Speed regulating mechanism of tractor and continuously variable transmission device

Abstract

The present invention discloses a method for setting a speed regulating mechanism of a conical disc type stepless speed change device. The conical disc type stepless speed change device includes a conical disc type transmission device and a speed regulating device. In the conical disc type transmission device, a flexible transmission element is clamped on an active conical disc group and a driven conical disc group. The speed regulating mechanism drives the active moving conical disc and the driven moving conical disc to move axially. The speed regulating structure includes a driving machine for outputting power, a speed regulating shaft, and a linear reciprocating mechanism for converting rotation into linear motion. By reasonably setting the relationship between the maximum power of the driving machine and various parameters, the speed regulating mechanism of the conical disc type stepless speed change device of the present invention can reasonably select the power and setting form of the driving machine of the speed regulating mechanism of the conical disc type stepless speed change device, ensuring the efficient and normal operation of the conical disc type stepless speed change device.

Description

Technical Field

[0001] The present invention relates to the field of continuously variable transmissions, and particularly to a method for setting a speed regulation mechanism of a conical disc type continuously variable transmission device. Background Art

[0002] In recent years, domestic working machine transmission devices generally adopt stepped shifting and rear axles. Although stepped speed conversion between multiple gears can be achieved, since the speed of each gear is a fixed value, when performing a certain type of operation, only a speed close to the requirements of this type of operation can be selected for operation, or the engine speed is adjusted for speed increase or decrease. It is difficult to achieve the best operation efficiency and the best engine efficiency.

[0003] The conical disc type continuously variable transmission transmits power in a frictional manner, has a wide speed change range and high efficiency, and is widely used in multiple working fields. When used in conjunction with forward and reverse transmission devices, it can meet the requirements of high-efficiency operation of power machinery. The conical disc type continuously variable transmission changes the working radius of the contact point between the chain and the conical disc by pushing two conical discs in different directions through the speed regulation mechanism, thereby achieving speed change. The speed regulation mechanism is an important part of the conical disc type continuously variable transmission. However, due to the working characteristics of the conical disc type continuously variable transmission, the required speed regulation force for different speed ratios varies. Too small a speed regulation force will not be able to meet the speed change requirements, and too large a speed regulation force will cause too long a speed regulation time and low operability of the whole machine under the condition of a certain power of the existing hydraulic motor or motor. It is impossible to simply use the existing driving machine as the power source to drive the conical disc type continuously variable transmission for speed regulation.

[0004] Chinese Patent Invention Publication Text CN114233847A discloses a speed regulation mechanism of a continuously variable transmission and a continuously variable transmission. This technical solution can meet the requirements of rapid speed change and is beneficial to improving the driving experience and other advantages, but it is not applicable to power machinery such as tractors. Summary of the Invention

[0005] The present invention provides a method for setting a speed regulation mechanism of a conical disc type continuously variable transmission device, which can reasonably select the power source of the speed regulation mechanism of the conical disc type continuously variable transmission device and set the speed regulation mechanism to ensure the normal operation of the conical disc type continuously variable transmission device.

[0006] To solve the above technical problems, one technical solution adopted by the present invention is:

[0007] A speed regulating mechanism for a continuously variable transmission, wherein the continuously variable transmission is a cone-disc type continuously variable transmission, comprising a cone-disc transmission device and a speed regulating mechanism, wherein the cone-disc transmission device comprises a driving cone disc group, a driven cone disc group, and a flexible transmission element, wherein the driving cone disc group comprises a driving fixed cone disc and a driving driven cone disc mounted on a driving shaft, and the driven cone disc group comprises a driven fixed cone disc and a driven driven cone disc mounted on a driven shaft, and one end of the flexible transmission element is clamped between the driving fixed cone disc and the driving driven cone disc, and the other end is clamped between the driven fixed cone disc and the driven driven cone disc.

[0008] The speed regulating mechanism is used to drive the active cone disc and the driven cone disc to move axially. The speed regulating mechanism includes a driving machine for outputting power, a speed regulating shaft, a fixed ratio transmission mechanism, and a linear reciprocating mechanism for converting rotation into linear motion. The driving machine is directly or indirectly connected to the speed regulating shaft. The maximum power of the driving machine is P, in watts, and meets the following requirements: where i max It is the maximum transmission ratio of the cone-disc continuously variable transmission device and the center distance between the driving shaft and the driven shaft of the cone-disc continuously variable transmission device, in mm.

[0009] In a preferred embodiment of the present invention, the linear reciprocating mechanism is a screw mechanism, the driving machine is connected to the speed regulating shaft by direct transmission or indirect transmission, the speed ratio of the connection mechanism between the driving machine and the speed regulating shaft is i, the fixed ratio transmission mechanism includes a first fixed ratio transmission mechanism and a second fixed ratio transmission mechanism; the driving ends of the first fixed ratio transmission mechanism and the second fixed ratio transmission mechanism are both installed on the speed regulating shaft, and the screw mechanism includes a first nut, a first hollow screw, a second nut and a second hollow screw, the driven end of the first fixed ratio transmission structure is connected to the first nut, the first nut is spirally connected with the outer spiral of the first hollow screw through the inner spiral, the first hollow screw is sleeved on the driving shaft, the driven end of the second fixed ratio transmission structure is connected to the second nut, the second nut is spirally connected with the outer spiral of the second hollow screw through the inner spiral, the second hollow screw is sleeved on the driven shaft, and the lead of the first hollow screw and the first nut is P h1 , the lead of the second hollow screw and the second nut is P h2 , where P h1 and P h2 The unit is mm, the ratio of the number of teeth on the driven end to the number of teeth on the driving end of the first fixed ratio transmission mechanism is i1, the ratio of the number of teeth on the driven end to the number of teeth on the driving end of the second fixed ratio transmission mechanism is i2, the P j1 、P h2 , i1 and i2 satisfy P h1 / i1=P h2 / i2.

[0010] 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 axially opposed active cams and driven cams. On the diameter end faces at the centers of the active cams and the driven cams, n raceways with monotonically changing angles are provided oppositely. The driving machine is connected to the speed regulating shaft through a direct connection or an indirect transmission method, and the speed ratio of the connecting mechanism between the driving machine and the speed regulating shaft is i. The constant ratio transmission mechanism includes a third constant ratio transmission mechanism, a fourth constant ratio transmission mechanism, a fifth constant ratio transmission mechanism, and a sixth constant ratio transmission mechanism. The active cams include a first active cam and a second active cam, and the driven cams include a first driven cam and a second driven cam. One end of the speed regulating shaft is connected to the first active cam through the third constant ratio transmission mechanism, and the fourth constant ratio transmission mechanism is connected to the first driven cam. The first active cam and the first driven cam are connected by rollers clamped on the opposed raceways. The first active cam abuts against the back of the active cone disk in a manner allowing relative rotation (such as a bearing). The first driven cam abuts against the active shaft or the housing directly or indirectly. The other end of the speed regulating shaft is connected to the second active cam through the fifth constant ratio transmission mechanism, and the sixth constant ratio transmission mechanism is connected to the second driven cam. The second active cam and the second driven cam are connected by rollers clamped on the opposed raceways. The second active cam abuts against the driven cone disk in a manner allowing relative rotation (such as a bearing). The second driven cam abuts against the driven shaft or the housing directly or indirectly. The angle between the raceways of the first active cam and the first driven cam and the vertical plane of the cam center line is β1, and the diameter at the uniform center where the raceways of the first active cam and the first driven cam are located (i.e., the diameter on the end face provided with n raceways with monotonically changing angles) is d1. The angle between the raceways of the second active cam and the second driven cam and the vertical plane of the end face cam center line is β2, and the diameter at the center where the raceways of the second active cam and the second driven cam are located is d2. The ratio of the number of teeth of the driven end to the number of teeth of the active end of the third constant ratio transmission mechanism is i3, the ratio of the number of teeth of the driven end to the number of teeth of the active end of the fourth constant ratio transmission mechanism is i4, the ratio of the number of teeth of the driven end to the number of teeth of the active end of the fifth constant ratio transmission mechanism is i5, and the ratio of the number of teeth of the driven end to the number of teeth of the active end of the sixth constant ratio transmission mechanism is i6. β1, β2, i3, i4, i5, and i6 satisfy d1tanβ1(1 / i3 - 1 / i4) = d2tanβ2(1 / i5 - 1 / i6).

[0011] In a preferred embodiment of the present invention, the maximum output speed of the driving machine is n w , with the unit of r / min, and it satisfies

[0012] In a preferred embodiment of the present invention, the number of turns of the outer helix of the first hollow screw is N1, the number of turns of the inner helix of the first nut is N2, the number of turns of the outer helix of the second hollow screw is N3, and the number of turns of the inner helix of the second nut is N4. N1, N2, N3, and N4 satisfy:

[0013] In a preferred embodiment of the present invention, the center distance between the speed regulation shaft and the driving shaft is equal to the center distance between the speed regulation shaft and the driven shaft. P h1 、P h2 、i1 and i2 satisfy P h1 =P h2 and i1 = i2.

[0014] In a preferred embodiment of the present invention, the driving machine is a motor or a hydraulic motor.

[0015] A stepless speed change device, the stepless speed change device is a conical disk type stepless speed change device, and the conical disk type stepless speed change device uses the above speed regulation mechanism.

[0016] A non-road working machine, the non-road working machine is provided with the above stepless speed change device.

[0017] A tractor, the tractor is provided with the above stepless speed change device.

[0018] The beneficial effects of the present invention are:

[0019] 1. By specifically setting the speed regulation mechanism of the conical disk type stepless speed change device, the device can reasonably select the power and setting form of the driving machine of the speed regulation mechanism of the conical disk type stepless speed change device, ensuring the efficient and normal operation of the conical disk type stepless speed change device.

[0020] 2. The present invention reasonably sets the parameters that match each other between the power source and the speed regulation device of the speed regulation mechanism of the conical disk type stepless speed change device, and converts the rotational motion into an effective linear motion. By reasonably setting the components of the speed regulation mechanism and the ratio between the components, the structure of the speed regulation mechanism is made more compact, and it is avoided that the too small speed regulation force cannot meet the requirements of speed change under different speed ratios and different engine input torques, or the defect of too long speed regulation time is avoided; when encountering sudden changes in load (such as road ditches, sudden encounter of waterlogged road surfaces) during the operation of the whole machine, the speed change requirements can be quickly completed, ensuring the reliability of the system operation. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] To more clearly illustrate the technical solutions in the embodiments of the present invention, the following will briefly introduce the accompanying drawings required for the description of the embodiments. Obviously, the accompanying drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other accompanying drawings can be obtained based on these drawings, where:

[0022] Figure 1 is a schematic structural diagram of Embodiment 1 of the conical disk type continuously variable transmission device of the present invention.

[0023] Figure 2 is a schematic structural diagram of Embodiment 2 of the conical disk type continuously variable transmission device of the present invention.

[0024] Figure 3 is a diagram showing the change of the theoretically required speed regulation force of the nut in Embodiment 1 when moving from a large speed ratio to a small speed ratio.

[0025] Figure 4 is a diagram showing the change of the theoretically required speed regulation force of the nut in Embodiment 1 when moving from a small speed ratio to a large speed ratio.

[0026] Figure 5 is a diagram showing the change of the actual output speed regulation force of the drive machine in Embodiment 1 under different directions and different speed ratios.

[0027] The reference numerals of each component in the drawings are as follows: 1. driving shaft, 2. end face cam pressing mechanism, 3. second constant ratio transmission mechanism, 4. driving fixed conical disk, 5. driving movable conical disk, 6. speed regulation gear set, 7. drive machine, 8. speed regulation shaft, 9. first constant ratio transmission mechanism, 10. first nut, 11. first hollow screw rod, 12. driven fixed conical disk, 13. flexible transmission element, 14. driven movable conical disk, 15. second nut, 16. second hollow screw rod, 17. third constant ratio transmission mechanism, 18. fourth constant ratio transmission mechanism, 19. first driven cam, 20. roller, 21. first driving cam, 22. second driven cam, 23. second driving cam, 24. sixth constant ratio transmission mechanism, 25. fifth constant ratio transmission mechanism. Detailed Embodiments

[0028] The following will clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only some of the embodiments of the present invention, rather than all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts fall within the scope of protection of the present invention.

[0029] Embodiment 1

[0030] As Figure 1As shown in the figure, a conical disc type continuously variable transmission device includes a speed regulating mechanism for outputting power and a conical disc type power device directly or indirectly connected to the speed regulating mechanism.

[0031] The conical disc type power device includes a driving conical disc group, a driven conical disc group, an end face cam pressing mechanism and a flexible transmission element. The flexible transmission element is clamped between the driving conical disc group and the driven conical disc group. The driving conical disc group includes a driving fixed conical disc and a driving movable conical disc mounted on the driving shaft. The driven conical disc group includes a driven fixed conical disc and a driven movable conical disc mounted on the driven shaft. The speed regulating mechanism drives the driving movable conical disc and the driven movable conical disc to move axially. The speed regulating mechanism includes a driving machine for outputting power, a speed regulating shaft and a linear reciprocating mechanism for converting rotation into linear motion. The driving machine is indirectly connected to the speed regulating shaft through a speed regulating gear set. The speed regulating shaft is provided with a first constant ratio transmission mechanism and a second constant ratio transmission mechanism. The linear reciprocating mechanism is a spiral mechanism, which includes a first nut, a second nut, a first hollow screw rod and a second hollow screw rod. The first constant ratio transmission mechanism is connected to the first nut. The first nut is arranged on the first hollow screw rod. The first hollow screw rod is sleeved on the driving shaft. The second constant ratio transmission structure is connected to the second nut. The second nut is arranged on the second hollow screw rod. The second hollow screw rod is sleeved on the driven shaft.

[0032] In addition, at least one of the driving fixed conical disc and the driven fixed conical disc has an end face cam pressing mechanism on the back, and the driving movable conical disc and the driven movable conical disc are connected to the speed regulating mechanism.

[0033] In addition, the maximum power P of the driving machine is 9.74KW, where i max is the maximum transmission ratio of the conical disc type continuously variable transmission device (in this embodiment, it is 5), and is the center distance between the driving shaft and the driven shaft of the conical disc type continuously variable transmission device (in this embodiment, it is 350mm), satisfying:

[0034] In addition, the linear reciprocating mechanism is a spiral mechanism. There is a transmission mechanism directly or indirectly connected between the driving machine and the speed regulating shaft. The speed ratio of the connecting mechanism between the driving machine and the speed regulating shaft is i which is 8.22. The speed regulating shaft is provided with a first constant ratio transmission mechanism and a second constant ratio transmission mechanism. The nut includes a first nut and a second nut. The hollow screw rod includes a first hollow screw rod and a second hollow screw rod. The first constant ratio transmission structure is connected to the first nut. The first nut is arranged on the first hollow screw rod. The first hollow screw rod is sleeved on the driving shaft. The second constant ratio transmission structure is connected to the second nut. The second nut is arranged on the second hollow screw rod. The second hollow screw rod is sleeved on the driven shaft. The lead P of the first hollow screw rod and the first nut h1 is 10mm, and the lead P of the second hollow screw rod and the second nut h2is 10mm, the ratio i1 of the number of teeth of the driven end to the number of teeth of the driving end of the first constant-ratio transmission mechanism is 2.39, the ratio i2 of the number of teeth of the driven end to the number of teeth of the driving end of the second constant-ratio transmission mechanism is 2.39, P h1 , P h2 , i1 and i2 satisfy P h1 / i1 = P h2 / i2.

[0035] In addition, the maximum output speed of the driving machine is n w is 300 r / min, satisfying

[0036] In addition, the number of turns N1 of the outer helix of the first hollow screw is 9, the number of turns of the inner helix of the first nut is N2 is 5, the number of turns of the outer helix of the second hollow screw is N3 is 9, and the number of turns of the inner helix of the second nut is N4 is 5. The N1, N2, N3 and N4 satisfy:

[0037] In addition, the distance between the speed regulation shaft and the center distance between the main and driven shafts are equal, P h1 , P h2 , i1 and i2 also satisfy P h1 = P h2 and i1 = i2.

[0038] In addition, the first nut abuts against the driving dynamic cone disc, and the first hollow screw abuts against the driving shaft through an axial locking device; the second nut abuts against the driven dynamic cone disc, and the second hollow screw abuts against the driven shaft through an axial locking device.

[0039] In addition, the driving machine is an electric motor or a hydraulic motor.

[0040] The specific working principle of the cone-disc type continuously variable transmission device of this embodiment is as follows: The engine transmits power to the cone-disc type transmission device. When continuously variable transmission is required, the driving machine transmits the speed regulation force to the first nut and the second nut through the speed regulation gear set and the first and second constant-ratio transmission mechanisms respectively. The first and second nuts rotate relative to the corresponding hollow screws, and feed one lead P h1 and P h2 each time they rotate one circle, pushing the driving dynamic cone disc and the driven dynamic cone disc to move axially, and the working radius of the contact points between the flexible transmission element and the driving cone disc group and the driven cone disc group changes, thus completing continuously variable transmission.

[0041] As an important component of the continuously variable transmission device, when the speed regulation mechanism of the present invention pushes the driving dynamic cone disc and the driven dynamic cone disc to move at the same speed and in the same direction, the axial force to be overcome should be the difference between the axial forces of the main and driven shafts. And the axial pulling force of the flexible element remains unchanged during the power transmission process. Since the included angles of the main and driven shafts are not equal during the speed change process, it is reflected that the axial forces on the driving shaft and the driven shaft of the continuously variable transmission device are not equal, that is, asFigure 3-4 As shown Figure 3 When adjusting the speed from a large speed ratio to a small speed ratio, when the initial speed ratio is greater than a certain value, the theoretically required speed adjustment force is zero. As the speed ratio decreases and when the speed ratio is less than a certain value, the theoretically required speed adjustment force increases as the speed ratio decreases, and the growth rate decreases as the speed ratio decreases; while Figure 4 When adjusting the speed from a small speed ratio to a large speed ratio, when the speed ratio is less than a certain value, the theoretically required speed adjustment force is zero. As the speed ratio increases and when the speed ratio is greater than a certain value, the theoretically required speed adjustment force increases as the speed ratio increases, and the increase rate increases as the speed ratio increases. That is, the speed adjustment force required by the nut is different during the speed adjustment process in different directions. As Figure 5 shown in the actual output speed adjustment force change diagram of the drive machine. Considering the existence of actual mechanical loss power, the situation where the theoretically required speed adjustment force is zero is reduced. However, it is obvious that the maximum speed adjustment force during the speed adjustment process from a small speed ratio to a large speed ratio is significantly greater than that during the speed adjustment process from a large speed ratio to a small speed ratio, and the maximum speed adjustment force occurs at the minimum speed ratio or the maximum speed ratio. The output speed adjustment force of the drive machine is also different in different directions and at different speed ratios. That is, the designed speed adjustment mechanism should meet the efficiency and at the same time make the point where the required maximum speed adjustment force occurs. Different from the prior art, the method for setting the speed adjustment mechanism of the conical disk type continuously variable transmission device of the present invention can reasonably select the power and setting form of the drive machine of the speed adjustment mechanism of the conical disk type continuously variable transmission device, ensuring that the conical disk type continuously variable transmission device can quickly and reliably complete the speed change requirement.

[0042] Embodiment 2

[0043] As Figure 2As shown, the linear reciprocating mechanism in this embodiment is a cam mechanism. The cam mechanism includes at least two pairs of driving cams and driven cams arranged axially opposite to each other. On the diameter end faces at the centers of the driving cams and the driven cams, there are 3 raceways with monotonically changing angles relatively arranged. The driving machine is connected to the speed regulation shaft through a direct connection or an indirect transmission method. The speed ratio i of the connection mechanism between the driving machine and the speed regulation shaft is 1.74. The constant ratio transmission mechanism includes a third constant ratio transmission mechanism, a fourth constant ratio transmission mechanism, a fifth constant ratio transmission mechanism, and a sixth constant ratio transmission mechanism. The driving cam includes a first driving cam and a second driving cam, and the driven cam includes a first driven cam and a second driven cam. One end of the speed regulation shaft is connected to the first driving cam through the third constant ratio transmission mechanism, and the fourth constant ratio transmission mechanism is connected to the first driven cam. The first driving cam and the first driven cam are connected by rollers clamped on the opposite raceways. The first driving cam abuts against the back of the driving cone disc in a way that allows relative rotation through bearings. The first driven cam abuts against the driving shaft or the box body directly or indirectly; the other end of the speed regulation shaft is connected to the second driving cam through the fifth constant ratio transmission mechanism, and the sixth constant ratio transmission mechanism is connected to the second driven cam. The second driving cam and the second driven cam are connected by rollers clamped on the opposite raceways. The second driving cam abuts against the driven cone disc in a way that allows relative rotation through bearings. The second driven cam abuts against the driven shaft or the box body directly or indirectly. The angle β1 between the raceway of the first driving cam and the first driven cam and the vertical plane of the center line of the end face cam is 6°, and the diameter d1 at the center where the raceway of the first driving cam and the first driven cam is located is 224 mm. The angle β2 between the raceway of the second driving cam and the second driven cam and the vertical plane of the center line of the end face cam is 6°, and the diameter d2 at the center where the raceway of the second driving cam and the second driven cam is located is 224 mm. The ratio i3 of the number of teeth of the driven end to the number of teeth of the driving end of the third constant ratio transmission mechanism is 3.94, the ratio i4 of the number of teeth of the driven end to the number of teeth of the driving end of the fourth constant ratio transmission mechanism is 3.68, the ratio i5 of the number of teeth of the driven end to the number of teeth of the driving end of the fifth constant ratio transmission mechanism is 3.94, and the ratio i6 of the number of teeth of the driven end to the number of teeth of the driving end of the sixth constant ratio transmission mechanism is, β1, β2, i3, i4, i5, and i6 meet the requirement of d1tanβ1(1 / i3 - 1 / i4) = d2tanβ2(1 / i5 - 1 / i6).

[0044] Embodiment 3

[0045] An embodiment of the combination of the tractor layout and the above speed control mechanism. The tractor power unit includes an engine, a clutch, a conical disc type continuously variable transmission device, a shift transmission device, and a rear axle; the engine is connected to the input end of the conical disc type continuously variable transmission device through the clutch, the driven shaft of the conical disc type continuously variable transmission device is connected to the shift transmission device, and the output end of the shift transmission device is directly connected to the input end of the rear axle.

[0046] The conical disc type continuously variable transmission device includes a driving shaft, a driving conical disc group, a driven shaft, a driven conical disc group, a cam pressing mechanism, a speed control mechanism, and a steel flexible transmission element; the driving conical disc group is sleeved on the driving shaft, the driven conical disc group is sleeved on the driven shaft, the steel flexible transmission element is clamped between the driving conical disc group and the driven conical disc group, the cam pressing mechanism is arranged on the back of the driving fixed conical disc and / or the driven fixed conical disc, and the speed control mechanism abuts against the driving movable conical disc and the driven movable conical disc through a bearing capable of bearing axial force.

[0047] The speed control mechanism includes a driving machine for outputting power, a speed control shaft, a constant ratio transmission mechanism, and a screw mechanism. The driving machine is connected to the speed control shaft through an indirect transmission method. The constant ratio transmission mechanism is a gear transmission mechanism, including a first constant ratio transmission mechanism and a second constant ratio transmission mechanism; the driving gears of the first constant ratio transmission mechanism and the second constant ratio transmission mechanism are both installed on the speed control shaft by means of spline fitting with a retaining ring; the screw mechanism includes a first nut, a first hollow screw, a second nut, a second hollow screw, a roller, and a reverser. The driven gear of the first constant ratio transmission structure is integrally formed with the first nut. The first nut is in screw connection with the outer screw of the first hollow screw through an internal screw. The first hollow screw abuts against the driving shaft through a bearing capable of bearing axial force and a locking nut; the driven gear of the second constant ratio transmission structure is integrally formed with the second nut. The second nut is in screw connection with the outer screw of the second hollow screw through an internal screw. The second hollow screw abuts against the driven shaft through a bearing capable of bearing axial force and a locking nut. The locking nut on the driving shaft is right-handed, and the locking nut on the driven shaft is left-handed. Rollers are arranged in the spiral grooves where the nuts are connected to the screws. Reversers that allow the rollers to pass are arranged on both the first nut and the second nut.

[0048] Comparative Example 1

[0049] Replace the driving machine in Embodiment 1. In this comparative example, the maximum power P of the driving machine is set to 3KW, and i max and a are set the same as in Embodiment 1 and do not meet According to the requirements, other setting methods are the same as those in Embodiment 1. After the full-stroke speed regulation test under the same conditions, it is found that in the process of speed regulation from a small speed ratio to a large speed ratio in the comparative example, it is difficult to adjust the speed when the speed ratio is greater than 1.55, and in the process of speed regulation from a large speed ratio to a small speed ratio, it is difficult to adjust the speed when the speed ratio is less than 0.75, while Embodiment 1 can complete the full-stroke speed regulation.

[0050] Comparative Example 2

[0051] In this comparative example, the ratio i1 of the number of teeth of the driven end to the number of teeth of the driving end of the first constant ratio transmission mechanism is 2.43, and the ratio i2 of the number of teeth of the driven end to the number of teeth of the driving end of the second constant ratio transmission mechanism is 2.3, which replace those in Embodiment 1. The lead P of the first hollow screw and the first nut h1 is 10 mm, and the lead P of the second hollow screw and the second nut h2 is 10 mm. P h1 and P h2 , i1 and i2 do not satisfy P h1 / i1 = P h2 / i2. When the flexible transmission element used is a chain, after the reliability test under the same conditions, during the operation at a small speed ratio, the chain in the comparative example deflects too much and the solder joints on the pins fall off, while Embodiment 1 can complete the reliability test at different speed ratios.

[0052] Comparative Example 3

[0053] Replace the drive machine in Embodiment 1. In this comparative example, the maximum output speed of the drive machine is n w is 100 r / min. When the center distance a between the driving shaft and the driven shaft of the conical disk type continuously variable transmission device is 350 mm, the speed ratio i of the connecting mechanism between the drive machine and the speed regulation shaft is 8.22, and the ratio i1 of the number of teeth of the driven end to the number of teeth of the driving end of the first constant ratio transmission mechanism is 2.39, and the lead P of the first hollow screw and the first nut h1 is 10 mm, it does not satisfy After the full-stroke speed regulation test under the same conditions, it is found that the cyclic speed regulation time of this comparative example is too long and cannot meet the dynamic response requirements of the walking machinery.

[0054] The above are only the embodiments of the present invention, and thus do not limit the patent scope of the present invention. Any equivalent structure or equivalent process transformation made by using the content of the specification of the present invention, or directly or indirectly applied in other related technical fields, shall be equally included in the patent protection scope of the present invention.

Claims

1. A speed regulating mechanism for a continuously variable transmission, wherein the continuously variable transmission is a cone-disc type continuously variable transmission, comprising a cone-disc transmission device and a speed regulating mechanism. The cone-disc transmission device comprises a driving cone disc assembly, a driven cone disc assembly, and a flexible transmission element. The driving cone disc assembly comprises a driving fixed cone disc and a driving driven cone disc mounted on a driving shaft. The driven cone disc assembly comprises a driven fixed cone disc and a driven driven cone disc mounted on a driven shaft. One end of the flexible transmission element is clamped between the driving fixed cone disc and the driving driven cone disc, and the other end is clamped between the driven fixed cone disc and the driven driven cone disc. The characteristics of the invention are: The speed regulating mechanism is used to drive the active cone disc and the driven cone disc to move axially. The speed regulating mechanism includes a driving machine for outputting power, a speed regulating shaft, a fixed ratio transmission mechanism, and a linear reciprocating mechanism that converts rotation into linear motion. The driving machine is directly or indirectly connected to the speed regulating shaft. The maximum power of the driving machine is P, in watts, and meets the requirements. where i max is the maximum transmission ratio of the cone-disc continuously variable transmission device, a is the center distance between the driving shaft and the driven shaft of the cone-disc continuously variable transmission device, the unit is mm; The speed ratio of the connection mechanism between the driving machine and the speed regulating shaft is i, and the maximum output speed of the driving machine is n w , the unit is r / min, satisfying The linear reciprocating mechanism is a screw mechanism or a cam mechanism; the fixed ratio transmission mechanism includes a first fixed ratio transmission mechanism and a second fixed ratio transmission mechanism, the active ends of which are both installed on the speed regulating shaft, the screw mechanism includes a first nut, a first hollow screw, a second nut and a second hollow screw, the driven end of the first fixed ratio transmission structure is connected to the first nut, the first nut is spirally connected to the outer spiral of the first hollow screw through an inner spiral, the first hollow screw is sleeved on the active shaft, the driven end of the second fixed ratio transmission structure is connected to the second nut, the second nut is spirally connected to the outer spiral of the second hollow screw through an inner spiral, the second hollow screw is sleeved on the driven shaft, and the lead of the first hollow screw and the first nut is P h1 , the lead of the second hollow screw and the second nut is P h2 , the ratio of the number of teeth on the driven end to the number of teeth on the driving end of the first fixed ratio transmission mechanism is i1, and the ratio of the number of teeth on the driven end to the number of teeth on the driving end of the second fixed ratio transmission mechanism is i2, satisfying P h1 / i1=P h2 / i2.

2. The speed regulating mechanism of the continuously variable transmission according to claim 1, characterized in that: The linear reciprocating mechanism is a screw mechanism, and the driving machine is connected to the speed regulating shaft by direct transmission or indirect transmission. h1 and P h2 The unit is mm.

3. The speed regulating mechanism of the continuously variable transmission according to claim 1, characterized in that: The linear reciprocating mechanism is a cam mechanism, which includes at least two pairs of active cams and driven cams arranged axially opposite to each other. The diameter end faces at the centers of the active cam and the driven cam are oppositely provided with n rollers with monotonically changing angles. The driving machine is connected to the speed regulating shaft by a direct connection or an indirect transmission method. The speed ratio of the connection mechanism between the driving machine and 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 active cam includes a first active cam and a second active cam. The driven cam includes a first driven cam and a second driven cam, one end of the speed regulating shaft is connected to the first driving cam through a third fixed ratio transmission mechanism, the fourth fixed ratio transmission mechanism is connected to the first driven cam, the first driving cam and the first driven cam are connected by rollers clamped on opposite raceways, the first driving cam is against the back of the active driving cone disc by allowing mutual rotation, and the first driven cam is against the driving shaft or the box body directly or indirectly; the other end of the speed regulating shaft is connected to the second driving cam through a fifth fixed ratio transmission mechanism, and the sixth fixed ratio transmission mechanism is connected to the first driving cam. The driving mechanism is connected to the second driven cam, the second driving cam and the second driven cam are connected by rollers clamped on opposite raceways, the second driving cam is against the driven cone disk by allowing mutual rotation, and the second driven cam is against the driven shaft or box by direct or indirect means, the angle between the raceways of the first driving cam and the first driven cam and the vertical plane of the cam centerline is β1, the diameter of the uniform center of the raceways of the first driving cam and the first driven cam is d1, the raceways of the second driving cam and the second driven cam are perpendicular to the centerline of the end face cam The angle between the driven end and the driving end is β2, the diameter of the center of the raceway of the second driving cam and the second driven cam is d2, the ratio of the number of teeth at the driven end of the third fixed ratio transmission mechanism to the number of teeth at the driving end is i3, the ratio of the number of teeth at the driven end of the fourth fixed ratio transmission mechanism to the number of teeth at the driving end is i4, the ratio of the number of teeth at the driven end of the fifth fixed ratio transmission mechanism to the number of teeth at the driving end is i5, and the ratio of the number of teeth at the driven end of the sixth fixed ratio transmission mechanism to the number of teeth at the driving end is i6. The β1, β2, i3, i4, i5 and i6 satisfy d1tanβ1(1 / i3-1 / i4)=d2tanβ2(1 / i s -1 / i6).

4. The speed regulating mechanism of the continuously variable transmission according to claim 1, characterized in that: The number of turns of the outer helix of the first hollow screw is N1, the number of turns of the inner helix of the first nut is N2, the number of turns of the outer helix of the second hollow screw is N3, and the number of turns of the inner helix of the second nut is N4. N1, N2, N3 and N4 satisfy:

5. The speed regulating mechanism of the continuously variable transmission according to claim 1, characterized in that: The center distance between the speed regulating shaft and the driving shaft is equal to the center distance between the speed regulating shaft and the driven shaft. h1 、P h2 , i1 and i2 satisfy P h1 =P h2 And i1=i2.

6. The speed regulating mechanism of a continuously variable transmission according to any one of claims 1 to 5, characterized in that: The driving machine is an electric motor or a hydraulic motor.

7. A continuously variable transmission device, characterized in that: The continuously variable transmission device is a cone-disc type continuously variable transmission device, and the cone-disc type continuously variable transmission device uses the speed regulating mechanism according to any one of claims 1 to 5.

8. A non-road working machine, characterized in that: The non-road working machine is provided with the continuously variable transmission according to claim 7 .

9. A tractor, characterized in that: The tractor is provided with the continuously variable transmission according to claim 7.

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