JP2011163461A - Continuously variable transmission mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent slip between a chain link and pulley, in a chain and V-belt type continuously variable transmission. <P>SOLUTION: A movable tooth meshing groove 14b of a link plate 14 is arranged within the range of the angle obtained by subtracting a delayed phase angle which is defined as the angle around the rotation center of the pulley for the range of the meshing contact between a movable tooth 17 and the movable tooth meshing groove 14b, from a link pace angle which is the angle between radial lines connecting the centers Op of link pin insertion holes 14a of the link plate 14 on both ends and the rotation center Os of the pulley, so as to mesh with the radially movable tooth 17 on the periphery of a pulley center boss part 16. The number of the movable gear meshing grooves 14b is set to a number (four pieces) with which the number of effective meshing teeth of the movable tooth 17 which meshes with the movable tooth meshing groove 14b within the winding range of the pulley (from a first tooth to seventh tooth) becomes one or more (three pieces). Thereby, at least one movable tooth 17 always meshes with the movable tooth meshing groove 14b of the link plate 14, and the slip between the chain link 13 and pulley can be prevented. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  TECHNICAL FIELD The present invention relates to a continuously variable transmission mechanism comprising an endless chain link in which a large number of link plates are sequentially connected in a daisy chain with link pins, and a pulley around which the endless chain link is wound so as to be continuously variable. Is.

As this type of continuously variable transmission mechanism, a V-belt type continuously variable transmission is well known, and the endless chain link is stretched over the V groove of the pulley to enable power transmission,
By continuously changing the winding diameter of the endless chain link with respect to the pulley by changing the groove width of the pulley V groove during the power transmission, the continuously variable transmission can be performed.

On the other hand, as a technique for increasing the transmission efficiency by suppressing the slip of the continuously variable transmission mechanism, conventionally, as described in Patent Document 1, for example, teeth are projected on the outer peripheral surface of the central boss portion of the pulley that defines the bottom surface of the pulley V groove. Set up
While the tooth groove formed on the inner periphery of the endless chain link is in the transmission ratio that meshes with the teeth on the outer peripheral surface of the pulley center boss, the transmission efficiency of the continuously variable transmission mechanism is prevented by preventing slippage between the pulley and the endless chain link. A technique for improving the above has been proposed.

  However, in this technology, since the teeth provided on the outer peripheral surface of the pulley central boss portion are fixed on the outer peripheral surface of the pulley central boss portion, when these teeth fail to mesh with the inner peripheral tooth groove of the endless chain link, the endless chain There was a problem of interfering with and damaging the link.

Therefore, the applicant of the present application previously described in Patent Document 2, the tooth provided on the outer peripheral surface of the pulley center boss part is a movable tooth that is movable in the radial direction with respect to the outer periphery of the pulley center boss part,
If this movable tooth fails to mesh with the inner peripheral tooth groove of the endless chain link, the teeth on the outer periphery of the pulley center boss can be retracted radially inward by the inner periphery of the endless chain link. A continuously variable transmission mechanism has been proposed in which it is not damaged by interference with the endless chain link.

JP-A-63-120950 JP 2010-014269 A

  However, in the above-described proposed technique, there is a meshing between the plurality of link plates provided with one endless chain link inner peripheral tooth groove and the pulley center boss outer peripheral movable tooth. Although there is a scene where a simultaneous meshing state occurs at an instant (at a certain phase) but a simultaneous non-meshing state occurs at the next moment (at the next phase), the following problems occur.

In other words, when there is a phase that is in the simultaneous meshing state and a phase that is in the simultaneous non-meshing state as described above, the slip between the endless chain link and the pulley is not constant, and stable slip prevention is achieved. I can not expect.
In order to solve this problem, the number of movable tooth meshing grooves provided on each link plate may be increased from one to a plurality. However, even if the number of movable tooth meshing grooves is increased without any consideration, Since only the probability of meshing increases, the simultaneous non-meshing state does not disappear, so a radical solution cannot be obtained.

The present invention increases the number of movable tooth meshing grooves provided in the link plate in such a manner that the simultaneous non-meshing state is eliminated, and at least one movable tooth is always meshed with the movable tooth meshing groove of the link plate. No way,
Accordingly, it is an object of the present invention to propose a continuously variable transmission mechanism that can realize stable slip prevention between the endless chain link and the pulley and does not cause the above-described problem.

For this purpose, the continuously variable transmission mechanism according to the present invention is constituted as follows.
First, the continuously variable transmission mechanism that is the basic premise of the gist configuration of the present invention is:
It consists of an endless chain link formed by connecting a large number of link plates in a daisy chain with link pins and a pulley around which this endless chain link is wound so as to be continuously variable. By engaging the movable teeth provided so as to be able to advance and retreat and the movable teeth engaging grooves provided on the link plate, slip prevention at a transmission ratio capable of the engagement is made possible.

The present invention provides such a continuously variable transmission mechanism.
From the link pitch angle θps, which is the angle between the radial lines that connect the center of the link pin insertion hole at both ends of the link plate and the center of the pulley in a state of meshing with the movable tooth, the movable tooth and the movable tooth The movable tooth meshing groove is within an angle range θps−Δθsub obtained by subtracting the delay phase angle Δθsub defined as the mesh contact range with the meshing groove as an angle around the pulley center.
A number Zsub is provided so that the number of effective meshing teeth Ze of the movable teeth meshing with the movable tooth meshing groove within the pulley winding range of the endless chain link is 1 or more.

In such a continuously variable transmission mechanism according to the present invention, the movable tooth meshing grooves are disposed in the angular range θps−Δθsub, and the number of the movable tooth meshing meshes is effectively meshed with the movable teeth within the pulley winding range. Because the number Zsub is such that the number of teeth is 1 or more,
At least one movable tooth is always meshed with the movable tooth meshing groove, so there is no phase that is not meshed at the same time, which realizes stable slip prevention between the endless chain link and the pulley can do.

It is a schematic side view which illustrates the continuously variable transmission mechanism to which the idea of this invention can be applied. FIG. 2 is a detailed view showing a slip prevention mechanism of a winding transmission portion on the secondary pulley side of the continuously variable transmission mechanism shown in FIG. FIGS. 1 and 2 show an anti-slip mechanism between the endless chain link and the secondary pulley of the continuously variable transmission mechanism shown in FIGS. 1 and 2, (a) is a detailed explanatory view showing the meshing state of the anti-slip mechanism, and (b) FIG. 5 is a detailed explanatory view showing a non-engagement state of the slip prevention mechanism. FIG. 4 is an explanatory diagram showing the relationship between the number of movable tooth meshing grooves provided on the link plate of the continuously variable transmission mechanism shown in FIGS. 1 to 3 and the meshing state of the movable teeth with respect to these movable tooth meshing grooves. It is detail drawing which shows the slip prevention mechanism of the winding transmission part in the secondary pulley side of the continuously variable transmission mechanism which becomes one Example of this invention. FIG. 6 is an explanatory diagram of various specifications of a link plate constituting an endless chain link of the continuously variable transmission mechanism shown in FIG. FIG. 6 is an explanatory diagram of various specifications related to a slip prevention mechanism of a winding transmission portion on the secondary pulley side of the continuously variable transmission mechanism shown in FIG. FIG. 8 is an explanatory diagram showing the relationship between the number of movable tooth meshing grooves provided on the link plate of the continuously variable transmission mechanism shown in FIGS. 5 to 7 and the meshing state of the movable teeth with respect to these movable tooth meshing grooves.

Hereinafter, embodiments of the present invention will be described in detail based on examples shown in the drawings.
<Example of continuously variable transmission mechanism to which the present invention is applicable>
1 and 2 illustrate a continuously variable transmission mechanism to which the concept of the present invention can be applied, FIG. 1 is a schematic side view of a continuously variable transmission mechanism 10, and FIG. 2 is a winding transmission on the secondary pulley side thereof. FIG.

In FIG. 1, 11 is a primary pulley that is a driving pulley of the continuously variable transmission mechanism 10, and 12 is a secondary pulley that is a driven pulley.
An endless chain link 13 is provided between the primary pulley 11 and the secondary pulley 12, and
The continuously variable transmission mechanism 10 can transmit power between the primary pulley 11 and the secondary pulley 12 via the endless chain link 13.

  Each of the primary pulley 11 and the secondary pulley 12 has opposed sheaves 11a and 12a that face each other in the rotation axis direction (in FIG. 1, for convenience, the front sheave is removed and only the sheave on the other side is shown). A V-groove pulley that defines a pulley V-groove between 11a and between the opposing sheaves 12a.

As clearly shown in FIG. 2, the endless chain link 13 is formed in a continuous annular shape by connecting a large number of link plates 14 in a chain shape with link pins 15 in link pin insertion holes 14a at both ends.
Both end surfaces of each link pin 15 are inclined so as to come into surface contact with the inner surfaces of the opposed sheave 11a and the opposed sheave 12a that provide the pulley V groove side walls of the primary pulley 11 and the secondary pulley 12.

  Thus, the endless chain link 13 is clamped between the opposed sheave 11a of the primary pulley 11 and the opposed sheave 12a of the secondary pulley 12 in the pulley winding region, and between the primary pulley 11 and the secondary pulley 12. Power transmission can be performed.

One of the opposed sheaves 11a of the primary pulley 11 is a fixed sheave, and the other is a movable sheave capable of stroke control in the axial direction.
The facing sheave 12a of the secondary pulley 12 has a sheave on the same side as the movable sheave of the primary pulley 11 as a fixed sheave, and a sheave on the same side as the fixed sheave of the primary pulley 11 as a movable sheave capable of stroke control in the axial direction.

As the movable sheave of the primary pulley 11 approaches the fixed sheave to narrow the pulley V groove width, the movable sheave of the secondary pulley 12 is moved away from the fixed sheave to widen the pulley V groove width.
The endless chain link 13 has an increased winding diameter with respect to the primary pulley 11 and a reduced winding diameter with respect to the secondary pulley 12, and the continuously variable transmission mechanism 10 moves toward the highest gear ratio selection state shown in FIG. It can be increased under infinitely variable speed.

Conversely, as the movable sheave of the primary pulley 11 is moved away from the fixed sheave to increase the pulley V groove width, the movable sheave of the secondary pulley 12 is brought closer to the fixed sheave to narrow the pulley V groove width.
The endless chain link 13 has a reduced winding diameter with respect to the primary pulley 11 and an increased winding diameter with respect to the secondary pulley 12, and the continuously variable transmission mechanism 10 is shown in the state from the highest gear ratio selection state shown in FIG. It is possible to downshift under a continuously variable transmission toward a lowest gear ratio selection state not shown.

In order to improve the transmission efficiency of the continuously variable transmission mechanism 10 by suppressing the slip of the endless chain link 13 with respect to the secondary pulley 12 in the state where the highest gear ratio is selected, the central boss of the secondary pulley 12 is shown in FIGS. The portion 16 is provided with a plurality of movable teeth 17 arranged at equal intervals in the circumferential direction so as to protrude from the outer peripheral surface thereof.
These movable teeth 17 are fitted to a cylindrical movable tooth holder 18 fitted to the outer peripheral surface of the secondary pulley central boss portion 16 so as to be able to advance and retreat in the radial direction within a limited range, and by means of elastic means 19 such as a spring, FIG. , 2 is elastically supported at the advancing position protruding radially outward from the movable tooth holder 18.

Provided on the inner edge of each link plate 14 that defines the inner peripheral edge of the endless chain link 13 is a movable tooth engagement groove 14b for engaging the protruding tip of the movable tooth 17 in the winding region with respect to the secondary pulley 12.
By engaging the movable tooth 17 and the movable tooth meshing groove 14b, it is possible to suppress the slip of the endless chain link 13 with respect to the secondary pulley 12 in the highest gear ratio selection state, and to improve the transmission efficiency of the continuously variable transmission mechanism 10. it can.

  Accordingly, when the movable tooth 17 is not aligned with the movable tooth engagement groove 14b and cannot be engaged with the movable tooth engagement groove 14b, the retracted position is pushed into the movable tooth holder 18 by the inner edge of the link plate 14 against the elastic means 19. And can be prevented from being damaged by interference with the endless chain link 13.

<Problems of the above continuously variable transmission mechanism>
However, in the continuously variable transmission mechanism described above, the meshing between the plurality of link plates 14 each having one movable tooth meshing groove 14b and the movable tooth 17 on the outer periphery of the pulley center boss portion 16 occurs at a certain moment. Since the simultaneous meshing shown in FIG. 3 (a) (at a certain phase), the following non-meshing state shown in FIG. 3 (b) exists at the next moment (at the next phase). Such a problem arises.

The leftmost column in FIG. 4 shows how the simultaneous meshing state shown in FIG. 3 (a) and the simultaneous non-meshing state shown in FIG. 3 (b) occur according to the progress of the phase. .
In phase 1, as shown by the symbol “1” in the leftmost column of FIG. 4, all the movable teeth 17 from the first movable tooth to the sixth movable tooth are moved to the movable tooth meshing grooves 14b of the corresponding link plate 14. As shown in FIG.
In the subsequent phases 2 to 20, as shown in the leftmost column in FIG. 4, all the movable teeth 17 from the first movable tooth to the sixth movable tooth are movable gear meshing grooves of the corresponding link plate 14. As shown in FIG. 3 (b) with respect to 14b, a simultaneous non-engagement state is established.

  In this way, when there is a phase that is in the simultaneous meshing state and a phase that is in the simultaneous non-meshing state, the slip between the endless chain link 13 and the secondary pulley 12 is not constant, and stable slip prevention Can not expect.

  Incidentally, the case where the number of movable tooth meshing grooves 14b provided on each link 14 plate is increased from one to a plurality will be considered below.

When the number of movable tooth meshing grooves 14b provided on each link 14 plate is increased to 2, as indicated by the symbol “1” in the second column from the left side of FIG.
In phase 1, all the movable teeth 17 from the first movable teeth to the sixth movable teeth are engaged with the movable teeth meshing grooves 14b of the corresponding link plate 14 as shown in FIG. In addition to
Also in phase 11, all the movable teeth 17 from the first movable tooth to the sixth movable tooth are simultaneously meshed with the movable tooth meshing grooves 14b of the corresponding link plate 14 as shown in FIG. It becomes.

  However, in the other phases 2 to 10 and phases 12 to 20, as shown in the blank in the second column from the left side of FIG. 4, all the movable teeth 17 from the first movable tooth to the sixth movable tooth, As shown in FIG. 3B, the movable tooth meshing grooves 14b of the corresponding link plates 14 are not meshed at the same time and are in a non-meshing state.

When the number of movable tooth meshing grooves 14b provided on each link 14 plate is increased to 3, as indicated by the symbol “1” in the third column from the left side of FIG.
In each of the phases 1, 8, and 15, all the movable teeth 17 from the first movable tooth to the sixth movable tooth mesh with the movable tooth meshing groove 14b of the corresponding link plate 14 as shown in FIG. Will be engaged at the same time,
In the other phases 2 to 7, phase 9 to 14, and phase 16 to 20, all the movable teeth from the first movable tooth to the sixth movable tooth are shown as blank in the third column from the left side of FIG. As shown in FIG. 3 (b), 17 is in a simultaneous non-engagement state as shown in FIG. 3 (b) with respect to the movable tooth engagement groove 14b of the corresponding link plate 14.

When the number of movable tooth meshing grooves 14b provided on each link 14 plate is increased to 4, as shown by the symbol “1” in the fourth column from the left side of FIG.
In each of the phases 1, 6, 11, and 16, all the movable teeth 17 from the first movable tooth to the sixth movable tooth are simultaneously meshed with the movable tooth meshing groove 14b of the corresponding link plate 14. But,
In other phases 2 to 5, phase 7 to 10, phase 12 to 15, and phase 17 to 20, as indicated by a blank in the fourth column from the left side of FIG. 4, from the first movable tooth to the sixth movable tooth All the movable teeth 17 are brought into a simultaneous non-engagement state in which the movable teeth 17 do not mesh with the corresponding movable tooth meshing grooves 14b of the link plate 14.

When the number of movable tooth engagement grooves 14b provided on each link 14 plate is increased to 5, as indicated by the symbol “1” in the fifth column from the left side of FIG.
In the phases 1, 5, 9, 13, and 17, all the movable teeth 17 from the first movable tooth to the sixth movable tooth are simultaneously meshed with the movable tooth meshing groove 14b of the corresponding link plate 14, respectively. But
In the other phases 2 to 4, phase 6 to 8, phase 10 to 12, phase 14 to 16, and phase 18 to 20, as indicated by the blank in the fifth column from the left side of FIG. All the movable teeth 17 up to the six movable teeth are in a non-engagement state at the same time where they do not mesh with the movable tooth meshing grooves 14b of the corresponding link plate 14.

  As is clear from the above, simply increasing the number of movable tooth meshing grooves 14b provided on each link 14 plate without any consideration only increases the probability of simultaneous meshing and does not eliminate the simultaneous non-meshing state. Therefore, it cannot be a radical solution.

<Configuration of Example>
FIG. 5 shows a main part of a continuously variable transmission mechanism according to an embodiment of the present invention. In this embodiment, the continuously variable transmission mechanism is basically configured in the same manner as described above with reference to FIGS. However, the slip prevention mechanism between the secondary pulley central boss portion 16 and the endless chain link 13 is as shown in FIG. 5 in order to make it possible to solve the above problem.
In FIG. 5, parts that function in the same manner as in FIGS. 1 and 2 are denoted by the same reference numerals, and redundant description is avoided.

As in FIGS. 1 and 2, the movable teeth 17 provided in the outer periphery of the secondary pulley central boss portion 16 through the movable tooth holder 18 so as to be able to advance and retract in the radial direction are set at equal intervals in the circumferential direction as a set of 18 in this embodiment. Deploy.
Then, the number and arrangement of the movable tooth engagement grooves 14b provided on the inner edge of each link plate 14 so that the movable teeth 17 are engaged with each other are determined as follows.

  That is, as shown in FIG. 5, the radial lines A1 and A2 connecting the center Op of the link pin insertion hole 14a at both ends of the link plate 14 and the secondary pulley rotation center Os in a state of meshing with the movable tooth 17 (see FIG. 6). ) Is subtracted from the link pitch angle θps, which is the angle between them, as shown in FIG. The movable tooth meshing groove 14b is disposed and provided within the obtained angle range θps−Δθsub (see FIG. 6).

Then, the number Zsub of the movable tooth meshing grooves 14b provided in the angle range θps−Δθsub is determined as follows.
That is, the effective movement of the movable teeth 17 meshing with the movable tooth meshing groove 14b within the pulley wrapping range of the endless chain link 13 shown in FIG. 5 (seven movable teeth from the first tooth to the seventh tooth at the start of meshing) It is movable so that the number of meshing teeth Ze is 1 or more (in FIG. 5, three movable teeth 17 from the first tooth to the third tooth are effective meshing teeth meshing with the movable tooth meshing groove 14b, Ze = 3). The number Zsub of the tooth engagement grooves 14b is determined as Zsub = 4 as clearly shown in FIG.

  Incidentally, the four movable teeth 17 from the fourth tooth to the seventh tooth in the pulley winding range do not mesh with the movable tooth meshing groove 14b, so that the endless chain link 13 moves to the retracted position against the elastic means 19. It is pushed in.

Note that the lagging phase angle Δθsub shown in FIG. 7 defined above is the following when the pressure angle of the movable tooth 17 is α, the height of the movable tooth 17 is h, and the meshing pitch diameter Rp of the movable tooth 17 is Formula Δθsub≡ {sin ⁻¹ [((h × tanα) / 2) / Rp]} × 2 (1)
It is represented by

Further, as described above, the movable tooth meshing groove 14b is provided in the angle range θps−Δθsub (see FIG. 6) obtained by subtracting the delay phase angle Δθsub from the link pitch angle θps, and the number of effective meshing teeth of the movable tooth 17 within the pulley winding range. When only a few Zsubs are provided such that Ze is 1 or more, the sub-pitch angle θsub, which is an angle for one groove, is as shown in the following equation.
θsub = (θps−Δθsub) / Zsub (2)

<Effects of Example>
In the continuously variable transmission mechanism of the above-described embodiment, the movable tooth meshing groove 14b is disposed in the angular range θps−Δθsub, and the number Zsub is determined by the number of the movable teeth 17 in the pulley winding range. Since the number Zsub = 4 so that the number of effective meshing teeth Ze is 1 or more (Ze = 3), the following effects can be obtained.

FIG. 8 shows the case where there is one movable tooth engagement groove 14b provided in each link plate 14 in FIG. 5, two cases, and three cases, as in the present embodiment described above with reference to FIG. In the case of 4 and the case of 5 more than that,
A situation in which the first to sixth teeth of the movable teeth 17 mesh with the movable teeth meshing groove 14b (similar to FIG. 4, the case where the movable teeth 17 are meshed is indicated by the symbol “1”, and the movable teeth 17 mesh. The case where it is not shown is indicated by a blank) according to the progress of the phase.

When there is one movable tooth meshing groove 14b provided on each link plate 14, as shown in FIG. 8 with the symbol “1” in the leftmost column, the first to sixth teeth in phases 1-6. Any one of the movable teeth 17 until is meshed with the corresponding movable tooth meshing groove 14b of the link plate 14,
In the subsequent phases 7 to 20, as indicated by blanks in the leftmost column of FIG. 8, any movable tooth 17 from the first tooth to the sixth tooth is in contact with the movable tooth meshing groove 14b of the corresponding link plate 14. It will be in the non-engagement state which is not meshing.

In the case where there are two movable tooth meshing grooves 14b provided in each link plate 14, as indicated by the symbol "1" in the second row from the left side of FIG. Any one movable tooth 17 from the first tooth to the sixth tooth is engaged with the movable tooth engagement groove 14b of the corresponding link plate 14,
In other phases 7 to 10 and phases 17 to 20, any movable tooth 17 from the first tooth to the sixth tooth is the corresponding link plate 14 as shown in the blank in the second column from the left side of FIG. In this state, the movable tooth meshing groove 14b is not meshed.

When there are three movable tooth meshing grooves 14b provided in each link plate 14, as shown in FIG. 8 with the symbol “1” in the third column from the left side, phase 1-6, phase 8-13, and In the phases 15 to 20, any one of the movable teeth 17 from the first tooth to the sixth tooth is engaged with the movable tooth engagement groove 14b of the corresponding link plate 14,
In other phases 7 and 14, as shown in the blank in the third column from the left side of FIG. 8, any movable tooth 17 from the first tooth to the sixth tooth is engaged with the movable tooth mesh of the corresponding link plate 14. A non-engagement state in which the groove 14b is not meshed is established.

By the way, when there are four or more movable tooth meshing grooves 14b provided on each link plate 14, the fourth and fifth columns from the left side of FIG. Any one of the movable teeth 17 from the first tooth to the sixth tooth meshes with the movable tooth meshing groove 14b of the corresponding link plate 14,
None of the movable teeth 17 from the first tooth to the sixth tooth has a phase in which the movable teeth 17 are not meshed with the movable teeth meshing grooves 14b of the corresponding link plate 14 and are not meshed simultaneously.

Therefore, as in this embodiment, the movable tooth meshing groove 14b is disposed in the angle range θps−Δθsub, and the number Zsub is equal to the number of effective meshing teeth Ze of the movable tooth 17 within the pulley winding range. When the number Zsub = 4 so that (Ze = 3)
Since at least one movable tooth 17 is always meshed with the movable tooth meshing groove 14b, there is no phase that is in a non-engagement state at the same time, which makes it stable between the endless chain link 13 and the secondary pulley. Slip prevention can be realized.

In the illustrated example, the reason why the number of effective meshing teeth Ze of the movable teeth 17 is three is that the required number of effective meshing teeth Ze according to the use condition of the continuously variable transmission mechanism is three,
In this case, even if the torque transmission capacity per tooth of the movable teeth 17 is insufficient with respect to the input torque, the torque to be transmitted can be reliably transmitted by the cooperation of the three movable teeth 17, and each movable tooth 17 The size of the continuously variable transmission mechanism can be reduced by reducing the size of the teeth 17, and nevertheless, the damage and wear of the movable teeth 17 can be reduced and the durability of the continuously variable transmission mechanism can be improved.

<Other examples>
When determining the number Zsub of the movable tooth meshing grooves 14b provided in the angle range θps−Δθsub and the effective meshing tooth number Ze of the movable teeth 17 in the pulley winding range as in the above-described embodiment,
When the number of movable teeth in the pulley wrapping range of the endless chain link 13 is Zf and the number of meshing teeth in each link plate 14 is esub, the following formula
Ze = Zf × esub (3)
esub≡ (Δθsub / θps) × Zsub (4)
So that the effective meshing tooth number Ze of the movable tooth 17 and the movable tooth meshing groove number Zsub within the angular range θps−Δθsub can be determined.

  In this case, it is possible to determine the movable tooth effective meshing tooth number Ze and the movable tooth meshing groove number Zsub so as to obtain the operational effects of the above-described embodiment only by satisfying the above expressions (3) and (4). This is a great advantage, making the design easier.

The number of effective meshing teeth Ze of the movable tooth 17 is not limited to the three in the embodiment, and according to the use condition of the continuously variable transmission mechanism, the effective meshing tooth of the movable tooth 17 if the use condition transmits a large torque. The number of effective meshing teeth Ze of the movable tooth 17 can be reduced to less than 3 if the number Ze is set to 4 or more, or under a use condition in which a small torque is transmitted.
Thus, when the effective meshing tooth number Ze of the movable tooth 17 is adjusted according to the use conditions of the continuously variable transmission mechanism, the effective meshing tooth number Ze of the movable tooth 17 depends on the use conditions of the continuously variable transmission mechanism. Therefore, the cost of the continuously variable transmission mechanism can be reduced while reducing the damage and wear of the movable teeth 17 and improving the durability of the continuously variable transmission mechanism.

Further, in the illustrated example, a slip prevention mechanism (movable teeth 17) is provided between the endless chain link 13 and the secondary pulley 12 in order to prevent slippage between the endless chain link 13 and the secondary pulley 12 in the highest gear ratio selection state. The idea of the present invention was applied to the case where the movable tooth meshing groove 14b) exists,
The present invention also includes a case in which a similar slip prevention mechanism exists between the endless chain link 13 and the primary pulley 11 in order to prevent a slip between the endless chain link 13 and the primary pulley 11 in the lowest speed ratio selection state. It is needless to say that the above-described idea can be applied, and that the same effect as described above can be obtained by this application.

10 Continuously variable transmission mechanism
11 Primary pulley
12 Secondary pulley
13 Endless chain link
14 Link plate
14a Link pin insertion hole
14b Movable tooth engagement groove
15 Link pin
16 Pulley center boss
17 movable teeth
18 Movable tooth holder
19 Elastic means

Claims (3)

It consists of an endless chain link formed by connecting a large number of link plates in a daisy chain with link pins and a pulley around which this endless chain link is wound so as to be continuously variable. In a continuously variable transmission mechanism capable of preventing slipping at a transmission ratio capable of meshing by meshing a movable tooth provided so as to be able to advance and retreat and a movable tooth meshing groove provided on the link plate,
From the link pitch angle θps, which is the angle between the radial lines that connect the center of the link pin insertion hole at both ends of the link plate and the center of the pulley in a state of meshing with the movable tooth, the movable tooth and the movable tooth The movable tooth meshing groove is within an angle range θps−Δθsub obtained by subtracting the delay phase angle Δθsub defined as the mesh contact range with the meshing groove as an angle around the pulley center.
A continuously variable transmission mechanism having a number Zsub of effective meshing teeth Ze of 1 or more of movable teeth meshing with the movable teeth meshing groove within the pulley winding range of the endless chain link. . In the continuously variable transmission mechanism according to claim 1,
When the number of movable teeth in the pulley wrapping range of the endless chain link is Zf and the number of meshing teeth in one link plate is esub, the effective meshing number Ze of the movable teeth and the angle range θps−Δθsub The number of movable tooth meshing grooves Zsub in the
Ze ＝ Zf × esub
esub≡ (Δθsub / θps) × Zsub
Is a continuously variable transmission mechanism characterized in that In the continuously variable transmission mechanism according to claim 1 or 2,
A continuously variable transmission mechanism, wherein the number of effective meshing teeth Ze of the movable teeth is determined to be equal to or greater than a predetermined value according to a use condition of the continuously variable transmission mechanism.

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