Toroidal type continuously variable transmission

• US 6,113,513 A
• Filed: 02/03/1998
• Issued: 09/05/2000
• Est. Priority Date: 02/26/1997
• Status: Expired due to Term

• Current Assignee: NSK Limited
• Original Assignee: NSK Limited
• Inventors: Iwahashi, Ryota, Itoh, Hiroyuki, Machida, Hisashi
• Primary Examiner(s): Bucci, David A.
• Assistant Examiner(s): Joyce, William C.
• Application Number:
  US09/017,684
• Time in Patent Office: 945 Days
• Field of Search: 476/9, 476/10, 476/40, 476/41
• US Class Current: 476/10
• CPC Class Codes: F16C 19/163 with angular contact
• CPC Class Codes: F16C 19/547 with two angular contact rolling bearings
• CPC Class Codes: F16C 19/548 in O-arrangement
• CPC Class Codes: F16C 39/04 using hydraulic or pneumatic means
• CPC Class Codes: F16H 15/38 with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
• CPC Class Codes: F16H 61/664 Friction gearings

Abstract

A toroidal type continuously variable transmission improves transmission efficiency. The thrust loads applied to first and second ball-and-roller bearings as a pressing device is actuated are reduced, and the rotational torques of these two ball-and-roller bearings are decreased so as to achieve higher transmission efficiency. When the pressing device is actuated, the inner rings of the first and second ball-and-roller bearings are subjected to thrust loads which act on them to move them toward each other. The thrust loads are reduced by pushing the inner rings in such directions as to move them away from each other by first and second pistons constituting first and second hydraulic cylinders, respectively. Further, a hydraulic force generator is provided between the output bearing and the input bearing; it produces a hydraulic force acting in the opposite direction from that of the reaction force applied to the outer rings of an output bearing and an input bearing, respectively, so as to reduce the thrust loads on the output bearing and the input bearing. A high-pressure oil employed in the hydraulic circuit for speed change control is introduced to the hydraulic force generator.

Claims

1. A toroidal continuously variable transmission comprising:

a transmission housing;

a torque input shaft;

an input disc and an output disc which are supported around said torque input shaft with inner surfaces thereof opposed to each other such that they are free to rotate with respect to said torque input shaft;

a pressuring device which is provided between an outer surface of said input disc and said torque input shaft and which rotates said input disc together with said torque input shaft while pressing said input disc toward said output disc;

a trunnion which rocks about a pivot disposed in a plane which intersects central axes of said input disc and said output disc;

a power roller held between the opposed inner surfaces of said input disc and said output disc while the power roller is rotatably joined to said trunnion;

a first ball-and-roller bearing which is provided between said torque input shaft and a first fixed portion of said transmission housing and which supports a first thrust load applied from said torque input shaft in a direction parallel to said torque input shaft as said pressing device is actuated; and

a second ball-and-roller bearing which is provided between said output disc and a second fixed portion of said transmission housing, and which supports a second thrust load applied from said output disc in a direction opposite from said first thrust load as said pressuring device is actuated;

wherein a hydraulic force generator provided in a position adjacent to said first ball-and-roller bearing and said second ball-and-roller bearing reduces said first thrust load applied to said first ball-and-roller bearing and said second thrust load applied to said second ball-and-roller bearing by;

a hydraulic force in the opposite direction from the direction in which said first thrust load is applied to a first bearing race positioned on the input end of said first thrust load of said first ball-and-roller bearing; and

a hydraulic force in the opposite direction from the direction in which said second thrust load is applied to a second bearing race positioned on the input end of said second thrust load of said second ball-and-roller bearing;

thereby reducing the rotational resistance of said first ball-and-roller bearing and the rotational resistance of said second ball-and-roller bearing;

said hydraulic force in the opposite direction of action of said first thrust load and said hydraulic force in the opposite direction from the action of said second thrust load are respectively generated by an oil supplied into a first cylinder bore and a second cylinder bore through a common oil passage port formed through a third fixed portion of said transmission housing and a cylinder block of said hydraulic force generator;

said first and second ball-and-roller bearings are positioned on one side of said input disc.

2. A toroidal continuously variable transmission according to claim 1, wherein the hydraulic force in the opposite direction from the direction of action of said first thrust load and the hydraulic force in the opposite direction from the direction of action of said second thrust load are respectively smaller than said first thrust load and said second thrust load.

3. The toroidal continuously variable transmission according to claim 1 or 2, wherein a high-pressure oil employed in a hydraulic circuit for speed change control is introduced to said hydraulic force generator and the pressure of the oil introduced to said hydraulic force generator is a line pressure of said hydraulic circuit for speed change control.

4. The toroidal continuously variable transmission according to claim 1 or 2, wherein

a high-pressure oil employed in a hydraulic circuit for speed change control is introduced to said hydraulic force generator and the pressure of the oil introduced to said hydraulic force generator is a line pressure of said hydraulic circuit for speed change control, which line pressure has been adjusted through a pressure regulator.

5. The toroidal continuously variable transmission according to claim 1 or 2, wherein a high-pressure oil employed in a hydraulic circuit for speed change control is introduced to said hydraulic force generator and the pressure of the oil introduced to said hydraulic force generator is a line pressure of said hydraulic circuit for speed change control, the oil having the pressure produced by a high-pressure cylinder subjected to a traction force.

6. The toroidal continuously variable transmission according to claim 1 or 2, wherein a high-pressure oil employed in a hydraulic circuit for speed change control is introduced to said hydraulic force generator and the pressure of the oil introduced to said hydraulic force generator is a line pressure of said hydraulic circuit for speed change control, the oil having a pressure produced by adjusting the pressure of the high-pressure cylinder subjected to a traction force by a pressure regulator.

7. The toroidal continuously variable transmission according to claim 1 or 2, wherein a high-pressure oil employed in a hydraulic circuit for speed change control is introduced to said hydraulic force generator and the pressure of the oil introduced to said hydraulic force generator is a pressure difference between a pressure of a high-pressure cylinder for speed change control which is subjected to a traction force, and a pressure of a low-pressure cylinder for speed change control.

8. The toroidal continuously variable transmission according to claim 1, wherein said hydraulic force generator comprises:

said cylinder block which has said first cylinder bore and said second cylinder bore formed along the torque input shaft so that they are opposed to each other, with a side surface thereof, closer to an outside diameter of said cylinder block, joined to said transmission housing; and

a first piston and a second piston which are respectively fitted in said first cylinder bore and said second cylinder bore;

wherein said first piston and said second piston apply the hydraulic force in the opposite direction from the direction of action of said first thrust load and the hydraulic force in the opposite direction from the direction of action of said second thrust load to said first bearing race and said second bearing race, respectively.

9. The toroidal continuously variable transmission according to claim 8, wherein an outside diameter of said first piston and an outside diameter of said second piston are larger than an outside diameter of said first ball-and-roller bearing and an outside diameter of said second ball-and-roller bearing, respectively.

10. The toroidal continuously variable transmission according to claim 8, wherein a sealing member for providing said oil passage port, said first cylinder bore, and said second cylinder bore with an oil tight barrier is attached to the surface where said cylinder block and said fixed portion are joined.

11. A toroidal continuously variable transmission according to claim 8, wherein:

said first bearing race integrally rotates with said torque input shaft; and

said second bearing race integrally rotates with said output disc.

12. The toroidal continuously variable transmission according to claim 11, wherein said first bearing race and said second bearing race are an inner race of said first ball-and-roller bearing and an inner race of said second ball-and-roller bearing, respectively.

13. The toroidal continuously variable transmission according to claim 12, wherein thrust roller bearings are respectively provided between said inner race of said first ball-and-roller bearing and a piston surface of said first piston, and between said inner race of said second ball-and-roller bearing and a piston surface of said second piston.

14. The toroidal continuously variable transmission according to claim 12, wherein:

said inner race of said first ball-and-roller bearing and said first piston, and said inner race of said second ball-and-roller bearing and said second piston are respectively formed integrally; and

said first piston and said second piston respectively rotate in said first cylinder bore and said second cylinder bore.

15. The toroidal continuously variable transmission according to claim 14, wherein seal rings mounted on an outer peripheral surface and an inner peripheral surface of said first piston, and an outer peripheral surface and an inner peripheral surface of said second piston are nearly frictionless and provide an oil tight barrier.

16. The toroidal continuously variable transmission according to claim 11, wherein said first bearing race and said second bearing race are an outer race of said first ball-and-roller bearing and an outer race of said second ball-and-roller bearing, respectively.

17. The toroidal continuously variable transmission according to claim 16, wherein said outer race of said second ball-and-roller bearing is secured by internally fitting it to a recession formed on an inside diameter portion of said output gear which is joined to said output disc so as to integrally rotate.

18. The toroidal continuously variable transmission according to claim 16, wherein said outer race of said first ball-and-roller bearing is fitted internally and secured by a holder which is integrally formed with an outer peripheral surface of said torque input shaft.

19. The toroidal continuously variable transmission according to claim 16, wherein said outer race of said first ball-and-roller bearing is secured by internally fitting it to a flange member which is jointed to an outer peripheral surface of said torque input shaft.

20. The toroidal continuously variable transmission according to claim 17, wherein the outer race of said first ball-and-roller bearing is fitted internally and secured by a holder which is integrally formed with an outer peripheral surface of said torque input shaft.

21. The toroidal continuously variable transmission according to claim 16, 17, 18, 19 or 20, wherein thrust roller bearings are respectively provided between said outer race of said first ball-and-roller bearing and a piston surface of said first piston, and between said outer race of said second ball-and-roller bearing and a piston surface of said second piston.

22. The toroidal continuously variable transmission according to claim 16, 17, 18, 19 or 20, wherein:

said outer race of said first ball-and-roller bearing and said first piston, and said outer race of said second ball-and-roller bearing and said second piston are respectively formed integrally; and

said first piston and said second piston respectively rotate in said first cylinder bore and said second cylinder bore.

23. The toroidal continuously variable transmission according to claim 22, wherein seal rings mounted on an outer peripheral surface and an inner peripheral surface of said first piston, and an outer peripheral surface and an inner peripheral surface of said second piston are nearly frictionless and provide an oil tight barrier.

24. The toroidal continuously variable transmission according to claim 16, wherein:

a first protuberance and a second protuberance are respectively formed on a piston surface of said first piston and a piston surface of said second piston;

an end surface of said first protuberance and an end surface of said second protuberance respectively provide guiding surfaces of said outer race of said first ball-and-roller bearing and said outer race of said second ball-and-roller bearing, respectively;

said first protuberance provides a collar joint between said first piston and said outer race of said first ball-and-roller bearing so that they rotate integrally; and

said second protuberance provides a collar joint between said second piston and said outer race of said second ball-and-roller bearing so that they rotate integrally.

25. The toroidal continuously variable transmission according to claim 24, wherein:

an outer peripheral surface and an inner peripheral surface of said first piston, and the outer surface and the inner surface of said first cylinder bore in which said piston is fitted, and

an outer peripheral surface and an inner peripheral surface of said second piston, and an outer surface and an inner surface of said second cylinder bore in which said piston is fitted

respectively, form a stepped structure of at least two steps with a predetermined gap provided therebetween.

26. The toroidal continuously variable transmission according to claim 25, wherein said stepped structure formed by said first cylinder bore and said first piston, respectively, is shaped having a larger diameter adjacent to a bottom surface of said first cylinder bore, and a smaller diameter in the direction toward said first piston;

and wherein said stepped structure formed by said second cylinder bore and said second piston, respectively, is shaped having a larger diameter adjacent to a bottom surface of said second cylinder bore, and a smaller diameter in the direction toward said second piston.

27. A toroidal continuously variable transmission according to claim 25, wherein the hardness of said first piston and said second piston is higher than the hardness of said first cylinder bore and said second cylinder bore.

28. The toroidal continuously variable transmission according to claim 25, wherein a low-friction material is coated on:

said outer peripheral surface of said first piston and said outer peripheral surface of said second piston; and

said inner peripheral surface of said first piston and said inner peripheral surface of said second piston.

29. The toroidal continuously variable transmission according to claim 25, wherein a low friction material is coated on;

said outer surface of said first cylinder bore and said outer surface of said second cylinder bore in which said pistons are fitted; and

said inner peripheral surface of said first piston and said inner peripheral surface of said second piston.

30. The toroidal continuously variable transmission according to claim 25, wherein a low friction material is coated on:

said outer peripheral surface of said first piston and said outer peripheral surface of said second piston; and

said inner surface of said first cylinder bore and said inner surface of said second cylinder bore in which said pistons are fitted.

31. The toroidal continuously variable transmission according to claim 25, wherein a low friction material is coated on:

the outer surface of said first cylinder bore and the outer surface of said second cylinder bore in which said pistons are fitted; and

the inner surface of said first cylinder bore and the inner surface of said second cylinder bore in which said pistons are fitted.

32. The toroidal continuously variable transmission according to claim 24, wherein seal rings mounted on an outer peripheral surface and an inner peripheral surface of said first piston, and an outer peripheral surface and an inner peripheral surface of said second piston are nearly frictionless and provide an oil tight barrier.