Non-circular gear set for combing machine cylinder speed change

Abstract

The non-circular gear set comprises a first driving wheel, a first driven wheel, a second driving wheel and a second driven wheel, the first driving wheel and the first driven wheel are meshed with each other, the second driving wheel and the second driven wheel are meshed with each other, the first driving wheel is connected with a power input shaft, and the second driven wheel is connected with a power output shaft; the first driven wheel and the second driving wheel are in key connection or fixed connection through a transmission shaft, the first driving wheel and the second driving wheel are the same in structure, and the first driven wheel and the second driven wheel are the same in structure; the assembly phase between the first driving wheel and the first driven wheel is the same as the assembly phase between the second driving wheel and the second driven wheel. Through related design, when the first driving wheel of the non-circular gear set performs input motion at a constant rotating speed, the second driven wheel can realize large-amplitude high-low speed transition change, and the second driven wheel can realize stable operation, so that the advantages of better carding effect, better dynamic characteristics and longer service life are obtained.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of non-circular gear transmission, in particular to a non-circular gear set for variable speed of a carding cylinder. BACKGROUND

[0002] At present, there are two kinds of carding cylinder movement driving mechanism devices: one is a uniform rotation movement mechanism driving device; and the other is a variable speed rotation movement mechanism driving device. The uniform rotation movement mechanism driving device is commonly used in the medium and low speed of the carding machine, and the variable speed rotation movement mechanism driving device is commonly used in the high speed of the carding machine. The non-circular gear transmission pair for the existing carding cylinder can realize the variable speed carding function of the cylinder, but has a series of problems such as poor short fiber and impurity carding effect, poor high-speed running stability, short gear pair service life, and cannot meet the carding requirements of high speed, high quality and long service life. SUMMARY

[0003] The present application aims at the above problems, and provides a non-circular gear set for variable speed of a carding cylinder, which has better carding effect and dynamic characteristics.

[0004] In order to achieve the above purpose, the technical scheme of the present application is as follows:

[0005] A non-circular gear set for variable speed of a carding cylinder, comprising a first driving wheel, a first driven wheel and a second driving wheel, and a second driven wheel, which are meshed with each other, the first driving wheel is connected with a power input shaft, and the second driven wheel is connected with a power output shaft; the first driven wheel and the second driving wheel are connected by a transmission shaft key or fixedly connected, the first driving wheel and the second driving wheel are the same in structure, and the first driven wheel and the second driven wheel are the same in structure; the assembly phase between the first driving wheel and the first driven wheel is the same as the assembly phase between the second driving wheel and the second driven wheel.

[0006] Further, in a rotation period, the first driven wheel has a transmission ratio value greater than 1, and the proportion of the interval greater than 1 in the total interval of the first driven wheel is 50% to 60%.

[0007] Further, the rotation angle of the first driven wheel and the rotation angle of the first driving wheel in a rotation period of the first driving wheel satisfy the following formula:

[0008]

[0009] Wherein, k is a constant coefficient; G is a constant speed ratio interval of the first driving wheel and the first driven wheel; a to h are the coefficients of the 7th spline in turn.

[0010] Further, the transmission ratio of the second driven wheel and the first driving wheel ranges from 0.35 to 1.8, and the highest transmission ratio range is in the rotation angle interval [0, G] of the first driving wheel.

[0011] Further, the first driving wheel, the first driven wheel, the second driving wheel and the second driven wheel have the same number of teeth, and the number of teeth ranges from 23 to 35.

[0012] Further, the first driving wheel, the first driven wheel, the second driving wheel and the second driven wheel have the same normal module, and the normal module ranges from 3.2 to 3.8 mm.

[0013] Further, the first driving wheel, the first driven wheel, the second driving wheel and the second driven wheel have the same pressure angle, and the pressure angle ranges from 23 to 28 degrees.

[0014] Further, the first driving wheel, the first driven wheel, the second driving wheel and the second driven wheel are straight-toothed gears or helical gears; when the first driving wheel, the first driven wheel, the second driving wheel and the second driven wheel are helical gears, the helix angle of the gear teeth of the helical gears ranges from 8 to 15 degrees.

[0015] Compared with the prior art, the present application has the advantages and positive effects that:

[0016] In the present application, the non-circular gear set for variable-speed transmission of the combing cylinder of a combing machine defines the angular displacement transmission relationship of a single pair of non-circular gears by seven times of spline, realizes the continuous and smooth speed, acceleration and jerk of motion transmission; through approximation and experimental optimization of the variable-speed law required for combing, the high-low speed ratio range and the transmission ratio range of the non-circular gear set are determined; at the same time, through matching design of the combing working condition, the optimal tooth number, module and pressure angle range of the non-circular gear set are determined; through relevant design, the non-circular gear set can realize large-amplitude high-low speed transition change when the first driving wheel inputs motion at a constant speed, and the second driven wheel can realize smooth running, so that better combing effect, dynamic characteristics and service life advantages are obtained; and, the power gear can be designed as a helical gear transmission structure, which can further improve the transmission stability, high speed and service life of the non-circular gear set. BRIEF DESCRIPTION OF DRAWINGS

[0017] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the drawings needed to be used in the embodiments or prior art description will be briefly introduced below. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can be obtained by those skilled in the art without creative labor.

[0018] Figure 1This is a schematic diagram of the non-circular gear transmission in this invention;

[0019] Figure 2 This is a graph showing the angular relationship between the first driven wheel and the first driving wheel;

[0020] Figure 3 The graph shows the angular velocity of the first driven wheel.

[0021] Figure 4 The graph shows the angular acceleration of the first driven wheel.

[0022] Figure 5 This is a graph showing the transmission ratio between the first driven wheel and the first driving wheel.

[0023] Figure 6 This is a pitch curve diagram for non-circular gears;

[0024] Figure 7 This is a schematic diagram of a single-axis non-circular gear pair.

[0025] Figure 8 This is a schematic diagram of a single-axis helical non-circular gear pair. Detailed Implementation

[0026] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, any modifications, equivalent substitutions, improvements, etc., made by those skilled in the art to all other embodiments obtained without creative effort should be included within the protection scope of the present invention.

[0027] Example 1

[0028] This embodiment discloses a non-circular gear set for cylinder speed change in a combing machine, such as... Figure 1 As shown, it includes a first driving wheel and a first driven wheel that mesh with each other, and a second driving wheel and a second driven wheel that mesh with each other. The first driving wheel is connected to the power input shaft, and the second driven wheel is connected to the power output shaft. The first driving wheel and the second driving wheel have the same structure, and the first driven wheel and the second driven wheel have the same structure. The first driven wheel and the second driving wheel are fixedly connected by a transmission shaft, and the assembly phase between the first driving wheel and the first driven wheel is the same as the assembly phase between the second driving wheel and the second driven wheel.

[0029] The mathematical relationship between the rotation angle ψ of the first driven wheel and the rotation angle φ of the first driving wheel is expressed as a piecewise function as follows:

[0030]

[0031] In this embodiment, each coefficient calculation in the above formula requires 8 boundary conditions;

[0032] The mathematical relationship of the first driven wheel rotation angle ψ relative to the first driving wheel rotation angle φ is as shown in Figure 2 ; Figure 2 In this embodiment, the interval [0, G] is a uniform straight line segment, and [A, D] is a 7th order spline segment. Eight boundary conditions are set as follows:

[0033] Boundary conditions Value explanation 1 A point first driven wheel rotation angle 2 A point first driven wheel angular velocity 3 A point first driven wheel angular acceleration 4 B point first driven wheel angular velocity 5 C point first driven wheel angular velocity 6 D point first driven wheel rotation angle 7 D point first driven wheel angular velocity 8 D point first driven wheel angular acceleration

[0034] The selection of points B and C is determined at the moment when the transmission ratio of the first driven wheel to the first driving wheel is 1. In this embodiment, the first driving wheel rotation angle from point A to point B is 95 degrees, and the first driving wheel rotation angle from point C to point D is 93 degrees. The eight unknown parameters of the 7th order spline are as follows:

[0035] Parameter Value a 1.9840*10-15 b -2.5693*10-12 c 1.1121*10-9 d -1.4932*10-7 e -7.0712*10-6 f 2.9099*10-4 g 1.3168 h 0.0109

[0036] According to the above parameters, the calculation of the segmented function can obtain the mathematical relationship curve of the first driven wheel rotation angle ψ relative to the first driving wheel rotation angle φ as shown in Figure 2 ; that is, according to the above data, the change curve of the driven wheel rotation angle of the single amplitude non-circular gear relative to the driving wheel rotation angle is obtained;

[0037] Taking the first driving wheel rotation speed as constant at 300 RPM, the angular velocity and angular acceleration curves of the first driven wheel are as shown in Figure 3 and Figure 4 From Figure 3 , Figure 4 it can be seen that in this embodiment, the angular velocity and angular acceleration of the first driven wheel are continuous and smooth, without impact, which can meet the high-speed stable transmission demand.

[0038] In order to obtain the pitch curve of the first driving wheel and the first driven wheel, the transmission ratio of the two needs to be known. The calculation of the transmission ratio i is as follows:

[0039]

[0040] It is obtained that:

[0041]

[0042] According to the above formula, the transmission ratio curve of the first driven wheel relative to the first driving wheel is as shown in Figure 5 ; according to Figure 5 , the non-circular gear pair of this embodiment is used to build a non-circular gear transmission group for a variable-speed cylinder, and the transmission ratio relationship curve of the second driven wheel relative to the first driving wheel is obtained; as shown in Figure 5As shown, the interval [0,G] is the interval with the highest transmission ratio. Two boundary conditions, points B and C, are introduced during the 7th spline solution. The transmission ratio corresponding to these two points is 1.

[0043] Based on the transmission ratio i, the pitch curves of the first driven wheel and the first driving wheel can be calculated using the following formula:

[0044]

[0045] like Figure 6 As shown, the non-circular gear pitch curve is calculated using the relevant parameters of the non-circular gear in this embodiment. Figure 6 In the calculation, the pitch curves of the first driving wheel and the first driven wheel are expressed as tabular curves (taking 315 points), as shown in the table below. Based on these discrete points, a smooth and continuous pitch curve vector graphic can be obtained through spline interpolation or fitting methods.

[0046]

[0047]

[0048]

[0049]

[0050]

[0051]

[0052]

[0053]

[0054]

[0055]

[0056]

[0057]

[0058] by Figure 6 The pitch curve example described above, with 25 teeth, a normal module of 3.5, and a pressure angle of 25 degrees, yields a single-axis non-circular gear tooth profile, as shown below. Figure 7 As shown.

[0059] In the prior research method, the method for obtaining the full-circle tooth profile of the non-circular gear based on the known pitch curve data and the basic parameters of the non-circular gear tooth profile design is provided with relevant technical means; of course, the non-circular gear tooth profile software program can also be used for generation, such as the KISSsoft non-circular gear design tool.

[0060] Embodiment two,

[0061] As Figure 8 shown, on the basis of embodiment one, the helical gear design can further improve the transmission characteristics, and the helix angle is 10 degrees, so that the single-amplitude non-circular gear helical gear transmission structure is obtained.

[0062] In the present application, the assembly phase of the first driving wheel and the first driven wheel is the same as that of the second driving wheel and the second driven wheel; at each moment during operation, the meshing states of the two non-circular gears are the same, for example, the driving wheel short shaft is opposite to the driven wheel long shaft or the driving wheel long shaft is opposite to the driven wheel short shaft. In this layout mode, the matching U-shaped structure will cause the long shafts of the two non-circular driven wheels to be 180 degrees out of phase.

[0063] Through the optimization design of the pitch curve of the non-circular gear pair, a specific transmission ratio rule is set to realize the optimization of the carding characteristics and the optimization of the high-speed running dynamics; specific gear parameters (module, pressure angle) are designed to improve the service life; to realize the smooth transmission, continuous acceleration and jerk; through the specific transmission ratio value and angle range setting, the best carding effect is realized; at the same time, the stability, low vibration and long service life of the high-speed mechanical transmission characteristics are considered.

[0064] In the present application, the non-circular gear set for the variable-speed transmission of the cylinder of the combing machine is designed through the optimization design of the pitch curve of the non-circular gear pair, a specific transmission ratio rule is set to realize the optimization of the carding characteristics and the optimization of the high-speed running dynamics; specific gear parameters (module, pressure angle) are designed to improve the service life; the seven spline definition is used to define the angular displacement transmission relationship of the single non-circular gear pair, and the continuous stability of the speed, acceleration and jerk of the motion transmission is realized; through the approximation and experimental optimization of the variable-speed rule required for carding, the high-low speed ratio range and the transmission ratio range of the non-circular gear set are determined; at the same time, through the matching design of the carding working condition, the optimal gear number, module and pressure angle range of the non-circular gear set are determined; through the related design, the non-circular gear set can realize the large-amplitude high-low speed transition change when the first driving wheel inputs the motion at a constant speed, and the second driven wheel can realize the stable operation, so that better carding effect, dynamics and service life advantages are obtained; and the power gear can be designed as a helical gear transmission structure, which can further improve the transmission stability, high speed and service life of the non-circular gear set.

Claims

1. A non-circular gear set for a combing machine cylinder transmission, comprising a first driving gear and a first driven gear meshing with each other, and a second driving gear and a second driven gear meshing with each other, wherein the first driving gear is connected to a power input shaft, and the second driven gear is connected to a power output shaft; characterized in that: The first driven wheel and the second driving wheel are connected or fixedly connected by a drive shaft key. The first driving wheel and the second driving wheel have the same structure, and the first driven wheel and the second driven wheel have the same structure. The assembly phase between the first driving wheel and the first driven wheel is the same as the assembly phase between the second driving wheel and the second driven wheel. Within one revolution cycle, the transmission ratio is obtained by comparing the speed of the first driven wheel with the speed of the first driven wheel. The proportion of the transmission ratio greater than 1 in the total range of one revolution is 50% to 60%. The rotation angle ψ of the first driven wheel and the rotation angle φ of the first driving wheel, within one rotation cycle of the first driving wheel, conform to the following formula: Where k is a constant coefficient; G is the constant speed ratio range between the first driving wheel and the first driven wheel; and a to h are the coefficients of the 7th order spline, respectively.

2. The non-circular gear set for cylinder speed change in a combing machine as described in claim 1, characterized in that: The transmission ratio between the second driven wheel and the first driving wheel varies from 0.35 to 1.8, and the transmission ratio is highest within the rotation angle range [0, G] of the first driving wheel.

3. The non-circular gear set for cylinder speed change in a combing machine as described in claim 1, characterized in that: The first driving wheel, the first driven wheel, the second driving wheel, and the second driven wheel have the same number of teeth, ranging from 23 to 35.

4. The non-circular gear set for cylinder speed change in a combing machine as described in claim 1, characterized in that: The first driving wheel, the first driven wheel, the second driving wheel, and the second driven wheel have the same normal module, which ranges from 3.2 to 3.8 mm.

5. The non-circular gear set for cylinder speed change in a combing machine as described in claim 1, characterized in that: The pressure angles of the first driving wheel, the first driven wheel, the second driving wheel, and the second driven wheel are the same, and the pressure angle range is 23 to 28 degrees.

6. The non-circular gear set for cylinder speed change in a combing machine as described in claim 1, characterized in that: The first driving gear, the first driven gear, the second driving gear, and the second driven gear are spur gears or helical gears; when the first driving gear, the first driven gear, the second driving gear, and the second driven gear are helical gears, the helix angle of the helical gear is in the range of 8 to 15 degrees.

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