e1+ e2 is larger than e. Because of the variable eccentricity supporting shaft structure, the phase adjuster can adjust the eccentricity of the supporting shaft in time according to the actual internal clearance in the working process so as to eliminate the gear clearance, and the phase adjuster has the outstanding advantages of improving the phase control precision, reducing the working noise and the like.

Description

Zero-backlash phase adjuster structure

Technical Field

The utility model belongs to the technical field of phase regulator structural design and specifically relates to an use motor drive's zero backlash phase regulator structure is related to.

Background

Although conventional phase adjusters, which adjust the phase angle of a camshaft with respect to a crankshaft by oil pressure, have been used in engines, they have slow response speed, poor phase stability, and large influence of oil temperature on operation in actual operation.

The existing electric phase regulator driven by a motor adopts a single-stage planetary reduction principle of a minus mechanism, and has the advantages of small geometric size and the like. The electric phase adjuster comprises a motor and a phase adjuster, wherein the phase adjuster is a planetary reducer, and a gear meshing pair, a sliding friction pair, a rolling friction pair and other matching pairs exist in the phase adjuster. The existing electric phase adjuster has the disadvantages that in the actual use process, the phase control precision is low, the gear abrasion is fast, and the phase adjuster can generate larger abnormal noise during working, and the accumulation of the factors inevitably reduces the service life of the phase adjuster.

SUMMERY OF THE UTILITY MODEL

The to-be-solved technical problem of the utility model is: to the problems existing in the prior art, the zero-backlash phase adjuster structure is provided, the phase control precision is improved, and the working noise is reduced.

The to-be-solved technical problem of the utility model adopts following technical scheme to realize: a zero-backlash phase adjuster structure comprises a shell, a supporting shaft and a driving gear, wherein the supporting shaft comprises a central shaft, an elastic element and an eccentric sleeve, a movable connecting structure capable of rotating relatively is formed between the central shaft and the shell, a movable connecting structure capable of rotating relatively is formed between the eccentric sleeve and the driving gear, the elastic element is arranged between the central shaft and the eccentric sleeve, and a relative rotating structure is formed between the eccentric sleeve and the central shaft; the eccentric structure with the eccentricity of e1 is formed between the first excircle and the second excircle on the central shaft, the eccentric structure with the eccentricity of e2 is formed between the excircle of the eccentric sleeve on the eccentric sleeve and the inner hole of the eccentric sleeve, the eccentric structure with the eccentricity of e is formed between the shell and the driving gear, and e1+ e2 > e.

Preferably, a first connecting pin is formed on the elastic element, an axial hole is formed on the central shaft, and a clamping structure is formed between the first connecting pin and the axial hole.

Preferably, a second connecting pin is formed on the elastic element, a radial notch is formed on the eccentric sleeve, and a clamping structure is formed between the second connecting pin and the radial notch.

Preferably, a movable connecting structure which rotates relatively is formed between the eccentric sleeve and the driving gear through a second bearing.

Preferably, the eccentric sleeve is sleeved on the central shaft.

Preferably, a meshing transmission structure is formed between the driving gear and the driven gear, and a relative rotation structure is formed between the driven gear and the driving wheel.

Preferably, the driving gear on form the external tooth, driven gear on form the internal tooth, driving gear and driven gear between form the internal gearing transmission structure, and the number of external tooth teeth on the driving gear is less than the number of internal tooth teeth on the driven gear.

Preferably, the casing includes drive wheel and apron, apron and drive wheel between form the fixed connection structure of detachable through the screw, and form axial assembly space between apron and the drive wheel.

Preferably, a limit step is formed on the driving wheel, and an axial assembly space is formed between the limit step and the cover plate.

Preferably, a movable connecting structure capable of rotating relatively is formed between the central shaft and the cover plate through a first bearing.

Compared with the prior art, the beneficial effects of the utility model are that: the elastic element is matched with the central shaft and the eccentric sleeve to enable the supporting shaft to be an elastic supporting shaft structure, and meanwhile, the sum of the eccentric distance of the central shaft and the eccentric distance of the eccentric sleeve is larger than the eccentric distance formed between the shell and the driving gear, so that a variable eccentric distance supporting shaft structure is formed And to reduce operating noise.

Drawings

Fig. 1 is a structural cross-sectional view of a zero backlash phase adjuster structure according to the present invention.

Fig. 2 is a schematic diagram of the structure explosion of the zero backlash phase adjuster structure of the present invention.

Fig. 3 is a schematic configuration diagram of the housing in fig. 1.

Fig. 4 is an exploded view illustrating the construction of the support shaft of fig. 1.

Fig. 5 is a three-dimensional structure diagram of the central shaft in fig. 4.

Fig. 6 is a cross-sectional view of the central shaft shown in fig. 5.

Fig. 7 is a three-dimensional structure diagram of the eccentric sleeve of fig. 4.

Fig. 8 is a sectional view of the eccentric sleeve shown in fig. 7.

Fig. 9 is a graph of the relationship between the torsion angle of the elastic element and the peak torque of the camshaft.

Part label name in the figure: 1-motor, 2-motor shaft, 3-drive wheel, 4-drive gear, 5-driven gear, 6-central shaft, 7-elastic element, 8-eccentric sleeve, 9-connecting plate, 10-first bearing, 11-cover plate, 12-screw, 13-bolt, 14-housing axis, 15-camshaft, 16-second bearing, 17-drive gear axis, 31-limit step, 61-axial hole, 62-first excircle, 63-second excircle, 71-first connecting pin, 72-second connecting pin, 81-radial gap, 82-eccentric sleeve excircle, 83-eccentric sleeve inner hole.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more clearly understood, the present invention will be described in detail with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

The zero-backlash phase adjuster structure shown in fig. 1 and 2 mainly comprises a shell, a support shaft, a driving gear 4, a driven gear 5 and a connecting plate 9, wherein the shell is of a hollow cavity structure, preferably adopts the hollow cavity structure shown in fig. 3, and specifically comprises a driving wheel 3 and a cover plate 11, the cover plate 11 and the driving wheel 3 form a detachable fixed connecting structure through a screw 12, and an axial assembly space is formed between the cover plate 11 and the driving wheel 3. The structure of the supporting shaft is shown in fig. 4, and comprises a central shaft 6, an elastic element 7 and an eccentric sleeve 8, wherein the elastic element 7 is arranged between the central shaft 6 and the eccentric sleeve 8, and a relative rotation structure is formed between the eccentric sleeve 8 and the central shaft 6. Specifically, a movable connection structure capable of rotating relatively is formed between the central shaft 6 and the cover plate 11 through a first bearing 10, and a movable connection structure capable of rotating relatively is formed between the eccentric sleeve 8 and the driving gear 4 through a second bearing 16, so that the support shaft and the housing and the driving gear 4 form a movable connection structure capable of rotating relatively respectively.

As shown in fig. 5 and 6, an eccentric structure with an eccentricity e1 is formed between the first outer circle 62 and the second outer circle 63 on the central shaft 6; as shown in fig. 7 and 8, an eccentric structure with an eccentricity e2 is formed between the eccentric sleeve outer circle 82 and the eccentric sleeve inner hole 83 on the eccentric sleeve 8, the housing axis 14 of the housing is arranged in parallel with respect to the driving gear axis 17 of the driving gear 4, that is, an eccentric structure with an eccentricity e is also formed between the housing axis 14 and the driving gear axis 17, as shown in fig. 1, and the sum of the eccentricity e1 of the central shaft 6 and the eccentricity e2 of the eccentric sleeve 8 is greater than the eccentricity e between the housing and the driving gear 4.

In order to ensure the operational reliability of the elastic element 7, generally, a first connection pin 71 and a second connection pin 72 are respectively formed on the elastic element 7, as shown in fig. 4; an axial hole 61 is formed on the central shaft 6, as shown in fig. 5 and 6; the eccentric sleeve 8 is formed with a radial notch 81, as shown in fig. 7. The first connecting pin 71 and the axial hole 61 form a clamping structure, the second connecting pin 72 and the radial gap 81 form a clamping structure, so that the central shaft 6 and the eccentric sleeve 8 are connected through the elastic element 7 to form an elastic supporting shaft structure, the eccentric sleeve 8 is sleeved on the central shaft 6, at the moment, the supporting shaft radially and eccentrically supports the driving gear 4, and the eccentric sleeve 8 can rotate relative to the central shaft 6 and can be reset through the elastic element 7.

Driving gear 4, driven gear 5, connecting plate 9 and back shaft all be located the cavity intracavity portion of casing, and connecting plate 9 is located between apron 11 and the driving gear 4 to transmit the rotary motion of casing for driving gear 4 through connecting plate 9. Driving gear 4 and driven gear 5 between form meshing transmission structure, and the number of teeth on the driving gear 4 is less than the number of teeth on the driven gear 5, driven gear 5 and camshaft 15 between form fixed connection structure through bolt 13 to make camshaft 15 and driven gear 5 synchronous revolution. Generally, as shown in fig. 3, a limit step 31 is formed on the driving wheel 3, and an axial assembly space is formed between the limit step 31 and the cover plate 11 so as to limit the axial displacement of the driven gear 5 and the connecting plate 9.

In order to further reduce the radial dimension of zero backlash phase adjuster structure to improve the operational reliability of zero backlash phase adjuster structure, driving gear 4 on form the external tooth, driven gear 5 on form the internal tooth, driving gear 4 and driven gear 5 between form the internal gearing transmission structure, and the external tooth number of teeth on the driving gear 4 is less than the internal tooth number of teeth on the driven gear 5.

When the zero backlash phase adjuster of the present invention is operated, as shown in fig. 1, a motor 1 drives a support shaft through a motor shaft 2 to rotate the support shaft relative to a housing, the support shaft radially supports a driving gear 4, and a driven gear 5 driven by the driving gear 4 and engaged with the driving gear is driven, the driven gear 5 forms a coaxial rotation structure relative to a driving wheel 3, the driving wheel 3 rotates synchronously with a crankshaft through a chain or a belt, and when the rotation speed of the support shaft is different from that of the driving wheel 3, the phase of a camshaft 15 relative to the crankshaft can be controlled. When the second connection pin 72 of the elastic element 7 rotates by an angle θ relative to the first connection pin 71, as shown in fig. 4, the torque generated by the elastic element 7 is t, and the torque t is smaller than the peak torque Tmax of the camshaft after being decelerated by the phaser, as shown in fig. 9.

When the phase adjuster is normally adjusted, the elastic element 7 is used for transferring kinetic energy output by the motor 1; however, when the phase adjuster collides, the elastic support shaft structure can timely absorb energy generated by the collision, so as to reduce the impact on the phase adjuster and the motor 1, which is beneficial to reducing working noise and prolonging the service life of the phase adjuster and the motor 1. More importantly, the sum of the eccentricity e1 of the central shaft 6 and the eccentricity e2 of the eccentric sleeve 8 is larger than the eccentricity e between the shell and the driving gear 4, so that the phase adjuster can adjust the eccentricity of the supporting shaft in time according to the actual internal clearance to eliminate the gear clearance, thereby achieving the purposes of improving the phase control precision and reducing the working noise.

The above description is only exemplary of the present invention and should not be taken as limiting, and all changes, equivalents, and improvements made within the spirit and principles of the present invention should be understood as being included in the scope of the present invention.

Claims (10)

1. The utility model provides a zero backlash phase regulator structure, includes casing, back shaft and driving gear (4), its characterized in that: the supporting shaft comprises a central shaft (6), an elastic element (7) and an eccentric sleeve (8), a movable connecting structure capable of rotating relatively is formed between the central shaft (6) and the shell, a movable connecting structure capable of rotating relatively is formed between the eccentric sleeve (8) and the driving gear (4), the elastic element (7) is arranged between the central shaft (6) and the eccentric sleeve (8), and a relative rotating structure is formed between the eccentric sleeve (8) and the central shaft (6); form the eccentric structure that the eccentricity is e1 between first excircle (62) on center pin (6) and second excircle (63), form the eccentric structure that the eccentricity is e2 between eccentric cover excircle (82) on eccentric cover (8) and eccentric cover hole (83), casing and driving gear (4) between form the eccentric structure that the eccentricity is e, and e1+ e2 > e.

2. A zero backlash phase adjuster structure according to claim 1, wherein: a first connecting pin (71) is formed on the elastic element (7), an axial hole (61) is formed on the central shaft (6), and a clamping structure is formed between the first connecting pin (71) and the axial hole (61).

3. A zero backlash phase adjuster structure according to claim 1, wherein: the elastic element (7) is provided with a second connecting pin (72), the eccentric sleeve (8) is provided with a radial notch (81), and a clamping structure is formed between the second connecting pin (72) and the radial notch (81).

4. A zero backlash phase adjuster structure according to claim 1, wherein: the eccentric sleeve (8) and the driving gear (4) form a movable connecting structure which rotates relatively through a second bearing (16).

5. A zero backlash phase adjuster structure according to claim 1, wherein: the eccentric sleeve (8) is sleeved on the central shaft (6).

6. A zero backlash phase adjuster structure according to any one of claims 1 to 5, wherein: the driving gear (4) and the driven gear (5) form a meshing transmission structure, and the driven gear (5) and the driving wheel (3) form a relative rotation structure.

7. The zero backlash phase adjuster structure according to claim 6, wherein: driving gear (4) on form the external tooth, driven gear (5) on form the internal tooth, driving gear (4) and driven gear (5) between form the inner gearing transmission structure, and the external tooth number of teeth on driving gear (4) is less than the internal tooth number of teeth on driven gear (5).

8. A zero backlash phase adjuster structure according to any one of claims 1 to 5, wherein: the casing include drive wheel (3) and apron (11), apron (11) and drive wheel (3) between form detachable fixed connection structure through screw (12), and form axial assembly space between apron (11) and drive wheel (3).

9. The zero backlash phase adjuster structure according to claim 8, wherein: the driving wheel (3) is provided with a limiting step (31), and an axial assembly space is formed between the limiting step (31) and the cover plate (11).

10. The zero backlash phase adjuster structure according to claim 8, wherein: the central shaft (6) and the cover plate (11) form a movable connecting structure which rotates relatively through a first bearing (10).

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