JP2006170340A - V-pulley continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a V-pulley continuously variable transmission with longer-life rolling bearings arranged on an input shaft and an output shaft. <P>SOLUTION: A first rolling bearing 8 arranged on the input shaft 1 outside a first V-pulley 3 and at the side of a first fixed portion 20 (an engine arrangement side) has a shared torque ratio of 0.07 or greater. A second rolling bearing 9 arranged on the input shaft 1 outside the first V-pulley 3 and at the side of a fist movable portion 21 (an opposite engine arrangement side) has a shared torque ratio of 0.08 or greater. A third rolling bearing 10 arranged on the output shaft 2 outside a second V-pulley 4 and at the side of a second fixed portion 22 (the opposite engine arrangement side) has a shared torque ratio of 0.05 or greater. A fourth rolling bearing 11 arranged on the output shaft 2 outside the second V-pulley 4 and at the side of the second movable portion 23 (the engine arrangement side) has a shared torque ratio of 0.09 or greater. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a V-type pulley continuously variable transmission.

  Conventionally, as a V-type pulley continuously variable transmission, there is one described in Japanese Patent Laid-Open No. 2004-11712 (Patent Document 1).

  The V-type pulley continuously variable transmission includes an input shaft, a first V-type pulley fixed to the input shaft, an output shaft, a second V-type pulley fixed to the output shaft, and the first V-type pulley. The belt includes a V-shaped groove, a belt stretched over the V-shaped groove of the second V-shaped pulley, and four rolling bearings.

  The rotational power of the engine is transmitted to the input shaft, and the output shaft is configured to transmit the rotational power to the axle.

  The four rolling bearings include a first rolling bearing and a second rolling bearing arranged on each side of the first V-type pulley on the input shaft, and both sides of the second V-type pulley on the output shaft. The third rolling bearing and the fourth rolling bearing are arranged one by one.

  In the conventional V-type pulley continuously variable transmission, the widths of the V-shaped grooves of the first and second V-type pulleys are appropriately changed, so that the belt can be connected to the first V-type pulley and the second V-type pulley. By moving in the radial direction, the rotational speed of the output shaft is appropriately adjusted.

  As described above, the conventional V-type pulley continuously variable transmission has two rolling bearings on the input shaft and two on the output shaft in order to hold the input shaft and the output shaft at predetermined positions. Rolling bearings are arranged.

  However, the conventional V-type pulley continuously variable transmission has a problem that the life of the four rolling bearings arranged on the input shaft and the output shaft is shorter than the calculated life.

  CVT oil uses low-viscosity oil compared to normal gear oil and other lubricants, and wear powder generated by friction between the belt and the pulley and the second to third axes, the third to fourth axes Wear powder generated by friction at the gear meshing part that transmits torque is generated, so the oil film forming capacity of the bearing rolling part is low, and the life is short compared to the life determined by the bearing load and the rated load of the bearing There are many cases.

  At that time, we want to increase the bearing size in order to increase the rated load of the bearing itself, but the actual situation is that the size cannot be increased due to the demand for compact unit. Therefore, in order to improve the physical strength of the surface of the rolling part against foreign matter, a special heat treatment is applied to any or all of the inner ring, outer ring, and rolling element of the bearing to impart residual compressive stress to the surface, thereby improving the bearing life. .

  However, there are cases in which the bearing life cannot be secured even if such measures are taken. One of the factors is the influence of the shaft rigidity and housing rigidity of the bearing section that supports the pulley, and the load distribution of the bearing section becomes non-uniform, which makes it difficult to design an optimal bearing.

That is, there is a problem that a method for extending the life of the four rolling bearings is not known, and a method for extending the life of the four rolling bearings has not been established.
Japanese Patent Laid-Open No. 2004-11712

  Therefore, an object of the present invention is to provide a V-type pulley continuously variable transmission having a long life of rolling bearings arranged on an input shaft and an output shaft.

In order to solve the above problems, the V-type pulley continuously variable transmission of the present invention is:
An input shaft;
An output shaft arranged parallel to the input shaft;
A first fixed portion fixed to the input shaft; and a first movable portion movable in the axial direction on the input shaft; A first V-shaped pulley in which a groove is formed;
A second fixed portion fixed to the output shaft; and a second movable portion movable in the axial direction on the output shaft. A second V-shaped pulley in which a groove is formed;
A first rolling bearing disposed on the outer side of the first V-type pulley and on the first fixed portion side to support the input shaft and having a first inner ring, a first outer ring, and a first rolling element;
A second rolling bearing that is disposed outside the first V-type pulley and on the first movable portion side to support the input shaft, and includes a second inner ring, a second outer ring, and a second rolling element;
A third rolling bearing disposed outside the second V-type pulley and on the second fixed portion side to support the output shaft and having a third inner ring, a third outer ring, and a third rolling element;
A fourth rolling bearing disposed outside the second V-type pulley and on the second movable part side to support the output shaft and having a fourth inner ring, a fourth outer ring, and a fourth rolling element;
Torque is transmitted between the V-shaped groove of the first V-shaped pulley and the V-shaped groove of the second V-shaped pulley to transmit torque between the first V-shaped pulley and the second V-shaped pulley, and the first V-shaped pulley. And a flexible endless transmission member slidable in the radial direction of the second V-shaped pulley,
Each of the first to fourth rolling bearings has a dynamic load rating of C [kN], each of the first to fourth rolling bearings has an inner diameter of I _d [m], and each of the first to fourth rolling bearings. , The shared torque is S _T , the rolling element coefficient is p in each of the first to fourth rolling bearings, the bearing characteristic coefficient is a ₂ , and the first rolling bearing and the first rolling bearing are each in the first to fourth rolling bearings. The distance between the two rolling bearings is L ₁ [m], the distance between the third rolling bearing and the fourth rolling bearing is L ₂ [m],
Further, the distance from the center of the first V-type pulley to the center of the first rolling bearing is n ₁ [m], and the distance from the center of the first V-type pulley to the center of the second rolling bearing is m ₁ [m. ], The distance from the center of the second V-type pulley to the center of the third rolling bearing is n ₂ [m], and the distance from the center of the _second V-type pulley to the center of the fourth rolling bearing is m ₂ [m when a], the said allotted torque _{S T} of the first rolling bearing _m 1 / _{L 1,} the the allotted torque _{S T n} 1 / _{L 1} of the second rolling bearing, the allotted torque of the third rolling bearing the S _{T m 2} / _L 2, the allotted torque _{S T} of the fourth rolling bearing as _{n 2} / _L 2,
The rolling element coefficient p of each of the first to fourth rolling bearings is 3 when the rolling element is a ball and 10/3 when the rolling element is a roller,
The first to fourth rolling bearing of each of the bearing characteristic coefficient a _2, the inner ring, a case where even special heat treatment to any of the outer ring and the rolling elements are not subjected 1, a special heat treatment to the outer ring and the rolling elements is subjected On the other hand, the case where the inner ring is specially heat treated is 2, the case where the outer ring is not specially heat treated, while the inner ring and rolling element are specially heat treated, 4, the inner ring, outer ring and rolling element. In the case where a special heat treatment is applied,
Share torque ratio STR
When STR = (C × a ₂ ^{1 / p} × I _d ) / (S _T × L),
However, here, L = L _{1 for} the input shaft and L = L ₂ for the output shaft,
The first rolling bearing has a shared torque ratio STR value of 0.07 or more,
The second rolling bearing has a shared torque ratio STR value of 0.08 or more,
The third rolling bearing has a shared torque ratio STR value of 0.05 or more,
The fourth rolling bearing is characterized in that the value of the shared torque ratio STR is 0.09 or more.

  The input shaft and the first fixing portion may be integrally formed, or the input shaft and the first fixing portion that is a separate member may be fixed to the input shaft. Further, the output shaft and the second fixing portion may be integrally formed, or the output shaft and the second fixing portion which is a separate member may be fixed to the output shaft.

  The roller includes a cylindrical roller and a tapered roller.

  The special heat treatment refers to carburizing, nitriding, or carbonitriding.

Further, the distance between the bearings L ₁ between the first rolling bearing and said second rolling bearing, a point on the center axis of the first rolling bearing and the point of the axial center of the first rolling bearing, the It is defined as the distance between the point on the center axis of the two rolling bearing and the center point in the axial direction of the second rolling bearing. Similarly, the distance between the bearings L ₂ between the third rolling bearing and the fourth rolling bearing, the point on the central axis of the third rolling bearing and the point of the center of the axial direction of the third rolling bearing And the point on the central axis of the fourth rolling bearing and the distance from the central point in the axial direction of the fourth rolling bearing.

  The inventor of the present invention, in various types of bearings, the first rolling bearing disposed on the first fixed portion side of the input shaft and the second rolling bearing disposed on the first movable portion side of the input shaft. The shared torque for each of the bearing, the third rolling bearing disposed on the second fixed portion side of the output shaft, and the fourth rolling bearing disposed on the second movable portion side of the output shaft The relationship between the ratio STR and the ratio of the actual life to the calculated life of the first to fourth rolling bearings is examined in detail, and there is a correlation between the shared torque ratio STR and the ratio value. discovered.

  Specifically, when the value of the shared torque ratio STR of the first rolling bearing is smaller than 0.07, the value of the ratio of the first rolling bearing is a small value of 0.2 or less, It has been found that when the value of the shared torque ratio STR of the first rolling bearing is set to 0.07 or more, the value of the ratio of the first rolling bearing is remarkably increased to 1.5 or more.

  When the value of the shared torque ratio STR of the second rolling bearing is smaller than 0.08, the ratio value of the second rolling bearing is a small value of 0.2 or less, while It has been found that when the value of the shared torque ratio STR of the two rolling bearings is set to 0.08 or more, the ratio value of the second rolling bearing is significantly increased to 1.9 or more.

  Further, when the value of the shared torque ratio STR of the third rolling bearing is smaller than 0.05, the ratio value of the third rolling bearing is a small value of 0.2 or less, whereas It has been found that when the value of the shared torque ratio STR of the three rolling bearing is set to 0.05 or more, the value of the ratio of the third rolling bearing is remarkably increased to 1.8 or more.

  When the value of the shared torque ratio STR of the fourth rolling bearing is smaller than 0.09, the ratio value of the fourth rolling bearing is a small value of 0.2 or less, while It has been found that when the value of the shared torque ratio STR of the four rolling bearing is set to 0.09 or more, the value of the ratio of the fourth rolling bearing is significantly increased to 2.0 or more.

  According to the present invention, the value of the shared torque ratio STR of the first rolling bearing is 0.07 or more, the value of the shared torque ratio STR of the second rolling bearing is 0.08 or more, Since the value of the shared torque ratio STR of the three rolling bearings is 0.05 or more and the value of the shared torque ratio STR of the fourth rolling bearing is 0.09 or more, the first to fourth rolling bearings of the first to fourth rolling bearings. The service life can be greatly increased.

The V-type pulley continuously variable transmission of the present invention is
An input shaft;
An output shaft disposed substantially parallel to the input shaft;
A first fixed portion fixed to the input shaft; and a first movable portion movable in the axial direction on the input shaft; A first V-shaped pulley in which a groove is formed;
A second fixed portion fixed to the output shaft; and a second movable portion movable in the axial direction on the output shaft. A second V-shaped pulley in which a groove is formed;
A first rolling bearing that is disposed outside the first V-type pulley and on the rotational power source arrangement side to support the input shaft, and includes a first inner ring, a first outer ring, and a first rolling element;
A second rolling bearing disposed outside the first V-type pulley and on the side opposite to the rotational power source arrangement side to support the input shaft and having a second inner ring, a second outer ring, and a second rolling element;
A third rolling bearing arranged outside the second V-type pulley and on the opposite side of the rotational power source arrangement side to support the output shaft, and having a third inner ring, a third outer ring, and a third rolling element;
A fourth rolling bearing arranged outside the second V-type pulley and on the rotational power source arrangement side to support the output shaft and having a fourth inner ring, a fourth outer ring, and a fourth rolling element;
Torque is transmitted between the V-shaped groove of the first V-shaped pulley and the V-shaped groove of the second V-shaped pulley to transmit torque between the first V-shaped pulley and the second V-shaped pulley, and the first V-shaped pulley. And a flexible endless transmission member slidable in the radial direction of the second V-shaped pulley,
Each of the first to fourth rolling bearings has a dynamic load rating of C [kN], each of the first to fourth rolling bearings has an inner diameter of I _d [m], and each of the first to fourth rolling bearings. , The shared torque is S _T , the rolling element coefficient is p in each of the first to fourth rolling bearings, the bearing characteristic coefficient is a ₂ , and the first rolling bearing and the first rolling bearing are each in the first to fourth rolling bearings. The distance between the two rolling bearings is L ₁ [m], the distance between the third rolling bearing and the fourth rolling bearing is L ₂ [m],
Further, the distance from the center of the first V-type pulley to the center of the first rolling bearing is n ₁ [m], and the distance from the center of the first V-type pulley to the center of the second rolling bearing is m ₁ [m. ], The distance from the center of the second V-type pulley to the center of the third rolling bearing is n ₂ [m], and the distance from the center of the _second V-type pulley to the center of the fourth rolling bearing is m ₂ [m when a], the said allotted torque _{S T} of the first rolling bearing _m 1 / _{L 1,} the the allotted torque _{S T n} 1 / _{L 1} of the second rolling bearing, the allotted torque of the third rolling bearing the S _{T m 2} / _L 2, the allotted torque _{S T} of the fourth rolling bearing as _{n 2} / _L 2,
The rolling element coefficient p of each of the first to fourth rolling bearings is 3 when the rolling element is a ball and 10/3 when the rolling element is a roller,
The first to fourth rolling bearing of each of the bearing characteristic coefficient a _2, the inner ring, a case where even special heat treatment to any of the outer ring and the rolling elements are not subjected 1, a special heat treatment to the outer ring and the rolling elements is subjected On the other hand, when the inner ring is specially heat treated, 2 when the outer ring is not specially heat treated, while when the inner ring and rolling element are specially heat treated, 4, the inner ring, outer ring and rolling element Especially when heat treatment is applied,
Share torque ratio STR
When STR = (C × a ₂ ^{1 / p} × I _d ) / (S _T × L),
However, here, L = L _{1 for} the input shaft and L = L ₂ for the output shaft,
The first rolling bearing has a shared torque ratio STR value of 0.07 or more,
The second rolling bearing has a shared torque ratio STR value of 0.08 or more,
The third rolling bearing has a shared torque ratio STR value of 0.05 or more,
The fourth rolling bearing is characterized in that the value of the shared torque ratio STR is 0.09 or more.

  The input shaft and the first fixing portion may be integrally formed, or the input shaft and the first fixing portion which is a separate member may be fixed to the input shaft. Further, the output shaft and the second fixing portion may be integrally formed, or the output shaft and the second fixing portion which is a separate member may be fixed to the output shaft.

  The roller includes a cylindrical roller and a tapered roller.

  The special heat treatment refers to carburizing, nitriding, or carbonitriding.

Further, the distance between the bearings L ₁ between the first rolling bearing and said second rolling bearing, a point on the center axis of the first rolling bearing and the point of the axial center of the first rolling bearing, the It is defined as the distance between the point on the center axis of the two rolling bearing and the center point in the axial direction of the second rolling bearing. Similarly, the distance between the bearings L ₂ between the third rolling bearing and the fourth rolling bearing, the point on the central axis of the third rolling bearing and the point of the center of the axial direction of the third rolling bearing And the point on the central axis of the fourth rolling bearing and the distance from the central point in the axial direction of the fourth rolling bearing.

  The rotational power source side refers to the side where the rotational power source is arranged with respect to the first V-type pulley or the second V-type pulley. Of course, the rotational power source side is uniquely determined by the spatial arrangement relationship between the first V-type pulley or the second V-type pulley and the rotational power source.

  The inventor of the present invention, in various types of bearings, the first rolling bearing disposed on the rotational power source arrangement side of the input shaft, and the above described disposed on the side opposite to the rotational power source arrangement side of the input shaft. The second rolling bearing, the third rolling bearing arranged on the side opposite to the rotational power source arrangement side of the output shaft, and the fourth rolling bearing arranged on the rotational power source arrangement side of the output shaft. The relationship between the shared torque ratio STR and the ratio of the actual life to the calculated life of the first to fourth rolling bearings is examined in detail, and there is a correlation between the shared torque ratio STR and the ratio value. Found that there is.

  Specifically, when the value of the shared torque ratio STR of the first rolling bearing is smaller than 0.07, the value of the ratio of the first rolling bearing is a small value of 0.2 or less, It has been found that when the value of the shared torque ratio STR of the first rolling bearing is set to 0.07 or more, the value of the ratio of the first rolling bearing is remarkably increased to 1.5 or more.

  When the value of the shared torque ratio STR of the second rolling bearing is smaller than 0.08, the ratio value of the second rolling bearing is a small value of 0.2 or less, while It has been found that when the value of the shared torque ratio STR of the two rolling bearings is set to 0.08 or more, the ratio value of the second rolling bearing is significantly increased to 1.9 or more.

  Further, when the value of the shared torque ratio STR of the third rolling bearing is smaller than 0.05, the ratio value of the third rolling bearing is a small value of 0.2 or less, whereas It has been found that when the value of the shared torque ratio STR of the three rolling bearing is set to 0.05 or more, the value of the ratio of the third rolling bearing is remarkably increased to 1.8 or more.

  When the value of the shared torque ratio STR of the fourth rolling bearing is smaller than 0.09, the ratio value of the fourth rolling bearing is a small value of 0.2 or less, while It has been found that when the value of the shared torque ratio STR of the four rolling bearing is set to 0.09 or more, the value of the ratio of the fourth rolling bearing is significantly increased to 2.0 or more.

  According to the present invention, the value of the shared torque ratio STR of the first rolling bearing is 0.07 or more, the value of the shared torque ratio STR of the second rolling bearing is 0.08 or more, Since the value of the shared torque ratio STR of the three rolling bearings is 0.05 or more and the value of the shared torque ratio STR of the fourth rolling bearing is 0.09 or more, the first to fourth rolling bearings of the first to fourth rolling bearings. The service life can be greatly increased.

  According to the V-type pulley continuously variable transmission of the present invention, the value of the shared torque ratio STR of the first rolling bearing that supports the input shaft and is arranged outside the first V-type pulley and on the first fixed portion side is 0.07 or more, the value of the shared torque ratio STR of the second rolling bearing disposed outside the first V-type pulley and on the first movable part side while supporting the input shaft is 0.08 or more, While supporting the output shaft, the value of the shared torque ratio STR of the third rolling bearing disposed outside the second V-shaped pulley and on the second fixed portion side is 0.05 or more, and supports the output shaft, Since the value of the shared torque ratio STR of the fourth rolling bearing disposed outside the second V-type pulley and on the second movable part side is 0.09 or more, the life of the first to fourth rolling bearings is significantly improved. Can be long.

  Further, according to the V-type pulley continuously variable transmission of the present invention, the value of the shared torque ratio STR of the first rolling bearing that supports the input shaft and is arranged outside the first V-type pulley and on the side of the rotational power source arrangement. Is 0.07 or more, and the value of the shared torque ratio STR of the second rolling bearing disposed outside the first V-type pulley and on the side opposite to the rotational power source is 0.08 or more. And the value of the shared torque ratio STR of the third rolling bearing disposed outside the second V-type pulley and on the side opposite to the rotational power source is 0.05 or more, and supports the output shaft. Since the value of the shared torque ratio STR of the fourth rolling bearing disposed on the outer side of the second V-type pulley and on the rotational power source arrangement side is 0.09 or more, the first to fourth rolling bearings are supported. The service life can be greatly increased.

  Hereinafter, the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a view showing an embodiment of a V-type pulley continuously variable transmission according to the present invention.

  This V-type pulley continuously variable transmission includes an input shaft 1, an output shaft 2, a first V-type pulley 3, a second V-type pulley 4, and a belt 5 as an example of an endless transmission member. In this embodiment, the belt 5 is used as the endless transmission member, but a chain may be used instead of the belt 5 as the endless transmission member.

  Rotational power from an engine as a rotational power source (not shown) is transmitted to the input shaft 1. The output shaft 2 is arranged in parallel with the input shaft 1. In this embodiment, an engine is used as the rotational power source, but an electric motor or the like may be used as the rotational power source.

  The first V-type pulley 3 includes a first fixed portion 20 fixed to the input shaft 1 and a first movable portion 21 that can move in the axial direction on the input shaft 1 in the direction indicated by the arrow α. Yes. A V-shaped groove 25 is formed between the first fixed portion 20 and the first movable portion 21. By appropriately moving the first movable portion 21 on the input shaft 1 in the direction indicated by the arrow α, the width of the V-shaped groove 25 is adjusted to an appropriate value.

  The second V-type pulley 4 includes a second fixed portion 22 fixed to the output shaft 2 and a second movable portion 23 that can move in the axial direction on the output shaft in the direction indicated by the arrow β. . A V-shaped groove 26 is formed between the second fixed portion 22 and the second movable portion 23. The width of the V-shaped groove 26 is adjusted to an appropriate value by appropriately moving the second movable portion 23 on the output shaft 2 in the direction indicated by the arrow β. The V-shaped groove 26 is disposed opposite to the V-shaped groove 25.

  The belt 5 is stretched over the V-shaped groove 25 and the V-shaped groove 26 arranged to face each other, and transmits torque between the first V-type pulley 3 and the second V-type pulley 4. The belt 5 slides in the radial direction of the first V-type pulley 3 and the second V-type pulley 4 when the width of the V-shaped grooves 25 and 26 is changed by the above-described method.

  The V-type pulley continuously variable transmission includes a first rolling bearing 8, a second rolling bearing 9, a third rolling bearing 10, and a fourth rolling bearing 11.

  The first rolling bearing 8 is fixed to the outside of the first V-type pulley 3 on the input shaft 1 and to the first fixing portion 20 side. The first rolling bearing 8 includes a first outer ring (not shown), a first inner ring (not shown), and a first rolling element (figure shown) disposed between the first outer ring and the first inner ring. Not shown).

  The second rolling bearing 9 is fixed to the outside of the first V-type pulley 3 on the input shaft 1 and on the first movable portion 21 side. The second rolling bearing 9 includes a second outer ring (not shown), a second inner ring (not shown), and a second rolling element (figure shown) disposed between the second outer ring and the second inner ring. Not shown).

  The third rolling bearing 10 is fixed to the outside of the second V-type pulley 4 on the output shaft 2 and to the second fixing portion 22 side. The third rolling bearing 10 includes a third outer ring (not shown), a third inner ring (not shown), and a third rolling element (figure shown) disposed between the third outer ring and the third inner ring. Not shown).

  The fourth rolling bearing 11 is fixed to the outside of the second V-type pulley 4 on the output shaft 2 and on the second movable portion 23 side. The fourth rolling bearing 11 includes a fourth outer ring (not shown), a fourth inner ring (not shown), and a fourth rolling element (see FIG. 4) disposed between the fourth outer ring and the fourth inner ring. Not shown).

  As shown in FIG. 1, in the V-type pulley continuously variable transmission of this embodiment, the first fixing portion 20 of the first V-type pulley 3 is arranged on the same side of one of the regions divided into two with the belt 5 as a boundary. And the 2nd movable part 23 of the 2nd V type pulley 4 is arranged. The first movable portion 21 of the first V-type pulley 3 and the second fixed portion 22 of the second V-type pulley 4 are disposed on the same other side of the region divided into two with the belt 5 as a boundary.

  An engine (not shown) is arranged in a region opposite to the first fixed portion 20 side in the first rolling bearing 8 and a region opposite to the second movable portion 23 side in the fourth rolling bearing 11.

  FIG. 2 is a schematic diagram showing an arrangement relationship of the first V-type pulley 3, the first rolling bearing 8, and the second rolling bearing 9 on the input shaft 1.

  In FIG. 2, an arrow 30 indicates the direction and magnitude of the input torque acting on the first V-type pulley 3, and an arrow 31 is assumed that the input torque is shared and supported by the first rolling bearing and the second rolling bearing. In this case, the direction and magnitude of the torque applied to the first rolling bearing 8 are shown, and the arrow 32 indicates the direction and magnitude of the torque applied to the second rolling bearing 9 in the same case. In addition, what is actually supported by these rolling bearings is a radial load resulting from the input torque and is equally supported by the first and second rolling bearings. The torque applied to the rolling bearing is a value obtained by multiplying the radial load supported by each rolling bearing by the radius of rotation of each bearing.

As shown in FIG. 2, the inter-bearing distance between the first rolling bearing 8 and the second rolling bearing 9 is set to L ₁ [m]. The distance between the first V-type pulley 3 and the first rolling bearing 8 is set to n ₁ [m], and the distance between the first V-type pulley 3 and the second rolling bearing 9 is set to m ₁ [m]. Has been.

As shown in FIG. 2, by appropriately setting the above n ₁ and m ₁ , the magnitude of torque applied to the first rolling bearing 8 and the magnitude of torque applied to the second rolling bearing 9 are set to desired values. I am trying to set it.

Although not shown, the distance between the bearings of the third rolling bearing 10 and the fourth rolling bearing 11 on the output shaft 2 is L ₂ [m], similarly to the input shaft 1 shown in FIG. Is set. The distance between the second V-type pulley 4 and the third rolling bearing 8 is set to n ₂ [m], and the distance between the _second V-type pulley 4 and the fourth rolling bearing 9 is set to m ₂ [m]. Has been.

  The first rolling bearing 8 has a sharing torque ratio STR, which will be described in detail below, set to 0.07 or more, and the second rolling bearing 9 has a sharing torque ratio STR set to 0.08 or more. The third rolling bearing 10 has a sharing torque ratio STR set to 0.05 or more, and the fourth rolling bearing 11 has a sharing torque ratio STR set to 0.09 or more.

Here, assuming that the dynamic load rating is C [kN], the inner diameter is I _d [m], the shared torque is S _T , the rolling element coefficient is p, and the bearing characteristic coefficient is a ₂ , the shared torque ratio STR is 1) It is defined by the formula.
STR = (C × a ₂ ^{1 / p} × I _d ) / (S _T × L) (1)

However, here, L = L ₁ for the first and second rolling bearings 8 and 9 set on the input shaft 1, and L = L for the third and fourth rolling bearings 10 and 11 set on the output shaft 2. ₂ .

In the above equation (1),
_M 1 / _{L 1} of the allotted torque _{S T} of the first rolling bearing 8, the allotted torque _{S T} of the second rolling bearing 9 _n 1 / _{L 1,} the allotted torque _{S T} of the third rolling bearing 10 _m 2 / L _2, the allotted torque _{S T} of the fourth rolling bearing 11 is defined as _n 2 / _{L 2.}

  In the first to fourth rolling bearings 8, 9, 10, and 11, the rolling element coefficient p is 3 when the rolling element is a ball and 10/3 when the rolling element is a roller.

In the first to fourth rolling bearing 8, 9, 10, 11, the bearing characteristic coefficient a _2, the inner ring, a case where even special heat treatment to any of the outer ring and the rolling elements are not subjected 1, an outer ring and The case where the rolling element is not specially heat treated while the inner ring is specially heat treated 2. The case where the outer ring is not specially heat treated while the inner ring and rolling element are specially heat treated. 4. The case where the inner ring, the outer ring and the rolling element are subjected to a special heat treatment is defined as 10.

  In the above-described configuration, the V-type pulley continuously variable transmission according to the above embodiment adjusts the width of the V-shaped grooves 25 and 26 so that the belt 5 is moved in the radial direction of the first V-type pulley 3 and the second V-type pulley 4. And the rotational speed of the input shaft 1 rotating by the rotational power from the engine is converted, and the rotational speed of the output shaft 2 is adjusted appropriately.

  The present inventor conducted a durability test of the rolling bearing with respect to various types of V-type pulley continuously variable transmissions with different sharing torque ratios.

  FIG. 3 is a schematic diagram showing a test apparatus used for the durability test.

  As shown in FIG. 3, the test apparatus includes a drive motor 50 and a load absorption dynamo 55.

  The durability test is performed as follows.

  First, the input shaft of the V-type pulley continuously variable transmission, which is the device under test, is connected to the rotating shaft 51 of the drive motor 50 of the test apparatus, and the output shaft of the V-type pulley continuously variable transmission is connected to the test apparatus. The load absorbing dynamo 55 is connected to the rotating shaft 57.

  Next, the drive motor 50 is rotated at a predetermined rotational speed, a predetermined input torque is applied to the V-type pulley continuously variable transmission, the input shaft of the V-type pulley continuously variable transmission is rotated, and there is no V-type pulley. The rotational power output from the output shaft of the step transmission is absorbed by the load absorption dynamo 55.

  Next, in a state where the V-type pulley continuously variable transmission is being operated (in a state where the test is performed), for each of the four rolling bearings installed in the V-type pulley continuously variable transmission, Observe for seizure and abnormal vibration of rolling bearings.

  For each of the four rolling bearings, the time between when the V-type pulley continuously variable transmission was started (time when the test was started) and the time when abnormal vibration occurred was measured, and the measured time was measured for the rolling time. The life of the bearing.

Finally, to calculate the ratio of the real life and the measurement for the calculated life L _h shown below in (2) commonly used among those skilled in the art, the value of the ratio is the reliability of one or more of the rolling bearing On the other hand, it is determined that the rolling bearing is high, and the rolling bearing having the above ratio value smaller than 1 is determined as a rolling bearing having low reliability.
L _h = (C / S _T ) ^p × a ₂ (2)
,

Here, C is dynamic rated weight [kN], S _T is allotted torque which is defined above, a ₂ is the bearing characteristic coefficient defined above, p is is the rolling elements coefficients defined above .

  Table 1 below is a table showing the endurance test results of the first rolling bearing disposed on the outside of the first V-type pulley on the input shaft and on the first fixed portion side (engine arrangement side). FIG. 4 illustrates the results of Table 1.

[Table 1]

  As shown in Table 1, the first rolling bearing of Samples 1, 7, and 12 having a calculated life ratio smaller than 1 and poor in reliability has a shared torque ratio STR value of 0.063 or less. On the other hand, the first rolling bearing of Samples 2, 3, 4, 5, 6, 8, 9, 10, 11, 13 has a very high reliability with a calculated life ratio of 1.5 or more. STR values are all 0.07 or more.

  In addition, as shown in FIG. 4, the calculated life ratio value of the first rolling bearing changes abruptly with the shared torque ratio value of 0.07 as a boundary. Specifically, the first rolling bearing with a shared torque ratio value smaller than 0.07 has a calculated life ratio value of 0.2 or less, while the shared torque ratio value is 0. The first rolling bearing of 0.07 or more has a very large calculated life ratio of 1.5 or more.

  For this reason, when the value of the shared torque ratio of the first rolling bearing is set to 0.07 or more, the life of the first rolling bearing can be significantly increased, and the reliability can be significantly improved.

  Table 2 is a table showing the endurance test results of the second rolling bearing arranged on the outside of the first V-type pulley on the input shaft and on the first movable part side (non-engine arrangement side). FIG. 5 illustrates the results of Table 2.

[Table 2]

  As shown in Table 2, the second rolling bearing of Samples 5 and 10 having a calculated life ratio smaller than 1 and poor in reliability has a value of the shared torque ratio STR of 0.067 or less, The first rolling bearing of Samples 1, 2, 3, 4, 6, 7, 8, 9 has a very high reliability with a calculated life ratio of 1.9 or more, and the value of the shared torque ratio STR is all 0 0.086 or more.

  In addition, as shown in FIG. 5, the calculated life ratio value of the second rolling bearing changes abruptly with the shared torque ratio value of 0.08 as a boundary. Specifically, the second rolling bearing with a shared torque ratio value of less than 0.08 has a calculated life ratio value of 0.2 or less, whereas the shared torque ratio value is 0. The second rolling bearing of 0.08 or more has a very large calculated life ratio of 1.9 or more.

  For this reason, when the value of the shared torque ratio of the second rolling bearing is set to 0.08 or more, the life of the second rolling bearing can be significantly increased, and the reliability can be significantly improved.

  Table 3 is a table showing the endurance test results of the third rolling bearing disposed on the output shaft on the outer side of the second V-type pulley and on the second fixed portion side (non-engine arrangement side). FIG. 6 illustrates the results of Table 3.

[Table 3]

  As shown in Table 3, the third rolling bearing of Samples 5 and 10 having a calculated life ratio smaller than 1 and poor in reliability has a shared torque ratio STR value of 0.037 or less, The third rolling bearing of Samples 1, 2, 3, 4, 6, 7, 8, 9 has an extremely high reliability with a calculated life ratio of 1.8 or more, and the value of the shared torque ratio STR is all 0. 0.056 or more.

  In addition, as shown in FIG. 6, in the third rolling bearing, the value of the calculated life ratio changes abruptly when the value of the shared torque ratio is 0.05. Specifically, the third rolling bearing with a shared torque ratio value less than 0.05 has a calculated life ratio value of 0.2 or less, while the shared torque ratio value is 0. The second rolling bearing of 0.08 or more has a very large calculated life ratio of 1.8 or more.

  For this reason, when the value of the shared torque ratio of the third rolling bearing is set to 0.05 or more, the life of the third rolling bearing can be significantly increased, and the reliability can be significantly improved.

  Table 4 is a table showing the durability test results of the fourth rolling bearing arranged on the output shaft outside the second V-type pulley and on the second movable part side (engine arrangement side). FIG. 7 illustrates the results of Table 4.

[Table 4]

  As shown in Table 4, the fourth rolling bearing of Samples 6 and 8 having a calculated life ratio smaller than 1 and poor in reliability has a shared torque ratio STR value of 0.08 or less, The fourth rolling bearings of Samples 1, 2, 3, 4, 5, 7, and 9 with a very high calculated life ratio of 2.0 or more and very high reliability all share torque ratio STR values of 0.100. That's it.

  In addition, as shown in FIG. 7, in the fourth rolling bearing, the value of the calculated life ratio changes abruptly when the value of the shared torque ratio is 0.09. Specifically, the fourth rolling bearing having a sharing torque ratio value of less than 0.09 has a calculated life ratio value of 0.2 or less, whereas the sharing torque ratio value is 0. The fourth rolling bearing of 0.09 or more has a very large calculated life ratio of 2.0 or more.

  For this reason, when the value of the torque sharing ratio of the fourth rolling bearing is set to 0.09 or more, the life of the fourth rolling bearing can be remarkably increased, and the reliability can be remarkably improved.

  According to the V-type pulley continuously variable transmission of the above embodiment, the value of the shared torque ratio STR of the first rolling bearing 8 disposed on the input shaft 1 on the outer side of the first V-type pulley 3 and on the first fixed portion 20 side. Is 0.07 or more, and the value of the shared torque ratio STR of the second rolling bearing 9 disposed outside the first V-type pulley 3 on the input shaft 1 and on the first movable portion 21 side is 0.08 or more. And the value of the shared torque ratio STR of the third rolling bearing 10 disposed outside the second V-type pulley 4 on the output shaft 2 and on the second fixed portion 22 side is 0.05 or more, and the output shaft 2 Since the value of the shared torque ratio STR of the fourth rolling bearing 11 disposed on the outer side of the second V-type pulley 4 and on the second movable portion 23 side is 0.09 or more, the first to fourth rolling bearings 8 are provided. , 9,10,11 can prevent seizure and rattle, The service life of the fourth to fourth rolling bearings 8, 9, 10, and 11 can be significantly increased, and the reliability of the first to fourth rolling bearings 8, 9, 10, and 11 can be significantly improved. . Therefore, the life and performance of the V-type pulley continuously variable transmission can be significantly improved.

  Further, according to the V-type pulley continuously variable transmission of the above embodiment, the value of the shared torque ratio STR of the first rolling bearing 8 arranged on the input shaft 1 outside the first V-type pulley 3 and on the engine arrangement side is 0.07 or more, and the value of the shared torque ratio STR of the second rolling bearing 9 arranged outside the first V-type pulley 3 on the input shaft 1 and on the side opposite to the engine arrangement is 0.08 or more, The value of the shared torque ratio STR of the third rolling bearing 10 disposed outside the second V-type pulley 4 on the output shaft 2 and on the side opposite to the engine arrangement is 0.05 or more, and the second V-type on the output shaft 2 Since the value of the shared torque ratio STR of the fourth rolling bearing 11 arranged outside the pulley 4 and on the engine arrangement side is 0.09 or more, the seizure of the first to fourth rolling bearings 8, 9, 10, 11 is performed. And can prevent rattling, the first The life of the fourth to fourth rolling bearings 8, 9, 10, and 11 can be significantly increased, and the reliability of the first to fourth rolling bearings 8, 9, 10, and 11 can be significantly improved. . Therefore, the life and performance of the V-type pulley continuously variable transmission can be significantly improved.

It is a figure which shows one Embodiment of the V-type pulley continuously variable transmission of this invention. It is a schematic diagram which shows the arrangement | positioning relationship of the 1st V-type pulley on the input shaft with which the V-type pulley continuously variable transmission of the said embodiment is equipped, a 1st rolling bearing, and a 2nd rolling bearing. It is a schematic diagram which shows the test apparatus used for the durability test of the 1st thru | or 4th rolling bearing. It is a figure which shows the endurance test result of the 1st rolling bearing arrange | positioned on the outer side of the 1st V type | mold pulley in an input shaft, and the 1st fixing | fixed part side (engine arrangement | positioning side). It is a figure which shows the endurance test result of the 2nd rolling bearing arrange | positioned on the outer side of the 1st V type | mold pulley in an input shaft, and the 1st movable part side (anti-engine arrangement | positioning side). It is a figure which shows the endurance test result of the 3rd rolling bearing arrange | positioned on the outer side of the 2nd V type | mold pulley in an output shaft, and the 2nd fixing | fixed part side (anti-engine arrangement | positioning side). It is a figure which shows the endurance test result of the 4th rolling bearing arrange | positioned on the 2nd movable part side (engine arrangement | positioning side) outside the 2nd V type | mold pulley in an output shaft.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Input shaft 2 Output shaft 3 1st V type pulley 4 2nd V type pulley 5 Belt 8 1st rolling bearing 9 2nd rolling bearing 10 3rd rolling bearing 11 4th rolling bearing 20 1st fixed part 21 1st movable part 22 1st 2 fixed part 23 2nd movable part

Claims (2)

An input shaft;
An output shaft arranged parallel to the input shaft;
A first fixed portion fixed to the input shaft; and a first movable portion movable in the axial direction on the input shaft; A first V-shaped pulley in which a groove is formed;
A second fixed portion fixed to the output shaft; and a second movable portion movable in the axial direction on the output shaft. A second V-shaped pulley in which a groove is formed;
A first rolling bearing disposed on the outer side of the first V-type pulley and on the first fixed portion side to support the input shaft and having a first inner ring, a first outer ring, and a first rolling element;
A second rolling bearing that is disposed outside the first V-type pulley and on the first movable portion side to support the input shaft, and includes a second inner ring, a second outer ring, and a second rolling element;
A third rolling bearing disposed outside the second V-type pulley and on the second fixed portion side to support the output shaft and having a third inner ring, a third outer ring, and a third rolling element;
A fourth rolling bearing disposed outside the second V-type pulley and on the second movable part side to support the output shaft and having a fourth inner ring, a fourth outer ring, and a fourth rolling element;
Torque is transmitted between the V-shaped groove of the first V-shaped pulley and the V-shaped groove of the second V-shaped pulley to transmit torque between the first V-shaped pulley and the second V-shaped pulley, and the first V-shaped pulley. And a flexible endless transmission member slidable in the radial direction of the second V-shaped pulley,
Each of the first to fourth rolling bearings has a dynamic load rating of C [kN], each of the first to fourth rolling bearings has an inner diameter of I _d [m], and each of the first to fourth rolling bearings. , The shared torque is S _T , the rolling element coefficient is p in each of the first to fourth rolling bearings, the bearing characteristic coefficient is a ₂ , and the first rolling bearing and the first rolling bearing are each in the first to fourth rolling bearings. The distance between the two rolling bearings is L ₁ [m], the distance between the third rolling bearing and the fourth rolling bearing is L ₂ [m],
Further, the distance from the center of the first V-type pulley to the center of the first rolling bearing is n ₁ [m], and the distance from the center of the first V-type pulley to the center of the second rolling bearing is m ₁ [m. ], The distance from the center of the second V-type pulley to the center of the third rolling bearing is n ₂ [m], and the distance from the center of the _second V-type pulley to the center of the fourth rolling bearing is m ₂ [m when a], the said allotted torque _{S T} of the first rolling bearing _m 1 / _{L 1,} the the allotted torque _{S T n} 1 / _{L 1} of the second rolling bearing, the allotted torque of the third rolling bearing the S _{T m 2} / _L 2, the allotted torque _{S T} of the fourth rolling bearing as _{n 2} / _L 2,
The rolling element coefficient p of each of the first to fourth rolling bearings is 3 when the rolling element is a ball and 10/3 when the rolling element is a roller,
The first to fourth rolling bearing of each of the bearing characteristic coefficient a _2, the inner ring, a case where even special heat treatment to any of the outer ring and the rolling elements are not subjected 1, a special heat treatment to the outer ring and the rolling elements is subjected On the other hand, the case where the inner ring is specially heat treated is 2, the case where the outer ring is not specially heat treated, while the inner ring and the rolling element are specially heat treated, 4, the inner ring, the outer ring and the rolling element. In the case where a special heat treatment is applied,
Share torque ratio STR
When STR = (C × a ₂ ^{1 / p} × I _d ) / (S _T × L),
However, here, L = L _{1 for} the input shaft and L = L ₂ for the output shaft,
The first rolling bearing has a shared torque ratio STR value of 0.07 or more,
The second rolling bearing has a shared torque ratio STR value of 0.08 or more,
The third rolling bearing has a shared torque ratio STR value of 0.05 or more,
The fourth rolling bearing has a shared torque ratio STR value of 0.09 or more, and is a V-type pulley continuously variable transmission. An input shaft;
An output shaft disposed substantially parallel to the input shaft;
A first fixed portion fixed to the input shaft; and a first movable portion movable in the axial direction on the input shaft; A first V-shaped pulley in which a groove is formed;
A second fixed portion fixed to the output shaft; and a second movable portion movable in the axial direction on the output shaft. A second V-shaped pulley in which a groove is formed;
A first rolling bearing that is disposed outside the first V-type pulley and on the rotational power source arrangement side to support the input shaft, and includes a first inner ring, a first outer ring, and a first rolling element;
A second rolling bearing disposed outside the first V-type pulley and on the side opposite to the rotational power source arrangement side to support the input shaft and having a second inner ring, a second outer ring, and a second rolling element;
A third rolling bearing arranged outside the second V-type pulley and on the opposite side of the rotational power source arrangement side to support the output shaft, and having a third inner ring, a third outer ring, and a third rolling element;
A fourth rolling bearing arranged outside the second V-type pulley and on the rotational power source arrangement side to support the output shaft and having a fourth inner ring, a fourth outer ring, and a fourth rolling element;
Torque is transmitted between the V-shaped groove of the first V-type pulley and the V-shaped groove of the second V-type pulley so as to transmit torque between the first V-type pulley and the second V-type pulley, and the first V-type pulley. And a flexible endless transmission member slidable in the radial direction of the second V-shaped pulley,
Each of the first to fourth rolling bearings has a dynamic load rating of C [kN], each of the first to fourth rolling bearings has an inner diameter of I _d [m], and each of the first to fourth rolling bearings. , The shared torque is S _T , the rolling element coefficient is p in each of the first to fourth rolling bearings, the bearing characteristic coefficient is a ₂ , and the first rolling bearing and the first rolling bearing are each in the first to fourth rolling bearings. The distance between the two rolling bearings is L ₁ [m], the distance between the third rolling bearing and the fourth rolling bearing is L ₂ [m],
Further, the distance from the center of the first V-type pulley to the center of the first rolling bearing is n ₁ [m], and the distance from the center of the first V-type pulley to the center of the second rolling bearing is m ₁ [m. ], The distance from the center of the second V-type pulley to the center of the third rolling bearing is n ₂ [m], and the distance from the center of the _second V-type pulley to the center of the fourth rolling bearing is m ₂ [m when a], the said allotted torque _{S T} of the first rolling bearing _m 1 / _{L 1,} the the allotted torque _{S T n} 1 / _{L 1} of the second rolling bearing, the allotted torque of the third rolling bearing the S _{T m 2} / _L 2, the allotted torque _{S T} of the fourth rolling bearing as _{n 2} / _L 2,
The rolling element coefficient p of each of the first to fourth rolling bearings is 3 when the rolling element is a ball and 10/3 when the rolling element is a roller,
The first to fourth rolling bearing of each of the bearing characteristic coefficient a _2, the inner ring, a case where even special heat treatment to any of the outer ring and the rolling elements are not subjected 1, a special heat treatment to the outer ring and the rolling elements is subjected On the other hand, the case where the inner ring is specially heat treated is 2, the case where the outer ring is not specially heat treated, while the inner ring and the rolling element are specially heat treated, 4, the inner ring, the outer ring and the rolling element. In the case where a special heat treatment is applied,
Share torque ratio STR
When STR = (C × a ₂ ^{1 / p} × I _d ) / (S _T × L),
However, here, L = L _{1 for} the input shaft and L = L ₂ for the output shaft,
The first rolling bearing has a shared torque ratio STR value of 0.07 or more,
The second rolling bearing has a shared torque ratio STR value of 0.08 or more,
The third rolling bearing has a shared torque ratio STR value of 0.05 or more,
The fourth rolling bearing has a shared torque ratio STR value of 0.09 or more, and is a V-type pulley continuously variable transmission.

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