JPS5918191Y2 - speed change pulley - Google Patents

Description

[Detailed Description of the Invention] This invention relates to a belt-type continuously variable transmission, and more specifically, to an improvement of a speed change pulley in a belt-type continuously variable transmission in which the facing distance between groove side surfaces is variable.

BACKGROUND OF THE INVENTION Belt-type continuously variable transmissions in which the opposing distance between groove sides is variable are often used as transmission mechanisms for power transmission in agricultural machinery, civil engineering machinery, small fishing boats, and the like.

In the speed change pulley used in the above device, as shown in FIG. By making one or both of the conical plates slidable in the axial direction, the pitch diameter can be freely changed by making the opposing distance d of the groove side surfaces variable.

In FIG. 1, the area above the center line of the figure shows the case where the groove interval d is widened, and the area below the center line shows the case where the groove interval d is narrowed.

By the way, the sliding conical plates of the conical plates 11L and 11R need to always slide smoothly along the axial direction with respect to the rotation axis so that smooth gear changes can be performed.

However, in the case of agricultural machinery and civil engineering machinery that are not in use for a long time, the conical plate
1. Since the sliding surface S on which L slides is left exposed, this part is prone to rust, and if it is a fishing boat that is easily affected by salt, etc. Even during a short interruption period, there is a risk of rust forming on the sliding surface S, and there is a problem in that if rust occurs, the transmission mechanism will no longer function at all.

For this reason, in the past, the sliding portions were plated, made of metal with no risk of rusting, or the sliding surfaces were hermetically sealed with lubricating oil. However, all of these methods require complicated manufacturing steps, and the structure of the sliding surface itself is also complicated, making manufacturing time-consuming and extremely expensive.

In view of the above-mentioned drawbacks, this invention was made with the aim of providing a belt-type continuously variable transmission that can effectively prevent rust on the sliding surfaces and has a simple structure. A belt-type stepless belt-type stepless belt type belt type stepless belt system in which a fixed conical plate and a movable conical plate are provided on one or each of the drive rotating shaft and the conventional rotating shaft, and a belt is passed through the groove formed by the fixed conical plate and the movable conical plate. In a transmission, the axially inner sliding surface formed on the inner surface of a movable conical plate that is in sliding contact with the outer peripheral sliding surface of the rotating shaft has both ends located on the outer peripheral surface of the rotating shaft in the axial direction of the outer peripheral sliding surface. The length is set to match both ends, and when the distance between the fixed conical plate and the movable conical plate is maximized on the drive rotating shaft side, and when the gap between the fixed conical plate and the movable conical plate is the minimum on the driven rotating shaft side. The outer circumferential sliding surface of the rotating shaft and the inner circumferential sliding surface of the movable conical plate match, and the structure is such that no exposed portion is formed on the sliding surfaces of both the rotating shaft and the movable conical plate. It is.

Next, this invention will be explained using examples.

FIG. 2 is a sectional view of an embodiment of this invention.

The belt-type continuously variable transmission 1 of this invention is configured such that speed change boots 'JIA and IB are provided on both the drive shaft A and the driven shaft B, and the effective pitch diameter of the winding of the belt 2 can be changed relative to the drive shaft A and the driven shaft B. In Fig. 2, a fixed conical plate 1 is attached to each of the driving rotation shaft A and the driven rotation shaft B arranged in parallel.
0 A, 10 B and movable conical plates 11 A, 11 B
and a fixed conical plate 10A.

10B and movable conical plates 11A, IIB, the belt 2 is passed through the grooves 3A, 3B formed by the movable conical plates 11A, IIB.
Both axial ends of the inner circumferential sliding surfaces 13A and 13B provided on the inner surfaces of the movable conical plates 11A and IIB that are in sliding contact with the movable conical plates 12B are the axially opposite ends PX of the outer circumferential sliding surfaces 12A and 12B that are present on the rotating shaft. , PY, and when the distance d between the fixed conical plate 10A and the movable conical plate 11A is maximized on the driving rotation axis A side, and the fixed conical plate 10B and the movable conical plate 11A on the driven rotation axis B side. 11B, the outer circumferential sliding surfaces 12A, 12B of the rotating shaft and the inner circumferential sliding surfaces 13A, 13B of the movable conical plate match, and the rotating shaft A,
The sliding surfaces 12A and 13A, 12B and 13B on both the B side and the movable conical plates 11A and 11B are configured so that no exposed portions are formed.

In addition, in the above, the maximum and minimum of the groove spacing d are the groove spacing when the speed change pulley is driven, and the rotation speed ratio to be transmitted is in the most decelerating state on the driven rotating shaft B side, or the speed change pulley. Refers to the state of the groove spacing of each pulley that inevitably occurs when the drive operation of the pulley is stopped.

Next, the operation of the embodiment of this invention will be explained.

In the state shown in FIG. 2, the groove spacing d of the speed change boob 'JIA on the driving rotation shaft A side is set to the maximum, and the groove spacing d of the speed change boob IJIB on the driven rotation shaft B side is set to the minimum.

Therefore, based on these correlations, the rotation transmission to the driven rotation shaft B side is in the most decelerated state.

At this time, the outer circumferential sliding surfaces 12A, 12B of the rotating shaft and the inner circumferential sliding surfaces 13A, 13B of the movable conical plate are in a state of matching, and are not exposed to the outside at all.

In addition, since the non-sliding surfaces 19A and 19B of the rotating shaft are placed one step closer to the shaft center than the outer peripheral sliding surfaces 12A and 12B of the rotating shaft, even if they are exposed to the outside and rust occurs, the movable conical plate will not be damaged. Since it does not come into contact with the inner peripheral sliding surfaces 13A and 13B, there is no problem in operation.

Next, if the drive rotation shaft A is rotationally driven, and then the movable conical plate 11A of the drive rotation shaft A is slid in the axial direction (arrow P) to narrow the interval d between the grooves 3A, the driven rotation shaft B is
The interval d between the grooves 3B of the side speed change pulley 1B is gradually expanded via the belt 2, and the increased speed rotation is transmitted.

At this time, the outer circumferential sliding surfaces 12A, 12B of the rotating shaft and the inner circumferential sliding surfaces 13A, 13B of the movable conical plates are partially exposed to the outside depending on the amount of axial movement of the movable conical plates 11A, 11B. However, the movable conical plates 11A and 11B
The sliding surfaces 12A, 12B and 13A are in sliding contact with each other because they are reciprocated from beginning to end depending on the amount of rotation.

There is no risk of rusting with 13B.

Moreover, as mentioned above, the non-sliding surface 19A on the rotating shaft.

Even if there is rust on the movable conical plates 11A and 19B, there is no problem in the operation of the movable conical plates 11A and IIB.

Next, when stopping the device 1, the number of rotations on the driven rotating shaft B side is usually minimized, and then the driving rotating shaft A is stopped.
, IB are returned to the state shown in FIG. 2, and each sliding surface 12
A and 13A, 12B and 13B match each other, and no exposed portion is formed.

Therefore, even if the sliding surfaces 12A, 13A, 12B, and 13B are stored in this state for a long period of time, they are shielded from the outside air, and there is no possibility of rusting.

FIG. 3 is a sectional view showing another embodiment of the present invention, in which the outer circumferential sliding surfaces 12A, 12B of the respective rotation axes A, B on which the movable conical plates 11A, 11B slide are It is divided into two in the direction, and there are movable conical plates 1 on 15A and 15B between them.
Keys 16A and 16B, which also serve as stoppers, are provided to protrude inward from the inner circumferential sliding surfaces 13A and 13B of IA and IIB, thereby regulating the amount of movement of the respective movable conical plates 11A and 11B.

Even in this case, the movable conical plates 11A, 11B
Both axial ends of the inner peripheral sliding surfaces 13A and 13B are connected to the rotation axis A.
, B at both axial ends PX of the outer peripheral sliding surfaces 12A and 12B.

Since the length is set to match PY, the sliding surfaces 12A and 13A, 12B and 13B are not exposed to the outside at all in the retracted state as described above.

In addition, in FIG. 3, 17A and 17B indicate O-rings provided on the respective sliding surfaces, and are provided by the same technique as those normally inserted between the sliding surfaces.

In addition, as shown in FIG. 4, movable conical plates 11A, 1
In order to regulate the sliding amount of 1B, stoppers 18A and 18 are used instead of keys 16A and 16B as shown in FIG.
B, 18 B' may be provided.

In addition, in Figures 3 and 4, configurations other than the above are shown in Figure 2.
Since it is the same as that shown in the figure, the corresponding parts are simply given the same reference numerals and the explanation will be omitted.

Furthermore, in the above embodiment, a case was shown in which variable speed pulleys were provided on both the driving rotation shaft and the driven rotation shaft, but one of the rotation shafts was provided with a speed change pulley similar to that of the present invention, and the other rotation shaft was The same method can be applied to a belt transmission device in which a fixed pulley with a constant effective pitch diameter is provided and an idler for tensioning the belt is provided.

As described above, this invention is such that both axial ends of the inner circumferential sliding surface provided on the inner surface of the movable conical plate that is in sliding contact with the outer circumferential sliding surface provided on the rotating shaft The length is set to match both ends of the sliding surface in the axial direction, and the sliding surfaces on the drive rotating shaft side and the driven rotating shaft side are provided at positions that match when the respective sliding surfaces are in the lowest speed state, so that the device can be kept in a low speed state. If the machine stops at this point, each sliding surface will not be exposed to the outside at all, and therefore, the sliding surface will be cut off from the outside air and there will be no risk of rusting.

In addition, according to this invention, it is very easy to form the sliding surface, and there is no need to plate the sliding surface, use special metals, or create a complicated structure as in the past, so the structure of the speed change pulley It has various practical effects such as being extremely simple and being able to provide it at low cost.

[Brief explanation of the drawing]

Fig. 1 is an explanatory diagram of a conventional example, Fig. 2 is a sectional view of an embodiment of this invention, Fig. 3 is a sectional view of another embodiment, and Fig. 4 is a sectional view of essential parts of yet another embodiment. be.

Claims (1)

[Scope of utility model registration request] A fixed conical plate and a movable conical plate are provided on one or each of the driving co-rotating shaft and the driven rotating shaft arranged in parallel, and a belt is passed through the groove formed by the fixed conical plate and the movable conical plate. In a belt-type continuously variable transmission, both ends of an axially inner circumferential sliding surface provided on the inner surface of a movable conical plate that makes sliding contact with the outer circumferential sliding surface of the rotating shaft are outer circumferential sliding surfaces that exist on the outer circumferential surface of the rotating shaft. The length corresponds to both ends of the moving surface in the axial direction, and when the distance between the fixed conical plate and the movable conical plate is maximized on the drive rotating shaft side, and the distance between the fixed conical plate and the movable conical plate on the driven rotating shaft side. The outer circumferential sliding surface of the rotating shaft matches the inner circumferential sliding surface of the movable conical plate when Belt type % type % characterized by