JPS5980550A - Multirotation speed change gear - Google Patents

Abstract

PURPOSE:To make the rotation of plural output shafts deceleratable simultaneously and separately from one input shaft, by coupling plural planetary gears carrying two types of external gears, which rotate and revolve around an eccentric shaft rotated solidly with an input shaft, and either of annular internal gears engaged with these planetary gears to the output shaft, while braking the others. CONSTITUTION:When a coil 15 is energized with current, it locks a brake member 11 and rotates in the reverse against direction rotation in an eccentric shaft 1a as far as a portion for (n) teeth per rotation in the eccentric shaft 1a rotated solidly with an input shaft 1. Next, when an internal gear 5a is locked, an external gear 2a rotates by n/M in the reverse direction per rotation in the input shaft 1. External gears 2a and 2b both are unified with a planetary gear 2 and when the internal gear 5a is set free, this internal gear 5a rotates in the reverse direction against the rotation of the planetary gear 2 and rotates by l.n/N (N+l) in the direction per rotation in the input shaft 1. Therefore, an input shaft 9 rotates in the same direction as that of the input shaft 1 at such a reduction gear ratio R as N(N+l)/l. Next, when a coil 28 is energized with current, an output shaft 10 rotates in the same direction as the input shaft does at the same reduction gear ratio R so that rotation in both shafts can be made at will.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a multi-acting transmission device in which a plurality of at least two narrow output shafts are rotated simultaneously or individually while being decelerated by one input shaft.

Conventionally, this type of multi-variable transmission device transmits power from one human power shaft to transmission gears paired with each of multiple output shafts. Clutches are required as many times as there are output shafts for transmission and disconnection.
One drawback is that the structure is complex and expensive.

The present invention eliminates the drawbacks of the conventional devices mentioned above.

The object of the present invention is to provide a multi-acting transmission that does not use a clutch, has a relatively simple structure, and is inexpensive.

Hereinafter, the present invention will be explained based on FIGS. 1 to 3.

FIG. 1 is a side sectional view showing the main parts of an embodiment of a multi-acting transmission according to the present invention, and what is shown on the right is the main body of an annular internal gear that becomes a brake member. An example is shown in which the fixed brake is a swing type solenoid, and the one shown on the left shows an example in which the brake is a reciprocating type solenoid. The second figure is a view taken along the line A--A of the eleventh engine 1 showing a state in which the brake member and the swinging solenoid are engaged, and FIG. 3 is a front view of the gear portion of FIG. 1.

In FIGS. 1 to 3, 1 is the human power axis.

1a is an eccentric shaft that rotates together with the human power shaft.

The 11III center shaft 1a is provided in the middle part of the human power shaft 1.
In this embodiment, it is formed integrally with the human power shaft 1.

1b, 1b are counterweights fixed to the input shaft 1 and in contact with both end surfaces of the eccentric shaft 1a, and are used to balance the input shaft 1. 2.3 are planetary gears arranged on the eccentric shaft la via bearings 4 fixed to the outer periphery of the eccentric shaft 1a, and these planetary gears 2 and 3 each rotate around the eccentric shaft 1a. At the same time, it revolves due to the rotation of the eccentric shaft 1a. On the outer periphery of each of the planetary gears 2 and 3, a plurality of external gears 2a, 2b and 3a, 3b having different numbers of teeth are formed at the front stage in the axial direction.

The outer 5 has the plurality of external gears 2a, 2b [6a, 6b each having a plurality of annular internal gears 5a, 5b that mesh with each other in four contacting manners.
This is an internal gear set with Each of the internal gear sets 5.6 includes one annular internal gear 5a, (3ai), a plurality of different output units 19 fixed to the input shaft 1 and rotatably supported on bearings 7 and 8, respectively; Output Menno (-) connected to 10. In this implementation?11, the annular internal gear 5
a, the output shaft 9, the ring 4, the internal canine gear 6, and the output shaft 10 are each integrally constructed.

Reference numerals 11 and 12 are the main bodies of the other annular internal gears 5b and 6b, respectively, and brake men)<-.

The number of teeth of the external gear 2a and the external gear 2b and the number of teeth of the external gear 3a and the external gear 3b (although it is a tool,
The number of teeth 1t'i of the external gear 2a and the external gear 3a and the number of teeth 1t'i of the external gear 2b and the external gear 3b may be the same or different. In this actual trip, the number of teeth of the external gears 2a and 3a is set to iN, and the number of teeth of the external gears 2b and 3b is set to N+e.
The annular internal gear 5a is ingeniously increased by n teeth more than the external gear.
, the number of teeth of the annular internal gears 5b, 6b is N + l + n, the number of teeth of the external gears 2a, 2b and the annular internal gears 5a, 5b is 3rd. As shown in the figure, 1-IU is 11 large. The reason why the arc-shaped teeth i are used is that the difference in the number of teeth ni between the external gear and the annular internal gear that meshes with the core external gear can be reduced. In the case where the difference in the number of teeth is n>3, the tooth profile of each gear other than the circular arc shape can be sufficiently applied. Incidentally, the tooth shapes of the external gears 3a, 3b and the loam-like internal teeth i6a, 6b are also arcuate, although not shown.

Here, first, as shown on the right side of FIG. 1, the brake 13 that fixes the annular brake member 11 is assumed to be a swing type solenoid, and the case will be explained. 14 is a bobbin around which a coil 15 is wound, and a core 16 is fixed to the center of the bobbin 14. 17 is a 5-shaped base plate to which the 16 cores are fixed, and the case 2 is fixed with set screws 18 and 18.
This is attached to 3.

A swing armature 19 is hinged to the base plate 17 so as to be swingable. Reference numeral 19a is a claw of one swinging armature 19 provided on the opposite side to the hinge portion. 31 is a return spring, and coil 15! ! This is for energizing the swinging armature 19r to the position shown by the single-point chain section in FIG.

Numerals 20 and 21 are a plurality of large protrusions and a plurality of small protrusions that are alternately provided at the same pitch on the outer periphery of the annular brake handle <-11. When the coil 15 is energized, a four part 22 is formed into which the claw 19a fits. Flake member 1
1 is a case 23, a bearing tube 323a, and the case 2.
3 and supported by a single bearing 24, the output shaft 9
is supported by a bearing 11a press-fitted into the brake man/ri-11.

Next, as shown on the left side of FIG. 1, the brake 26 that fixes the two-rake member 12 of the four-ring ring is moved. The case of using a summer type solenoid will be explained. The annular brake member 12 has its outer periphery supported by a bearing 25 fixed to the case 23', and a cylindrical part 12b extending to the full rake member 12', which is integral with the crab case 23'. @ It is supported by the receiving part 23'a. In addition, it is also movable in the axial direction of the brake mennowy 1261, and Q'S is attached to the outer periphery of the 1261 axial direction, and the circle 1111L 5
12a is formed. It is press-fitted and fixed to the output shaft 10 and the brake shaft <-12, and is supported by a single bearing 12e.

27 is a bobbin around which a coil 28 is wound;
A magnetic core 29' (f) is fixed to the core 29. The tip of the core 29 is formed into a conical cylindrical portion 29a, and is disposed opposite the conical portion 12a.

30 is arranged between the brake member 12 and the bobbin 27;
This spring is used to normally bias the conical portion 12a of the brake member 12 in a direction away from the conical cylindrical portion 29a.

Next, the operation of this device having the following configuration will be explained.

When the coils 15 and 28 are not energized, the oscillating solenoid 13 and the reciprocating solenoid 26 are inactive, and the brake members 11 and 12 are open, so that the motor (not shown) Even when the human power shaft 1 is rotated, no driving force is transmitted to the output shaft 9.10.

Next, when the coil 15 is energized, the swinging armature 19 is attracted to the core 16 as shown by the solid line in Figure 2.
a fits into the recess 22 of the brake member 11 and fixes the brake member 11. At this time, for each rotation of the eccentric shaft 1a that rotates together with the input shaft 1, the external gear 2b
That is, the difference in the number of teeth between the planetary gear 2 and the annular internal gear 5b is n.
It rotates in a direction opposite to the rotational direction of the eccentric shaft 1a by a fraction.

In other words, the planetary gear 2 rotates the input shaft 1 per rotation of the human power shaft 1.
Rotates N+e in the direction opposite to the direction of rotation.

Here, assuming that the annular internal gear 5ai is fixed, the external gear 2a, that is, the planetary gear 2 rotates 11 times in the direction opposite to the rotational direction of the input shaft 1 for each rotation of the input shaft 101. Since the external gears 2a and 2b are each formed on the planetary gear 2, they are integral, and if the annular internal gear 5a is freed, the internal gear 5a will rotate in the opposite direction to the rotational direction of the planetary gear 2. For every rotation of the input shaft 101, the input shaft 1 rotates up -1, that is, by 7 rotations in the same direction as the rotation direction of the input shaft 1. Therefore, the output shaft 9 connected to the ring N N+e-shaped internal gear 5a is N(N+'
) rotates in the same direction as the rotational direction of the input shaft 1. When the coil 15 is de-energized,
The swing armature tool a 19 returns to the position shown by the dashed line in FIG. 2 due to the urging force of the return spring 31, and the claw 19a
is removed from the recess 22 and the brake member 11 is released, so the driving force from the input shaft 1 is not transmitted to the output shaft 9 and the output shaft 9 stops.

Next, when looking through the coil 28, a magnetic circuit is formed by the core 29 and the cylindrical portion 12b that is an extension of the brake member 12, and the brake member 12 is moved in the direction of arrow B shown in FIG. The conical part 12a is attracted to the conical cylinder part 29a of the core 29, and a rotational frictional force is generated between the two.

The frictional force becomes, for example, several times the attraction force of the solenoid due to the wedge action of the cone, and the brake member 12 is fixed by the frictional force, and when the input shaft 1 (z1 rotates), the annular inner The output shaft 10 connected to the gear 6a rotates in the same direction as the rotation direction of the human power shaft 10 at a reduction ratio R of N(N+').When the coil 28 is de-energized, the brake member 12
is opened, so the driving force from the input shaft is transferred to the output shaft 10.
The output shaft 10 is stopped because the signal is not transmitted to the output shaft 10.

Therefore, in this device, it is possible to simultaneously decelerate and rotate one input shaft 1 to output shaft 9.10 by energizing the coils 15.28 at the same time, without using multiple clutches as in the conventional case. At the same time, by energizing only one coil 15 or 28, one output IM
Since a multi-acting transmission device capable of rotating with a speed reduction of only 9 or 10 II is obtained, its structure becomes relatively elaborate and inexpensive. Also, each output shaft 9.1
0 can easily cut off power transmission from the input shaft 1 by cutting off current to the coil 15.28 and opening the brake member 11.12'ff.

In the above description, the brake 13 that fixes the brake member 11 is a swinging type solenoid, and the brake 26 that fixes the brake member 12 is a reciprocating type solenoid. Both brakes 13 and 26 are used as swinging solenoids or as reciprocating solenoids.

In the present embodiment, a pair of devices each including a planetary gear formed with a plurality of external gears and an internal gear set having a plurality of annular internal gears that mesh with each other in two contact with each of the external gears is used as a pair of devices. each one of the plurality of annular internal gears constituting the two internal gear sets is connected to the two output shafts. However, by increasing the number of planetary gears and internal gears, the number of output shafts can be further increased. In addition, although the number of external gears formed on each planetary gear and the annular internal gears of each incisor gear set meshing with the external gears was two each, three or more of each were used to form the main body of the annular internal gear. By alternately connecting brake members to the brakes, the reduction ratio of the same output shaft can be changed, or the same output shaft can be rotated forward or reverse.

1 As described above, the multi-acting transmission device of the present invention is capable of decelerating and rotating multiple output shafts from one input shaft simultaneously or individually, without using multiple clutches as in the conventional case. Therefore, the structure of the multi-acting transmission is relatively simple and can be obtained at low cost. Further, by opening the respective brake members of each output shaft, power transmission from the input shaft can be easily interrupted. Furthermore, the present invention has the advantage that the number of output shafts can be easily increased by arranging a pair of devices consisting of a planetary gear and an internal gear set in series on a plurality of input shafts and an integral eccentric shaft.

[Brief explanation of drawings]

FIG. 1 is a side cross-sectional view showing the main parts of an embodiment of the multi-speed transmission according to the present invention, and FIG. 2 is a side sectional view of FIG. A-
The A arrow view and Figure 3 are front views of both parts of Figure 1. 1... Input shaft 1a... Eccentric shaft 2, 3...
Planetary gears 2a, 2b, 3a, 3b=...external gears
5.6...Internal gear set 5a, 5b, 6a, 6b
... Annular internal gear 9.10 ... Output shaft 11.1
2...Main body of the annular internal gear (brake member)
13.29...Brake collection 1 Diagram 2

Claims (1)

[Claims] 1) an eccentric shaft that rotates integrally with the input shaft; a plurality of planetary gears that rotate around the eccentric shaft and revolve around the eccentric shaft, each forming a plurality of external gears each having a different number of teeth; It has a plurality of annular internal gears that mesh with each of the external gears, the same number of internal gear sets as the planetary gears, and a plurality of output shafts, each of the internal gear sets. A multi-acting transmission in which each one of the plurality of annular internal gears is used as an output member that is connected to the plurality of output shafts, and the main bodies of the other annular internal gears are used as brake members that are alternately connected to the brake. Device.