Pin-tooth shell assembly and speed reducer

Abstract

The application discloses a needle-tooth shell assembly and a speed reducer, and solves the problem of high difficulty in needle selection and the problem of speed reducer failure caused by needle-tooth groove wear in the prior art. The needle-tooth shell assembly comprises a needle-tooth shell and a needle-tooth sleeve. The needle-tooth sleeve is arranged to be movable on the needle-tooth shell, so that the position of the needle-tooth groove on the needle-tooth sleeve for cooperating with the needle can be adjusted, and the diameter of the needle-tooth shell is adjusted, so that the needle-tooth groove can be adapted according to the selection of the needle, the problem that the needle engagement top gap is too different from the theory due to the error in the diameter screening of the needle in the prior art is solved, the purpose of weakening the adverse effect of the large diameter fluctuation of the needle on the service life of the speed reducer is achieved, the assembly precision of the speed reducer and the service life of the speed reducer are improved, the purpose of reducing the idle stroke of the speed reducer and the attenuation rate of the stiffness curve is achieved, and the service life of the speed reducer is improved.

Description

Technical Field

[0001] This invention relates to the field of transmission equipment technology, and more specifically, to a pin gear housing assembly and a speed reducer. Background Technology

[0002] The RV reducer is a new type of cycloidal pinwheel planetary transmission mainly composed of a primary gear transmission and a secondary cycloidal transmission. It has the advantages of high transmission accuracy, low backlash, high rigidity, strong impact resistance, compact structure, and high transmission efficiency. Among them, pinwheel-cycloidal meshing is one of the core technologies of the RV reducer.

[0003] A common pinwheel meshing structure includes a pin tooth housing, pin tooth grooves, needle rollers, and a cycloidal wheel, with the needle rollers inserted into the pin tooth housing and pin tooth grooves for positioning. During pin tooth meshing, the cycloidal wheel tooth surface contacts and meshes with the needle roller surface to transmit force. To achieve an ideal meshing state, the dimensional fit of these three components must be strictly controlled. To improve efficiency and reduce difficulty, needle rollers of different diameter grades are generally used to adjust the dimensional relationship. However, this method increases the workload, and because the needle roller diameter is graded at the micrometer level, the selected needle roller diameter often changes due to environmental factors, measurement methods, etc., causing significant inconvenience for measurement and selection. Another problem is that during reducer operation, due to the material of the pin tooth housing, the pin tooth grooves wear relatively quickly, leading to increased cycloidal tip clearance, looser pinwheel meshing, increased idle backlash, reduced stiffness, and even premature reducer failure, resulting in decreased reducer reliability. Summary of the Invention

[0004] This invention discloses a needle tooth housing assembly and a reducer that can adjust the position of the needle tooth groove to improve assembly accuracy and operational reliability, solving the problems of high difficulty in selecting needle rollers and reducer failure caused by wear of the needle tooth groove in the prior art.

[0005] This invention discloses a needle-tooth shell assembly, comprising:

[0006] Needle-shaped shell;

[0007] A needle tooth sleeve is movably disposed on the needle tooth shell, and the needle tooth sleeve has a needle tooth groove formed facing the inside of the needle tooth shell;

[0008] An adjustment structure is provided on the needle tooth shell, the needle tooth sleeve is connected to the adjustment structure, and the adjustment structure can drive the needle tooth sleeve to move to adjust the position of the needle tooth groove within the needle tooth shell.

[0009] The number of needle sleeves is at least two, and all the needle sleeves are distributed in a ring on the needle shell with the central axis of the needle shell as the axis. The adjustment structure can drive all the needle sleeves to move at the same time.

[0010] The needle sleeve is provided with a guide groove, and the needle shell is provided with a guide structure. The guide groove and the guide structure correspond one-to-one, and the needle sleeve can move along the radial direction of the needle shell under the guidance of the guide groove and the guide structure.

[0011] The guide structure includes at least two guide blocks, all of which are arranged in a ring around the axis of the needle tooth shell, and the guide blocks are able to slide within the corresponding guide grooves.

[0012] The adjustment structure includes a transmission ring, which is rotatably disposed within the needle tooth housing and is connected to all the needle tooth sleeves.

[0013] The needle sleeve is provided with a first thread structure, and the transmission ring is provided with a second thread structure, and the first thread structure and the second thread structure are threadedly engaged.

[0014] The transmission ring is provided with helical teeth, the axis of the helical teeth is collinear with the axis of the transmission ring, the needle tooth sleeve is provided with meshing teeth, the helical teeth are threadedly engaged with the meshing teeth on all the needle tooth sleeves, the meshing teeth form the first thread structure, and the helical teeth form the second thread structure.

[0015] Along the direction of increasing diameter of the helical teeth, the minimum distance from the meshing teeth on the needle tooth sleeve to the central axis of the needle tooth shell gradually increases, and in two adjacent needle tooth sleeves, the difference b between the minimum distances b of the two meshing teeth to the central axis of the needle tooth shell satisfies the following formula:

[0016] b = 360a / v;

[0017] Where a is the change in the extreme diameter of the helical teeth when the transmission ring rotates by 1°; v is the number of needle sleeves.

[0018] The adjustment structure further includes an adjustment ring, which is rotatably disposed on the needle tooth housing. The first end of the adjustment ring is located inside the needle tooth housing, and the transmission ring is disposed on the first end. The second end of the adjustment ring is exposed outside the needle tooth housing.

[0019] The adjustment structure further includes an adjustment ring and a driving member. The adjustment ring is rotatably disposed inside the needle tooth housing, the transmission ring is disposed on the adjustment ring, and the driving member is rotatably disposed on the needle tooth housing, and the driving member can drive the adjustment ring to rotate.

[0020] The driving component is provided with a first bevel tooth structure, and the adjusting ring is provided with a second bevel tooth structure, the first bevel tooth structure and the second bevel tooth structure meshing with each other.

[0021] The needle tooth sleeves are distributed in at least two rings on the needle tooth shell. The adjustment structure corresponds one-to-one with the rings, and each adjustment structure can drive all the needle tooth sleeves in the corresponding ring to move.

[0022] The pin tooth housing includes a flange and two bearing seats, both of which are connected to the flange. A receiving cavity is formed between each bearing seat and the flange. All the pin tooth sleeves in each annulus can be movably disposed in the corresponding receiving cavity.

[0023] The needle housing and / or the driving component are provided with scales.

[0024] The relationship between the change in scale m corresponding to the movement of the driving component and the position movement distance L of the needle groove satisfies the following formula:

[0025] i = d 调 / d 驱 (Ⅰ);

[0026] ρ=at+r (Ⅱ);

[0027] x = 360a / i (Ⅲ);

[0028] x b =x / n (Ⅳ);

[0029] L = mx b (V);

[0030] Where i is the transmission ratio between the driving component and the adjusting ring; d 调 To adjust the diameter of the portion of the ring that meshes with the drive component, d 驱 ρ is the diameter of the part where the drive component meshes with the adjusting ring; ρ is the polar diameter of the helix corresponding to the helical teeth; a is the helical linear density, that is, the change in the polar diameter ρ of the helix when the helix rotates by 1°; r is the minimum distance from the helical teeth to the central axis of the needle tooth shell; t is the independent variable, in degrees; x is the displacement of the needle tooth sleeve per revolution of the drive component; x b is the displacement accuracy of the needle sleeve; n is the number of divisions into which the scale is divided.

[0031] Another aspect of the present invention provides a speed reducer including the above-described needle gear housing assembly.

[0032] The pin tooth housing assembly and reducer of the present invention configure the pin tooth sleeve to be movable on the pin tooth housing, thereby adjusting the position of the pin tooth groove on the pin tooth sleeve for engaging with the needle roller, and thus adjusting the top diameter of the pin tooth housing. This allows the pin tooth groove to be adapted according to the selected needle roller, solving the problem in the prior art where the pin-to-cylinder meshing clearance differs too much from the theoretical value due to errors in needle roller diameter selection. This achieves the goal of mitigating the adverse effects of large needle roller diameter fluctuations on the reducer's lifespan, improving the reducer's assembly accuracy and operating life. It also solves the problem of increased pin-to-cylinder meshing clearance due to wear of the pin tooth groove during long-term running-in, achieving the goal of reducing the reducer's idle travel and stiffness curve attenuation rate, thus improving the reducer's lifespan. Furthermore, because the position of the pin tooth groove is adjustable, it solves the problem of unusable equipment due to inconsistent root diameters of the upper and lower cycloidal wheels, expanding the usable range of the cycloidal wheels and improving the utilization rate of parts. Attached Figure Description

[0033] Figure 1 This is a schematic diagram of the structure of the needle-tooth shell assembly according to an embodiment of the present invention;

[0034] Figure 2 This is a cross-sectional view of the needle-tooth shell assembly according to an embodiment of the present invention;

[0035] Figure 3 yes Figure 2 A partial schematic diagram of point A;

[0036] Figure 4 yes Figure 3 A partial schematic diagram of point B;

[0037] Figure 5 This is a schematic diagram of the transmission ring structure of the needle-tooth housing assembly according to an embodiment of the present invention;

[0038] Figure 6 yes Figure 5 A partial schematic diagram at point C;

[0039] Figure 7 This is a partial cross-sectional view of the transmission ring and the adjusting ring according to an embodiment of the present invention;

[0040] Figure 8 This is a front view of the needle sleeve according to an embodiment of the present invention;

[0041] Figure 9 This is a cross-sectional view of the needle sleeve according to an embodiment of the present invention;

[0042] Figure 10 yes Figure 9 A partial schematic diagram at point D;

[0043] Figure 11 This is a cross-sectional view of the driving component according to an embodiment of the present invention;

[0044] Figure 12 This is a cross-sectional view of the bearing housing according to an embodiment of the present invention;

[0045] Legend: 1. Needle tooth housing; 2. Needle tooth sleeve; 21. Needle tooth groove; 22. Guide groove; 4. Guide block; 31. Transmission ring; 22. First thread structure; 32. Second thread structure; 33. Adjusting ring; 34. Drive component; 11. Flange; 12. Bearing seat. Detailed Implementation

[0046] The present invention will be further described below with reference to embodiments, but is not limited to the contents of the specification.

[0047] like Figures 1 to 12 As shown, the present invention discloses a needle tooth shell assembly, comprising: a needle tooth shell 1; a needle tooth sleeve 2, the needle tooth sleeve 2 being movably disposed on the needle tooth shell 1, and the needle tooth sleeve 2 having a needle tooth groove 21 formed facing the interior of the needle tooth shell 1; and an adjustment structure, the adjustment structure being disposed on the needle tooth shell 1, the needle tooth sleeve 2 being connected to the adjustment structure, and the adjustment structure being capable of driving the needle tooth sleeve 2 to move to adjust the position of the needle tooth groove 21 within the needle tooth shell 1. The needle sleeve 2 is designed to be movable on the needle housing 1, thereby allowing the position of the needle groove 21 on the needle sleeve 2 that mates with the needle roller to be adjusted. This, in turn, adjusts the top diameter of the needle housing 1, enabling the needle groove 21 to be adapted to the selected needle roller. This solves the problem in the prior art where the needle roller diameter selection error leads to a large difference between the needle roller meshing clearance and the theoretical value. It achieves the goal of mitigating the adverse effects of large needle roller diameter fluctuations on the lifespan of the reducer, improving the assembly accuracy and service life of the reducer. It also solves the problem of increased needle roller meshing clearance due to wear of the needle groove 21 during long-term running-in, achieving the goal of reducing the reducer's idle travel and stiffness curve attenuation rate, thus improving the reducer's lifespan. Furthermore, since the position of the needle groove 21 is adjustable, it solves the problem of unusable cycloidal wheels due to inconsistent tooth root diameters, expanding the usable range of the cycloidal wheels and improving the utilization rate of parts.

[0048] Since the needle tooth housing assembly needs to cooperate with the cycloidal wheel, and the cycloidal wheel has multiple cycloidal teeth, multiple needle rollers are required to cooperate with the cycloidal wheel. Each needle roller corresponds to a needle tooth groove 21. Therefore, the number of needle tooth sleeves 2 is at least two. All needle tooth sleeves 2 are arranged in a ring around the central axis of the needle tooth housing 1. The adjustment structure can simultaneously drive all needle tooth sleeves 2 to move. At this time, the needle tooth housing 1 can reliably cooperate with the needle rollers and the cycloidal wheel. At the same time, in order to ensure that the movement of the needle tooth sleeves 2 does not cause the needle tooth grooves 21 to move in a direction other than the radial direction of the needle tooth housing 1, the needle tooth sleeves 2 are provided with guide grooves 23, and the needle tooth housing 1 is provided with guide structures. The guide grooves 23 and guide structures correspond one-to-one, and the needle tooth sleeves 2 can move in the radial direction of the needle tooth housing 1 under the guidance of the guide grooves 23 and guide structures. The movement of the needle sleeve 2 is restricted by the guide groove 23, ensuring that the needle groove 21 can only move along the radial direction of the needle housing 1. This allows the needle groove 21 to reliably engage with the needle roller, ensuring the reliable operation of the reducer. Specifically, the guide structure includes at least two guide blocks 4, all of which are arranged in a ring around the axis of the needle housing 1. Each guide block 4 can slide within its corresponding guide groove 23. The guide blocks 4 restrict the axial and circumferential directions of the needle sleeve 2, ensuring that the needle sleeve 2 can only move along the predetermined radial direction of the needle housing 1. This prevents the needle sleeve 2 from moving in a non-radial direction, which could cause deviation between the needle groove 21 and the needle roller, thus ensuring the reliability of the reducer.

[0049] The adjustment structure includes a transmission ring 31, which is rotatably disposed within the pin tooth housing 1 and connected to all the pin tooth sleeves 2. The transmission ring 31 drives all the pin tooth sleeves 2 to move synchronously, thereby adjusting the position of all the pin tooth grooves 21 and changing the top diameter of the pin tooth housing 1. Therefore, after the reducer has been running for a period of time, the top diameter can be reduced by rotating the drive component, allowing the pin pendulum to return to its optimal meshing state, ultimately improving the reducer's performance once again. This also reduces the effect of the needle roller diameter adjustment meshing dimension chain. Therefore, the large or small needle roller diameter can be ignored during assembly, solving the problem in the existing technology where the needle roller diameter selection error leads to a large difference between the needle roller meshing clearance and the theoretical value. This achieves the goal of weakening the adverse effect of large needle roller diameter fluctuations on the reducer's lifespan, improving the reducer's assembly accuracy and operating life. It also solves the problem of increased needle roller meshing clearance due to wear of the needle tooth groove 21 during long-term running-in, achieving the goal of reducing the reducer's idle stroke and stiffness curve attenuation rate, thus improving the reducer's lifespan. Furthermore, since the position of the needle tooth groove 21 is adjustable, it solves the problem of unusable cycloidal wheels due to inconsistent tooth root diameters, expanding the usable range of the cycloidal wheels and improving the utilization rate of parts.

[0050] In one embodiment, the pin sleeve 2 is provided with a first threaded structure 22, and the transmission ring 31 is provided with a second threaded structure 32. The first threaded structure 22 and the second threaded structure 32 are threadedly engaged. When the transmission ring 31 rotates, the second threaded structure 32 on it also rotates. At this time, the first threaded structure 22 will also move under the drive of the second threaded structure 32, thereby driving the pin sleeve 2 to move. Moreover, under the limiting effect of the guide groove 23, the pin sleeve 2 can only move in the radial direction of the pin housing 1, thereby realizing the movement of the pin groove 21 and the adjustment of the top diameter within the pin housing 1. Since the transmission ring 31 needs to be threadedly engaged with all the pin sleeves 2, optionally, the transmission ring 31 is provided with helical teeth, the axis of the helical teeth being collinear with the axis of the transmission ring 31. The pin sleeve 2 is provided with meshing teeth, and the helical teeth are threadedly engaged with the meshing teeth on all the pin sleeves 2. The meshing teeth constitute the first threaded structure 22, and the helical teeth constitute the second threaded structure 32. When the transmission ring 31 rotates, the helical teeth will also rotate. At any position of the needle tooth sleeve 2, the position of the helical teeth corresponding to the needle tooth sleeve 2 changes due to the rotation. This is equivalent to the part of the helical teeth that mates with the needle tooth sleeve 2 changing in the radial direction of the needle tooth shell 1. This can drive the needle tooth sleeve 2 to move in the radial direction of the needle tooth shell 1, thereby realizing the adjustment of the top diameter of the needle tooth shell 1.

[0051] Due to the presence of parameter 'a' in the helical formula ρ = at + r, where 'a' represents the helical density, the change in polar diameter ρ per 1° rotation; ρ is the polar diameter; r is the helical radius at the minimum polar diameter ρ; and t is the independent variable in degrees, the radial dimension changes with each 1° rotation of the helical tooth. To ensure that the center of all needle tooth grooves 21 coincides with the center of the needle tooth shell 1, the positions of the meshing teeth in the needle tooth grooves 21 need to be corrected. That is, the positions of the meshing teeth on each needle tooth groove 21 must be different to ensure that all needle tooth grooves 21 simultaneously mesh with a single helical tooth. Therefore, along the direction of increasing diameter of the helical tooth, the minimum distance from the meshing teeth on the needle tooth sleeve 2 to the central axis of the needle tooth shell 1 gradually increases. Furthermore, in two adjacent needle tooth sleeves 2, the difference 'b' between the minimum distances of the two meshing teeth to the central axis of the needle tooth shell 1 satisfies the following formula:

[0052] b = 360a / v;

[0053] Where a is the change in the extreme diameter of the helical teeth when the transmission ring 31 rotates by 1°; v is the number of needle sleeves 2.

[0054] That is, the method for correcting the position of the meshing teeth on the pin tooth groove 21 is as follows: the pin tooth groove 21 located at the maximum value of the extreme diameter ρ is defined as the first pin tooth groove 21, and the pin tooth groove 21 is defined sequentially according to the decreasing direction of the extreme diameter ρ up to the vth pin tooth groove 21. The position of the spiral structure of each pin tooth groove 21 is increased by b compared to the previous one. In other words, the spiral structure of each pin tooth groove 21 is the same, but the position of the pin tooth groove 21 is different, and the position difference between two adjacent pin tooth grooves 21 is b.

[0055] The spiral of the helical teeth is an Archimedean spiral, which can lock with the meshing teeth at any position, ensuring the reliable position of the needle tooth sleeve 2 and the needle tooth groove 21.

[0056] The polar radius ρ is a parameter used to represent the position of a point in polar coordinates. It represents the distance between the point and the center. It can also be combined with the angle t to represent the position of a point in polar coordinates. For example, the coordinates of point a are (ρ, t), where the polar radius ρ represents the distance from point a to the coordinate center, and t represents the angle between the polar radius ρ and the polar axis (the ray at 0°).

[0057] The formula for a helix is ​​ρ = at + r, where the extreme radius ρ represents the distance from each point on the helix to the center (the center of the helical teeth). r can also be called the extreme radius when t is 0. at + r represents the distance from the point to the center at different angles. For example, if t equals 30° and ρ equals 120mm, it means that at 30°, the distance from the point to the center is 120mm.

[0058] Since the needle tooth sleeve 2 is located inside the needle tooth housing 1, and the transmission ring 31 needs to be located within the guide groove 23, also inside the needle tooth housing 1, it is inconvenient for the user to operate the transmission ring 31 from outside the needle tooth housing 1. Therefore, the adjustment structure also includes an adjustment ring 33, which is rotatably mounted on the needle tooth housing 1. The first end of the adjustment ring 33 is inside the needle tooth housing 1, and the transmission ring 31 is located on the first end. The second end of the adjustment ring 33 is exposed outside the needle tooth housing 1. The adjustment ring 33 drives the transmission ring 31 to rotate, facilitating the adjustment of the position of the needle tooth groove 21. The user only needs to operate the adjustment ring 33 from outside the needle tooth housing 1. The central axis of the adjustment ring 33 is collinear with the central axis of the needle tooth housing 1, ensuring that the adjustment ring 33 can reliably rotate on the needle tooth housing 1.

[0059] Furthermore, the adjustment structure also includes an adjustment ring 33 and a drive member 34. The adjustment ring 33 is rotatably disposed within the pin tooth housing 1, the transmission ring 31 is disposed on the adjustment ring 33, and the drive member 34 is rotatably disposed on the pin tooth housing 1, and the drive member 34 can drive the adjustment ring 33 to rotate. Using the adjustment ring 33 to drive the transmission ring 31 to rotate facilitates the adjustment of the position of the pin tooth groove 21. However, the central axis of the adjustment ring 33 is collinear with the central axis of the pin tooth housing 1, resulting in a relatively large size for the adjustment ring 33 and making its operation more difficult for the user. To further reduce this difficulty, a drive member 34 is disposed on the pin tooth housing 1 to cooperate with the adjustment ring 33. By operating the drive member 34 at its designated position on the pin tooth housing 1, the rotation of the adjustment ring 33 can be achieved, thereby reducing the difficulty of operating the adjustment ring 33, and consequently reducing the difficulty of adjusting the position of the pin tooth groove 21 and the top diameter of the pin tooth housing 1, thus improving the reliability of the reducer. Optionally, the driving member 34 is provided with a first bevel gear structure, and the adjusting ring 33 is provided with a second bevel gear structure, the first bevel gear structure and the second bevel gear structure meshing with each other. The meshing of the first and second bevel gear structures enables the driving member 34 to drive the adjusting ring 33 to rotate. Figure 2As shown in Figure 3, the transmission ring 31 is located at the first end of the adjusting ring 33, and a second bevel tooth structure is provided at the second end of the adjusting ring 33. The driving member 34 is located at the second end of the adjusting ring 33 and is exposed on the surface of the pin tooth housing 1. The user can directly operate the driving member 34 to rotate the transmission ring 31. To ensure reliable connection between the driving member 34 and the pin tooth housing 1 and the rotation of the driving member 34, a driving groove is formed on the pin tooth housing 1. The driving member 34 is rotatably disposed in the driving groove, and the second end of the adjusting ring 33 is located in the driving groove. The driving member 34 meshes with the second end of the adjusting ring 33 for transmission. The driving member 34 is provided with a mounting hole, and the driving member 34 can be installed in the driving groove by bolts fitting into the mounting hole. To facilitate driving the driving member 34, a mating hole for mates with tools is provided on the driving member 34, such as a hexagonal hole for mates with a hex wrench, or a square hole, etc. The user can insert the corresponding tool into the corresponding mating hole to rotate the driving member 34. Figure 2 As shown, the drive groove is formed by the flange 11 and the corresponding bearing seat 12. That is, a partial groove is provided on the flange 11 and a partial groove is provided on the bearing seat 12. The two grooves are engaged to form the drive groove.

[0060] To achieve static balance of the input shaft and improve the axial load capacity during motion, a speed reducer typically employs two identical odd-numbered-tooth cycloidal gears. Therefore, the pin tooth sleeves 2 are arranged in at least two annular rings on the pin tooth housing 1. The adjusting structures correspond one-to-one with these annular rings, and each adjusting structure can move all the pin tooth sleeves 2 within its corresponding annulus. This allows for adjustment of the different top diameters of the corresponding cycloidal gears within the pin tooth housing 1, ensuring the reliability of the speed reducer.

[0061] like Figure 2 As shown, the needle tooth housing 1 includes a flange 11 and two bearing seats 12. Both bearing seats 12 are connected to the flange 11, and a receiving cavity is formed between each bearing seat 12 and the flange 11. All the needle tooth sleeves 2 in each annulus are movably disposed within their respective receiving cavities. Two cycloidal wheels and corresponding needle rollers are also disposed within their respective receiving cavities, allowing the cycloidal wheels to rotate within their respective receiving cavities.

[0062] Each bearing housing 12 is provided with a guide block 4, which cooperates with the guide groove 23 on the corresponding needle sleeve 2 to limit the needle sleeve 2 installed on the bearing housing 12. The drive component 34 is rotatably set on the outer wall of the bearing housing 12, and the adjusting ring 33 is located between the flange 11 and the bearing housing 12.

[0063] During assembly, the drive component 34 is first fixed to the bearing housing 12 with bolts. Then, the two adjustment structures are placed in the two bearing housings 12 respectively, and the adjustment ring 33 of the adjustment structure is made to engage with the conical drive component 34. The two parts are then positioned and fixed together with the flange 11 using pins and bolts. Finally, the pin tooth sleeves 2 are arranged in sequence and placed in the preset positions. The pin tooth sleeves 2 are brought in by rotating the drive component 34, completing the assembly of the pin tooth housing 1. When assembling the needle rollers and cycloidal wheels in the reducer, smaller diameter needle rollers can be selected first for easier assembly. After the cycloidal wheel and needle rollers are installed in the corresponding positions of the pin tooth groove 21, the pin tooth groove 21 can be moved radially by rotating the drive component 34 until the pin tooth groove 21 contacts the needle rollers. During operation, because this type of helix has a self-locking function, it can be ensured that the pin tooth groove 21 will not move backward. Also, because there is a guide block 4, the pin tooth groove 21 will not move left or right. Therefore, the pin tooth groove 21 can maintain a relatively stable state in actual operation. After a period of operation, the drive component 34 can be further adjusted to compensate for the wear on the hole wall of the needle tooth groove 21, thereby restoring the needle pendulum engagement state to its optimal state. Furthermore, the movement distance of the needle tooth groove 21 can be recorded to determine the current hole wear condition.

[0064] Specifically, the needle tooth housing 1 and / or the driving member 34 are provided with scales. When the driving member 34 is rotated, the driving member 34 and the needle tooth housing 1 will undergo relative displacement, thereby realizing the change of the scale. At this time, the movement distance of the needle tooth groove 21 can be determined by reading the scale.

[0065] The movement control structure and principle of the needle groove 21 are as follows:

[0066] The movement control of the needle tooth groove 21 can be divided into the bevel gear meshing transmission between the driving component 34 and the adjusting ring 33, and the helical transmission structure formed by the transmission ring 31 and the needle tooth sleeve 2. The transmission distance is calculated as follows:

[0067] The first stage of transmission consists of a bevel gear meshing structure between the driving component 34 and the adjusting ring 33, with a transmission ratio i of:

[0068] i = d 调 / d 驱 (Ⅰ);

[0069] Where d 调 To adjust the diameter of the portion of the ring 33 that meshes with the drive member 34, d 驱 d is the diameter of the meshing portion between the driving member 34 and the adjusting ring 33. When the meshing portion between the adjusting ring 33 and the driving member 34 is a bevel gear, d 调 To adjust the pitch circle diameter of ring 33, similarly, d 驱 The pitch circle diameter of the drive component 34;

[0070] The second-stage transmission consists of a helical meshing mechanism between the adjusting ring 33 and the needle sleeve 2. To ensure that v needle tooth grooves 21 move simultaneously, the threaded teeth on the transmission ring 31 are designed using the helical principle, and its polar coordinate formula is as follows:

[0071] ρ=at+r (Ⅱ);

[0072] ρ is the extreme diameter of the helix corresponding to the helical tooth; a represents the helical linear density, that is, the change in the extreme diameter ρ of the helix when the helix rotates by 1°; r represents the minimum distance from the helical tooth to the central axis of the needle tooth shell 1 (the initial radius of the helix); t is the independent variable, in degrees.

[0073] According to formulas (Ⅰ) and (Ⅱ), the displacement x of the pin sleeve 2 per revolution of the driving component 34 can be obtained as follows:

[0074] x = 360a / i (Ⅲ);

[0075] To accurately record the displacement of the needle tooth groove 21, the scale on the drive component 34 or the needle tooth housing 1 is divided into at least n equal parts. Then, the displacement accuracy x of the needle tooth sleeve 2 is... b for:

[0076] x b =x / n (Ⅳ);

[0077] In summary, the displacement distance L of the needle tooth groove 21 can be calculated by the change in scale m corresponding to the movement of the driving component 34:

[0078] L = mx b (V);

[0079] Where parameter x b The value needs to be less than 1μm. In the helix formula, the parameter 'a' affects the helix density. If 'a' is too small, it will cause difficulties in machining and assembly, but if it is too large, it will reduce accuracy. It needs to be selected comprehensively based on factors such as machining conditions. Specifically, 'm' can be represented as the number of minimum scale divisions the driving component has rotated.

[0080] The specific machining steps for the helical teeth are as follows:

[0081] Step S1: Select the initial displacement accuracy x according to the usage requirements. b And equal fractions n;

[0082] Step S2: Preliminarily select d based on the design dimensions of the needle tooth shell 1. 调 and d 驱 ;

[0083] Step S3: Calculate the helix parameter a according to formulas (Ⅲ) and (Ⅳ);

[0084] Step S4: Determine whether the spiral parameter a meets the process feasibility requirements;

[0085] If satisfied, the initial radius r is selected based on the minimum value of the apex diameter of the needle shell 1;

[0086] If not satisfied, then determine whether to adjust x. b and n;

[0087] If adjustments are required, steps S1 to S4 are repeated.

[0088] If no adjustment is made, repeat steps S2 to S4;

[0089] Step S5: Based on d determined in steps S1 to S4 调 d 驱 , r, x b Draw the helix of the helical teeth with n.

[0090] Another aspect of the present invention provides a speed reducer including the above-described needle gear housing assembly.

[0091] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. Those skilled in the art can make other variations or modifications based on the above description. It is impossible to exhaustively list all embodiments here. All obvious variations or modifications derived from the technical solutions of the present invention are still within the protection scope of the present invention.

Claims

1. A needle-tooth shell assembly, characterized in that, include: Needle-tooth shell (1); A needle tooth sleeve (2) is movably disposed on the needle tooth shell (1), and a needle tooth groove (21) is formed on the needle tooth sleeve (2) facing the interior of the needle tooth shell (1); An adjustment structure is provided on the needle tooth shell (1), the needle tooth sleeve (2) is connected to the adjustment structure, and the adjustment structure can drive the needle tooth sleeve (2) to move to adjust the position of the needle tooth groove (21) in the needle tooth shell (1); The adjustment structure includes a rotatable transmission ring (31) disposed inside the needle tooth shell (1), and the transmission ring (31) drives the needle tooth sleeve (2) to move synchronously through a threaded structure.

2. The needle-tooth housing assembly according to claim 1, characterized in that, The number of needle sleeves (2) is at least two. All the needle sleeves (2) are arranged in a ring on the needle shell (1) with the central axis of the needle shell (1) as the axis. The adjustment structure can drive all the needle sleeves (2) to move at the same time.

3. The needle-tooth housing assembly according to claim 2, characterized in that, The needle sleeve (2) is provided with a guide groove (23), and the needle shell (1) is provided with a guide structure. The guide groove (23) corresponds one-to-one with the guide structure, and the needle sleeve (2) can move along the radial direction of the needle shell (1) under the guidance of the guide groove (23) and the guide structure.

4. The needle-tooth housing assembly according to claim 3, characterized in that, The guide structure includes at least two guide blocks (4), all of which are arranged in a ring around the axis of the needle tooth shell (1) and can slide in the corresponding guide groove (23).

5. The needle-tooth housing assembly according to claim 1, characterized in that, The needle sleeve (2) is provided with a first thread structure (22), and the transmission ring (31) is provided with a second thread structure (32). The first thread structure (22) and the second thread structure (32) are threaded together.

6. The needle-tooth housing assembly according to claim 5, characterized in that, The transmission ring (31) is provided with helical teeth, the axis of the helical teeth is collinear with the axis of the transmission ring (31), the needle sleeve (2) is provided with meshing teeth, the helical teeth are threadedly engaged with the meshing teeth on all the needle sleeves (2), the meshing teeth constitute the first thread structure (22), and the helical teeth constitute the second thread structure (32).

7. The needle-tooth housing assembly according to claim 6, characterized in that, Along the direction of increasing diameter of the helical teeth, the minimum distance from the meshing teeth on the pin tooth sleeve (2) to the central axis of the pin tooth shell (1) gradually increases, and in two adjacent pin tooth sleeves (2), the difference b between the minimum distances b of the two meshing teeth to the central axis of the pin tooth shell (1) satisfies the following formula: b = 360a / v; Where a is the change in the extreme diameter of the helix corresponding to the helix tooth when the transmission ring (31) rotates by 1°; v is the number of needle sleeves (2).

8. The needle-tooth housing assembly according to claim 1, characterized in that, The adjustment structure further includes an adjustment ring (33), which is rotatably disposed on the needle tooth shell (1). The first end of the adjustment ring (33) is located inside the needle tooth shell (1), and the transmission ring (31) is disposed on the first end. The second end of the adjustment ring (33) is exposed outside the needle tooth shell (1).

9. The needle-tooth housing assembly according to claim 1, characterized in that, The adjustment structure further includes an adjustment ring (33) and a drive member (34). The adjustment ring (33) is rotatably disposed inside the needle tooth shell (1). The transmission ring (31) is disposed on the adjustment ring (33). The drive member (34) is rotatably disposed on the needle tooth shell (1), and the drive member (34) can drive the adjustment ring (33) to rotate.

10. The needle-tooth housing assembly according to claim 9, characterized in that, The drive component (34) is provided with a first bevel tooth structure, and the adjusting ring (33) is provided with a second bevel tooth structure, the first bevel tooth structure and the second bevel tooth structure meshing with each other.

11. The needle-tooth housing assembly according to claim 2, characterized in that, The needle sleeves (2) are distributed in at least two rings on the needle shell (1). The adjustment structure corresponds one-to-one with the rings, and each adjustment structure can drive all the needle sleeves (2) in the corresponding ring to move.

12. The needle-tooth housing assembly according to claim 11, characterized in that, The needle tooth shell (1) includes a flange (11) and two bearing seats (12). The two bearing seats (12) are connected to the flange (11), and a receiving cavity is formed between each bearing seat (12) and the flange (11). All the needle tooth sleeves (2) in each annulus can be movably disposed in the corresponding receiving cavity.

13. The needle-tooth housing assembly according to claim 9, characterized in that, The needle housing (1) and / or the drive member (34) are provided with scales.

14. The needle-tooth housing assembly according to claim 13, characterized in that, The relationship between the change in scale m corresponding to the movement of the driving component and the position movement distance L of the needle groove (21) satisfies the following formula: i = d 调 / d 驱 (I); ρ=at+r (Ⅱ); x=360a / i (Ⅲ); X b = x / n (IV); L = mx b (V); Where i is the transmission ratio between the driving component (34) and the adjusting ring (33); d 调 To adjust the diameter of the portion of the ring (33) that meshes with the drive member (34), d 驱 ρ is the diameter of the meshing part between the drive component (34) and the adjusting ring (33); ρ is the extreme diameter of the helix corresponding to the helical tooth; a is the helical linear density, that is, the change in the extreme diameter ρ of the helix when the helix rotates by 1°; r is the minimum distance from the helical tooth to the central axis of the needle tooth shell (1); t is the independent variable, in degrees; x is the displacement of the needle tooth sleeve (2) when the drive component (34) rotates by 1 revolution; xb is the displacement accuracy of the needle tooth sleeve (2); n is the number of divisions of the scale.

15. A speed reducer, characterized in that, Includes the needle-tooth housing assembly according to any one of claims 1 to 14.

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