JP2002266952A - Driving transmission mechanism device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a driving transmission mechanism device capable of inhibiting a transmission of a load caused by a disturbance torque at a gear engagement frequency to a driven shaft, simply adjusting a rotation rigidity of a fastening part corresponding to the gear engagement frequency and simply setting a switching of the rotation rigidity required at the time of activation and at the time of constant speed. SOLUTION: Only a rotation direction is elastically deformed at the fastening part 3 of the driven shaft 2 and a driven gear 1 and the rotation rigidity K2 is adjusted so as to satisfy a relationship formula: fp>fz (provided that fz=(1/2π×(K2/J2)<1/2> ×2<1/2> ) when the rotation rigidity is defined as K2, an inertia moment of the driven shaft 2 is defined as J2 and the gear engagement frequency at the time of operation is defined as fp. The rotation rigidity K2 is adjusted by changing any one of a mounting position radius r of a pin-receiving part, a thickness t in the rotation direction, a pin receiving width b, an axial contact height L and a pin diameter dp. The pin-receiving part 4 is set such that it varies the contact points with a driven shaft pin 5 corresponding to a load torque.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive transmission mechanism device comprising a drive shaft, a driven shaft and a transmission mechanism, and more particularly to a drive transmission mechanism device emphasizing constant speed of a driven shaft. is there.

[0002]

2. Description of the Related Art Conventionally, there are roughly two methods for maintaining the rotation of a driven shaft at a constant speed in a drive transmission mechanism device. One is a method called an inertia effect that increases the moment of inertia (J) of the driven shaft so that it does not respond to disturbance torque at the gear meshing frequency or fluctuation torque of the motor. This is a method of intercepting vibration by passing a member through a transmission mechanism. In either method, the natural frequency f (= 1 / 2π × √ (K / J)) is reduced. The former increases the moment of inertia (J), and the latter decreases the rotational rigidity (K) of the elastic member. How to However, the method of increasing the moment of inertia (J) requires an increase in driving force, and is not suitable for a small-sized and low-cost device. Therefore, in order to solve this problem, Japanese Patent Application Laid-Open Nos. 6-249321 and 6-294.
No. 453 and JP-A-7-325445 propose a method of reducing the rotational rigidity (K).

[0003] JP-A-6-249321 and JP-A-6-294453 propose a method of incorporating an elastic member in a transmission mechanism such as a gear to absorb vibration in the rotational direction. However, by incorporating an elastic member into a transmission mechanism such as a gear, rotational rigidity other than the rotational direction is also reduced. For example, when a thrust force is applied to a gear, which is a transmission mechanism, such as a helical gear, the elastic member is deformed in a direction in which it escapes, and normal meshing cannot be performed. An increase in vibration is predicted by this tooth skew phenomenon. Further, when the elastic member is incorporated in the radial direction, there is a concern about an axial center error between the center axis and the driven shaft center viewed from the gear teeth, that is, a so-called coaxiality of the gear teeth.

Japanese Patent Application Laid-Open No. Hei 7-325445 proposes a method in which an elastic member is formed as an independent component instead of being integrated, assembled, and absorbs vibration. According to this technique, the coaxiality can be cleared because the components are assembled independently, but there is a problem of an increase in cost due to an increase in the number of parts.

[0005]

SUMMARY OF THE INVENTION In view of the above problems, in the present invention according to the first aspect, the coaxiality of the gear teeth is maintained with high precision without adding an elastic part or the like, and the gear meshing frequency is reduced. It is an object of the present invention to provide a drive transmission mechanism device that does not transmit the disturbance torque to the driven side. Another object of the present invention is to provide a drive transmission mechanism device that can easily adjust the rotational rigidity of a fastening portion that needs to be set in accordance with the gear meshing frequency. A further object of the present invention is to provide a drive transmission mechanism device capable of performing a quick operation at the time of acceleration at the time of starting. A further object of the present invention is to provide a drive transmission mechanism device which can easily set the required switching of the rotational rigidity at the time of startup and at a constant speed.

[0006]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention according to claim 1 provides a drive shaft connected to a drive source such as a motor, a driven shaft for performing work, and a drive shaft driven by a driven shaft. In a drive transmission mechanism device having a transmission mechanism for transmitting a force, it is assumed that only the rotational direction is elastically deformed at a fastening portion between the driven shaft and the driven gear, the rotational rigidity is K2, the inertia moment of the driven shaft is J2, and the operation is J2. The drive transmission mechanism device is characterized in that the driven gear engaging portion rotational rigidity K2 is adjusted so as to satisfy the following relational expression as the gear meshing frequency fp at the time. fp> fz where fz = (1 / 2π × √ (K2 / J2)) × √2

According to a second aspect of the present invention, the gear of the transmission mechanism is formed of resin, and the radius of the mounting position of the pin receiving portion is changed at the fastening portion formed by the pin receiving portion of the gear corresponding to the driven shaft pin. The drive transmission mechanism device according to claim 1, wherein the rotational rigidity is adjusted by (1). According to the third aspect of the present invention, the gear of the transmission mechanism is formed of a resin, and the driven shaft pin is a fastening portion comprising a pin receiving portion of the gear corresponding to the driven shaft pin.
The drive transmission mechanism device according to claim 1, wherein the rotational rigidity is adjusted by changing the thickness of the pin receiving portion in the rotational direction. According to a fourth aspect of the present invention, the gear of the transmission mechanism is formed of resin, and the pin receiving portion of the pin receiving portion in the radial direction is changed at the fastening portion including the driven shaft pin and the corresponding pin receiving portion of the gear. The drive transmission mechanism device according to claim 1, wherein the rotational rigidity is adjusted by (1). Claim 5
In the invention described, the gear of the transmission mechanism is formed of resin,
The drive transmission mechanism device according to claim 1, wherein the rotational rigidity is adjusted by changing an axial contact height of the pin receiving portion at a fastening portion formed by a pin receiving portion of the gear corresponding to the driven shaft pin. I do. According to a sixth aspect of the present invention, there is provided the drive transmission mechanism device according to the first aspect, wherein a driven shaft pin is used as a fastening means for the driven shaft and the driven gear, and rotational rigidity is adjusted by changing a pin diameter. I do.

According to a seventh aspect of the present invention, there is provided a drive transmission mechanism device according to the first aspect, wherein the rotational rigidity at the time of starting changes more than the rotational rigidity at a constant speed. According to an eighth aspect of the present invention, there is provided the drive transmission mechanism device according to the first or seventh aspect, wherein the pin receiving portion of the gear corresponding to the driven shaft pin has a double beam structure. Claim 9
According to the present invention, there is provided a drive transmission mechanism device according to claim 1 or 7, wherein the number of contact points between the driven shaft pin and the corresponding pin receiving portion of the gear changes according to the load torque. According to a tenth aspect of the present invention, there is provided the drive transmission mechanism device according to the first or seventh aspect, wherein an interval between the two pin receiving portions is changed in the fastening portion.

[0009]

Embodiments of the present invention will be described below with reference to the drawings. (First Embodiment) The first embodiment of the present invention will be described. FIG. 1 shows a vibration model and equations for its transfer characteristics.
Between the drive gear on the drive shaft side and the driven gear on the driven shaft side, the gear teeth versus rigidity (K
The load due to the disturbance torque generated by 1) is applied. This force is applied to the teeth of the driven gear, and is transmitted to the driven shaft via the rotational rigidity (K2) of the fastening portion that connects the driven gear and the driven shaft. In the present invention, the value of the rotational rigidity (K2) of the fastening portion is adjusted so as to reduce the influence of the disturbance torque due to the load. As a method of this, instead of newly using an elastic body part as in the related art, a portion to be fastened to a driven shaft of a driven gear is used.

FIG. 2 shows an explanatory diagram thereof. The driven gear 1 is provided with a pin receiving portion 4 having a convex shape which is elastically deformed, and by deforming the pin receiving portion 4, the rotational rigidity K2 of the fastening portion can be set.
FIG. 3 is a sectional view showing a deformation of the pin receiving portion 4. FIG.
3A, the pin receiving portion 4 is not deformed when there is no load, but when a load is applied, the pin receiving portion 4 is deformed by ε as shown in FIG. 3B. As a result, the driven shaft 2 and the driven gear 1 are inclined at an angle φ. Assuming that the load at this time is Te, the rotational rigidity K2 of the fastening portion is K2 = Te / φ. The coaxiality of the driven shaft 2 and the driven gear 1 can be maintained with high precision because there is no portion that is elastically deformed in the radial direction.

FIG. 4 shows the result of adjusting K2. Frequency is plotted on the abscissa, and displacement on the driven shaft with respect to disturbance torque is the disturbance resistance characteristic on the ordinate. The further down in this graph,
Indicates that it is strong against disturbance torque. The rotational rigidity of the fastening part is K2
= A (broken line) and K2 = B (solid line) in the graph. The case of K2 = B is the adjustment result according to the present invention. Comparing the value of fz described in claim 1 with the value of the meshing frequency fp at the operating rotational speed, K2 = A
Fp <fz when K2 = B, and fp> f when K2 = B
z. As a result, it can be seen that the disturbance resistance was improved by δ.

(Second Embodiment) A second embodiment will be described. FIG. 5 is a view showing the pin receiving section 4. The load is Te, the load of the pin receiving portion 4 is Fe, the radius of the mounting position of the pin receiving portion 4 is r, the pin receiving width of the pin receiving portion 4 is b, the thickness of the pin receiving portion 4 is t, and the pin receiving portion 4 has a thickness of t. Assuming that the axial height is L, the Young's modulus of the material of the driven gear 1 is E, the deformation of the pin receiving portion 4 is ε, the torsion between the driven gear 1 and the driven shaft 2 is φ, and the rotational rigidity of the fastening portion is K2. From the bending equation of the material mechanics, ε = (4 · L ³ ) / (E · b · t ³ ) · Fe Further, assuming that the pin receiving portion has four axially symmetrical points (two contact points), Te = 2 · Fe · r in addition, the balance of the load, also Te = K2 · φ, and the deformation of the driven shaft pin 5 is small, epsilon = phi · r When obtaining them from K2, K2 = (E · b · t 3 · r 2 ) / (2 · L ³ ). Here, as a method for easily adjusting the rotational rigidity K2 of the fastening portion which needs to be set corresponding to the gear meshing frequency fp, as shown in FIG. 5, the mounting position radius r of the pin receiving portion is adjusted. I do. The position of r can be easily formed by setting it in the mold similarly to the gear teeth.
Since the rotational rigidity K2 of the fastening portion is proportional to the square of r,
Adjustment in a wide range is possible.

(Third Embodiment) A third embodiment will be described. As a further method for easily adjusting the rotational rigidity K2 of the fastening portion which needs to be set in accordance with the gear meshing frequency fp, in FIG. 5, the thickness t of the pin receiving portion is adjusted. The thickness t can be easily formed by setting the thickness in a mold similarly to the gear teeth. Since the rotational rigidity K2 of the fastening portion is proportional to the third power of t, adjustment in a wider range is possible.

(Fourth Embodiment) A fourth embodiment will be described. As a further method for easily adjusting the rotational rigidity K2 of the fastening portion which needs to be set in accordance with the gear meshing frequency fp, the pin receiving width b of the pin receiving portion is adjusted in FIG. This pin receiving width b is
It can be easily formed by setting it in a mold similarly to the gear teeth. Since the rotational rigidity K2 of the fastening portion is proportional to b, high-precision adjustment in a narrow range is possible.

(Fifth Embodiment) A fifth embodiment will be described. As a further method for easily adjusting the rotational rigidity K2 of the fastening portion which needs to be set in accordance with the gear meshing frequency fp, in FIG. 5, the pin contact axial height L is adjusted. The contact height L can be easily formed by setting the contact height L in a mold similarly to the gear teeth. Since the rotational rigidity K2 of the fastening portion is inversely proportional to the third power of L, adjustment in a wider range is possible.

(Sixth Embodiment) A sixth embodiment will be described. FIG. 6 is a view showing the pin receiving section 4. In FIG. 6, the load is Te, the load of the pin receiving portion 4 is Fe, the mounting position radius of the pin receiving portion 4 is r, the length of one pin is Lp, the pin diameter is dp, and the Young's modulus of the material of the driven shaft pin 5 is Ep. Assuming that the amount of deformation of the driven shaft pin 5 is εp, the torsion between the driven gear 1 and the driven shaft 2 is φ, and the rotational rigidity of the fastening portion is K2, εp = (64 · Lp ³ ) / ( 3 ・ Ep ・ π ・ dp ⁴ ) ・
Fe In addition, assuming that the pin receiver has four locations on the axis (two contacts), Te = 2 · Fe · r Also, from the balance of the load, Te = K2 · φ Also, assuming that the deformation of the pin receiver is small, εp = Φ · r When K2 is obtained from these, K2 = (3 · π · Ep · dp ⁴ · r ² ) / (32 · Lp
³ ) Here, as a further method for easily adjusting the rotational rigidity K2 of the fastening portion which needs to be set in accordance with the gear meshing frequency fp, as shown in FIG. 6, the pin diameter dp is adjusted. The diameter of the driven shaft pin 5 made of metal is reduced to make the resin receiving pin receiving portion 4 not elastically deform. As a result, the driven shaft pin 5 is elastically deformed, and the rotational rigidity K2 of the fastening portion can be set. Driven shaft pin 5
Is not brittle as compared with the resin-molded pin receiving portion 4, so that it can be deformed without breaking even when an impact load is applied.

(Seventh Embodiment) A seventh embodiment will be described. FIG. 7 is a graph showing the relationship between load and rotational rigidity in the present invention. In order to enable the driven shaft to perform a quick operation corresponding to the acceleration at the time of start-up, the rotational rigidity K2 at the time of a high-load start-up is larger than the rotational rigidity K2 at a constant speed. As can be seen from FIG. 7, by setting the rotational rigidity K2 at a constant speed, which is a steady state, and the rotational rigidity K2 'at the time of startup, the delay of the driven shaft due to the torsion of the fastening portion at the time of startup is reduced. It has the effect of shortening the startup time.

(Eighth Embodiment) An eighth embodiment will be described. FIG. 8 is a perspective view showing a pin receiving portion. As a method for easily setting the switching of the rotational rigidity required at the time of starting and at a constant speed, the driven gear receiving portion is provided with two
The beam structure will be heavy. The driven shaft pin 5 has a rotational rigidity K2 that deforms only the beam portion of the portion A in a steady state when the load is small, but when a high load is applied at the time of starting, the beam of the portion A is deformed and reaches the beam of the portion B. It will be deformed. The rotational rigidity at this time is K2 ', and the rotational rigidity can be set variable with a simple structure.

(Ninth Embodiment) A ninth embodiment will be described. FIG. 9 is a perspective view showing a pin receiving portion. As a further method for easily setting the switching of the rotational rigidity required at the time of starting and at a constant speed, the number of contact points of the pin receiving portion 4 is changed according to the disturbance torque.
When the load on the driven shaft pin 5 is small and steady, the beam portion of the portion A which is close to the driven shaft pin 5 and has low rigidity has a rotational rigidity K2 in which the beam portion A contacts by δp. The driven shaft pin 5 is deformed and also comes into contact with the beam in the portion B. For this reason, the rotational rigidity is the rotational rigidity K2 'obtained by combining the portions A and B. By providing the pin receiving portion corresponding to the rotational rigidity to be changed in this way, the number of contact points changes according to the load, so that the rotational rigidity can be varied with a simple structure.

(Tenth Embodiment) The tenth embodiment will be described. FIG. 10 is a sectional view showing a set position of the pin receiving portion. As a further method for easily setting the switching of the rotational rigidity required at the time of startup and at a constant speed, the interval between the two pin receiving portions is changed and set. Figure 1
At 0, one interval is δu and the other interval is δd. In a steady state where the load of the driven shaft pin 5 is small, only the driven shaft pin 5 on the δu side with a small interval contacts the pin receiving portion 4. At this time, since the driven shaft pin 5 on the δd side is not in contact, the load is supported only by the driven shaft pin 5 on the δu side. At this time, the rotational rigidity corresponds to K2. At the time of startup when a high load is applied, the deformation on the δu side increases, and comes into contact with the pin receiver 4 on the δd side. In this state, the rotational rigidity corresponds to K2 '. In this way, by setting the magnitudes of δu and δd, the switching of the rotational rigidity can be easily adjusted.

[0021]

As described above, according to the first aspect of the present invention, the coaxiality of the gear teeth can be maintained with high precision without adding any elastic parts, and the disturbance torque at the driving gear meshing frequency can be maintained. Is not transmitted to the driven gear side, and a highly accurate drive transmission mechanism device can be provided. Further, according to the present invention, the rotational rigidity of the fastening portion can be easily adjusted, and the influence of the disturbance torque generated at the driving gear meshing frequency is not transmitted to the driven gear side. An accurate drive transmission mechanism device can be provided. Further, according to the present invention, it is possible to provide a drive transmission mechanism device in which a delay due to rotational rigidity at the time of starting is reduced and a quick operation is possible. Further, according to the present invention as set forth in claims 8 to 10, it is possible to easily set the switching of the rotational rigidity required at the time of startup and at a constant speed, to suppress the influence of disturbance torque generated at the drive gear meshing frequency, and A delay due to rotational rigidity at the time of startup is reduced, and a highly accurate drive transmission mechanism device can be provided.

[Brief description of the drawings]

FIG. 1 shows a vibration model relating to a driven gear and equations for its transmission characteristics.

FIG. 2 is a schematic configuration diagram of a driven gear.

FIG. 3 is a sectional view showing a deformation of a pin receiving portion.

FIG. 4 is a graph showing adjustment results of rotational rigidity.

FIG. 5 is a perspective view showing a pin receiving portion of the present invention.

FIG. 6 is a perspective view showing a pin receiving portion of the present invention.

FIG. 7 is a graph showing a relationship between load and rotational rigidity.

FIG. 8 is a perspective view showing a shape of a pin receiving portion of the present invention.

FIG. 9 is a perspective view showing a set position of a pin receiving portion of the present invention.

FIG. 10 is a sectional view showing a set interval of a pin receiving portion of the present invention.

[Explanation of symbols]

 DESCRIPTION OF REFERENCE NUMERALS 1 driven gear 2 driven shaft 3 fastening portion 4 pin receiving portion 5 driven shaft pin

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification code FI Theme coat ゛ (Reference) F16F 15/133 F16H 55/06 F16H 55/06 55/14 55/14 F16F 15/12 Z

Claims (10)

[Claims] 1. A drive transmission mechanism device comprising: a drive shaft connected to a drive source such as a motor; a driven shaft for performing an operation; and a driven gear as a transmission mechanism for transmitting a driving force to the driven shaft. Assuming that only the rotational direction is elastically deformed at the joint between the shaft and the driven gear, the rotational rigidity is K2, the inertia moment of the driven shaft is J2, and the gear meshing frequency fp during operation is as follows. Rotational rigidity of driven gear fastening part K2
A drive transmission mechanism device, characterized in that: fp> fz where fz = (1 / 2π × √ (K2 / J2)) × √2 2. The driven gear of the transmission mechanism is formed of resin, and the rotational rigidity is adjusted by changing the mounting position radius of the pin receiver at a fastening portion comprising the driven shaft pin and the corresponding pin receiver of the driven gear. The drive transmission mechanism device according to claim 1, wherein: 3. The driven gear of the transmission mechanism is formed of resin, and the rigidity is changed by changing the thickness of the pin receiver in the rotating direction at a fastening portion comprising a driven shaft pin and a corresponding pin receiving portion of the driven gear. The drive transmission mechanism device according to claim 1, wherein: 4. A driven gear of a transmission mechanism is formed of resin, and is rotated by changing a radial pin receiving width of the pin receiving portion at a fastening portion including a driven shaft pin and a pin receiving portion of the driven gear corresponding to the driven gear. The drive transmission mechanism device according to claim 1, wherein rigidity is adjusted. 5. The driven gear of the transmission mechanism is formed of resin, and is rotated by changing the contact height in the axial direction of the pin receiving portion at a fastening portion formed of a driven shaft pin and a corresponding pin receiving portion of the driven gear. The rigidity is adjusted.
The drive transmission mechanism device as described in the above. 6. The driven gear of the transmission mechanism is formed of resin, a driven shaft pin is used as a fastening means for the driven shaft and the driven gear, and rotational rigidity is adjusted by changing a pin diameter. Item 2. The drive transmission mechanism device according to Item 1. 7. The drive transmission mechanism device according to claim 1, wherein the driven gear of the transmission mechanism section is formed of resin, and the rotational rigidity at the time of startup changes more than the rotational rigidity at a constant speed. 8. The drive transmission mechanism device according to claim 1, wherein a pin receiving portion of the driven gear corresponding to the driven shaft pin has a double beam structure. 9. The drive transmission mechanism device according to claim 1, wherein the number of contact points between the driven shaft pin and the corresponding pin receiving portion of the driven gear changes according to the load torque. 10. The drive transmission mechanism device according to claim 1, wherein an interval between the two pin receiving portions is changed in the fastening portion.