CN218761171U - Tractor, stepless speed change device and speed regulation mechanism of stepless speed change device - Google Patents
Tractor, stepless speed change device and speed regulation mechanism of stepless speed change device Download PDFInfo
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- CN218761171U CN218761171U CN202223283316.5U CN202223283316U CN218761171U CN 218761171 U CN218761171 U CN 218761171U CN 202223283316 U CN202223283316 U CN 202223283316U CN 218761171 U CN218761171 U CN 218761171U
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Abstract
The invention discloses a method for setting a speed regulation mechanism of a conical disc type stepless speed change device, wherein the conical disc type stepless speed change device comprises a conical disc type transmission device and a speed regulation device, a flexible transmission element in the conical disc type transmission device is clamped on a driving conical disc group and a driven conical disc group, the speed regulation mechanism drives a driving dynamic conical disc and a driven dynamic conical disc to axially move, the speed regulation structure comprises a driving machine for outputting power, a speed regulation shaft and a linear reciprocating mechanism for converting rotation into linear motion, and the relationship between the maximum power of the driving machine and each parameter is reasonably set, so that the speed regulation mechanism of the conical disc type stepless speed change device can reasonably select the power and the setting form of the driving machine of the speed regulation mechanism of the conical disc type stepless speed change device, and the conical disc type stepless speed change device is ensured to efficiently and normally work.
Description
Technical Field
The invention relates to the field of a continuously variable transmission, in particular to a method for setting a speed regulating mechanism of a conical disc type continuously variable transmission.
Background
In recent years, domestic work machine transmission devices generally adopt stepped gear shifting and rear axles, although stepped conversion among speeds of a plurality of gears can be realized, because the speeds of all gears are fixed values, when a certain work mode is carried out, only speeds close to the work requirement can be selected for work or the rotating speed of an engine can be regulated for speed increase and speed reduction, and the optimal work efficiency and the optimal efficiency of the engine are difficult to exert.
The cone disc type continuously variable transmission transmits power in a friction mode, has wide speed change range and higher efficiency, is widely applied to a plurality of working fields, is matched with a forward and backward transmission device for use, and can meet the requirement of high-efficiency operation of power machinery. The conical disc type stepless speed changer pushes the two conical discs in different directions through the speed regulating mechanism, so that the working radius of the contact point of the chain and the conical discs is changed, and the speed change is realized. The speed regulating mechanism is an important component of the cone disc type continuously variable transmission, but due to the working characteristics of the cone disc type continuously variable transmission, the speed regulating forces required by different speed ratios are different, the speed regulating force which is too small cannot meet the speed changing requirement, the speed regulating force which is too large causes overlong speed regulating time and low operability of the whole machine under the condition that the power of the existing hydraulic motor or motor is certain, and the existing driving machine cannot be used as a power source to drive the cone disc type continuously variable transmission to regulate the speed.
Chinese patent publication CN114233847A discloses a speed regulating mechanism of a continuously variable transmission and a continuously variable transmission, and the technical scheme can meet the requirement of fast speed change, and is beneficial to improving the driving experience, but the speed regulating mechanism cannot be applied to power machines such as tractors.
Disclosure of Invention
The invention provides a method for setting a speed regulation mechanism of a conical disc type stepless speed change device, which can reasonably select a power source of the speed regulation mechanism of the conical disc type stepless speed change device, set the speed regulation mechanism and ensure the normal work of the conical disc type stepless speed change device.
In order to solve the technical problems, the invention adopts a technical scheme that:
a speed regulation mechanism of a stepless speed change device is a cone disc type stepless speed change device and comprises a cone disc type transmission device and a speed regulation mechanism, wherein the cone disc type transmission device comprises a driving cone disc set, a driven cone disc set and a flexible transmission element, the driving cone disc set comprises a driving fixed cone disc and a driving movable cone disc which are installed on a driving shaft, the driven cone disc set comprises a driven fixed cone disc and a driven movable cone disc which are installed on a driven shaft, one end of the flexible transmission element is clamped between the driving fixed cone disc and the driving movable cone disc, and the other end of the flexible transmission element is clamped between the driven fixed cone disc and the driven movable cone disc.
Speed adjusting mechanism is used for the drive initiative to move the conical disk and carry out axial displacement with driven moving the conical disk, speed adjusting mechanism is including being used for output power's driver, speed governing axle, fixed ratio drive mechanism and turning into rectilinear motion's straight reciprocating mechanism with rotating, the driver is connected with the speed governing axle is direct or indirect, the maximum power of driver is P, and the unit is tile (watt), satisfies:
wherein i max The maximum transmission ratio of the cone disc type stepless speed change device is the center distance between a driving shaft and a driven shaft of the cone disc type stepless speed change device, and the unit is mm. />
In a preferred embodiment of the invention, the linear reciprocating mechanism is a screw mechanism, the driving machine is connected with the speed regulating shaft in a direct transmission or indirect transmission mode, the speed ratio of the connecting mechanism of the driving machine and the speed regulating shaft is i, and the fixed-ratio transmission mechanism comprises a first fixed-ratio transmission mechanism and a second fixed-ratio transmission mechanism; the driving ends of the first constant ratio transmission mechanism and the second constant ratio transmission mechanism are both arranged on the speed regulating shaft, the screw mechanism comprises a first nut, a first hollow screw, a second nut and a second hollow screw, the driven end of the first constant ratio transmission mechanism is connected with the first nut, the first nut is spirally connected with the outer screw of the first hollow screw through an inner screw,the first hollow screw rod is sleeved on the driving shaft, the driven end of the second constant-ratio transmission structure is connected with the second nut, the second nut is spirally connected with the outer screw of the second hollow screw rod through the inner screw, the second hollow screw rod is sleeved on the driven shaft, and the lead of the first hollow screw rod and the lead of the first nut are P h1 The lead of the second hollow screw and the second nut is P h2 In which P is h1 And P h2 The unit of (a) is mm, and the ratio of the number of teeth at the driven end to the number of teeth at the driving end of the first fixed ratio transmission mechanism is i 1 The ratio of the number of teeth at the driven end to the number of teeth at the driving end of the second constant ratio transmission mechanism is i 2 Said P is h1 、P h2 、i 1 And i 2 Satisfy P h1 /i 1 ＝P h2 /i 2 。
In a preferred embodiment of the present invention, the linear reciprocating mechanism is a cam mechanism, the cam mechanism includes at least two pairs of driving cams and driven cams which are arranged axially opposite to each other, the diameter end faces at the centers of the driving cams and the driven cams are provided with n raceways which change monotonically in n angles, the driving machine is connected with the speed regulating shaft through a direct connection or an indirect transmission manner, the speed ratio of the driving machine to the speed regulating shaft is i, the fixed ratio transmission mechanism includes a third fixed ratio transmission mechanism, a fourth fixed ratio transmission mechanism, a fifth fixed ratio transmission mechanism and a sixth fixed ratio transmission mechanism, the driving cams include a first driving cam and a second driving cam, the driven cams include a first driven cam and a second driven cam, one end of the speed regulating shaft is connected with the first driving cam through the third fixed ratio transmission mechanism, the fourth fixed ratio transmission mechanism is connected with the first driven cam, the first driving cam and the first driven cam are abutted through rollers clamped on the opposite raceways, the first driving cam is abutted through a manner (such as a bearing) which allows mutual rotation with the driving cone disc, and the first driving cam is indirectly abutted through a driving shaft or a driven cam box body; the other end of the speed regulating shaft is connected with a second driving cam through a fifth constant ratio transmission mechanism, a sixth constant ratio transmission mechanism is connected with a second driven cam, and the second driving camAnd a second driven cam connected with the rollers via the opposite raceways, the second driving cam abutting against the driven cone in a manner allowing for mutual rotation (e.g., a bearing), the second driven cam abutting against the driven shaft or the casing in a direct or indirect manner, the raceways of the first driving cam and the first driven cam making an angle β with respect to the vertical plane of the cam centerline 1 The diameter of the uniformly distributed centers of the raceways of the first driving cam and the first driven cam (i.e. the diameter of the end face of the raceway provided with n monotonically-changing angles) is d 1 The included angle between the roller paths of the second driving cam and the second driven cam and the vertical plane of the central line of the end face cam is beta 2 The diameter of the center of the roller path of the second driving cam and the second driven cam is d 2 The ratio of the number of teeth at the driven end to the number of teeth at the driving end of the third fixed-ratio transmission mechanism is i 3 The ratio of the number of teeth at the driven end to the number of teeth at the driving end of the fourth constant ratio transmission mechanism is i 4 The ratio of the number of teeth at the driven end to the number of teeth at the driving end of the fifth constant-ratio transmission mechanism is i 5 The ratio of the number of teeth at the driven end to the number of teeth at the driving end of the sixth constant-ratio transmission mechanism is i 6 Said beta is 1 、β 2 、i 3 、i 4 、i 5 And i 6 Satisfy d 1 tanβ 1 (1/i 3 -1/i 4 )＝d 2 tanβ 2 (1/i 5 -1/i 6 )。
In a preferred embodiment of the invention, the maximum output speed of the drive machine is n w The unit is r/min, satisfies
In a preferred embodiment of the present invention, the number of the external screw turns of the first hollow screw is N 1 The number of turns of the inner screw of the first nut is N 2 The number of turns of the external screw thread of the second hollow screw is N 3 The number of turns of the inner screw of the second nut is N 4 Said N is 1 、N 2 、N 3 And N 4 Satisfies the following conditions:
/>
in a preferred embodiment of the invention, the distance between the center of the speed regulating shaft and the driving shaft is equal to the distance between the center of the speed regulating shaft and the center of the driven shaft, and P is h1 、P h2 、i 1 And i 2 Satisfy P h1 ＝P h2 And i is 1 ＝i 2 。
In a preferred embodiment of the invention, the drive machine is an electric or hydraulic motor.
A stepless speed change device is a conical disk type stepless speed change device, and the conical disk type stepless speed change device uses the speed regulating mechanism.
A non-road working machine is provided with the continuously variable transmission.
A tractor is provided with the stepless speed change device.
The invention has the beneficial effects that:
the method comprises the following steps that 1, the speed regulating mechanism of the cone disc type stepless speed change device is specifically set, so that the device can reasonably select the power and the arrangement form of a driving machine of the speed regulating mechanism of the cone disc type stepless speed change device, and the cone disc type stepless speed change device is ensured to work efficiently and normally.
2, the invention reasonably sets the parameters matched with each other between the power source of the speed regulating mechanism of the conical disc type stepless speed change device and the speed regulating device, and converts the rotary motion into effective linear motion. By reasonably setting the components of the speed regulating mechanism and the proportioning mode among the components, the structure of the speed regulating mechanism is more compact, and the requirement that the speed change cannot be completed by undersize speed regulating force under the conditions of different speed ratios and different engine input torques is avoided, or the defect that the speed regulating time is too long is avoided; the speed change requirement can be quickly finished when the load suddenly changes (such as the ditch ridge on the road surface and the ponding road surface suddenly) in the operation process of the whole machine, and the working reliability of the system is ensured.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments are briefly introduced below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings can be obtained by those skilled in the art without inventive efforts, wherein:
fig. 1 is a schematic structural view of an embodiment 1 of a conical disc type continuously variable transmission according to the present invention.
Fig. 2 is a schematic structural view of embodiment 2 of the conical-disc continuously variable transmission of the present invention.
FIG. 3 is a graph showing the theoretical required shifting force of the nut of embodiment 1 from a high speed ratio to a low speed ratio.
FIG. 4 is a graph of the theoretical required shifting force for the nut of embodiment 1 as it moves from a low speed ratio to a high speed ratio.
FIG. 5 is a graph showing the change of the actual output governing force of the driving machine of embodiment 1 under the conditions of different directions and different speed ratios.
The parts in the drawings are numbered as follows: 1. the variable-speed transmission mechanism comprises a driving shaft, 2, an end face cam pressurizing mechanism, 3, a second fixed-ratio transmission mechanism, 4, a driving fixed cone disc, 5, a driving movable cone disc, 6, a speed regulating gear set, 7, a driving machine, 8, a speed regulating shaft, 9, a first fixed-ratio transmission mechanism, 10, a first nut, 11, a first hollow screw, 12, a driven fixed cone disc, 13, a flexible transmission element, 14, a driven movable cone disc, 15, a second nut, 16, a second hollow screw, 17, a third fixed-ratio transmission mechanism, 18, a fourth fixed-ratio transmission mechanism, 19, a first driven cam, 20, a roller, 21, a first driving cam, 22, a second driven cam, 23, a second driving cam, 24, a sixth fixed-ratio transmission mechanism and 25.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Example 1
As shown in fig. 1, a conical-disc type continuously variable transmission includes: the speed regulating mechanism is used for outputting power, and the conical disc type power device is directly or indirectly connected with the speed regulating mechanism.
The cone disc type power device comprises a driving cone disc set, a driven cone disc set, an end face cam pressurizing mechanism and a flexible transmission element, wherein the flexible transmission element is clamped on the driving cone disc set and the driven cone disc set, the driving cone disc set comprises a driving fixed cone disc and a driving movable cone disc which are installed on a driving shaft, the driven cone disc set comprises a driven fixed cone disc and a driven movable cone disc which are installed on a driven shaft, the speed regulating mechanism drives the driving movable cone disc and the driven movable cone disc to axially move, the speed regulating mechanism comprises a driving machine used for outputting power, a speed regulating shaft and a linear reciprocating mechanism used for converting rotation into linear motion, the driving machine is indirectly connected with the speed regulating shaft through the speed regulating gear set, a first ratio transmission mechanism and a second ratio transmission mechanism are installed on the speed regulating shaft, the linear reciprocating mechanism is a spiral mechanism, the spiral mechanism comprises a first nut, a second nut, a first hollow screw and a second hollow screw, the first ratio transmission mechanism is connected with the first nut, the first hollow screw is arranged on the first hollow screw, the first hollow screw is sleeved on the driving shaft, the second nut is connected with the second hollow screw, the second nut is arranged on the second hollow screw, and the driven shaft is sleeved on the second hollow screw.
In addition, the back of at least one pressurizing cone disk of the driving fixed cone disk and the driven fixed cone disk is provided with an end face cam pressurizing mechanism, and the driving movable cone disk and the driven movable cone disk are connected with a speed regulating mechanism.
In addition, the maximum power P of the drive is 9.74KW, where i max The maximum transmission ratio (5 in the embodiment) of the cone-disc type stepless speed change device and the center distance (350 mm in the embodiment) between a driving shaft and a driven shaft of the cone-disc type stepless speed change device satisfy the following conditions:
in addition, the linear reciprocating mechanism is a spiral mechanism, a transmission mechanism is directly or indirectly connected between the driving machine and the speed regulating shaft, and the driving machine and the speed regulatorThe coupling mechanism velocity ratio of fast axle is 8.22 for i, install first definite proportion drive mechanism and second definite proportion drive mechanism on the speed governing axle, the nut includes first nut and second nut, hollow screw includes first hollow screw and the hollow screw of second, first definite proportion drive mechanism is connected with first nut, first nut sets up on first hollow screw, first hollow screw cover is established on the driving shaft, second definite proportion drive mechanism is connected with the second nut, the second nut sets up on the hollow screw of second, the hollow screw cover of second is established on the driven shaft, first hollow screw and first nut helical pitch P h1 10mm, second hollow screw and second nut lead P h2 10mm, the ratio i of the number of teeth at the driven end to the number of teeth at the driving end of the first fixed ratio transmission mechanism 1 2.39, the ratio i of the number of teeth at the driven end to the number of teeth at the driving end of the second fixed ratio transmission mechanism 2 Is 2.39,P h1 、P h2 、i 1 And i 2 Satisfies P h1 /i 1 ＝P h2 /i 2 。
In addition, the maximum output rotating speed of the driver is n w Is 300r/min, meets the requirements
In addition, the number of turns of the external screw of the first hollow screw is N 1 Is 9, the number of turns of the inner screw of the first nut is N 2 Is 5, the number of the external screw turns of the second hollow screw is N 3 Is 9, the number of turns of the inner screw of the second nut is N 4 Is 5, the said N 1 、N 2 、N 3 And N 4 Satisfies the following conditions:
in addition, the speed regulation wheelbase has equal center distance between the driving axle and the driven axle, P h1 、P h2 、i 1 And i 2 Also satisfies P h1 ＝P h2 And i is 1 ＝i 2 。
In addition, the first nut abuts against the driving cone disc, and the first hollow screw abuts against the driving shaft through the axial locking device; the second nut is abutted against the driven taper disc, and the second hollow screw is abutted against the driven shaft through the axial locking device.
In addition, the driving machine is an electric motor or a hydraulic motor.
The conical disc type stepless speed change device of the embodiment specifically works according to the following principle: the engine transmits power to the conical disc type transmission device, when stepless speed change is needed, the driving machine transmits speed regulating force to the first nut and the second nut through the speed regulating gear set and the first and second fixed ratio transmission mechanisms respectively, the first and second nuts rotate relative to the corresponding hollow screw, and one lead P is fed every rotation h1 And P h2 The flexible transmission element and the connecting contact of the driving cone disc set and the driven cone disc set are changed in working radius, so that stepless speed change is completed.
As an important part of the stepless speed change device, the speed regulating mechanism of the invention needs to overcome that the axial force is the difference value of the axial force of the driving shaft and the driven shaft in the process of pushing the driving cone disc and the driven cone disc to move in the same speed and the same direction, while the pulling force of the flexible element keeps unchanged in the process of transmitting power, because the wrap angles of the driving shaft and the driven shaft are not equal in the speed changing process, the axial force of the stepless speed change device on the driving shaft and the driven shaft is reflected to be not equal, namely as shown in figures 3-4, when the speed is regulated in the direction of small speed ratio at large speed ratio in figure 3, when the initial speed ratio is greater than a certain value, the theoretically required speed regulating force is zero, when the speed ratio is less than a certain value along with the reduction of the speed ratio, the theoretically required speed regulating force is increased along with the reduction of the speed ratio, and the increasing rate is decreased along with the reduction of the speed ratio; when the speed is adjusted in the direction of the small speed ratio to the large speed ratio in fig. 4, when the speed ratio is smaller than a certain value, the theoretically required speed adjusting force is zero, when the speed ratio is larger than a certain value along with the increase of the speed ratio, the theoretically required speed adjusting force is increased along with the increase of the speed ratio, and the increasing rate is increased along with the increase of the speed ratio, namely, the speed adjusting force required by the nut in the speed adjusting process in different directions is different, as shown in a change diagram of the actual output speed adjusting force of the driving machine shown in fig. 5, the theoretically required speed adjusting force is reduced under the condition that the actual mechanical loss power exists, but it is obvious that the maximum speed adjusting force in the speed adjusting process of the small speed ratio to the large speed ratio is obviously larger than the speed adjusting process of the large speed ratio to the small speed ratio, and the maximum speed adjusting force is generated in the minimum speed ratio or the maximum speed ratio, and the output speed adjusting force of the driving machine is also different under the different directions and different speed ratios, namely, the speed adjusting mechanism is designed to meet the efficiency and simultaneously meet the required maximum speed adjusting force generating point.
Example 2
As shown in fig. 2, the linear reciprocating mechanism of this embodiment is a cam mechanism, the cam mechanism includes at least two pairs of driving cams and driven cams which are axially arranged oppositely, the diameter end surfaces of the centers of the driving cams and the driven cams are provided with 3 raceways which change monotonically with angles, the driving machine is connected with the speed regulating shaft through a direct connection or an indirect transmission manner, the speed ratio i of the driving machine to the speed regulating shaft is 1.74, the proportional transmission mechanism includes a third proportional transmission mechanism, a fourth proportional transmission mechanism, a fifth proportional transmission mechanism and a sixth proportional transmission mechanism, the driving cam includes a first driving cam and a second driving cam, the driven cam includes a first driven cam and a second driven cam, one end of the speed regulating shaft is connected with the first driving cam through the third proportional transmission mechanism, the fourth proportional transmission mechanism is connected with the first driven cam, the first driving cam and the first driven cam are connected through rollers clamped on the raceways, the first driving cam is abutted against the driving conical disk through a bearing in a manner allowing mutual rotation, and the first driving cam is directly abutted against the driving shaft or the first driven cam indirectly abutted against the driving shaft through a bearing; the other end of the speed regulating shaft is connected with a second driving cam through a fifth constant ratio transmission mechanism, a sixth constant ratio transmission mechanism is connected with a second driven cam, the second driving cam and the second driven cam are connected through rollers clamped on opposite roller paths, the second driving cam abuts against a driven movable conical disc in a manner that the bearings allow mutual rotation, and a second driven cam abuts against the driven movable conical disc in a manner that the bearings allow mutual rotationThe movable cam is abutted against the driven shaft or the box body in a direct or indirect mode, and the included angle beta between the roller paths of the first driving cam and the first driven cam and the vertical plane of the central line of the end face cam 1 Is 6 degrees, and the diameter d of the center of the roller paths of the first driving cam and the first driven cam is 1 The included angle beta between the raceways of the second driving cam and the second driven cam and the vertical plane of the central line of the end cam is 224mm 2 Is 6 degrees, and the diameter d of the center of the roller path of the second driving cam and the second driven cam is 2 The tooth number of the driven end of the third fixed ratio transmission mechanism is 224mm, and the ratio i of the tooth number of the driven end to the tooth number of the driving end of the third fixed ratio transmission mechanism 3 3.94, the ratio i of the number of teeth at the driven end to the number of teeth at the driving end of the fourth fixed ratio transmission mechanism 4 3.68, the ratio i of the number of teeth at the driven end to the number of teeth at the driving end of the fifth fixed-ratio transmission mechanism 5 3.94, the ratio i of the number of teeth at the driven end to the number of teeth at the driving end of the sixth fixed ratio transmission mechanism 6 Is 3.68, the beta 1 、β 2 、i 3 、i 4 、i 5 And i 6 Satisfy d 1 tanβ 1 (1/i 3 -1/i 4 )＝d 2 tanβ 2 (1/i 5 -1/i 6 ) The requirements of (2).
Example 3
The tractor layout and the speed regulating mechanism are combined. The power device of the tractor comprises an engine, a clutch, a conical disc type stepless speed change device, a gear shifting transmission device and a rear axle; the power generation device is connected with the input end of the cone disc type stepless speed change device through the clutch, the driven shaft of the cone disc type stepless speed change device is connected with the gear shifting transmission device, and the output end of the gear shifting transmission device is directly connected with the input end of the rear axle.
The cone disc type stepless speed change device comprises a driving shaft, a driving cone disc set, a driven shaft, a driven cone disc set, a cam pressurizing mechanism, a speed regulating mechanism and a steel flexible transmission element; the driving cone disc set is sleeved on the driving shaft, the driven cone disc set is sleeved on the driven shaft, the steel flexible transmission element is clamped between the driving cone disc set and the driven cone disc set, the cam pressurizing mechanism is arranged on the back face of the driving fixed cone disc and/or the driven fixed cone disc, and the speed regulating mechanism is abutted to the driving movable cone disc and the driven movable cone disc through bearings capable of bearing axial force.
The speed regulating mechanism comprises a driving machine for outputting power, a speed regulating shaft, a fixed-ratio transmission mechanism and a spiral mechanism, wherein the driving machine is connected with the speed regulating shaft in an indirect transmission mode, and the fixed-ratio transmission mechanism is a gear transmission mechanism and comprises a first fixed-ratio transmission mechanism and a second fixed-ratio transmission mechanism; driving gears of the first constant ratio transmission mechanism and the second constant ratio transmission mechanism are arranged on the speed regulating shaft in a mode of spline matching with the retainer ring; the screw mechanism comprises a first nut, a first hollow screw, a second nut, a second hollow screw, a roller and a reverser, a driven gear of the first proportional transmission structure and the first nut are integrated, the first nut is in screw connection with the outer screw of the first hollow screw through the inner screw, and the first hollow screw is matched with a locking nut to abut against a driving shaft through a bearing capable of bearing axial force; the driven gear of second constant ratio transmission structure makes integratively with the second nut, the second nut realizes the spiral through the external screw of interior spiral and second hollow screw and meets, the second hollow screw offsets with the driven shaft through the bearing cooperation lock nut that can bear the axial force, lock nut is dextrorotation on the driving shaft, and lock nut is the levogyration on the driven shaft, all be provided with the roller in the nut links to each other the helicla flute with the screw rod, all be provided with the reverser that can make the roller pass through on first nut and the second nut.
Comparative example 1
Alternative to the drive of example 1, the maximum power P of the drive of this example was set to 3KW, and i max And a is set to be the same as in example 1, and is not satisfied
The other setting modes are the same as those of the embodiment 1, and through a full-stroke speed regulation test under the same conditions, the fact that the speed regulation is forced when the speed ratio is greater than 1.55 in the speed regulation process of a small speed ratio and is forced when the speed ratio is less than 0.75 in the speed regulation process of a large speed ratio in the speed regulation process of a small speed ratio of a comparative example is found, and the full-stroke speed regulation can be completed in the embodiment 1.
Comparative example 2
The constant ratio transmission mechanism of the comparison example adopts the ratio i of the number of teeth at the driven end to the number of teeth at the driving end of the first constant ratio transmission mechanism 1 2.43, the ratio i of the number of teeth at the driven end to the number of teeth at the driving end of the second fixed ratio transmission mechanism 2 2.3 alternative example 1, first hollow screw and first nut lead P h1 10mm, second hollow screw and second nut lead P h2 Is 10mm, P h1 、P h2 、i 1 And i 2 Does not satisfy P h1 /i 1 ＝P h2 /i 2 . When the flexible transmission element is a chain, through a reliability test under the same condition, in the process of running at a small speed ratio, the deviation of the comparative example chain is too large, and a welding point on a pin shaft falls off, while the reliability test under different speed ratios can be completed in the embodiment 1.
Comparative example 3
Alternative to the drive of example 1, the maximum output speed of the drive of this example was n w The central distance a between a driving shaft and a driven shaft of the cone disc type stepless speed change device is 350mm, the speed ratio of a connecting mechanism of a driving machine and a speed regulating shaft is 8.22, and the ratio i of the number of teeth at a driven end to the number of teeth at a driving end of a first constant ratio transmission mechanism is 100r/min 1 Is 2.39, the first hollow screw and the first nut lead P h1 In the case of 10mm, it is not satisfied
Through a full-stroke speed regulation test under the same condition, the comparison example is found to have too long circulating speed regulation time and cannot meet the dynamic response requirement of the walking machinery.
The above description is only an embodiment of the present invention, and not intended to limit the scope of the present invention, and all modifications of equivalent structures and equivalent processes, which are made by the present specification, or directly or indirectly applied to other related technical fields, are included in the scope of the present invention.
Claims (9)
1. A speed regulation mechanism of a stepless speed change device, wherein the stepless speed change device is a cone disc type stepless speed change device and comprises a cone disc type transmission device and a speed regulation mechanism, the cone disc type transmission device comprises a driving cone disc set, a driven cone disc set and a flexible transmission element, the driving cone disc set comprises a driving fixed cone disc and a driving movable cone disc which are arranged on a driving shaft, the driven cone disc set comprises a driven fixed cone disc and a driven movable cone disc which are arranged on a driven shaft, one end of the flexible transmission element is clamped between the driving fixed cone disc and the driving movable cone disc, and the other end of the flexible transmission element is clamped between the driven fixed cone disc and the driven movable cone disc, and the speed regulation mechanism is characterized in that:
speed adjusting mechanism is used for the drive initiative to move the conical disk and carry out axial displacement with driven moving the conical disk, speed adjusting mechanism is including being used for output power's driver, speed governing axle, fixed ratio drive mechanism and turning into rectilinear motion's straight reciprocating mechanism with rotating, the driver is connected with the speed governing axle is direct or indirect, the maximum power of driver is P, and the unit is tile (watt), satisfies:
wherein i max The maximum transmission ratio of the cone disc type stepless speed change device is the center distance between a driving shaft and a driven shaft of the cone disc type stepless speed change device, and the unit is mm.
2. The governor of the stepless speed change device according to claim 1, wherein the linear reciprocating mechanism is a screw mechanism, the driver is connected with the governor shaft by direct transmission or indirect transmission, the speed ratio of the driver to the governor shaft is i, and the fixed ratio transmission mechanism comprises a first fixed ratio transmission mechanism and a second fixed ratio transmission mechanism; the driving ends of the first constant ratio transmission mechanism and the second constant ratio transmission mechanism are both arranged on the speed regulating shaft, the screw mechanism comprises a first nut, a first hollow screw, a second nut and a second hollow screw, the driven end of the first constant ratio transmission mechanism is connected with the first nut, the first nut is spirally connected with the outer screw of the first hollow screw through an inner screw, the first hollow screw is sleeved on the driving shaft, the driven end of the second constant ratio transmission mechanism is connected with the second nut,the second nut is spirally connected with the outer screw of the second hollow screw rod through the inner screw, the second hollow screw rod is sleeved on the driven shaft, and the lead of the first hollow screw rod and the lead of the first nut are P h1 The lead of the second hollow screw and the second nut is P h2 In which P is h1 And P h2 The unit of (a) is mm, and the ratio of the number of teeth at the driven end to the number of teeth at the driving end of the first fixed ratio transmission mechanism is i 1 The ratio of the number of teeth at the driven end to the number of teeth at the driving end of the second constant ratio transmission mechanism is i 2 Said P is h1 、P h2 、i 1 And i 2 Satisfy P h1 /i 1 ＝P h2 /i 2 。
3. The speed-regulating mechanism of a continuously variable transmission according to claim 1, wherein the linear reciprocating mechanism is a cam mechanism, the cam mechanism includes at least two pairs of driving cams and driven cams which are axially arranged oppositely, the diameter end faces of the centers of the driving cams and the driven cams are provided with n raceways which are oppositely and monotonically varied in angle, the driving machine is connected with the speed-regulating shaft through a direct connection or an indirect transmission manner, the speed ratio of the driving machine to the speed-regulating shaft is i, the fixed ratio transmission mechanism includes a third fixed ratio transmission mechanism, a fourth fixed ratio transmission mechanism, a fifth fixed ratio transmission mechanism and a sixth fixed ratio transmission mechanism, the driving cams include a first driving cam and a second driving cam, the driven cams include a first driven cam and a second driven cam, one end of the speed-regulating shaft is connected with the first driving cam through the third fixed ratio transmission mechanism, the fourth fixed ratio transmission mechanism is connected with the first driven cam, the first driving cam and the first driven cam are connected with each other through clamping on the raceways, the first driving cam is directly abutted against the driving disk or against the driving disk through a driving shaft or a driving roller; the other end of the speed regulating shaft is connected with a second driving cam through a fifth constant-ratio transmission mechanism, a sixth constant-ratio transmission mechanism is connected with a second driven cam, and the second driving cam and the second driven cam are clampedThe rollers on the opposite roller paths are connected, the second driving cam is abutted against the driven cone disc in a manner of allowing mutual rotation, the second driven cam is abutted against the driven shaft or the box body in a direct or indirect manner, and the included angle between the roller paths of the first driving cam and the first driven cam and the vertical plane of the center line of the cam is beta 1 The diameters of the uniformly distributed centers of the raceways of the first driving cam and the first driven cam are d 1 The included angle between the roller paths of the second driving cam and the second driven cam and the vertical plane of the central line of the end face cam is beta 2 The diameter of the center of the roller path of the second driving cam and the second driven cam is d 2 The ratio of the number of teeth at the driven end to the number of teeth at the driving end of the third fixed-ratio transmission mechanism is i 3 The ratio of the number of teeth at the driven end to the number of teeth at the driving end of the fourth constant ratio transmission mechanism is i 4 The ratio of the number of teeth at the driven end to the number of teeth at the driving end of the fifth constant-ratio transmission mechanism is i 5 The ratio of the number of teeth at the driven end to the number of teeth at the driving end of the sixth constant-ratio transmission mechanism is i 6 Said beta is 1 、β 2 、i 3 、i 4 、i 5 And i 6 Satisfy d 1 tanβ 1 (1/i 3 -1/i 4 )＝d 2 tanβ 2 (1/i 5 -1/i 6 )。
4. The governor mechanism of the continuously variable transmission according to claim 1, wherein the maximum output rotation speed of the drive machine is n w Has a unit of r/min, satisfies
5. A governor mechanism for a continuously variable transmission according to claim 2, wherein the first hollow screw has an outer spiral of N turns 1 The number of turns of the inner screw of the first nut is N 2 The number of turns of the external screw thread of the second hollow screw is N 3 The number of turns of the inner screw of the second nut is N 4 Said N is 1 、N 2 、N 3 And N 4 Satisfies the following conditions:
6. a governor mechanism for a continuously variable transmission according to claim 2, wherein the governor shaft is located at the same distance from the center of the drive shaft and the center of the driven shaft, and P is the same distance from the center of the driven shaft h1 、P h2 、i 1 And i 2 Satisfy P h1 ＝P h2 And i is 1 ＝i 2 。
7. A variator of a continuously variable transmission as claimed in claim 6, wherein the drive machine is an electric or hydraulic motor.
8. A continuously variable transmission, characterized in that the continuously variable transmission is a conical-disk type continuously variable transmission and a governor mechanism of the continuously variable transmission according to any one of claims 1 to 7 is used for the conical-disk type continuously variable transmission.
9. A tractor characterized in that it is provided with a continuously variable transmission as claimed in claim 8.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223283316.5U CN218761171U (en) | 2022-12-08 | 2022-12-08 | Tractor, stepless speed change device and speed regulation mechanism of stepless speed change device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223283316.5U CN218761171U (en) | 2022-12-08 | 2022-12-08 | Tractor, stepless speed change device and speed regulation mechanism of stepless speed change device |
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| CN218761171U true CN218761171U (en) | 2023-03-28 |
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| CN202223283316.5U Active CN218761171U (en) | 2022-12-08 | 2022-12-08 | Tractor, stepless speed change device and speed regulation mechanism of stepless speed change device |
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