CN218063325U - Tractor and continuously variable transmission - Google Patents
Tractor and continuously variable transmission Download PDFInfo
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- CN218063325U CN218063325U CN202222290044.5U CN202222290044U CN218063325U CN 218063325 U CN218063325 U CN 218063325U CN 202222290044 U CN202222290044 U CN 202222290044U CN 218063325 U CN218063325 U CN 218063325U
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Abstract
The utility model relates to a tractor, this tractor are including continuously variable transmission, continuously variable transmission includes initiative shafting, driven shafting, pressure parts, speed governing part and flexible drive component, through carrying out detailed setting to each part, especially carries out concrete settlement to the position relation of the spline fit mode between deciding the awl dish and moving the awl dish, diaxon, lubricated mode and assembly type for continuously variable transmission's stability and reliability have obtained the promotion, make the whole drive capacity of tractor and the cooperation of transmission efficiency obtain optimizing.
Description
Technical Field
The utility model relates to a power machinery's infinitely variable field, concretely relates to tractor and buncher.
Background
Tractors are widely used as power machines for traction and drive operations in the fields of agriculture, industry, special applications, and the like. The existing tractor is generally provided with a set of transfer case assembly at the lower part of a gearbox, but the arrangement has certain influence on the efficiency of the tractor. At present, a continuously variable transmission for a tractor mainly stands in a functional view, but various problems of insufficient tensile strength of a flexible element of the continuously variable transmission, low overall efficiency, excessive heat generation between a movable cone disk and a fixed cone disk, insufficient system sealing pressure and the like can occur in the practical application process.
Chinese patent publication CN109353210A discloses a continuously variable transmission for a hybrid tractor, which widens the transmission range and improves the transmission efficiency, but does not concern the problem that the heat generation between a movable cone plate and a fixed cone plate is too large, which affects the practical application. How to extend the details of the problems in the practical application process in detail to realize the functionalization of the continuously variable transmission into the engineering, and the improvement of the overall efficiency and the reliability becomes the main focus of researchers.
SUMMERY OF THE UTILITY MODEL
The utility model aims at the above-mentioned technical problem, a tractor and buncher are provided.
The method is realized by the following technical scheme:
the stepless transmission comprises a driving shaft system, a driven shaft system, a pressurizing part, a speed regulating part and a flexible transmission element, wherein the flexible transmission element is clamped between the driving shaft system and the driven shaft system, the driving shaft system comprises a driving shaft, a driving fixed cone disc and a driving movable cone disc, and the driven shaft system comprises a driven shaft, a driven fixed cone disc and a driven movable cone disc.
The pressing part is arranged on the back of the driving fixed cone disc and/or the driven fixed cone disc, the pressing part is a cam pressing mechanism, the cam pressing mechanism comprises a disc spring, a driving cam, a driven cam, a retainer and a rolling body, one axial end of the disc spring abuts against the driving shaft, the other end of the disc spring abuts against the driving fixed cone disc or the other end of the disc spring abuts against the driving cam, a plurality of raceways uniformly distributed in the circumferential direction are respectively arranged on the opposite end surfaces of the driving cam and the driven cam, the driving cam and the driven cam are connected through the rolling body clamped between the oppositely arranged raceways, the retainer is sleeved on the rolling body and is arranged between the driving cam and the driven cam, and the back of the driven cam is connected with the driving fixed cone disc and/or the driven fixed cone disc; the speed regulating part comprises a driving machine, a speed regulating shaft and a linear reciprocating mechanism for converting rotation into linear motion, and the linear reciprocating mechanism is arranged on the back surfaces of the driving dynamic conical disc and the driven dynamic conical disc.
The center distance between the driving shaft and the driven shaft is a, the unit is mm, and the requirements are met:
wherein T is the maximum torque value of the external characteristic curve of the continuously variable transmission at the full speed of the input power source and has the unit of N.m.
Preferably, the driving fixed cone disc comprises a driving fixed cone disc conical surface section and a driving fixed cone disc shaft sleeve section, the driving fixed cone disc shaft sleeve section is sleeved outside the driving shaft, one end of the driving fixed cone disc shaft sleeve section is fixedly connected with the driving fixed cone disc conical surface section, the driving movable cone disc is connected to the outside of the driving fixed cone disc shaft sleeve section through a spline connecting sleeve, splines on the driving movable cone disc are internal splines, namely an internal spline A, and the minor diameter of the internal spline A is d 1 The external spline is arranged outside the driving fixed cone disc shaft sleeve section and defined as an external spline A, and the major diameter of the external spline A is d 2 The length of the internal spline A is L 1 The length of the external spline A is L 2 Wherein L is 1 L2 or more times 2 The spline surface of the internal spline A comprises two axial intervals L 3 A step surface of, L 3 L is more than or equal to 0.12a 3 Less than or equal to 0.45a, small diameter of the step surfaceIs (d) 1 -6.8)mm～(d 1 -0.1) mm, said d 1 And d 2 D is not less than 2.25mm 2 –d 1 Less than or equal to 7.5mm; the driven fixed cone disc comprises a driven fixed cone disc conical surface section and a driven fixed cone disc shaft sleeve section, the driven fixed cone disc shaft sleeve section is sleeved outside the driven shaft, one end of the driven fixed cone disc shaft sleeve section is fixedly connected with the driven fixed cone disc conical surface section, the driven movable cone disc is connected outside the driven fixed cone disc shaft sleeve section in a spline connecting mode, the spline on the driven movable cone disc is an internal spline and defined as an internal spline B, and the small diameter of the internal spline B is d 3 The external spline is arranged outside the driven fixed cone disc shaft sleeve section and defined as an external spline B, and the major diameter of the external spline B is d 4 The length of the internal spline B is L 4 The length of the external spline B is L 5 Wherein L is 4 L2 or more times 5 The spline surface of the internal spline B comprises two axial intervals L 6 The step surface of, L 6 L is more than or equal to 0.12a 6 Less than or equal to 0.45a, the small diameter of the step surface is (d) 3 -0.1mm)～(d 3 -1.8 mm), said d 3 And d 4 D is not less than 2.25mm 4 –d 3 ≤7.5mm。
Preferably, the driving shaft and the driven shaft are respectively provided with at least one axial long hole and a plurality of radial holes, one end of each radial hole is communicated with the outside, the other end of each radial hole is communicated with the inside of the corresponding axial long hole, at least one end of each axial long hole is communicated with the outside, and the diameter of each radial hole is 1-6 mm.
Preferably, the continuously variable transmission further comprises a box body which is arranged outside the continuously variable transmission body and used for accommodating the continuously variable transmission body, the box body is divided into a front box body and a rear box body, a separation bearing seat is arranged on the front box body, 2-4 (preferably 2) lip-shaped sealing rings are arranged between the driving shaft and the separation bearing seat, and the lips of the lip-shaped sealing rings face the continuously variable transmission body.
Preferably, the cam pressurizing mechanism further comprises a disc spring seat, the disc spring seat comprises an outer circular ring part, an inner circular ring part and an annular groove, one end of the outer circular ring part is fixedly connected with one end of the inner circular ring part through the annular groove, so that the inner circular ring part and the outer circular ring part are of circular ring structures with the same physical axis, a chamfer is arranged at the outer circle of the joint of the outer circular ring part and the annular groove, at least two U-shaped groove through holes are formed in the annular groove, the U-shaped groove through holes are connected with the annular groove, and the U-shaped openings of the U-shaped groove through holes face the outer circular ring part; the disc spring seat is arranged outside the disc spring and used for supporting the disc spring, the bevel end of the disc spring faces the fixed cone disc after the disc spring is stacked in parallel, the reverse side of the bevel end is abutted against the inner side of the annular groove of the disc spring seat, preferably, the thickness of the inner side of the annular groove of the disc spring seat is different from that of the outer side, the thickness of the inner side is larger than that of the outer side, the thickness of the inner side of the annular groove of the disc spring seat is S, and the S satisfies that S is not less than 0.021a and not more than 0.095a; the driving cam is also provided with a chamfer at the excircle of the circular end face at the side without the raceway.
The driving cam is also provided with a chamfer at the excircle of the circular end face at one side without the raceway.
Preferably, the retainer is a thin sheet with a circular ring structure, circular through holes with the same number as the rolling bodies are arranged on the retainer, the circular through holes are used for accommodating the rolling bodies, and the thickness of the retainer is 1.5-5.8 mm (preferably 2-3 mm). (preferably, the holder is made of lead brass).
Preferably, at least three U-shaped grooves are distributed in the circumferential direction of the back face of the conical surface of the driving movable conical disc and/or the driven movable conical disc, the U-shaped opening of each U-shaped groove faces towards the excircle, and the area of each U-shaped groove is 1% -15% of the surface area of the back face of the conical surface.
Preferably, the flexible transmission element is a chain, and the driven cam is integrally or separately provided with the driving fixed cone disc and/or the driven fixed cone disc. Preferably, one end of the shaft sleeve section of the driving fixed cone disc is fixedly connected with the conical surface section of the driving fixed cone disc in an integrally forming mode.
Preferably, one or more radial holes are arranged in the range from the spline of the driving fixed-cone-plate shaft sleeve section and/or the driven fixed-cone-plate shaft sleeve section to the end surface of the shaft sleeve section far away from the conical surface and/or close to the conical surface, wherein the maximum diameter of each radial hole is less than or equal to 55mmThe total cross-sectional area is e, in mm 2 And e satisfies 0.08 a-0.75 a.
A power machine comprises the continuously variable transmission.
More preferably, the power machine is a tractor.
The path is the diameter of the minimum department of circumference, the major diameter is the diameter of the maximum department of circumference department.
The technical effects of the utility model reside in that:
1. the utility model discloses a rationally set up the spline connection mode of initiative fixed cone dish and initiative movable cone dish, especially rationally set up the axial spacing and the diaxon centre-to-centre spacing's of mutual proportional relation and ladder face such as spline, ladder face relation, make the utility model discloses an interior external splines that move the cone dish and decide the cone dish are specific moves the connection to balanced speed governing stability and calorific relation, the utility model discloses the more good support that sets up on the one hand can make fixed cone dish moves the cone dish like this, promotes the stability of speed governing, and on the other hand can prevent to move the cone dish axial and remove the in-process calorific capacity and lead to the spline face burn, thereby specific setting makes buncher be suitable for more like this the utility model discloses the requirement of specific operating mode.
2. The center distance between two shafts of the continuously variable transmission and the design technical indexes and the performance of a plurality of continuously variable transmissions (particularly the continuously variable transmission of a tractor) have a relatively complex relationship of mutual influence: (1) Under the condition of certain input torque, the center distance of the continuously variable transmission directly influences the tension of the chain, so that the service life of the chain is indirectly influenced; (2) Because the friction coefficient of the friction pair is certain, the tension and the input torque of the chain determine the clamping force, namely the magnitude of the axial thrust, in an effective control range; the axial thrust determines the selection of the bearing and the highest rotating speed of the bearing, so that the overall arrangement of heat dissipation, system efficiency and the strength of each structural part is realized; (3) The tensile strength of the chain (namely the flexible transmission element) is determined by the thickness of the pin shaft and the width of the chain; the chain cannot be widened infinitely due to the inconsistency of the process; therefore, balancing is required according to the process and the load; the thickness of the pin shaft influences the pitch of the chain; on one hand, the pitch of the chain affects the smoothness of transmission, namely, the larger the pitch, the more serious the vibration of the chain is, so that the system abrasion and the service life are affected; on the other hand, the pitch of the chain influences the logarithm of the pin shaft bearing axial pressure in transmission, further influences the total pressure bearing area in transmission and contact pressure stress, and the wear condition of the pin shaft and the conical surface is influenced by the index and the factors such as surface hardness and hardened layer depth which can be achieved by the process, so that the service life of the system is influenced; although the stress of the chain in the transmission is mainly tensile force, the chain inevitably receives lateral vibration and load, and the vibration and the load are mainly born by the stop pin welded on the pin shaft; therefore, the design and the service life of the stop pin are indirectly influenced by the tension; (4) Under dynamic and severe non-road conditions, such as typical operation conditions of a tractor, because a friction pair serving as a main transmission 'component' of a continuously variable transmission is subjected to frequent and severe load switching, the relationship between rated load and abrasion is completely different from the road condition, in order to ensure the service life of a system, the design index of the continuously variable transmission is re-adapted according to the specific load condition, and the determination of the center distance of the continuously variable transmission needs to follow the design rule of the specific operation condition. The utility model discloses in the middle of infinitely variable transmission's design, experiment and concrete practice, the technological status of reality, concrete load condition have been synthesized and have been specifically calculated to combine the influence of aspects such as many-sided environmental factor (heat dissipation, vibration, crop and operation kind, region difference etc.), cost requirement simultaneously, derived the utility model discloses be fit for the injectment of the interrelation of tractor operating mode like this. Thereby can ensure conical disk buncher's transmission capacity (guarantee promptly the utility model discloses a guarantee under the operating mode condition buncher's transmission capacity inefficacy) and foretell requirement, obtain the utility model discloses relation between centre-to-centre spacing and the buncher input maximum torque. Guarantee transmission efficiency when making buncher's transmission capability obtain satisfying, if do not satisfy the utility model discloses the maximum torque and the requirement of centre-to-centre spacing of concrete settlement, then perhaps can not satisfy transmission capability's demand, perhaps can make buncher's transmission efficiency receive the influence. The restriction to relation between moment of torsion and centre-to-centre spacing is not conventional technological means at all, and the utility model discloses a research has obtained its and the most harmonious relation of input maximum torque to make transmission capacity and transmission efficiency etc. be in the utility model discloses a cooperation under the operating mode has realized the best cooperation.
3. Axial force arrives from cam loading system and moves between the fixed cone dish, final axial force can seal epaxially, the utility model discloses a set up axial slot hole and a plurality of radial hole of mutually supporting on driving shaft and driven shaft, and simultaneously through the size of injecing the radial hole, make axial slot hole and a plurality of radial hole that are suitable for as the oil through hole realize the close cooperation, make lubricating oil can flow through these axial slot hole and radial hole at the operation in-process, thereby lubricate each part at the operation in-process, through specifically setting up radial aperture, because at each part in-process of moving each other, the size in aperture sets up to the mobile influence of lubricating oil huge, consequently the aperture set up and maximum torque and the relation between the centre distance also coordinate closely, thereby can make lubricating oil can be in the utility model discloses realize fine initiative lubrication under the mode of setting up of specific structure, can realize initiative lubrication to driving shaft and driven shaft epaxial bearing axial force and can take place relative movement or rolling main spare part, thereby whole device's life-span has been promoted by a wide margin.
4. The lip-shaped sealing ring is arranged at a specific position, so that the integral sealing is realized, and the lip-shaped sealing ring can realize active lubrication and passive lubrication when lubricating oil is added to the box body; especially the utility model discloses the orientation of lip has specifically been set up to make lubricating oil can obtain fully sealed in the box, promoted sealed reliability by a wide margin, can make simultaneously the utility model discloses a continuously variable transmission connects dry clutch in the front.
5. Through carrying out concrete setting to the dish spring seat, especially to its structure, the specific position chamfer of annular groove and specific position chamfer cooperation initiative cam has carried out concrete setting, and the relation to the inboard thickness of annular groove and diaxon centre-to-centre spacing has carried out concrete setting, thereby make the in-process flexible transmission element (chain) of assembling realize the pretension, the in-process that the actual assembly process flexible transmission element is changed into the compact state by the relaxation state promptly and whether compresses tightly the judgement through dish spring and dish spring seat terminal surface parallel and level, make and leave suitable space in the specific position of the two excircle department through setting up the U-shaped groove at the dish spring, thereby make in maintenance and the assembling process, can better dismantle and assemble, thereby the degree of difficulty of maintenance and assembly has been reduced by a wide margin, from certain meaning both guaranteed the reliability of integrated device, maintenance cost has also been reduced simultaneously.
6. Through setting up specific holder, especially specifically prescribe a limit to its thickness for when holder and rolling element coordinated motion, can carry on spacingly to the installation of a plurality of rolling elements, and make the rolling element can keep the same trend of motion, especially the prescribe a limit to thickness can prevent that the rolling element from the unbalance loading and the atress that bring in the motion process are uneven, thereby promoted overall structure's life-span by a wide margin.
7. The U-shaped groove with specific properties and specific size is set at a specific position on the back of the movable cone disc, so that axial forces from the cam pressurizing mechanism to the movable cone disc, the flexible transmission element, the fixed cone disc and the shaft are all in the locking process of system transmission, the reliability of the whole device is improved, and the system is more convenient to disassemble and assemble.
8. The spline connecting part of the driving fixed cone disc and the driven fixed cone disc and the movable cone disc is a closed space, so that the lubricating condition is poor, and the spline at the position is in movable connection, so that fretting wear is easy to occur. Therefore, the lubricating oil hole is arranged in the designated space range of the spline and the end part, and the specific coordination relation of the sectional area of the lubricating oil hole is limited, so that active lubrication can be introduced, the lubricating oil is forced to enter the spline meshing gap, and the fretting wear problem is solved.
Drawings
Fig. 1 is a schematic view of a sectional structure of the continuously variable transmission of the present invention.
Fig. 2 is an external characteristic curve of the diesel engine of the present invention.
Fig. 3 is a schematic structural view of the active fixed cone disk of the present invention.
Fig. 4 is a schematic structural view of the active dynamic conical disc of the present invention.
Fig. 5 is a schematic view of the sectional structure of the active dynamic cone disk of the present invention.
Fig. 6 is a schematic structural view of the disc spring seat of the present invention.
Fig. 7 is a schematic sectional view of the disc spring seat of the present invention.
Fig. 8 is a schematic structural view of the retainer of the present invention.
Wherein: 1. the device comprises a driving shaft, 1-1 axial long holes in the driving shaft, 1-2 radial holes in the driving shaft, 2 separating bearing seats, 3 disc spring seats, 3-1 inner circular ring parts, 3-2 annular grooves, 3-3 outer circular ring parts, 3-5U-shaped grooves, 4 disc springs, 5 driving cams, 6 rolling bodies, 7 retainers, 7-1 circular through holes, 8 driving fixed cone discs, 8-1 radial holes in the driving fixed cone discs, 9 driving machines, 10 speed regulating shafts, 11 driving movable cone discs, 11-1U-shaped grooves, 12 linear reciprocating mechanisms, 13 driven shafts, 13-1 axial long holes in the driven shaft, 13-2 radial holes in the driven shaft, 13-3 radial holes in the driven fixed cone discs, 14 rear boxes, 15 flexible transmission elements, 16 driven movable cone discs, 17 lip-shaped front boxes, 18 sealing rings, d sealing rings 1 Minor diameter, L of inner spline A 1 Length of internal spline A, d 2 Major diameter, L of the external spline A 2 Length, L of external spline A 3 Axial distance between two step surfaces on the spline surface of the internal spline A and thickness of the inner side of the annular groove of the S-shaped disc spring seat.
Detailed Description
Example 1
As shown in fig. 1, a continuously variable transmission includes a driving shaft system, a driven shaft system, a pressing member, a speed adjusting member and a flexible transmission element, the flexible transmission element is clamped between the driving shaft system and the driven shaft system, the driving shaft system includes a driving shaft, a driving fixed cone disc and a driving movable cone disc, the driven shaft system includes a driven shaft, a driven fixed cone disc and a driven movable cone disc, the pressing member is disposed on a back surface of the driving fixed cone disc and/or the driven fixed cone disc, the pressing member is a cam pressing mechanism, the cam pressing mechanism includes a disc spring, a driving cam, a driven cam, a retainer and a rolling body, one axial end of the disc spring abuts against the driving shaft, the other end of the disc abuts against the driving fixed cone disc directly or indirectly, a plurality of raceways are uniformly distributed in a circumferential direction on end surfaces of the driving cam and the driven cam, the driving cam and the driven cam are connected by the rolling body clamped between the oppositely disposed raceways, the retainer is sleeved on the rolling body and disposed between the driving cam and the driven cam, and the back surface of the driven cam is connected with the driven fixed cone disc and/or the driven cone disc (in fig. 1, the driven cam is disposed as a separate body in an embodiment); the speed regulation part comprises a driving machine, a speed regulation shaft and a linear reciprocating mechanism for converting rotation into linear motion, and the linear reciprocating mechanism is arranged on the back surfaces of the driving movable conical disc and the driven movable conical disc. The flexible transmission element is a chain.
The center distance a between the driving shaft and the driven shaft is 220mm, the external characteristic curve of the continuously variable transmission is shown in figure 2 under the condition that the input power source of the continuously variable transmission is a diesel engine at the full speed, wherein T is 640 N.m, and the relation between the two is as follows:
the requirements of (1).
As shown in fig. 1 to 5, the driving fixed cone disc comprises a driving fixed cone disc conical surface section and a driving fixed cone disc shaft sleeve section, the driving fixed cone disc shaft sleeve section is sleeved outside the driving shaft, one end of the driving fixed cone disc shaft sleeve section is fixedly connected with the driving fixed cone disc conical surface section, and one end of the driving fixed cone disc shaft sleeve section of the embodiment is fixedly connected with the driving fixed cone disc conical surface section in an integrally formed manner. The driving movable cone disc is connected to the outside of the shaft sleeve section of the driving fixed cone disc by adopting a spline connection sleeve, as shown in fig. 3 and 4, the spline on the driving movable cone disc is an internal spline defined as an internal spline a, and the minor diameter d of the internal spline a 1 Is 72.4mm, as shown in fig. 2, the external spline is arranged outside the driving fixed cone disc shaft sleeve section and is defined as an external spline A, and the major diameter d of the external spline A 2 Is 76mm, the length L of the internal spline A 1 Is 65mm, the length of the external spline AL 2 Is 25mm in diameter and L is 1 L2 or more times 2 The surface of the internal spline A comprises two axial intervals L 3 Is a 36mm step surface, and the central distance a between the driving shaft and the driven shaft is 220mm, so that the L is more than or equal to 0.12a 3 Less than or equal to 0.45a, the small diameter of the step surface is 72.2mm, because d 1 Is 72.4mm, and the two relations satisfy d or less 1 -0.1mm, d or more 1 -6.8mm, said d 1 And d 2 Also satisfies d is not less than 2.25mm 2 –d 1 The requirement of less than or equal to 7.5mm; driven fixed cone dish is including driven fixed cone dish conical surface section and driven fixed cone dish sleeve section, driven fixed cone dish sleeve section cover is established in the driven shaft outside, the one end and the driven fixed cone dish conical surface section rigid coupling of driven fixed cone dish sleeve section, driven movable cone dish adopts spline adapter sleeve to connect in the outside of driven fixed cone dish sleeve section, the spline on the driven movable cone dish is the internal spline, and the definition is internal spline B, and the path d3 of internal spline B is 72.4mm, driven fixed cone dish sleeve section outside is provided with the external spline, and the definition is external spline B, and the major diameter d4 of external spline B is 76mm, the length L of internal spline B 4 Is 65mm, the length L of the external spline B 5 Is 25mm, wherein L 4 L2 or more times 5 The surface of the internal spline B comprises two axial intervals L 6 Is a 36mm step surface, and the central distance a between the driving shaft and the driven shaft is 220mm, so that the L is more than or equal to 0.12a 6 Not more than 0.45a, the small diameter of the step surface is 72.2mm, and d is not more than 3 -0.1mm greater than or equal to d 3 -6.8mm, said d 3 And d 4 D is not less than 2.25mm 4 –d 3 The thickness is less than or equal to 7.5 mm.
As shown in fig. 1, be equipped with an axial slot hole and 2 radial holes on the driving shaft, radial hole top and outside intercommunication, the bottom is linked together with the inside of axial slot hole, radial hole is the through-hole, and the diameter is 3mm, be equipped with an axial slot hole and 3 radial holes on the driven shaft, radial hole top and outside intercommunication, the bottom is linked together with the inside of axial slot hole, radial hole is the shoulder hole, and minimum aperture department diameter is 1.2mm, 1.2mm and 2mm respectively. The embodiment is as shown in the figure3, all be equipped with radial through-hole on initiative fixed cone dish and the driven fixed cone dish and be used for realizing initiative lubrication, the spline of initiative fixed cone dish shaft sleeve section all is equipped with 1 radial cylindrical through-hole to on the shaft sleeve section keep away from and be close to between the scope of the terminal surface less than or equal to 55mm of conical surface, the total sectional area of radial through-hole is that e is 18 pi mm 2 E is more than or equal to 0.08a and less than or equal to 0.75a; as shown in figure 1, as the driven shaft and the driven fixed cone disc are integrally arranged, 1 radial cylindrical through hole is arranged between the spline of the shaft sleeve section of the driven fixed cone disc and the end surface of the shaft sleeve section far away from and close to the conical surface and is less than or equal to 55mm, and the total sectional area of the radial through holes is 8 pi mm 2 And e is more than or equal to 0.08a and less than or equal to 0.75a.
The outer portion of the continuously variable transmission body of the continuously variable transmission is further provided with a box body used for containing the continuously variable transmission body, the box body is divided into a front box body and a rear box body, a separation bearing seat is further arranged on the front box body, 2 lip-shaped sealing rings are arranged between the driving shaft and the separation bearing seat, and lips of the lip-shaped sealing rings face towards the continuously variable transmission body.
The cam pressurizing mechanism further comprises a disc spring seat, as shown in fig. 6 and 7, the disc spring seat comprises an outer circular ring part, an inner circular ring part and an annular groove, the annular groove fixedly connects one end of the outer circular ring part with one end of the inner circular ring part, so that the inner circular ring part and the outer circular ring part are of circular ring structures with the same physical axis, a chamfer is arranged at the outer circle of the connection part of the outer circular ring part and the annular groove, at least two U-shaped groove through holes are formed in the annular groove, the U-shaped groove through holes are connected with the annular groove, and the U-shaped openings of the U-shaped groove through holes face the outer circular ring part; the disc spring seat is arranged outside the disc spring and used for supporting the disc spring, the bevel end of the disc spring faces the fixed cone disc after the disc spring is stacked in parallel, the reverse side of the bevel end is abutted against the inner side of the annular groove of the disc spring seat, as shown in fig. 7, the thickness of the inner side of the annular groove is slightly larger than the thickness of the outer side, the thickness S of the inner side of the annular groove of the disc spring seat is 6.9mm, and the S meets the requirement that S is not less than 0.021a and not more than 0.095a because the center distance a between the driving shaft and the driven shaft is 220 mm; the driving cam is also provided with a chamfer at the excircle of the circular end face at the side without the raceway.
As shown in fig. 8, the retainer is a thin sheet with a circular ring structure, circular through holes with the same number as the rolling elements are arranged on the retainer, the circular through holes are used for accommodating the rolling elements, the thickness of the retainer is 2mm, and the material of the retainer in this embodiment is lead brass.
As shown in fig. 4, 4U-shaped grooves are symmetrically and uniformly distributed on the back surface of the conical surface of the driving movable conical disk and/or the driven movable conical disk in the circumferential direction, as shown in fig. 4, the U-shaped grooves are all arranged on the back surface of the conical surface, the U-shaped opening of each U-shaped groove faces towards the outer circle, and the area of a single U-shaped groove is 5.7% of the surface area of the back surface of the conical surface.
Comparative example 1
The comparative example was otherwise arranged in the same manner as in example 1 except that the center-to-center distance a between the driving shaft and the driven shaft was 150mm, and T was 640 N.m, which was not satisfied
The requirements of (2).
Through a comparative test under the same condition, the axial force of the pressurizing cam mechanism in the embodiment 1 is 98KN, and the flexible transmission element is in good contact with the conical disc surface. And because the minimum working radius is reduced under the condition of a set speed ratio range due to the reduction of the center distance, the axial force of the pressurizing cam mechanism of the comparative example is 132KN, the contact area between the flexible transmission element and the conical surface is reduced when the axial force is increased and the speed ratio is large, the number of the pin shafts of the working flexible element is reduced, and the single pin shaft bears the axial force which exceeds the limit set value, so that the pin shaft is abraded and even broken.
Thereby obtain the utility model discloses compact structure under the centre-to-centre spacing that sets up satisfies the required axial force prerequisite of transmission moment of torsion.
Comparative example 2
The other arrangement mode of the comparison example is the same as that of the example 1, except that the length L of the internal spline A on the driving dynamic conical disc is the same as that of the internal spline A on the driving dynamic conical disc 1 Is 35mm, the length L of the external spline A on the driving fixed cone disc 2 Is 25mm, said L 1 And L 2 Does not satisfy L 1 L2 or more times 2 The length L of the internal spline B on the driven dynamic cone disc 3 Is 35mm, the length L of the external spline B on the driven fixed cone disc 4 Is 25mm, said L 3 And L 4 Does not satisfy L 3 L2 or more times 4 。
Compared with the embodiment 1, the function contrast test under the same condition is carried out on the premise that the conical surface angle is 11 degrees, and on the premise that the spline transmission strength and the axial movement stability of the movable conical disc are met, the embodiment 1 can realize that the axial stroke of the conical disc is 25mm and the maximum working radius R of the corresponding conical disc max -R min =64.31mm, cvt speed ratio range
The comparative example 2 can realize the axial stroke of the conical disc of 5mm and the maximum working radius R of the corresponding conical disc max -R min =12.9mm, corresponding to the CVT ratio range
While it is generally considered that when the CVT ratio range is less than 2, it is meaningless with respect to gearing, i.e., the arrangement of the present comparative example is meaningless with respect to gearing.
Comparative example 3
The other arrangement of this comparative example is the same as example 1, except that the faces of the internal splines A include two axial spaces L 3 Is a 20mm step surface, and because the center distance a between the driving shaft and the driven shaft is 220mm, L is not more than or equal to 0.12a 3 Less than or equal to 0.45a, the small diameter of the step surface is 70mm, and the small diameter d of the internal spline A of the driving movable conical disc 1 72.4mm, d is not more than or equal to 1 -0.1mm, d or more 1 6.8mm, said internal spline B comprising two axial spaces L on its face 6 Is a 20mm step surface, and because the center distance a between the driving shaft and the driven shaft is 220mm, L is not more than or equal to 0.12a 6 Not more than 0.45a, the small diameter of the step surface is 70mm, because the small diameter d of the internal spline B on the driven movable conical disc 3 72.4mm, d is not more than or equal to 3 -0.1mm or mored 3 -1.8mm。
The comparative example caused the temperature rise of the spline between the moving cone plate and the fixed cone plate to be excessively high, thereby causing the spline to burn, as obtained by the durability test under the same conditions as in example 1, but example 1 did not have such a problem.
Comparative example 4
The other arrangement of this comparative example is the same as that of example 1 except that the axially long holes and the radially long holes are not provided on the driving shaft and the driven shaft.
Compared with the embodiment 1, on the premise of the same amount of lubricating oil, the lubricating oil is obtained through a contrast test under the same condition, the embodiment 1 can meet the condition that the temperature of a continuously variable transmission box body is within 75 ℃ under the condition of 640 N.m, the transmission efficiency is more than 90 percent, the comparison example causes the burning of an axial force bearing on important parts on a shaft, particularly an axial force bearing needing to be born under a movable and fixed conical disc spline and a speed regulating mechanism, the service life is shortened, the oil stirring loss is improved, and the transmission efficiency is between 80 and 90 percent.
Comparative example 5
The other arrangement modes of the comparative example are the same as those of the embodiment 1, except that the disc spring seat is not provided with the annular groove and the chamfer, and the thickness of the inner side of the disc spring seat is 4.1mm, so that the requirement that the thickness is more than or equal to 0.021a and less than or equal to 0.095a is not met.
Therefore, the flexible transmission element (chain) cannot be pre-tightened and judged in the assembly process, so that the assembly is difficult, and more seriously, the flexible transmission element (chain) slips due to the fact that the cam pressurizing mechanism does not reach the working state or positive and negative rotation switching occurs in the initial stage and the reverse dragging process of the flexible transmission element in the operation process, the conical disc and the flexible transmission element (chain) generate dynamic friction, scratches occur, the service life is shortened, and on the other hand, relative play occurs between disc springs, so that the system stability is poor; whereas example 1 did not suffer from the above problems.
Comparative example 6
The other arrangement modes of the comparative example are the same as the embodiment 1, except that no retainer is arranged, and the rolling paths and the rolling bodies of the embodiment 1 and the comparative example are all 5, and the rolling bodies are all steel balls with the diameter of 30 mm.
The rolling element can synchronously realize axial movement, the uneven load distribution coefficient can be kept within 1.3, the rolling element in the comparative example does not move synchronously, a pressurizing mechanism is biased to load, the normal positive pressure of the contact point of part of the rolling element and the raceway rises, the raceway is pressed out of a pit, and the service life is shortened.
Claims (9)
1. The utility model provides a continuously variable transmission, continuously variable transmission includes initiative shafting, driven shafting, pressurization part, speed governing part and flexible transmission component, centre gripping flexible transmission component between initiative shafting and the driven shafting, initiative shafting includes driving shaft, initiative fixed cone dish and initiative movable cone dish, driven shafting includes driven shaft, driven fixed cone dish and driven movable cone dish, its characterized in that:
the pressing part is arranged on the back of the driving fixed cone disc and/or the driven fixed cone disc, the pressing part is a cam pressing mechanism, the cam pressing mechanism comprises a disc spring, a driving cam, a driven cam, a retainer and a rolling body, one axial end of the disc spring abuts against the driving shaft, the other end of the disc spring abuts against the driving fixed cone disc or the other end of the disc spring abuts against the driving cam, a plurality of raceways uniformly distributed in the circumferential direction are respectively arranged on the opposite end surfaces of the driving cam and the driven cam, the driving cam and the driven cam are connected through the rolling body clamped between the oppositely arranged raceways, the retainer is sleeved on the rolling body and is arranged between the driving cam and the driven cam, and the back of the driven cam is connected with the driving fixed cone disc and/or the driven fixed cone disc; the speed regulating part comprises a driver, a speed regulating shaft and a linear reciprocating mechanism for converting rotation into linear motion, and the linear reciprocating mechanism is arranged on the back surfaces of the driving dynamic conical disc and the driven dynamic conical disc;
the center distance between the driving shaft and the driven shaft is a, the unit is mm, and the following requirements are met:
wherein T is the maximum torque value of the external characteristic curve of the continuously variable transmission at the full speed of the input power source, and the unit is N.m.
2. The variable transmission according to claim 1, wherein the driving fixed cone disc includes a driving fixed cone disc conical surface section and a driving fixed cone disc sleeve section, the driving fixed cone disc sleeve section is sleeved outside the driving shaft, one end of the driving fixed cone disc sleeve section is fixedly connected with the driving fixed cone disc conical surface section, the driving movable cone disc is connected outside the driving fixed cone disc sleeve section by a spline connection sleeve, the splines on the driving movable cone disc are internal splines, which are defined as internal splines a, and the small diameter of the internal splines a is d 1 The outer part of the shaft sleeve section of the driving fixed cone disc is provided with an external spline defined as an external spline A, and the major diameter of the external spline A is d 2 The length of the internal spline A is L 1 The length of the external spline A is L 2 Wherein L is 1 L2 or more times 2 The spline surface of the internal spline A comprises two axial intervals L 3 A step surface of, L 3 L is more than or equal to 0.12a 3 Less than or equal to 0.45a, the small diameter of the step surface is (d) 1 -6.8)mm～(d 1 -0.1) mm, said d 1 And d 2 D is not less than 2.25mm 2 –d 1 Less than or equal to 7.5mm; the driven fixed cone disc comprises a driven fixed cone disc conical surface section and a driven fixed cone disc shaft sleeve section, the driven fixed cone disc shaft sleeve section is sleeved outside the driven shaft, one end of the driven fixed cone disc shaft sleeve section is fixedly connected with the driven fixed cone disc conical surface section, the driven movable cone disc is connected outside the driven fixed cone disc shaft sleeve section through a spline connecting sleeve, the spline on the driven movable cone disc is an internal spline, defined as an internal spline B, and the small diameter of the internal spline B is d 3 The external spline is arranged outside the driven fixed cone disc shaft sleeve section and defined as an external spline B, and the major diameter of the external spline B is d 4 The length of the internal spline B is L 4 The length of the external spline B is L 5 Wherein L is 4 L2 or more times 5 The spline surface of the internal spline B comprises two axial spaces L 6 The step surface of, L 6 L is more than or equal to 0.12a 6 Not more than 0.45a, the small diameter of the step surface is (d) 3 -0.1mm)～(d 3 -1.8 mm), said d 3 And d 4 Satisfies 2.25mm≤d 4 –d 3 ≤7.5mm。
3. The variable transmission according to claim 1, wherein the driving shaft and the driven shaft are each provided with at least one axial long hole and a plurality of radial holes, one end of each of the radial holes communicates with the outside, the other end of each of the radial holes communicates with the inside of the axial long hole, at least one end of each of the axial long holes communicates with the outside, and the diameter of the radial hole at the minimum aperture is 0.8 to 6mm.
4. The variable transmission according to claim 1, further comprising a case disposed outside the variable transmission body and configured to accommodate the variable transmission body, wherein the case is divided into a front case and a rear case, a separation bearing seat is disposed on the front case, 2 to 4 lip-shaped sealing rings are disposed between the driving shaft and the separation bearing seat, and the lips of the lip-shaped sealing rings face the variable transmission body.
5. The variable transmission according to claim 1, wherein the cam pressurizing mechanism further comprises a disc spring seat, the disc spring seat comprises an outer circular ring part, an inner circular ring part and an annular groove, the annular groove fixedly connects one end of the outer circular ring part with one end of the inner circular ring part, so that the inner circular ring part and the outer circular ring part are of circular ring structures with the same physical axis, a chamfer is arranged at the outer circle of the joint of the outer circular ring part and the annular groove, at least two U-shaped groove through holes are formed in the annular groove, the U-shaped groove through holes are connected with the annular groove, and the U-shaped openings of the U-shaped groove through holes face the outer circular ring part; the disc spring seat is arranged outside the disc spring and used for supporting the disc spring, the bevel end of the disc spring faces the fixed cone disc after the disc spring is stacked in parallel, the reverse side of the bevel end is abutted against the inner side of the annular groove of the disc spring seat, the thickness of the inner side of the annular groove of the disc spring seat is S, and the S satisfies that S is not less than 0.021a and not more than 0.095a; the driving cam is also provided with a chamfer at the excircle of the circular end face at one side without the raceway.
6. The variable transmission according to claim 1, wherein the cage is a thin plate with a circular ring structure, circular through holes with the same number as the rolling elements are arranged on the cage, the circular through holes are used for accommodating the rolling elements, and the thickness of the cage is 1.5-5.8 mm.
7. The variable transmission according to claim 1, wherein at least three U-shaped grooves are distributed in the circumferential direction of the back surface of the conical surface of the driving dynamic cone disk and/or the driven dynamic cone disk, the U-shaped opening of each U-shaped groove faces the outer circle, and the area of each U-shaped groove is 1% to 15% of the surface area of the back surface of the conical surface.
8. The variable transmission of claim 2, wherein one or more radial holes are provided in the range from the spline of the driving fixed cone sleeve section and/or the driven fixed cone sleeve section to the end surface of the sleeve section far away from the conical surface and/or close to the conical surface, which is less than or equal to 55mm, and the total cross-sectional area at the maximum diameter of the radial holes is e, which is measured in mm 2 And e satisfies 0.08 a-0.75 a.
9. A tractor characterized in that it is provided with a continuously variable transmission according to any one of claims 1 to 8.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222290044.5U CN218063325U (en) | 2022-08-30 | 2022-08-30 | Tractor and continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222290044.5U CN218063325U (en) | 2022-08-30 | 2022-08-30 | Tractor and continuously variable transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN218063325U true CN218063325U (en) | 2022-12-16 |
Family
ID=84404797
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202222290044.5U Active CN218063325U (en) | 2022-08-30 | 2022-08-30 | Tractor and continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN218063325U (en) |
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2022
- 2022-08-30 CN CN202222290044.5U patent/CN218063325U/en active Active
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