MXPA97001102A

MXPA97001102A - Board cardan speed consta

Info

Publication number: MXPA97001102A
Application number: MXPA/A/1997/001102A
Authority: MX
Inventors: Kudo Satoru; Nakao Shouichi; Kawakatsu Tsutomu; Kayano Takeshi; Nagaoka Atsushi
Original assignee: Honda Motor Co Ltd
Priority date: 1996-02-15
Filing date: 1997-02-12
Publication date: 1998-04-01

Abstract

The present invention relates to a constant velocity cardan joint having a cylindrical outer member coupled to a transmission shaft and having its internal circumferential surface, a plurality of guide grooves spaced apart by a predetermined spacing and extending along a axial direction and an internal member coupled to the other transmission shaft and inserted into an internal opening space of the outer member, the constant velocity cardan joint is characterized in that it comprises: a plurality of trunnions, each having a spherical surface and being they expand towards the guide grooves, cylindrical carriers for surrounding the trunnions, with which the roller members displaceable along the guide grooves are externally adjusted, and oil reserve sections disposed in each of the trunnions in a position wherein said stumps make contact with the inner wall surfaces of the p These oil reserve sections extend in a direction substantially perpendicular to an axis of said body.

Description

CARDAN CONSTANT SPEED GASKET BACKGROUND OF THE INVENTION Field of the Invention: The present invention relates to a cardan joint of constant speed, for coupling a transmission shaft and a secondary shaft, which will be used for example, for a transmission section of motive power of an automobile. .

Description of the Related Art: To date a cardan joint of constant speed has been used for a transmission section of motive power of an automobile in order to transmit a rotating driving force or torque of a transmission shaft towards the respective axes, through a secondary tree. This conventional constant speed cardan joint is based, for example, on the technical concepts disclosed in Japanese Public Patent Publications Nos. 4-282028 and 5-215141. In Japanese Patent Laid-open Publication Nos. 4-282028 and 5-215141, where a system comprising a spherical stump in which the stump is surrounded by a cylindrical ring (carrier) was adopted. In this P1057 / 97MX system, a surface of the spherical journal and an inner circumferential surface of the ring are formed to effect a point-to-point contact with each other. However, in the case of a conventional constant speed cardan joint, when the stump is inclined at a predetermined angle with respect to the ring, the stump slides along the inner circumferential surface of the ring while maintaining the state of point to point contact. Namely, the journal moves in a slidable manner along an axial direction or along a direction substantially perpendicular to the axial direction, while maintaining the state of point-to-point contact, at a point with respect to the ring. This sliding displacement of the stump is carried out while maintaining the state of point-to-point contact at one point, scraping or removing an oil film formed by a lubricating oil encased in an outer member. As a result, a disadvantage arises, since the driving force is not smoothly transmitted from a drive shaft to a secondary shaft. On the other hand, when the transmitting force is transmitted from the drive shaft to the secondary shaft while maintaining the state in which the die and the ring make a point-to-point contact in a P1 C 57 / 97MX point, the drive torque is concentrated at the point of contact between the stump and the ring. As a result, the disadvantage arises that the pressing force that is applied to an inner circumferential surface of the ring, to effect the point-to-point contact with the stump, becomes excessively large.

SUMMARY OF THE INVENTION A general objective of the present invention is to provide a constant velocity cardan joint which makes it possible to transmit, in a smoother form, the driving force from a shaft to a secondary shaft, even when the secondary shaft is relatively inclined at a predetermined angle with respect to the drive shaft. A principal object of the present invention is to provide a constant speed cardan joint which makes it possible to limit the pressure force applied to an internal circumferential surface of a carrier. According to the present invention, when a stump is inclined at a predetermined angle with respect to a carrier, lubricant performance is maintained by the aid of an oil reserve section formed between the carrier and the stump. In accordance with the above, a contact portion is protected between a P10 S7 / 97MX stump surface and an internal circumferential surface of the carrier. As a result, the driving force can be transmitted more smoothly or uniformly from a drive shaft to a secondary shaft. In this way, it is possible to obtain a good transmission efficiency. In addition, the force to press the inner circumferential surface of the carrier is dispersed due to the change in the contact portion between the carrier and the stump, to make contact in a point, in two points and in a line segment. In accordance with the above, it is possible to limit or restrict the pressure force. The foregoing objects as well as other objects, features and advantages of the present invention will become more apparent from the following description when taken in conjunction with the accompanying drawings, in which, by way of illustrative example, a preferred embodiment of the invention is shown. present invention.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 shows a vertical cross-sectional view illustrating a cardan joint of speed, constant in accordance with one embodiment of the present invention. P1C57 / 97MX Figure 2 shows a vertical cross-sectional view taken along the line II-II shown in Figure 1. Figure 3 shows an enlarged view with partial omission illustrating a cut formed in a stump to manufacture the constant velocity cardan joint shown in Figure 1. Figure 4 shows a partially omitted cross-sectional view illustrating a state in which the trunnion is inclined at a predetermined angle with respect to a carrier. Figure 5 shows a cross-sectional view, with partial omission, illustrating a state that changed the state shown in Figure 3, in which one axis of the carrier is coincident with a trunnion axis. Figure 6 shows a cross-sectional view, with partial omission, illustrating a state in which the trunnion is inclined at a predetermined angle with respect to the wearer. Figure 7 shows a cross-sectional view, with partial omission, illustrating a state in which the stump is inclined at a predetermined angle with respect to the wearer. Figure 8 shows an explicit illustration to adjust the width of the cut.

P1057 / 97MX Figure 9 shows a partial enlarged view of the stump shown in Figure 8 Figure 10 shows explicitly a relationship between the durability and the gap obtained when changing the width of the cut. Figure 11 shows a perspective view illustrating a modified embodiment of the oil reserve section formed in the stump. Figure 12 shows a perspective view illustrating a modified embodiment of the oil reserve section formed in the stump. Figure 13 shows a perspective view illustrating a modified embodiment of the oil reserve section formed in the stump. Figure 14 explicitly shows a relationship between durability and clearance obtained when changing the width of the cut, in a state in which an increased amount of lubricating oil is enclosed in an external bowl. Figure 15 shows a front view, with partial omission, illustrating a modified embodiment of the section of the oil reservoir formed in the stump. Figure 16 shows a front view, with partial omission, illustrating a modified embodiment of the oil reserve section formed in the stump.

P1057 / 97MX Figure 17 shows a front view, with partial omission, illustrating a modified embodiment of the oil reserve section formed in the stump. Figure 18 shows a front view, with partial omission, illustrating a modified embodiment of the section of oil reservoir formed in the stump. Figure 19 shows a front view, with partial omission, illustrating a modified embodiment of the section of the oil reservoir formed in the stump. Figure 20 shows a front view, with partial omission, illustrating a modified embodiment of the section of the oil reservoir formed in the stump. Figure 21 shows a front view, with partial omission, illustrating a modified embodiment of the section of the oil reservoir formed in the stump. Figure 22 shows a front view, with partial omission, illustrating a modified embodiment of the section of the oil reservoir formed in the stump.

DESCRIPTION OF THE PREFERRED MODALITIES In Figures 1 and 2, the reference number 10 indicates a constant velocity cardan joint, in accordance with an embodiment of the present invention. The constant speed cardan joint 10 of the present invention basically comprises an outer bowl Plr 57 / 17MX cylindrical (outer member) 12 integrally coupled to one end of a drive shaft, not shown, and having an opening and an internal member 16 secured to one end of a secondary shaft 14 and housed in a bowl hole outer 12. Three guide grooves 18a to 18c are formed on an inner circumferential surface of the outer bowl 12. The guide grooves 18a to 18c extend along an axial direction and are separated from each other by an angle of 120 degrees around the center axial, respectively. Each of the guide grooves 18a (18b, 18c) comprises a flat section 20 formed in a substantially central portion, an inclined section 22 formed to be inclined on both sides of the flat section 20, at a predetermined angle, and a surface of bearing 27 formed to be substantially perpendicular to planar section 20, to allow a roll member 24 described later to roll thereon. A section 28 that regulates the end surface, which projects towards the roller member 24 at a predetermined length to adjust the angle of inclination of roll member 24, is formed in a lower portion of the bearing surface 27. A spider 30 in the form of a ring is externally adjusted to the secondary shaft 14. Three trunnions 26a (26b, 26c) that expand towards the guide grooves 18a P1 57 / 97MX (18b, 18c) and which are separated from each other by an angle of 120 degrees around the axial center, respectively, are secured to an outer circumferential surface of the spider 30. Each of the trunnions 26a (26b, 26c) ) is spherical in shape and is surrounded by a cylindrical carrier 32 and a predetermined clearance is interposed between them. The stump 26a (26b, 26c) can be inclined within a predetermined angle with respect to the carrier 32. An oil reserve section, having a predetermined width A and extending along a direction substantially perpendicular to the axis, is form in a portion having the longest circumference in the stump 26a (26b, 26c). The oil reserve section is composed of a cut 34 formed by chamfering the portion having the longest circumference on the surface of the stump 26a (26b, 26c). The cut 34 comprises a circumferential section 36, having a substantially linear cross section, formed by cutting the spherical surface in the circumferential direction and, at both ends of the circumferential section 36, first and second annular flanges 38a, 38b are provided, along its width direction, to form boundaries between the circumferential section 36 and the spherical surface (see Figure 3). In this embodiment, the cut 34 is formed so that a point-to-point contact is made in P1? 7 / 97MX one or at two points or that a line-to-line contact is made with the inner circumferential surface of the carrier 32, as will be described later. An upper end of the carrier 32 is shaped such that the upper end is able to bear against the flat section 20 of the guide groove 18a (18b, 18c) and be spaced from said section. Namely, the upper end of the carrier 32 is located in an ordinary state so that it has a slight clearance with respect to the flat section 20 of the guide groove 18a (18b, 18c). In addition, the upper end of the carrier 32 is shaped to bear against the planar section 20 when the drive shaft or secondary shaft 14 is relatively inclined at a predetermined angle. The roller member 24 is externally adjusted to an outer circumferential section of the carrier 32 by means of a plurality of needle bearings 40. The roller member 24 has its outer circumferential surface with a cross section shaped to be linear correspondingly to the configuration in cross section of the guide groove 18a (18b, 18c). The respective needle bearings 40 and the roller member 24 are held by a ring lock assembly 42a, 42b and washers 44a, 44b fitted to the annular grooves of the carrier 32. It is possible to secure P1057 / 97MX the needle bearings 40 and the roller member 24 using only the ring locks 42a, 42b, without using the washers 44a, 44b. The outer circumferential surface of the roller member 24 makes a line-to-line contact with the bearing surface 27 of the guide groove 18a (18b, 18c). In this way, the roller member 24 is slidable in its axial direction (in a direction indicated by an arrow X in Figure 1). In addition, the roller member 24 can rotate laterally (in a direction indicated by an arrow Y in Figure 2) along the bearing surface 27. The constant speed cardan joint 10 in accordance with the embodiment of the present invention is basically manufactured as described above. Next, the operation, operation and effect of the constant velocity cardan joint 10 will be explained. When the unshown propeller shaft is rotated, its rotating driving force or torque is transmitted to the inner member 16 through the outer bowl 12. In accordance with the above, the secondary shaft 14 rotates in a predetermined direction by means of the trunnions 26a to 26c formed into a spherical configuration.

P1057 / 97MX Namely, the rotating driving force of the outer bowl 12 is transmitted to the roller members 24 which are displaceable along the guide grooves 18a (18b, 18c). The force is further transmitted to the trunnions 26a (26b, 26c) through the carriers 32 held by the roller members 24. In this way, the secondary shaft 14 rotates. In this operation, if the spindle shaft is not illustrated or the secondary shaft 14 is inclined, the roller members 24 roll along the guide grooves 18a to 18c. Accordingly, the rotation speed of the drive shaft is not affected by the angle of inclination of the secondary shaft 14, with respect to the outer bowl 12, and the force is always transmitted to the secondary shaft 14 at a constant rotation speed . Next, Figures 4 to 7 show the change in the state of the trunnion tilt 26a (26b, 26c) at a predetermined angle with respect to the carrier 32. In Figures 4 to 7 it is assumed that the motor torque is applied in a direction substantially perpendicular to the plane of the drawings, from the front to the rear of the drawings. When the stump 26a (26b, 26c) is inclined at a predetermined angle as shown in Figure 4, F1057 / 97MX the inner circumferential surface has the configuration of columns of the carrier 32 and the annular flanges, first and second, 38a, 38b, of the trunnion 26a (26b, 26c) effect a point-to-point contact at two points, of a point ai and a point a2"As a result of the tilt of the trunnion shaft 26a (26b, 26c) at a predetermined angle with respect to the axis of the carrier 32, a state is provided in which the trunnion 26a (26b, 26c) makes the contact point-to-point at two points of the point ai and the point a2"In the state shown in Figure 4 the surface of the trunnion 26a (26b, 26c) does not contact the inner circumferential surface of the carrier 32 in all portions, except for point a and point a2. Therefore, a clearance or set (eg 70μ to 100μ) is formed between the die surface 26a (26b, 26c) and the inner circumferential surface of the carrier 32. Except for the point ai and the point a2. In accordance with the above, the lubricating oil enclosed in the outer bowl 12 enters the slack. As a result, an oil film formed by the lubricating oil between the die surface 26a (26b, 26c) and the inner circumferential surface of the holder 32 is allowed to exist. Thus, the surface of the trunnion 26a (26b, 26c) and the inner circumferential surface of the carrier 32 are P3 57/97 X protected respectively by the oil film. Then, when the stump 26a (26b, 26c) is inclined at a predetermined angle as shown in Figure 5, the axis of the carrier 32 is coincident with the axis of the stump 26a (26b, 26c), providing a state in the that the inner circumferential surface of the carrier 32 and the circumferential section 36 of the stump 26a (26b, 26c) make a line-to-line contact in a line segment b. At this time. The portion making the line-to-line contact is protected by the oil film interposed between the inner circumferential surface of the carrier 32 and the circumferential section 36 of the stump 26a (26b, 26c), in the state shown in Figure 4. will note that the oil film to protect the circumferential section 36 has not been scraped or removed in the state shown in Figure 4, because the circumferential section 36 does not contact the inner circumferential surface of the carrier 32. In the shown state in Figure 5 the surface of the trunnion 26a (26b, 26c) does not contact the internal circumferential surface of the carrier 32, in all portions except the line segment b. Thus, on it there is an oil film that is formed by the lubricating oil that entered the slack. Then, when the stump 26a (26b, 26c) P1057 / 97MX is inclined at a predetermined angle as shown in Figure 6, a state is provided in which the inner circumferential surface of the carrier 32 and the trunnion surface 26a (26b, 26c) effect a point-to-point contact in a point of a point c. Namely, the inner circumferential surface of the carrier 32 and the first annular flange 38a of the stump 26a (26b, 26c) effect point-to-point contact at point c. At this time, the portion making the point-to-point contact is protected by the oil film that has been interposed in the state shown in Figure 5. In the state shown in Figure 6, the carrier 32 does not contact the stump 26a (26b, 26c) in all portions, except for point c. In this way, there is an oil film on it, which is formed by the lubricating oil that has entered the slack. Next, when the stump 26a (26b, 26c) is inclined at a predetermined angle as shown in Figure 7, a state is provided in which the inner circumferential surface of the carrier 32 and the surface of the stump 26a (26b, 26c) ) make a point-to-point contact, at a point of a point d. Namely, the inner circumferential surface of the carrier 32 and the second annular flange 38b of the stump 26a (26b, 26c) effect point-to-point contact at point d. In this P1057 / 97MX moment, the portion making the point-to-point contact is protected by the oil film that has been interposed in the state shown in Figure 6. It should be noted that the oil film to protect the second annular flange 38b does not It is scraped or removed in the state shown in Figure 6, because the second annular rim 38b does not contact the inner circumferential surface of the holder 32. In the state shown in Figure 7, the carrier 32 does not contact the stump 26a (26b, 26c) in all portions, except also for point d. In this way, there is an oil film on it that is formed by the lubricating oil that has entered the slack. As described above, when the stump 26a (26b, 26c) is inclined at a predetermined angle with respect to the carrier 32, the inner circumferential surface of the carrier 32 and the surface of the stump 26a (26b, 26c) undergo the change in state of contact, including the state of point-to-point contact, at the two points (see Figure 4), the state of contact of line to line in line segment b (see Figure 5) and, the state of point-to-point contact (see Figures 6 and 7), wherein the contact portion is protected by the oil film interposed between the surface of the carrier 32 and the internal circumferential surface of the stump 26a (26b, 26c) P1057 / 97MX in response to the present change. As a result, the driving force can be transmitted more smoothly from the drive shaft to the secondary shaft 14 and thus good transmission efficiency can be obtained. Further, the pressing force exerted on the inner circumferential surface of the carrier 32 is dispersed due to the change in the contact portion between the carrier 32 and the trunnion 26a (26b, 26c) to make a contact, at one point, at two points and in a line segment, in this way it is possible to limit the pressure force. Next, the width A of the cut 34 formed in the surface of each of the trunnions 26a (26b, 26c) will be explained (see Figures 8 and 10). At the beginning a circle O is drawn connecting the centers Bi to B3 of the plurality of stubs 26a, 26b, 26c (see Figure 8). A tangential line C that makes contact with the circle O is represented. Next, the dashed lines, first and second D, E, which form angles? A2, respectively, are drawn from the center Bi (B2, B3) of the trunnion 26a (26b, 26c) on the basis of the tangential line C. The intersections between the dashed lines D, E, and the specific surface of the trunnion 26a (26b, 26c) are designated as the rims, first and second, 38a, 38b, respectively. A distance of separation between P1057 / 97MX the first and second flanges 38a, 38b is designated as the width A of the cut 34 (circumferential section 36) (see Figure 9). In this mode, as shown in Figure 10, if each of the angles? I and? 2 is adjusted to be in the range of 1 degree to 1.5 degrees (the sum of the angles? And? 2 is 2 degrees to 3 degrees), the durability of the contact portion deteriorates due to the frictional force generated between the trunnion 26a (26b, 26c) and the carrier 32. According to the foregoing, each of the angles? I and? preferably it is not less than about 2 degrees (the sum of the angles? i to? 2 is not less than about 4 degrees). On the other hand, if each of the angles? I and? 2 is adjusted so that it is not less than 9 degrees (the sum of the angles? I and? 2 is not less than 18 degrees), a gap occurs due to the space formed between the stump 26a (26b, 26c) and the carrier 32. Accordingly, each of the angles? i and? 2 is preferably not greater than about 8 degrees (the sum of the angles? i and? 2 is not greater than about 16 degrees). Therefore, the first and second annular flanges 38a, 38b are formed in a range in which each of the angles? Y ? It has a lower limit of about 2 degrees and an upper limit P10-7 / 97MX of about 8 degrees (the angle formed between the dashed lines, first and second D, E, in a plane that includes tangential line C, is in a range of about 4 degrees to about 16 degrees ). In this way, the width A of the cut 34 (circumferential section 36) is adjusted by the distance of separation between the first and second flanges 38a, 38b. Next, the width A of the cut 34 (circumferential section 36) obtained when the quantity of lubricating oil enclosed in the outer bowl 12 is increased from 10% to 15% compared to an ordinary state will be explained. In this mode, as shown in Figure 14, if each of the angles? I and? 2 is set to be less than 0.5 degree (the sum of the angles? I and? 2 is less than 1 degree), the durability of the contact portion is deteriorated due to the frictional force generated between the trunnion 26a (26b, 26c) and the carrier 32. According to the foregoing, each of the angles? i and? preferably it is not less than about 0.5 degree (the sum of the angles? i and? 2 is not less than about 1 degree). On the other hand, if each of the angles? I and? 2 is adjusted so that it is not less than 9 degrees (the sum of the angles? I and? 2 is not less than 18 degrees), the P1057 / 97MX gap due to the space formed between the stump 26a (26b, 26c) and the carrier 32. In accordance with the above, each of the angles? I and? preferably it is not greater than about 8 degrees (the sum of the angles? i and? 2 is not greater than about 16 degrees). Therefore, when the quantity of lubricating oil enclosed in the outer bowl 12 increases by a predetermined amount, the first and second annular flanges 38a, 38b are formed in a range in which each of the angles? and? 2 has a lower limit of about 0.5 degrees and an upper limit of about 8 degrees (the angle formed between the dashed lines, first and second, D, E, in a plane that includes tangential line C, is in a range of about 1 degrees to about 16 degrees). In this way, the width A of the cut 34 (circumferential section 36) is preferably adjusted by the distance between the first and second flanges 38a, 38b. As described above, the advantage is obtained that the width of the cut 34 (circumferential section 36) can be decreased when the amount of lubricating oil enclosed in the outer bowl 12 is increased by a predetermined amount as compared to an ordinary state.

P1057 / 97MX In this embodiment, the explanation has been made using the cut 34 which extends in the direction substantially perpendicular to the trunnion axis 26a (26b, 26c). However, there is no limitation to it. Alternatively, as shown in Figure 11, a cut 34a that extends along the axis of the stump 26a (26b, 26c) can be provided. In addition, alternatively, as shown in Figure 12, a cut 34b may be provided in which a circular flat section 46 is formed at the transmission point for the driving force. Furthermore, alternatively, instead of the planar section 46, the spherical surface may be formed with a substantially circular recess or with a substantially circular protrusion 48 having a predetermined curvature that exceeds the curvature of the spherical surface (see Figure 13). Other modified embodiments of the oil reserve section formed on the surface of the trunnion 26a (26b, 26c) are shown in Figures 15 to 22. In Figure 15, a helical groove 50 is formed in the circumferential section 36 of the cut. 34 shown in Figure 1. In Figure 16, a sintered alloy 54 is embedded and shaped into an annular groove 52 provided along the spherical surface. In Figure 17, a plurality of P1057 / 97MX irregularities 56 by shot blasting in the circumferential section 33 of the cut 34 shown in Figure 1. In Figure 18, a plurality of linear grooves 58 are formed, so as to be spaced from each other by a predetermined distance along of the circumferential section 36. In this way, it is possible to further improve the lubrication performance. As shown in Figures 19 to 22, the following configurations are also preferred, in each of which the circumferential section 36 which is cut along the spherical surface of the stump 26a (26b, 26c) is not provided. Namely, a helical groove 60 is formed directly on the spherical surface of the stump 26a (26b, 26c) (Figure 19). A sintered alloy 64 is embedded and shaped into an annular groove 62 in the spherical journal 26a (26b, 26c) (Figure 20). A plurality of irregularities 66 are formed by blasting, so as to enclose the spherical stump 26a (26b, 26c) along the circumferential direction (Figure 21). A plurality of linear slots 68 are formed so as to be spaced apart from each other by a predetermined spacing, along the circumferential direction of the spherical surface of the stump 26a (26b, 26c) (Figure 22). In the foregoing, the lubrication performance of the carrier 32 and the stump 26a (26b, 26c) is maintained by the oil of P1057 / 97MX reserved lubrication in the helical groove 60, in the irregularities 66 or in the groove 68 or by the lubricating oil escaping from the sintered alloy. The entire spherical surface or the circumferential section 36 of the trunnion 26a (26b, 26c) can be subjected, for example, to the formation of a molybdenum layer by means of plasma spraying with molybdenum (Mo) or be subjected, for example, to the application of the composite treatment of dispersion coating (for example, a surface is coated with a metal coating solution obtained by dispersing in the same SiN) or a sulfurizing nitriding treatment. In this way, the oil holding property and the shaping capacity of the lubricating oil can be improved. In this embodiment, the cut 34 is formed flat.

However, the cut 34 can be formed as a recess that is concave with respect to the spherical surface. Alternatively, the cut 34 may be formed as a protrusion having a predetermined curvature that exceeds the curvature of the spherical surface. When the cut 34 is formed as a recess, contact with the carrier 32 only includes point-to-point contact at two points.

P1057 / 97MX

Claims

NOVELTY OF THE INVENTION Having described the present invention, it is considered as a novelty and, therefore, the content of the following CLAIMS is claimed as property: 1. A constant speed cardan joint having a cylindrical outer member coupled to a tree of transmission and shaped to have, on its internal circumferential surface, a plurality of guide grooves spaced apart from each other by a predetermined spacing and extending along an axial direction and a member coupled to the other shaft and inserted into a space internal opening of the outer member, the constant speed cardan joint is characterized in that it comprises: a plurality of trunnions, each formed to have a spherical configuration and which expands towards the guide slots; cylindrical carriers for surrounding the trunnions, with which the roller members displaceable along the guide slots are externally adjusted; and oil reserve sections formed in portions having the longest circumference on the spherical surfaces of the trunnions that make contact with P1057 / 97MX the internal wall surfaces of the carriers.
2. The constant speed cardan joint according to claim 1, characterized in that the oil reserve section is composed of a cut formed in the surface of the trunnion and, the cut has a circumferential section, extending in a direction substantially perpendicular to a trunnion shaft, and, first and second annular flanges to form boundaries between the circumferential section and the spherical surface.
The constant speed cardan joint according to claim 2, characterized in that the width of the circumferential section for manufacturing the cut is adjusted in such a way that the dashed lines, first and second, are provided so as to form an angle of approximately 4 degrees to about 16 degrees in a plane that includes a tangential line, which makes contact with a circle, to connect to the centers of the plurality of the stumps; the intersections formed between the spherical surface and the dashed lines, first and second, are designated as first and second annular flanges, respectively, and the width is adjusted by a separation distance between the first and second annular flanges.
4. The constant speed cardan joint according to claim 1, characterized in that the section of P1057 / 97MX oil reserve is composed of a protrusion that has a predetermined curvature that exceeds the curvature of the spherical surface of the stump.
The constant speed cardan joint according to claim 1, characterized in that the oil reserve section is composed of a substantially circular flat section, provided at a point of transmission of motive power in the stump.
The constant speed cardan joint according to claim 1, characterized in that the reserve section is composed along a axis of the trunnion, the cut includes a portion of the portion having the longest circumference of the trunnion and which is substantially perpendicular to the portion that has the longest circumference.
The constant speed cardan joint according to claim 2, characterized in that the circumferential section for manufacturing the cut is provided with a helical groove that surrounds the stump along its circumferential direction.
The constant speed cardan joint according to claim 2, characterized in that the circumferential section for manufacturing the cut is provided with a sintered alloy embedded in an annular groove.
9. The cardan joint of constant speed according to P1057 / 97MX claim 1, characterized in that the circumferential section for manufacturing the cut is provided with a plurality of irregularities.
10. The constant speed cardan joint according to claim 2, characterized in that the circumferential section for manufacturing the cut is provided with a plurality of linear grooves extending substantially parallel to the axis of the trunnion and which are separated from each other by a predetermined spacing along a circumferential direction.
The constant speed cardan joint according to claim 1, characterized in that the oil reserve section is composed of a helical groove formed in the spherical surface of the trunnion, the helical groove surrounds the trunnion along its circumferential direction.
The constant velocity cardan joint according to claim 1, characterized in that the oil reserve section is composed of a sintered alloy, embedded in an annular groove in the spherical surface of the core.
The constant speed cardan joint according to claim 1, characterized in that the oil reserve section is composed of a plurality of irregularities formed on the spherical surface of the P1057 / 97MX stump, the irregularities are provided along a circumferential direction.
The constant velocity cardan joint according to claim 1, characterized in that the oil reserve section is composed of a plurality of linear grooves, formed in the spherical surface of the core, the linear grooves extend substantially parallel to a shaft axis and they are separated from each other by a predetermined spacing along a circumferential direction.
15. The constant speed cardan joint according to claim 1, characterized in that the oil reserve section is composed of a recess formed in the spherical surface of the trunnion. P1057 / 97MX