WO1988009445A1 - Homokinetic transmission system for two axles with centerlines crossing at angles of up to 45 degrees in any direction, maintaining the same velocity of rotation of the two axles - Google Patents

Homokinetic transmission system for two axles with centerlines crossing at angles of up to 45 degrees in any direction, maintaining the same velocity of rotation of the two axles Download PDF

Info

Publication number
WO1988009445A1
WO1988009445A1 PCT/BR1988/000006 BR8800006W WO8809445A1 WO 1988009445 A1 WO1988009445 A1 WO 1988009445A1 BR 8800006 W BR8800006 W BR 8800006W WO 8809445 A1 WO8809445 A1 WO 8809445A1
Authority
WO
WIPO (PCT)
Prior art keywords
axles
centerlines
crossing
angles
degrees
Prior art date
Application number
PCT/BR1988/000006
Other languages
French (fr)
Inventor
Jorge Durval Menezes De Paiva
Jr Raimundo José GARBOGGINI DE PAIVA
Original Assignee
Jorge Durval Menezes De Paiva
Garboggini De Paiva Jr Raimund
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Jorge Durval Menezes De Paiva, Garboggini De Paiva Jr Raimund filed Critical Jorge Durval Menezes De Paiva
Publication of WO1988009445A1 publication Critical patent/WO1988009445A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22309—Details of grooves

Definitions

  • the present system refers to an improved system for torque transmission between two axles whose centerlines can be inclined with respect to each other, incorporating special features which permit high torque transmission capa ⁇ city and constant angular velocity of the two axles.
  • the system uses a bell-shaped outer member fixed to one of the axles and a ball-shaped inner member fixed to the other axle.
  • Six uniformly distributed steel balls, wor ⁇ king within special shaped ball races in the outer and in ⁇ ner transmission members, are used to transfer the torque from the driving axle to the driven axle.
  • a ball cage is mounted between the outer and inner transmiis sion members in such a way that the plane formed by the cen- ters of the six balls always divides the angle formed by the axles in two equal parts.
  • Figure B represents the theoretical arrangement of one of the six balls, shown on an enlarged scale.
  • the arrows PI are representing the forces acting between the inner transmission member (2) and the balls; the arrows P2,the cor responding forces acting between the balls and the outer transmission member (1).
  • Figure B also shows that the lenght of the circular arcs, represented with heavy lines, are par- ticipating in transmitting those forces, due to the fact that in this theoretical arrangement the radius of the ball and the ball races of inner and. outer transmission members are exactly the same.
  • This invention presents a new and improved design for the form of the ball races, solving at the same time the problems due to elastic deformation and also the friction problem caused by the elevated speed and direction differen ⁇ ces and eliminating the reduction of transmitting capacity due to the point contact between balls and elliptical races.
  • the radius of the balls equal to (r).
  • the ball races of the outer member (1) and the in ⁇ ner one (2) are also formed as arcs of a circle with the cor responding lenght (tl) and (t2) and with the radius (r) exac tly the same as the radius of the balls, but their centers are displaced to the right and to the left of the center of the ball to a distance (S) .
  • the balls are in perfect contact with the ball ra ⁇ ces of the outer and the inner transmission member within the lenght (b) , making this contact along the lines of cir ⁇ cular arcs instead of points, as it is in the case with el- liptical races.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

The present invention, homokinetic transmission system for two axles with centerlines crossing at angles of up to 45 degrees in any direction, maintaining the same velocity of rotation of the two axles, refers to an improved system for transmitting very high torques at constant angular speed between the two axles, without causing any kind of frictional wear of the power transmitting elements. This is obtained by the use of the linear contact along the arcs of circles instead of point contact as is usual with elliptical ball races. The system here proposed, using circular arcs for the contact between balls and ball races, is characterized by the fact of using two separate centers fo the two circular arcs at each inner and outer ball race. The widely broken edges of the ball races definitively avoid the possibility of jamming of the ball cage, due to elastic deformations of the power transmitting members of the system.

Description

Description concerning Invention Patent for "HOMO¬ KINETIC TRANSMISSION SYSTEM FOR TWO AXLES WITH CENTERLINES CROSSING AT ANGLES OF UP TO 45 DEGREES IN ANY DIRECTION,MAIN TAINING THE SAME VELOCITY OF ROTATION OF THE TWO AXLES". The present system refers to an improved system for torque transmission between two axles whose centerlines can be inclined with respect to each other, incorporating special features which permit high torque transmission capa¬ city and constant angular velocity of the two axles. The system uses a bell-shaped outer member fixed to one of the axles and a ball-shaped inner member fixed to the other axle. Six uniformly distributed steel balls, wor¬ king within special shaped ball races in the outer and in¬ ner transmission members, are used to transfer the torque from the driving axle to the driven axle.
To guarantee the same angular velocity of the two axles, independent of the angle formed by their centerlines, a ball cage is mounted between the outer and inner transmiis sion members in such a way that the plane formed by the cen- ters of the six balls always divides the angle formed by the axles in two equal parts.
The theoretical arrangement is shown on figure A , with the following meanings: 1: The bell-shaped outer transmission member, fixed to one of the axles;
2: The ball-shaped inner transmission member, fixed to the other axle; 3: The ball cage; 4: The torque transmitting balls.
Figure B represents the theoretical arrangement of one of the six balls, shown on an enlarged scale. The arrows PI are representing the forces acting between the inner transmission member (2) and the balls; the arrows P2,the cor responding forces acting between the balls and the outer transmission member (1). Figure B also shows that the lenght of the circular arcs, represented with heavy lines, are par- ticipating in transmitting those forces, due to the fact that in this theoretical arrangement the radius of the ball and the ball races of inner and. outer transmission members are exactly the same.
In real conditions, all transmitting member suffer elastic deformations, as is demonstrated in exaggerated form in Figure C.
It can be seen in this figure that the elastic de¬ formation (5) and (6) interferes with the ball cage (3), blocking the movement and leading to fast destruction of the cage.
Besides the elastic deformation, it is necessary to consider that the balls rotate during the transmission of forces in the direction indicated by (S) in Figure B.
At the parts of the races which transmit forces (shown in heavy lines), this movement is almost perfectly a rolling movement.
At the parts of the ball races located at right an gle to the direction of (S) (demonstrated with broken lines) substancial differences exists between direction and veloci- ty of balls and races,causing strong frictions not tolerable for normal working conditions.
The known solution, normally used to avoid the con ditions above described,consists in machining the ball races of the inner and the outer transmission members slightly el- liptical, as shown in Figure D.
This solution effectively separates the surface of the balls and the ball races near the cage and forms grease pockets near the regions of high friction, creating in this way good working conditions, as has been demonstrated by inumerable quantities of ball joints manufactured with el- liptical ball races during the last tens of years.
The most important incovenience of elliptically formed ball races is the fact that the forces between races and balls are transmited by point contact only, as can be seen in Figure D and not by line contact as shown in Figure B, reducing for this reason substantially the forces and the torques that can be transmited by the system.
This invention presents a new and improved design for the form of the ball races, solving at the same time the problems due to elastic deformation and also the friction problem caused by the elevated speed and direction differen¬ ces and eliminating the reduction of transmitting capacity due to the point contact between balls and elliptical races.
The new design of the transverse section of the ball races is represented at Figure E, where the system is shown as it appears without transmitting forces.
Shown again are the bell-shaped outer member (1) , the ball-shaped inner member (2), the ball cage (3) and one of the balls (4) .
The radius of the balls equal to (r). The ball races of the outer member (1) and the in¬ ner one (2) are also formed as arcs of a circle with the cor responding lenght (tl) and (t2) and with the radius (r) exac tly the same as the radius of the balls, but their centers are displaced to the right and to the left of the center of the ball to a distance (S) .
It is important to mention that the distance (S) is in reality very small in relation to the radius (r), and that it is represented for better clarity much enlarged in Figure E. The design of the ball races is completed with two recesses (8) and the breaking of the edges (9) at member (l) and (10) at member (2).
Finally, in Figure F the new design of the ball ra ces is represented in working conditions, transmitting tor¬ que in the direction of arrow (11).
The advantages obtained with the new design of the ball races are immediately visible in this figure.
The balls are in perfect contact with the ball ra¬ ces of the outer and the inner transmission member within the lenght (b) , making this contact along the lines of cir¬ cular arcs instead of points, as it is in the case with el- liptical races.
The rotation of the ball in direction the arrow (12) does not give rise to any friction with the rest of the outline of the ball races, not even at one single point, as in the case with elliptical races, eliminating in this way completely the loss of transmission efficiency and the des¬ truction of the balls and races by friction.
The broken edges (9) and (10) avoid the ball cage gets stuck because of the elastic deformation of the ball ra ces.

Claims

1. HOMOKINETIC TRANSMISSION SYSTEM FOR TWO AXLES WITH CENTERLINES CROSSING AT ANGLES OF UP TO 45 DEGREES IN ANY DIRECTION,MAINTAINING THE SAME VELOCITY OF ROTATION OF THE TWO AXLES, characterized by the special and original outline of the transverse section of the ball races which guarantees better performance than any known system.
2. HOMOKINETIC TRANSMISSION SYSTEM FOR TWO AXLES WITH CENTERLINES CROSSING AT ANGLES OF UP TO 45 DEGREES IN ANY DIRECTION,MAINTAINING THE SAME VELOCITY OF ROTATION OF THE TWO AXLES, in accordance with the above claim, charac¬ terized by using ball races at the outer and the inner transmission members whose lines of contact are arcs of circles with exactly the same radius as the radius of the transmitting balls.
3. HOMOKINETIC TRANSMISSION SYSTEM FOR TWO AXLES WITH CENTERLINES CROSSING AT ANGLES OF UP TO 45 DEGREES IN ANY DIRECTION,MAINTAINING THE SAME VELOCITY OF ROTATION OF THE TWO AXLES, in accordance with the above claim, charac- terized by the fact that the contact between balls and ball races are formed by a line in form of an arc of cir¬ cle instead of the point-contact which occurs with ellipti cal shaped ball races.
4. HOMOKINETIC TRANSMISSION SYSTEM FOR TWO AXLES WITH CENTERLINES CROSSING AT ANGLES OF UP TO 45 DEGREES IN
ANY DIRECTION,MAINTAINING THE SAME VELOCITY OF ROTATION OF THE TWO AXLES, in accordance with the above claim, charac¬ terized by the fact that the two arcs of circles of outer and inner ball races with radius equal to the radius of the transmitting balls, have their centers separated by a determined distance to the right and to the left of the center of the ball.
5. HOMOKINETIC TRANSMISSION SYSTEM FOR TWO AXLES WITH CENTERLINES CROSSING AT ANGLES OF UP TO 45 DEGREES IN ANY DIRECTION,MAINTAINING THE SAME VELOCITY OF ROTATION OF THE TWO AXLES, in accordance with the above claim,, charac- terized by the fact the corners of the ball races are wide_ ly broken near their contact points with the ball cage, . thus definitively avoiding the jamming of the cage due to elastic deformations of the transmission members.
6. HOMOKINETIC TRANSMISSION SYSTEM FOR TWO AXLES WITH CENTERLINES CROSSING AT ANGLES OF UP TO 45 DEGREES IN
ANY DIRECTION,MAINTAINING THE SAME VELOCITY OF ROTATION OF THE TWO AXLES, in accordance with the above claim, charac¬ terized by the fact that at working conditions does not exist any sliding contact between balls and transmission members.
7. HOMOKINETIC TRANSMISSION SYSTEM FOR TWO AXLES WITH CENTERLINES CROSSING AT ANGLES OF UP TO 45 DEGREES IN ANY DIRECTION,MAINTAINING THE SAME VELOCITY OF ROTATION OF THE TWO AXLES, in accordance with the above claim, charac- terized by the fact that no frictional wear exits, due to the absense of friction between balls and transmission mem bers.
PCT/BR1988/000006 1987-05-25 1988-05-25 Homokinetic transmission system for two axles with centerlines crossing at angles of up to 45 degrees in any direction, maintaining the same velocity of rotation of the two axles WO1988009445A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
BRPI8702662 1987-05-25
BR8702662A BR8702662A (en) 1987-05-25 1987-05-25 HOMOCINETIC TRANSMISSION SYSTEM FOR MISCELLANEOUS AXLES UP TO 45 DEGREES IN ANY DIRECTION, GUARANTEING THE SAME MOVEMENT IN BOTH AXLES

Publications (1)

Publication Number Publication Date
WO1988009445A1 true WO1988009445A1 (en) 1988-12-01

Family

ID=4042309

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/BR1988/000006 WO1988009445A1 (en) 1987-05-25 1988-05-25 Homokinetic transmission system for two axles with centerlines crossing at angles of up to 45 degrees in any direction, maintaining the same velocity of rotation of the two axles

Country Status (2)

Country Link
BR (1) BR8702662A (en)
WO (1) WO1988009445A1 (en)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5967900A (en) * 1996-12-27 1999-10-19 Ntn Corporation Cross-grove type constant velocity joint
US20110077090A1 (en) * 2009-03-27 2011-03-31 Gm Global Technology Operations, Inc. Constant velocity joint
WO2012010142A3 (en) * 2010-07-10 2012-03-22 Neumayer Tekfor Holding Gmbh Joint
US8235829B2 (en) 2009-03-02 2012-08-07 Steering Solutions Ip Holding Corporation Constant velocity joint
US8246475B2 (en) 2009-03-02 2012-08-21 Steering Solutions Ip Holding Corporation Constant velocity joint
US8323116B2 (en) 2007-12-17 2012-12-04 Steering Solutions Ip Holding Corporation Universal joint
US8348773B2 (en) 2009-03-13 2013-01-08 Steering Solutions Ip Holding Corporation Constant velocity joint and method of making

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU418182B2 (en) * 1966-11-16 1971-10-21 The Bendix Corporation Universal joint
DE2225499B2 (en) * 1971-05-25 1973-09-20 The Toyo Bearing Manufacturing Co., Ltd., Osaka (Japan) Constant velocity swivel
GB1354111A (en) * 1970-05-01 1974-06-05 Gkn Transmissions Ltd Manufacture of constant velocity ratio universal joint and shaft assemblies
DE2433349B1 (en) * 1974-07-11 1975-07-03 Loehr & Bromkamp Gmbh, 6050 Offenbach Constant velocity swivel with ball support in the base of the track
DE2617178A1 (en) * 1975-04-22 1976-11-04 Nissan Motor UNIVERSAL SLIDING JOINT
FR2357779A1 (en) * 1976-07-09 1978-02-03 Skf Ind Trading & Dev FLEXIBLE COUPLING
GB2050567A (en) * 1979-06-01 1981-01-07 Toyota Motor Co Ltd Constant velocity universal joints
DE3209596A1 (en) * 1982-03-17 1983-09-29 Uni-Cardan Ag, 5200 Siegburg CV DRIVE JOINT

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU418182B2 (en) * 1966-11-16 1971-10-21 The Bendix Corporation Universal joint
GB1354111A (en) * 1970-05-01 1974-06-05 Gkn Transmissions Ltd Manufacture of constant velocity ratio universal joint and shaft assemblies
DE2225499B2 (en) * 1971-05-25 1973-09-20 The Toyo Bearing Manufacturing Co., Ltd., Osaka (Japan) Constant velocity swivel
DE2433349B1 (en) * 1974-07-11 1975-07-03 Loehr & Bromkamp Gmbh, 6050 Offenbach Constant velocity swivel with ball support in the base of the track
DE2617178A1 (en) * 1975-04-22 1976-11-04 Nissan Motor UNIVERSAL SLIDING JOINT
FR2357779A1 (en) * 1976-07-09 1978-02-03 Skf Ind Trading & Dev FLEXIBLE COUPLING
GB2050567A (en) * 1979-06-01 1981-01-07 Toyota Motor Co Ltd Constant velocity universal joints
DE3209596A1 (en) * 1982-03-17 1983-09-29 Uni-Cardan Ag, 5200 Siegburg CV DRIVE JOINT

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5967900A (en) * 1996-12-27 1999-10-19 Ntn Corporation Cross-grove type constant velocity joint
US8323116B2 (en) 2007-12-17 2012-12-04 Steering Solutions Ip Holding Corporation Universal joint
US8235829B2 (en) 2009-03-02 2012-08-07 Steering Solutions Ip Holding Corporation Constant velocity joint
US8246475B2 (en) 2009-03-02 2012-08-21 Steering Solutions Ip Holding Corporation Constant velocity joint
US8348773B2 (en) 2009-03-13 2013-01-08 Steering Solutions Ip Holding Corporation Constant velocity joint and method of making
US8925204B2 (en) 2009-03-13 2015-01-06 Steering Solutions Ip Holding Corporation Constant velocity joint and method of making
US20110077090A1 (en) * 2009-03-27 2011-03-31 Gm Global Technology Operations, Inc. Constant velocity joint
US8251828B2 (en) * 2009-03-27 2012-08-28 Steering Solutions Ip Holding Corporation Constant velocity joint
WO2012010142A3 (en) * 2010-07-10 2012-03-22 Neumayer Tekfor Holding Gmbh Joint

Also Published As

Publication number Publication date
BR8702662A (en) 1988-12-13

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