Description:DESCRIPTION:
Field of the invention:
[0001] The present disclosure generally relates to the technical field of universal joint for propeller shafts, and in specific relates to a universal joint with a sealing assembly that enhances service life and transfers uniform forces from bearing cup sub assembly through bearing needles.
Background of the invention:
[0002] Universal joints are well-known devices that provide a drive connection between two elements suitable for rotating on unaligned rotation axes. Universal joints are used in propeller shafts which are also called Cardan shafts, to transmit the rotational moment or torque at an angle. Universal joints are assembled between yokes which allow rotary motion at an angle and connect yokes axes that are inclined to each other. A conventional universal joint consists of a cross with four bearing arms angularly projected outward from the center of the cross. Each bearing arm accommodates a bearing cup sub-assembly at their respective positions. A clearance is provided between the cross arm and the bearing cup sub for free rotatory motion between them.

[0003] Conventional universal joints include a pair of bifurcated yokes which are secured to the rotary shafts. The bifurcated yokes are interconnected by a spider or a cruciform for rotation about independent axes. Typically, a bearing cup is secured in each bore and a bearing assembly is retained in the bearing cup such that each yoke is supported for pivotal movement relative to one of the pairs of trunnions.

[0004] A conventional bearing cup sub-assembly comprises a bearing cup, thrust washer, plurality of bearing needles, and multiple seals. The thrust washer is placed at the bearing cup bottom face, the plurality of bearing needles are arranged tangentially in the inner diameter of the bearing cup sub-assembly. One end of the bearing needles is in contact with the thrust washer and at the bearing collar portion, the seals are assembled. However, when a torque is applied, the plurality of bearing needles slide axially at the location and make tangential contact with the cross arm, this is due to a relief provided between the plurality of bearing and the seals. Due to this, the tangentially contacted bearing needles are subjected to more load when compared to other needles.

[0005] In general, when a torque is applied on the cross, the force is transmitted to each cross arm and the bearing cup sub-assembly through the bearing needles. The portion of the cross which is in contact with the bearing needles carries the load. If the torque is constant, then the force exerted on the inner side of the bearing cup assembly is greater than the outer side. Hence the cross arm faces greater force on the outside and less force on the inside. Therefore, the compressive stress in the cross arm outermost end and bearing needles end tend to be substantially higher than those at the center of contact. This stress concentration is known as edge loading which fails in a continuous field application on the shaft.

[0006] The bearing cup sub-assembly consists of seals in between the bearing races and cross arm so that the lubricant is retained in the bearing cup assembly and dirt and foreign particles are excluded from penetrating the same. Typically, elastomeric seals are used to retain lubricant in the region between the outer surface of the trunnion and the inner surface of the bearing cup where the roller bearings are located. Additionally, it is known to provide rigid dust guards about the open ends of the bearing cups to protectively cover the elastomeric seals, and further prevent the entry of dirt and other contaminants into the regions where the roller bearings are located. In some instances, the elastomeric seal and rigid dust guard have been combined into a single seal and dust guard assembly.

[0007] Another “C” shaped seals are used in universal joints, in which the inner part of the seals are engaged with the cross arm and the other end is engaged with the bearing races. The design of “C” shaped seals shows a satisfactory mechanical characteristic. However, due to the accumulation of tolerance and seal lip wear during field application, these seals do not show satisfactory performance. Due to seal lip wear, the C” shaped seals are not able to retain the grease inside the bearing cup assembly which results in high friction in between the rolling elements causing high heat and leading to failure of the universal joints.

[0008] Therefore, the existing sealing system for universal joints fails to the universal joints from outside mud, dirt and dust, thereof. Due to wearing of seal lip the lubrication and grease does not retain inside the bearing cup assembly which results in high friction between the rolling elements causing high heat and results in failure performance of propeller shafts and decreases the life of the a universal joint. Since, the force exerted on the inner side of the bearing cup assembly is greater than the outer side, the cross arm faces greater force on the outside and less force on the inside resulting in higher compressive stress on outmost ends of cross arm bearing needles end. This uneven distribution of stress leads to failure of propeller shafts and decreases the life of the universal joint.

[0009] Therefore, there is a need for a sealing assembly for a universal joint to improve the performance of propeller shafts and to increase the life of the universal joint. There is a need for universal joints in which forces are transferred uniformly over each bearing needle. There is a need for a sealing assembly that protects the universal joint from outside mud, dirt, and dust, thereof.
Objectives of the invention:
[0010] The primary objective of the invention is to provide a sealing assembly for a universal joint in order to improve the performance of propeller shafts and to increase the life of the universal joint.

[0011] The other objective of the invention is to provide a universal joint in which forces are transferred uniformly from each bearing cup sub assembly and through needles.

[0012] Another objective of the invention is to provide a uniform wear on the components of the universal joint to prolong the life of universal joint.

[0013] Another objective of the invention is to provide multiple lips sealing for a universal joint to eliminate sealing failure.

[0014] Another objective of the invention is to provide a multiple lips sealing for a universal joint to prevent leakage of lubrication.

[0015] Another objective of the invention is to introduce a spring ring between needles and seals to forces the needles to be in one position to ensure uniform distribution of forces on the needles on the same plane.

[0016] Another objective of the invention is to provide a sealing assembly for a universal joint in order to protect from outside mud, dirt and dust, thereof.

[0017] Further objective of the invention is to provide a universal joint with proper alignment of the cross arms with a yoke assembly.

[0018] Another objective of the invention is to provide a universal joint with improved resistance towards bending, deflection and thereby reduces heat generation.

[0019] Another objective of the invention is to provide a universal joint that reduces the edge damages of the bearing needles and the cross arm during application.
Summary of the invention:
[0020] The present disclosure proposes a high enduring universal joint with special sealing system. The following presents a simplified summary in order to provide a basic understanding of some aspects of the claimed subject matter. This summary is not an extensive overview. It is not intended to identify key/critical elements or to delineate the scope of the claimed subject matter. Its sole purpose is to present some concepts in a simplified form as a prelude to the more detailed description that is presented later.

[0021] In order to overcome the above deficiencies of the prior art, the present disclosure is to solve the technical problem to provide a universal joint with a sealing assembly to enhance its service life and to transfer uniform forces from bearing cup sub assembly through bearing needles.

[0022] According to an aspect, the invention provides a high enduring universal joint with special sealing system to enhance service life of the universal joint and provide uniform forces. The high enduring universal joint with special sealing system comprises a central cross portion and a hollow cylindrical bearing cup assembly. The central cross portion consists of four orthogonal cross arms that are extending outward from the center of the central cross portion, configured to exert uniform force. Each orthogonal cross arm of the central cross portion is incorporated in a conical profile. An outer arm portion of the orthogonal cross arm facing away from the shoulder of the central cross portion and an inner arm portion of the orthogonal cross arm facing towards the shoulder of the central cross portion. In specific, diameter of the outer arm portion is larger than diameter of the inner arm portion with a difference of 15µ to 20µ in diameters.

[0023] The hollow cylindrical bearing cup assembly is mounted on the outer arm portion of each orthogonal cross arm. The hollow cylindrical bearing cup comprises an outer hollow cup, a plurality of bearing needles, a spring ring, a double lip seal, and a seal guard. The bearing needles are tangentially arranged in inner diameter of the outer hollow cup. A thrust washer is placed in inner diameter of the outer hollow cup which is in contact with one end of the bearing needles. In specific, the each orthogonal cross arm exerts uniform forces on the hollow cylindrical bearing cup assembly through the bearing needles. The spring ring is placed over other end of the bearing needles and is configured to put the bearing needles in one plane. Further, the spring ring ensures the uniform distribution of forces along length of the bearing needles.

[0024] The double lip seal is placed in inner diameter of the outer hollow cup and is configured to maintain a predefined radial force that is exerted by a reinforced sealing lip with a spring around a shaft surface. Outer face of the double lip seal aligns with the outer hollow cup and inner face of the double lip seal presses the spring ring to exert force on the bearing needles to keep them aligned. In specific, the double lip seal includes a case made of metal or other materials with similar properties and the reinforced seal lip with the spring, where the spring like garter spring or any other spring with similar properties is used. The spring with the reinforced seal lip compensates a seal lip wear, maintains the predefined radial force on the shaft diameter, and further ensures lubricant retention in the universal joint. The double lip seal axially forces the spring ring in upward direction to keep the bearing needles aligned in one plane in order to distribute force uniformly on the bearing needles.

[0025] The seal guard comprises with a sheet metal on outer surface and is configured to protect the double lip seal from dust particles. A resilient elastomeric portion of the seal guard is positioned in the inner periphery of the sheet metal, wherein one end of the seal guard is fixed to diameter of the outer arm portion. In specific, a space of 0.02 to 0.4 mm is maintained between inner surface the seal guard and surface the hollow cylindrical bearing cup assembly. The seal guard includes a seal lip that is positioned in inner periphery of the seal guard. An outer end of the seal lip forms an angular shape with respect to race of the hollow cylindrical bearing cup assembly to provide flexibility.

[0026] Further, objects and advantages of the present invention will be apparent from a study of the following portion of the specification, the claims, and the attached drawings.
Detailed description of drawings:
[0027] The accompanying drawings, which are incorporated in and constitute a part of the specification, illustrate an embodiment of the invention, and, together with the description, explain the principles of the invention.

[0028] FIG. 1A illustrates an exemplary schematic diagram of a high enduring universal joint with special sealing system in accordance with an exemplary embodiment of the invention.

[0029] FIG. 1B illustrates an exemplary exploded view of a universal joint in accordance with an exemplary embodiment of the invention.

[0030] FIG. 2 illustrates an exemplary enlarged section view of conical profile of an orthogonal cross arm in accordance with an exemplary embodiment of the invention.

[0031] FIG. 3A illustrates an exemplary enlarged view of a hollow cylindrical bearing cup assembly in accordance with an exemplary embodiment of the invention.

[0032] FIG. 3B illustrates an exemplary exploded view the hollow cylindrical bearing cup assembly in accordance with an exemplary embodiment of the invention.

[0033] FIG. 4 illustrates an exemplary enlarged section view of a double lip seal in accordance with an exemplary embodiment of the invention.

[0034] FIG. 5A illustrates an exemplary enlarged section view of a seal guard in accordance with an exemplary embodiment of the invention.

[0035] FIG. 5B illustrates an exemplary cross-sectional view of the seal guard in accordance with an exemplary embodiment of the invention.

[0036] FIG. 6A illustrates an exemplary cross-sectional view the universal joint in accordance with an exemplary embodiment of the invention.

[0037] FIG. 6B illustrates an exemplary enlarged section view of the universal joint for needles assembly in accordance with an exemplary embodiment of the invention.

[0038] FIG. 6C illustrates an exemplary enlarged section view of the universal joint for sealing assembly in accordance with an exemplary embodiment of the invention.
Detailed invention disclosure:
[0039] Various embodiments of the present invention will be described in reference to the accompanying drawings. Wherever possible, same or similar reference numerals are used in the drawings and the description to refer to the same or like parts or steps.

[0040] The present disclosure has been made with a view towards solving the problem with the prior art described above, and it is an object of the present invention to provide a high enduring universal joint with special sealing system to enhance its service life and to transfer uniform forces from bearing cup sub assembly through bearing needles.

[0041] According to an exemplary embodiment of the invention, FIG. 1A and FIG. 1B refer to different views of a universal joint 100 with bearing cup seal assembly. The universal joint 100 is connected to a pair of Yokes whose rotation axes are inclined with each other. The universal joint 100 with bearing cup seal assembly comprises a central cross portion 102 and a hollow cylindrical bearing cup assembly 104. The central cross portion 102 consists of four orthogonal cross arms 106 that are extending outward from the center of the central cross portion 102 is configured to exert uniform force. Each orthogonal cross arm 106 is incorporated in a conical profile. An outer arm portion of the orthogonal cross arm 106 facing away from the shoulder of the central cross portion 102 and an inner arm portion of the orthogonal cross arm 106 facing toward the shoulder of the central cross portion 102. In specific, diameter of the outer arm portion is larger than diameter of the inner arm portion with a difference of 15µ to 20µ in diameters.

[0042] The hollow cylindrical bearing cup assembly 104 is mounted on the outer arm portion of each orthogonal cross arm 106. The hollow cylindrical bearing cup 104 comprises an outer hollow cup (not shown), plurality of bearing needles (not shown), a spring ring (not shown), a double lip seal (not shown), and a seal guard (not shown). The bearing needles are tangentially arranged in inner diameter of the outer hollow cup. A thrust washer (not shown) is placed in inner diameter of the outer hollow cup which is in contact with one end of the bearing needles. In specific, the each orthogonal cross arm exerts uniform forces on the hollow cylindrical bearing cup assembly through the bearing needles. The spring ring is placed over other end of the bearing needles and is configured to put the bearing needles in one plane. Further, the spring ring ensures the uniform distribution of forces along length of the bearing needles.

[0043] The double lip seal is placed in inner diameter of the outer hollow cup and is configured to maintain a predefined radial force that is exerted by a reinforced sealing lip with a spring around a shaft surface. Outer face of the double lip seal aligns with the outer hollow cup and inner face of the double lip seal presses the spring ring to exert force on the bearing needles to keep them aligned. In specific, the double lip seal includes a case made of metal or materials with similar properties and the reinforced seal lip with the spring, where the spring like garter spring or thereof is used. The spring with the reinforced seal lip compensates a seal lip wear and the predefined radial force of more than 11 N is maintained on the shaft diameter, and further ensures lubricant retention in the universal joint. The double lip seal axially forces the spring ring in upward direction to keep the bearing needles aligned in one plane in order to distribute force uniformly on the bearing needles.

[0044] The seal guard comprises with a sheet metal on outer surface and is configured to protect the double lip seal from dust particles. A resilient elastomeric portion of the seal guard is positioned in the inner periphery of the sheet metal, wherein one end of the seal guard is fixed to diameter of the outer arm portion. In specific, a space of 0.02 to 0.4 mm is maintained between inner surface of the seal guard and surface of the hollow cylindrical bearing cup assembly. The seal guard includes a seal lip that is positioned in inner periphery of the seal guard. In specific, the double lip seal in assembled condition restricts the flow path of the grease to come out. Further, a space created in between the sealing surface and the double lip seal engagement point acts as reservoir for grease during application.

[0045] An outer end of the seal lip forms an angular shape with respect to race of the hollow cylindrical bearing cup assembly to provide flexibility. In specific, the outer end of the seal lip is rotatable and is engaged with the hollow cylindrical bearing cup assembly 104 and the orthogonal cross arm 106.

[0046] Further, during rotation of the yokes, a torque is applied on the central cross portion 102 that is transmitted over the four orthogonal cross arms 106 and the hollow cylindrical bearing cup assembly 104 by the means of the bearing needles. Circlips are symmetrically placed on yokes next to the hollow cylindrical bearing cup assembly 104 back faced to make the central cross portion 102 symmetric with Yoke Center.

[0047] According to another exemplary embodiment of the invention, FIG. 2 refers to an enlarged section view of conical profile of the orthogonal cross arm 200. Each orthogonal cross arm 200 of the universal joint is incorporated in a conical profile or a uniform taper profile. The conical profile starts at the outer arm portion 202 and ends at the inner arm portion 204 of the orthogonal cross arm 200. The difference in diameter of the outer arm portion 202 and the inner arm portion inner arm portion 204 lies from 15µ to 20µ. The larger diameter lies towards the orthogonal cross arm shoulder. The uniform taper profile of the orthogonal cross arm 200 ensures the alignment of the central cross portion with the yokes center during the application. Further, the uniform taper profile on the orthogonal cross arm 200 provides effective resistance towards bending and deflection during the application. For proper function and satisfactory life of the universal joint, the central cross portion accurately aligns with the axis of rotation of the yokes and thereby minimizes the unbalanced centrifugal forces that create undesirable vibration.

[0048] During torque application, the orthogonal cross arm 200 exerts forces on the hollow cylindrical bearing cup assembly by means of the bearing needles. The orthogonal cross arm 200 at the orthogonal cross arm 200 end exerts force on the bearing needles, which is situated at the outer hollow cup of the hollow cylindrical bearing cup assembly. Further, the uniform taper profile of the orthogonal cross arm 200 reduces the frictional contact area in between the outer arm portion 202 and the inner arm portion 204 with the bearing needles, which leads to the reduction in the high heat generation. The uniform taper profile ensures the uniform distribution of forces along the bearing needles and in the orthogonal cross arm 200.

[0049] The garter spring on the seal guard compensate the seal lip wear and the predefined radial force on the shaft diameter 206 is maintained. For sealing with double lip seal a sealing diameter is created on the orthogonal cross arm 200 after the needle engaging diameter. The garter spring with reinforced seal lip maintains the predefined radial force at about 11 N on the shaft diameter 206 and ensures the lubricant retention in the universal joint.

[0050] According to another exemplary embodiment of the invention, FIG. 3A and FIG. 3B refer to different views of the hollow cylindrical bearing cup assembly 300. The hollow cylindrical bearing cup 300 comprises the outer hollow cup 302, the bearing needles 304, the spring ring 308, the double lip seal 310, and the seal guard 312. The bearing needles 304 are tangentially arranged in inner diameter of the outer hollow cup 302. A thrust washer 306 is placed in inner diameter of the outer hollow cup 302, which is in contact with one end of the bearing needles 304. The spring ring 308 is placed over other end of the bearing needles 304 and is configured to put the bearing needles 304 in one plane. Further, the spring ring 308 ensures the uniform distribution of forces along length of the bearing needles 304.

[0051] In specific, the inner diameter and outer diameter of spring ring 308 have clearance with the diameter of cross-arm and inner diameter of hollow cylindrical bearing cup assembly 300 respectively. During fitment, the spring ring 308 is placed after the bearing needles 304. The double lip seal 310 forces the spring ring 308 axially in upward direction. This helps to keep the bearing needles 304 aligned in one plane so that the forces to be uniformly distributed over the bearing needles 304.

[0052] The double lip seal 310 is placed in inner diameter of the outer hollow cup 302 and is configured to maintain the predefined radial force that is exerted by the reinforced sealing lip (not shown) with the spring (not shown) around the shaft surface(not shown). Outer face of the double lip seal 310 aligns with the outer hollow cup 302 and inner face of the double lip seal 310 presses the spring ring 308 to exert force on the bearing needles 304 to keep them aligned. In specific, the double lip seal 310 includes a case made of metal or other materials with similar properties and the reinforced seal lip with the spring, where the spring like garter spring or thereof is used.

[0053] The seal guard 312 comprises with a sheet metal on outer surface and is configured to protect the double lip seal 310 from dust particles. A resilient elastomeric portion of the seal guard is positioned in the inner periphery of the sheet metal, wherein one end of the seal guard 312 is fixed to diameter of the outer arm portion. In specific, a space of 0.05 to 0.1 mm is maintained between inner surface the seal guard 312 and surface the hollow cylindrical bearing cup assembly 300. The seal guard 312 includes a seal lip that is positioned in inner periphery of the seal guard 312. An outer end of the seal lip forms an angular shape with respect to race of the hollow cylindrical bearing cup assembly 300 to provide flexibility.

[0054] According to another exemplary embodiment of the invention, FIG. 4 refers to an enlarged section view of double lip seal 400. In the proposed universal joint, for sealing, a double lip seal 400 is used, that is fitted in inner diameter of the hollow cylindrical bearing cup assembly. The double lip seal 400 consists of metal case 402 on its outer diameter and reinforced sealing lip 404 with the garter spring. The metal case is made of any other material with all required properties similar to metal such as, a stainless steel, alloy steel, and aluminum, thereof. The garter spring disclosed in the embodiment is not confined only for garter spring any other spring with similar functional properties can also be considered. The double lip seal 400 is pressed fit with the hollow cylindrical bearing cup assembly. The metal case 402 on the outer diameter of the double lip seal 400 provides proper alignment of seal with the hollow cylindrical bearing cup assembly. For sealing with the double lip seal 400, a sealing diameter is created on the orthogonal cross arm after the needle engaging diameter.

[0055] According to another exemplary embodiment of the invention, FIG. 5A and FIG. 5B refers to different views of the seal guard 500. The seal guard 500 comprises with a sheet metal 502 on outer surface and is configured to protect the double lip seal from dust particles. A resilient elastomeric portion 504 of the seal guard 500 is positioned in the inner periphery of the sheet metal 502, wherein one end of the seal guard 500 is fixed to diameter of the outer arm portion. In specific, a space of 0.05 to 0.1 mm is maintained between inner surface the seal guard 500 and surface the hollow cylindrical bearing cup assembly. The seal guard 500 includes a seal lip that is positioned in inner periphery of the seal guard 500. An outer end of the seal lip 506 forms an angular shape with respect to race of the hollow cylindrical bearing cup assembly to provide flexibility.

[0056] In specific, a stepped cross sectional annular metallic insert 502 (the sheet metal) is provided on the outer periphery of the seal guard 500. The thickness of the resilient elastomeric portion 504 of the seal guard 500 is maintained in such a way that when the hollow cylindrical bearing cup assembly is assembled on the orthogonal cross arms during an yokes assembly, the resilient elastomeric portion of seal lip 506 is compressed between the races of the hollow cylindrical bearing cup assembly and the stepped cross sectional annular metallic insert 502. Further, a face of the hollow cylindrical bearing cup assembly is not pressurized by horizontal face 508 of the seal guard to ensure satisfactory sealing.

[0057] The stepped cross sectional annular metallic insert is molded with the resilient elastomeric material. The stepped cross sectional annular metallic insert 502 is placed in such a way that it covers the seal lip 506 profiles of the seal guard 500. The inner seal lip profile 506 of the seal guard 500 engages the seal lip of the inner Seal. The inner fitment diameter 510 have undulated protrusions for effective fitment with the orthogonal cross arm. A suitable corrosion protection is provided on the metal insert 502 to protect from rust. The upper part of seal guard 500 near to seal lip 506 provided a relief with the bearing cup groove wall face.

[0058] According to another exemplary embodiment of the invention, FIG. 6A, FIG. 6B and FIG. 6C refer to different section views of the universal joint 600. The conical profile incorporated in cross arm indicated as the outer arm portion 608 and the inner arm portion 610. The conical profile starts with radius of the outer arm portion 608 and ends at the radius of the inner arm portion 610 position toward cross arm shoulder. The difference in diameter lies from 15µ to 20µ. The bigger diameter lies towards cross arm shoulder. The one end of bearing needles 612 is rested over thrust washer 616.

[0059] During torque application, the orthogonal cross arm exerts forces on the bearing cup sub assembly by means of bearing needles 612. So, being tapered cylindrical profile, the inner arm portion 610 of the orthogonal cross arm at second radius exert force on the bearing needles 612 end situated at bearing cup 614 outer side as depicted in FIG. 6B, the enlarged section view of universal joint 600 for bearing needles assembly 602. The difference in forces at both the end bearing needles 612 and the inner arm portion 610 of the orthogonal cross arm is substantially reduced which result in uniform distribution of forces in bearing needles 612 and in the inner arm portion 610 of the orthogonal cross arm. This phenomenon helps to improve performance of universal joint during field application.

[0060] FIG. 6C depict an enlarged section view of universal joint for sealing assembly 604. The spring ring 634 is placed in between the bottom of bearing needles 612 and the double lip seal to keep the bearing needles 612 in one plane to ensure the uniform distribution of forces along the length. In the universal joint 600, the double lip seal consists of metal case 606 on its outer diameter and reinforced sealing lip 618 with garter spring 620. The double lip sea is press fitted with the bearing cup and due to metal case 606 on its outer diameter, for proper alignment of double lip seal with bearing cup. The garter spring 620 on the double lip sea compensate the reinforced sealing lip 618 wear and maintains the predefined radial force on the shaft diameter. With garter spring 620 with reinforced seal lip 618, the predefined radial force at about 11 N is maintained on the shaft diameter and it ensures the lubricant retention in the universal joint. The garter spring disclosed in the embodiment is not confined only for garter spring any other spring with similar functional properties can also be considered.

[0061] Further, the inner diameter consists of an axially projected seal lip, which engages with the reinforced seal lip 618 during assembly, which in turn restricts the grease path to hold the grease inside the bearing cup. During assembly, the reinforced seal lip 618 is stretched to suit the shaft diameter and the reinforced seal lip 618 presses the axially projected seal lip diametrically to close to grease path. The space created on the orthogonal cross arm periphery at the connecting point of the axially projected seal lip and the reinforced seal lip 618 acts as the reservoir for grease.

[0062] The stepped cross sectional annular metallic insert 622 is provided on the outer periphery of the seal guard. The resilient elastomeric portion 624 of the seal guard lies on the inner periphery of the metal inserts 622. The seal lip 626 remains in the inner periphery. The seal lip 626 at its radially outer end has formed angular in shape with respect to the Bearing cup 628 race so as to provide the flexibility during assembly. The face 630 of the hollow cylindrical bearing cup assembly is not pressurized by horizontal face 632 of the seal guard to ensure satisfactory sealing.

[0063] Numerous advantages of the present disclosure may be apparent from the discussion above. In accordance with the present disclosure, a high enduring universal joint with special sealing system to enhance its service life and to transfer uniform forces from bearing cup sub assembly through bearing needles is disclosed herewith.

[0064] The proposed sealing assembly for a universal joint improves the performance of propeller shafts and to increase the life of the universal joint. The proposed universal joint transfers uniformly forces from each bearing cup sub assembly and through needles. The proposed sealing assembly provides uniform wear on the components of the universal joint to prolong the life of universal joint. In the proposed sealing assembly multiple lips sealing is introduced for a universal joint to prevent leakage of lubrication and eliminate sealing failure. The spring ring between needles and seals forces the needles to be in one position to ensure uniform distribution of forces on the needles on the same plane. The proposed sealing assembly protects the universal joint from outside mud, dirt and dust, thereof.

[0065] The proposed universal joint provides proper alignment of the cross arms with a yoke assembly. The proposed universal joint improves resistance towards bending, deflection and thereby reduces heat generation. The proposed universal joint reduces the edge damages of the bearing needles and the cross arm during application.

[0066] It will readily be apparent that numerous modifications and alterations can be made to the processes described in the foregoing examples without departing from the principles underlying the invention, and all such modifications and alterations are intended to be embraced by this application. , Claims:CLAIMS:
We Claim:
1. A high enduring universal joint with special sealing system, comprising:
a central cross portion with four orthogonal cross arms extending outward from center of said central cross portion configured to exert uniform force, wherein each orthogonal cross arm incorporated in a conical profile with an outer arm portion facing away from shoulder of said central cross portion and an inner arm portion positioned toward said shoulder of said central cross portion; and
a hollow cylindrical bearing cup assembly mounted on said outer arm portion of each orthogonal cross arm, wherein said hollow cylindrical bearing cup assembly comprising:
an outer hollow cup;
plurality of bearing needles arranged in inner diameter of said outer hollow cup tangentially, wherein a thrust washer is placed in inner diameter of said outer hollow cup in contact with one end of said plurality of bearing needles;
a spring ring placed over other end of said plurality of bearing needles configured to put said plurality of bearing needles in one plane and further to ensure uniform distribution of forces along length of said plurality of bearing needles;
a double lip seal placed in inner diameter of said outer hollow cup configured to maintain a predefined radial force exerted by a reinforced sealing lip with a spring around a shaft surface, wherein outer end of said double lip seal aligns with said outer hollow cup and inner face of said double lip seal press said spring ring to exert force on said plurality of bearing needles to keep them aligned; and
a seal guard with a sheet metal on outer surface configured to protect said double lip seal from dust particles, and a resilient elastomeric portion of said seal guard positioned in the inner periphery of said sheet metal, wherein one end of said seal guard is fixed to diameter of said outer arm portion,
whereby said high enduring universal joint with special sealing system enhances service life of said universal joint and provides uniform forces over said plurality of bearing needles.
2. The high enduring universal joint with special sealing system as claimed in claim 1, wherein said outer arm portion diameter is larger than said inner arm portion diameter with 15µ to 20µ of difference in diameters.
3. The high enduring universal joint with special sealing system as claimed in claim 1, wherein said orthogonal cross arms exerts uniform forces on said hollow cylindrical bearing cup assembly through said plurality of bearing needles.
4. The high enduring universal joint with special sealing system as claimed in claim 1, wherein said double lip seal includes a case made of metal or other materials with similar properties on outer diameter of said double lip seal, and reinforced sealing lip with spring wherein the spring like garter spring or other spring with similar properties is used.
5. The high enduring universal joint with special sealing system as claimed in claim 1, wherein said spring with said reinforced seal lip compensate a seal lip wear and the predefined radial force is maintained on said shaft diameter, and further ensures lubricant retention in said universal joint.
6. The high enduring universal joint with special sealing system as claimed in claim 1, wherein said double lip seal axially forces said spring ring in upward direction to keep said plurality of bearing needles aligned in one plane in order to distribute force uniformly on said plurality of bearing needles.
7. The high enduring universal joint with special sealing system as claimed in claim 1, wherein a space of 0.02 to 0.4 mm is maintained between inner surface of said seal guard and surface of said hollow cylindrical bearing cup assembly.
8. The high enduring universal joint with special sealing system as claimed in claim 1, wherein said seal guard includes a seal lip positioned in inner periphery of said seal guard, wherein outer end of said seal lip forms an angular shape with respect to race of said hollow cylindrical bearing cup assembly to provide flexibility.