A kind of double lead worm gear pair gap compensation device

Abstract

This invention discloses a backlash compensation device for a dual-lead worm gear pair, relating to the field of machine tool transmission reducer technology. It includes a reducer body comprising a housing and a worm and worm wheel disposed within the housing, with the worm and worm wheel meshing. A worm backlash compensation component, installed on the housing and worm, is used to compensate, adjust, and fix the backlash between the worm and worm wheel. The worm backlash compensation component includes: a bearing whose inner ring rotatably fits onto one end surface of the worm, and whose outer ring is fixed to the inner wall of the housing. This invention employs a worm + worm wheel bidirectional elastic compensation structure, which can automatically eliminate tooth flank backlash generated during long-term operation, maintaining zero backlash in the machine tool transmission. The elastic preload and bolt double locking provide sufficient rigidity after compensation, resisting cutting vibrations and preventing loosening, ensuring long-term high-precision stable operation of the machine tool without frequent shutdowns for re-inspection and adjustment. The adjustment process includes automatic oil injection, forcibly lubricating the meshing surfaces during compensation, reducing tooth surface wear, heat generation, abnormal noise, and the risk of galling.

Description

Technical Field

[0001] This invention relates to the field of machine tool transmission reducer technology, and in particular to a backlash compensation device for a double-lead worm gear pair. Background Technology

[0002] In precision machine tool transmission systems, the double-lead worm gear pair is a core component for achieving high-precision indexing, low-speed high torque, and no backlash error during reversal. It is widely used in key parts such as CNC indexing heads, rotary tables, precision slides, and cam mechanisms.

[0003] As machine tools operate at high speed, under heavy load, and continuously for extended periods, wear inevitably occurs on the meshing tooth surfaces of the worm gear and worm shaft. This leads to a gradual increase in the meshing clearance, directly causing problems such as increased return clearance, decreased positioning accuracy, reversing vibration, abnormal noise, and dimensional drift in machining, which seriously affect the machining accuracy of parts and the stability of the equipment.

[0004] However, in practical applications, there are still some unresolved problems. The following are some common problems of clearance compensation devices for dual-lead worm gear pairs: Traditional worm gear pair clearance compensation is mostly done by manually disassembling the whole machine and then adjusting the clearance compensation. The operation is cumbersome, and most structures can only adjust the worm or worm wheel alone. The compensation range is limited and the rigidity is insufficient. At the same time, there is a lack of supporting structures for automatic lubrication during operation, and the tooth surface is prone to dry friction, scuffing, and premature failure. Summary of the Invention

[0005] The purpose of this section is to outline some aspects of embodiments of the present invention and to briefly describe some preferred embodiments. Simplifications or omissions may be made in this section, as well as in the abstract and title of this application, to avoid obscuring the purpose of these documents; however, such simplifications or omissions should not be construed as limiting the scope of the invention.

[0006] In view of the problems existing in the above and / or existing backlash compensation devices for dual-lead worm gear pairs, the present invention is proposed.

[0007] Therefore, the problem to be solved by this invention is how to address the shortcomings of traditional compensation, which can only adjust a single component, lacks bidirectional compensation, and has no adaptive lubrication in the meshing area.

[0008] To solve the above-mentioned technical problems, the present invention provides the following technical solution: a clearance compensation device for a dual-lead worm gear pair, comprising a reducer body including a housing and a worm and a worm wheel disposed within the housing, the worm and the worm wheel meshing; a worm clearance compensation component, installed on the housing and the worm, used for compensating, adjusting, and fixing the clearance between the worm and the worm wheel, the worm clearance compensation component comprising: a bearing one, whose inner ring is rotatably sleeved on one end surface of the worm, and whose outer ring is fixed to the inner wall of the housing; a bearing two, whose inner ring is fixedly sleeved on the other end surface of the worm; and an elastic element one, installed on the housing, with the outer ring of the bearing two sliding within it, used to provide continuous worm clearance compensation during the initial adjustment. Axial preload automatically compensates for tooth backlash caused by meshing wear. Preload bolt one is threaded onto the housing and mates with the outer ring of bearing one. It is used to position and fix bearing two after the initial adjustment of the elastic element one and the position of bearing two and the worm. Fixing bolt one, one end of which passes through elastic element one and is threaded onto the housing, is used to apply pressure to elastic element one, thereby locking the axial position of bearing two and the worm. Worm wheel clearance compensation component is installed on the housing and worm wheel to compensate, adjust, and fix the clearance between the worm wheel and the worm. Lubrication assembly is installed on the housing and mates with preload bolt one to provide lubrication and protection between the worm and the worm wheel.

[0009] As a preferred embodiment of the clearance compensation device for the dual-lead worm gear pair described in this invention, the worm gear clearance compensation component includes: a bearing three, whose inner ring is rotatably sleeved on one end surface of the worm gear, and whose outer ring is fixed to the inner wall of the housing; a bearing four, whose inner ring is fixedly sleeved on the other end surface of the worm gear; an elastic element two, installed on the housing, with the outer ring of bearing four sliding within it, used to provide continuous axial preload force for the worm gear during initial adjustment, automatically compensating for tooth backlash caused by meshing wear; a preload bolt two, threadedly connected to the housing and cooperating with the outer ring of bearing four, used to position and fix bearing four after the position of bearing four and worm gear is adjusted by elastic element two during initial adjustment; and a fixing bolt two, one end of which passes through elastic element two and is threadedly connected to the housing, used to apply pressure to elastic element two, thereby locking the axial position of bearing four and worm gear.

[0010] As a preferred embodiment of the clearance compensation device for the dual-lead worm gear pair described in this invention, the reducer body further includes a drive motor fixed on the housing, and one end of the worm gear is provided with a mating groove, which is matched with the output shaft of the drive motor.

[0011] As a preferred embodiment of the clearance compensation device for the dual-lead worm gear pair described in this invention, the elastic element one includes: a bearing seat one, disposed on the housing, with one end extending into the housing; a bearing two, disposed within the bearing seat one, with the outer ring of the bearing two sliding on the inner wall of the bearing seat one; an annular plate one, fixed to the surface of the outer ring of the bearing two; a spring one, disposed in the inner cavity of the bearing seat one, with its two ends respectively abutting between the inner wall of the bearing seat one and the surface of the annular plate one; a limiting groove one, arranged in a circumferential array on the inner wall of the bearing seat one; and a limiting block one, arranged in a circumferential array and fixed to the surface of the outer ring of the bearing two, and sliding within the limiting groove one.

[0012] As a preferred embodiment of the clearance compensation device for the dual-lead worm gear pair described in this invention, the elastic element two includes: a bearing seat two, disposed on the housing, with one end extending into the housing; a bearing four disposed within the bearing seat two, with the outer ring of the bearing four sliding on the inner wall of the bearing seat two; an annular plate two, fixed to the surface of the outer ring of the bearing four; a spring two, disposed in the inner cavity of the bearing seat two, with its two ends respectively abutting between the inner wall of the bearing seat two and the surface of the annular plate two; a limiting groove two, arranged in a circumferential array on the inner wall of the bearing seat two; and a limiting block two, arranged in a circumferential array and fixed to the surface of the outer ring of the bearing four, and sliding within the limiting groove two.

[0013] As a preferred embodiment of the clearance compensation device for the dual-lead worm gear pair described in this invention, the housing is provided with a threaded hole 1 that mates with a preload bolt 1 and a threaded hole 2 that mates with a preload bolt 2; the bearing 1 is provided with a mounting hole 1 that mates with a fixing bolt 1; the bearing 2 is provided with a mounting hole 2 that mates with a fixing bolt 2; and the housing is provided with a threaded groove 1 that mates with a fixing bolt 1 and a threaded groove 2 that mates with a fixing bolt 2.

[0014] As a preferred embodiment of the clearance compensation device for the dual-lead worm gear pair described in this invention, the lubrication assembly includes: an outlet pipe installed on the housing, with one end extending into the inner cavity of the housing; a groove is provided inside the housing; an opening and closing element installed in the groove, penetrating the outlet pipe and cooperating with it; a drive element disposed in the groove and installed on the opening and closing element and the housing, the drive element cooperating with a pre-tightening bolt and the opening and closing element respectively; a trigger element disposed on the housing, the drive motor, and the opening and closing element, and cooperating with the drive element and the opening and closing element; and a lubricating fluid tank fixed to the surface of the housing, with one end of the outlet pipe connected to it.

[0015] As a preferred embodiment of the clearance compensation device for the dual-lead worm gear pair described in this invention, the opening and closing component includes: a round rod that slides within the tank and penetrates the liquid outlet pipe; a first through hole that is formed on the surface of the round rod and cooperates with the liquid outlet pipe; a second through hole that is formed on the surface of the round rod and cooperates with the liquid outlet pipe; a square groove formed on the inner wall of the tank; and a block that is fixed to the surface of the round rod and slides within the square groove.

[0016] As a preferred embodiment of the clearance compensation device for the dual-lead worm gear pair described in this invention, the driving component includes: a trigger block, which slides within the groove and is fixed to one end of a round rod; a driving block, which slides on the housing, with one end engaging with a pre-tightening bolt and a nut, and the other end engaging with the trigger block; a first sliding groove, which is formed in the inner wall of the groove; a first slider, which is fixed to the surface of the trigger block and slides within the first sliding groove; a third spring, which is disposed within the first sliding groove, with its two ends respectively fixed between the inner wall of the first sliding groove and the surface of the first slider; a second sliding groove, which is formed in the inner wall of the groove; a second slider, which is fixed to the surface of the driving block and slides within the second sliding groove; and a fourth spring, which is disposed within the second sliding groove, with its two ends respectively fixed between the inner wall of the second sliding groove and the surface of the second slider.

[0017] As a preferred embodiment of the backlash compensation device for the dual-lead worm gear pair described in this invention, the trigger element includes: a cavity, opened within a housing; a piston, sliding within the cavity, with the space formed by the cavity and one side of the piston filled with molten metal; a heat-conducting ring, mounted on the surface of the housing and sleeved on the surface of the drive motor; a heat-conducting rod, fixed to the surface of the heat-conducting ring, with one end penetrating the housing and extending into the cavity; a toothed plate, sliding on the housing, with one end fixed to the surface of the piston; a rotating column, rotating on the inner wall of the groove; a ratchet, its inner ring fixedly sleeved on the surface of the rotating column; a gear, fixedly sleeved on the outer ring surface of the ratchet and meshing with the toothed plate; a circular ring, fixed to the outer ring surface of the ratchet; a cam, fixed to the surface of the circular ring; and a roller, rotating at one end of the circular rod and cooperating with the cam.

[0018] The beneficial effects of this invention are as follows: The worm gear + worm wheel bidirectional elastic compensation structure automatically eliminates backlash generated during long-term operation, maintaining zero backlash in the machine tool transmission. The elastic preload and bolt double locking provide sufficient rigidity after compensation, resisting cutting vibrations and preventing loosening. This ensures long-term high-precision and stable operation of the machine tool, eliminating the need for frequent shutdowns for inspection and adjustment. The adjustment process includes automatic oil injection, providing forced lubrication to the meshing surfaces during compensation, reducing tooth wear, heat generation, abnormal noise, and the risk of galling. This significantly extends the service life of the worm gear pair. Motor temperature rise triggers automatic intermittent lubrication, achieving on-demand oil supply without waste. Attached Figure Description

[0019] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 This is a three-dimensional structural diagram of a clearance compensation device for a double-lead worm gear pair.

[0021] Figure 2This is a three-dimensional structural diagram of a clearance compensation device for a double-lead worm gear pair from another perspective.

[0022] Figure 3 This is a partial sectional perspective view of the clearance compensation device for a double-lead worm gear pair.

[0023] Figure 4 This is a partial sectional perspective view of the housing of the clearance compensation device for a double-lead worm gear pair.

[0024] Figure 5 This is a partial 3D view of the elastic component of the clearance compensation device for a double-lead worm gear pair.

[0025] Figure 6 This is a partial 3D view of the elastic component of the clearance compensation device for a double-lead worm gear pair.

[0026] Figure 7 This is a perspective sectional view of the preload bolts and housing of the clearance compensation device for a double-lead worm gear pair.

[0027] Figure 8 A backlash compensation device for a double-lead worm gear pair Figure 3 Enlarged view of point A in the middle.

[0028] Figure 9 A backlash compensation device for a double-lead worm gear pair Figure 3 Enlarged view of section B in the middle.

[0029] Figure 10 A backlash compensation device for a double-lead worm gear pair Figure 3 Enlarged view of point C.

[0030] Figure 11 This is a perspective view of the drive block and trigger block of the backlash compensation device for a double-lead worm gear pair.

[0031] Figure 12 This is a perspective view of the drive block and trigger block of the backlash compensation device for a double-lead worm gear pair.

[0032] Figure 13 This is a partial sectional perspective view of the ratchet in the backlash compensation device for a double-lead worm gear pair.

[0033] In the diagram: 1. Reducer body; 11. Housing; 12. Worm; 13. Worm wheel; 14. Drive motor; 2. Worm clearance compensation component; 21. Bearing 1; 22. Bearing 2; 23. Elastic component 1; 24. Preload bolt 1; 25. Fixing bolt 1; 3. Worm wheel clearance compensation component; 31. Bearing 3; 32. Bearing 4; 33. Elastic component 2; 34. Preload bolt 2; 35. Fixing bolt 2; 4. Lubrication assembly; 41. Discharge pipe; 42. Opening and closing component; 43. Drive component; 44. Trigger component; 45. Lubricating fluid tank; 231. Shaft seat 1; 232. Ring plate 1; 233. Spring 1; 234. Limiting groove 1; 235. Limiting block 1; 331. Shaft seat 2; 332. Ring plate 2; 333. Spring 2; 334. Limiting... 1. Groove 2; 3. Limiting Block 2; 1. Groove Body; 4. Round Rod; 4. Through Hole 1; 4. Through Hole 2; 4. Square Groove; 4. Square Block; 4. Trigger Block; 4. Drive Block; 4. Slide Groove 1; 4. Slider 1; 4. Spring 3; 4. Slide Groove 2; 4. Slider 2; 4. Spring 4; 4. Trigger Hole; 4. Square Hole; 4. Cavity; 4. Piston; 4. Heat Conducting Ring; 4. Heat Conducting Rod; 4. Gear Plate; 4. Rotary Column; 4. Ratchet; 4. Gear; 4. Ring; 4. Cam; 4. Roller; 4. L-shaped Rod; 4. Spring 5; 4. Heat Conducting Sheet; 4. Handle. Detailed Implementation

[0034] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

[0035] Many specific details are set forth in the following description in order to provide a full understanding of the invention. However, the invention may also be practiced in other ways different from those described herein, and those skilled in the art can make similar extensions without departing from the spirit of the invention. Therefore, the invention is not limited to the specific embodiments disclosed below.

[0036] Secondly, the term "one embodiment" or "embodiment" as used herein refers to a specific feature, structure, or characteristic that may be included in at least one implementation of the present invention. The phrase "in one embodiment" appearing in different places in this specification does not necessarily refer to the same embodiment, nor is it a single or selective embodiment that is mutually exclusive with other embodiments.

[0037] Example 1, referring to Figures 1-4 This is the first embodiment of the present invention. This embodiment provides a clearance compensation device for a dual-lead worm gear pair. The dual-lead worm gear pair clearance compensation device includes a reducer body 1, a worm clearance compensation component 2, a worm gear clearance compensation component 3, and a lubrication assembly 4.

[0038] Specifically, the reducer body 1 includes a housing 11 and a worm 12 and a worm wheel 13 disposed within the housing 11. The worm 12 meshes with the worm wheel 13. The worm 12 adopts a double-lead structure and meshes with the worm wheel 13 to form a high-precision transmission. This is existing technology, which is clearly known to those skilled in the art and will not be described in detail here. It is used in machine tool transmission systems.

[0039] Specifically, the worm clearance compensation component 2 is installed on the housing 11 and the worm 12, and is used to compensate, adjust and fix the clearance between the worm 12 and the worm wheel 13. The worm clearance compensation component 2 includes: a bearing 21, whose inner ring is rotatably sleeved on one end surface of the worm 12 and whose outer ring is fixed to the inner wall of the housing 11; a bearing 22, whose inner ring is fixedly sleeved on the other end surface of the worm 12; an elastic element 23, which is installed on the housing 11 and in which the outer ring of the bearing 22 slides, and is used to provide a continuous axial preload force on the worm 12 during the initial adjustment to automatically compensate for the tooth backlash caused by meshing wear; and a preload bolt 24, which is threadedly connected to the housing 11 and cooperates with the outer ring of the bearing 21, and is used to position and fix the bearing 22 after the elastic element 23 adjusts the position of the bearing 22 and the worm 12 during the initial adjustment.

[0040] A fixing bolt 25, one end of which passes through the elastic element 23 and is threaded to the housing 11, is used to apply pressure to the elastic element 23, thereby locking the axial position of the bearing 22 and the worm 12. The worm gear clearance compensation component 3 is installed on the housing 11 and the worm gear 13, and is used to compensate, adjust and fix the clearance between the worm gear 13 and the worm 12. There are three fixing bolts 25, which are arranged in a circumferential array. The worm gear clearance compensation component 3 and the worm 12 compensate and cooperate to achieve double-sided collaborative compensation, which is used in the machine tool transmission system.

[0041] Due to prolonged operation of the machine tool transmission system, the tooth surfaces of the double-lead worm 12 and worm wheel 13 experience wear and increased meshing clearance. By loosening the preload bolt 24 to release the fixation of the bearing 22, an axial preload force is continuously applied to the elastic element 23, causing the worm 12 and bearing 22 to float slightly axially, automatically eliminating the tooth backlash. Then, the preload bolt 24 is tightened to fix the bearing 22, and the fixing bolt 25 is rotated to push the elastic element 23 forward, thereby applying pressure to the axial position of the bearing 22 to lock it in place, preventing damage caused by forcibly pushing the worm 12 and worm wheel 13 into rigid contact.

[0042] Specifically, the lubrication component 4 is installed on the housing 11 and cooperates with the preload bolt 24. It is used for lubrication protection between the worm 12 and the worm wheel 13. When the preload bolt 24 is adjusted, the lubrication component 4 is triggered to automatically supply oil to the meshing surface, reduce meshing friction and prevent wear from aggravating. At the same time, the heat generated when the drive motor 14 of the reducer body 1 is running at high speed can trigger the lubrication component 4 to automatically supply oil to the meshing area of ​​the worm 12 and the worm wheel 13 for lubrication.

[0043] Example 2, refer to Figures 2-6 This is the second embodiment of the present invention, which is based on the previous embodiment.

[0044] Specifically, the worm gear clearance compensation component 3 includes: a bearing 31, whose inner ring is rotatably sleeved on one end surface of the worm gear 13, and whose outer ring is fixed to the inner wall of the housing 11; a bearing 42, whose inner ring is fixedly sleeved on the other end surface of the worm gear 13; an elastic element 23, which is installed on the housing 11, and the outer ring of the bearing 42 slides within it, used to provide continuous axial preload force for the worm gear 13 during initial adjustment, automatically compensating for the tooth backlash caused by meshing wear; a preload bolt 24, which is threadedly connected to the housing 11 and cooperates with the outer ring of the bearing 42, used to position and fix the bearing 42 after the elastic element 23 adjusts the position of the bearing 42 and the worm 12 during initial adjustment; and a fixing bolt 25, one end of which passes through the elastic element 23 and is threadedly connected to the housing 11, used to apply pressure to the elastic element 233 to tighten it, thereby locking the axial position of the bearing 42 and the worm gear 13.

[0045] One end of the worm gear 13 is supported by bearing 31, and the other end is axially supported by bearing 32 and elastic element 33. Due to the long-term operation of the machine tool transmission system, the tooth surfaces of the double-lead worm 12 and worm gear 13 wear and the meshing clearance increases. The bearing 32 can be released by loosening the preload bolt 34. The elastic element 33 continuously pushes the bearing 32 and worm gear 13, causing the worm gear 13 to move slightly axially to help compensate for the meshing clearance. Then, the preload bolt 34 is tightened to fix the bearing 32. The fixing bolt 35 is then rotated to push the elastic element 33 forward, thereby applying pressure to the axial position of the bearing 32 and locking it in place. This prevents the worm gear 13 from being forcibly and rigidly contacted with the worm 12, which could cause damage.

[0046] Specifically, the reducer body 1 also includes a drive motor 14 fixed on the housing 11. One end of the worm gear 12 is provided with a mating groove, and the mating groove is matched with the output shaft of the drive motor 14. The output shaft of the drive motor 14 is inserted into the mating groove, so that the output shaft of the drive motor 14 can drive the worm gear 12 to rotate when it is running. Moreover, the clearance compensation does not affect the movement when the worm gear 12 is adjusted. The structure of the mating groove on the worm gear 12 and the output shaft of the drive motor 14 can transmit torque, while allowing the worm gear 12 to move freely axially. The compensation action does not affect the power transmission.

[0047] Specifically, the elastic element 23 includes: a bearing seat 231, which is disposed on the housing 11 and extends into the housing 11 at one end. The bearing seat 231 slides on the housing 11 and is a floating bearing seat for the worm gear 12. A bearing 22 is disposed inside the bearing seat 231, and the outer ring of the bearing 22 slides on the inner wall of the bearing seat 231. The bearing 22 can slide axially along the inner wall of the bearing seat 231. An annular plate 232 is fixed to the outer ring surface of the bearing 22. A spring 233 is disposed in the inner cavity of the bearing seat 231, and its two ends abut against the inner wall of the bearing seat 231 and the annular plate 232, respectively. Between the surfaces, ring plate 232 is used to transmit spring force, spring 233 provides continuous axial preload, limiting groove 234 is formed in a circumferential array on the inner wall of bearing seat 231, and limiting block 235 is formed in a circumferential array and fixed to the outer ring surface of bearing 22, and slides in the limiting groove 234. The limiting groove 234 and limiting block 235 restrict the outer ring of bearing 22 to move axially and not rotate. The bearing seat 231 is provided with a slot hole 24 that cooperates with the preload bolt 24 so that the movement of bearing seat 231 is not hindered by the preload bolt 24.

[0048] Due to the long-term operation of the machine tool transmission system, when the tooth surface wears and gaps appear, the preload bolt 24 is rotated to disengage it from the outer ring surface of the bearing 22, releasing the fixation of the bearing 22. Under the elastic push of the spring 233, the bearing 22 and the worm 12 are preloaded in the meshing direction, pushing the worm 12 to feed axially and compensate for the gap in real time. The limit block 235 slides in the limit groove 234 to ensure that the axial movement of the bearing 22 is smooth, without deflection or shaking. Then, the preload bolt 24 is rotated so that one end is in close contact with the outer ring surface of the bearing 22 to fix the bearing 22. Then, the fixing bolt 25 is rotated to push the shaft seat 231 to move, so that the shaft seat 231 contacts and abuts against the ring plate 232, completing the gap compensation and locking. During this process, the spring 233 is compressed.

[0049] Specifically, the elastic element 2 33 includes: a bearing seat 2 331, disposed on the housing 11, with one end extending into the housing 11, the bearing seat 2 331 sliding on the housing 11, serving as a floating bearing seat for the worm gear 13; a bearing 4 32 disposed within the bearing seat 2 331, with its outer ring sliding against the inner wall of the bearing seat 2 331, and the bearing 4 32 axially sliding along the inner wall of the bearing seat 2 331; a ring plate 2 332 fixed to the outer ring surface of the bearing 4 32; and a spring 2 333 disposed within the inner cavity of the bearing seat 2 331, with its two ends respectively abutting against the inner wall of the bearing seat 2 331 and... Between the surfaces of the ring plate 2 332, the spring 2 333 provides axial preload to the worm gear 13. The limiting groove 2 334 is arranged in a circumferential array on the inner wall of the bearing seat 2 331. The limiting block 2 335 is arranged in a circumferential array and fixed to the outer ring surface of the bearing 4 32, and slides in the limiting groove 2 334. The limiting groove 2 334 and the limiting block 2 335 restrict the outer ring of the bearing 4 32 to move axially and not rotate. The bearing seat 2 331 is provided with a slot 2 that cooperates with the preload bolt 2 34, so that the movement of the bearing seat 2 331 is not hindered by the preload bolt 2 34.

[0050] Due to the long-term operation of the machine tool transmission system, when the tooth surface wears and gaps appear, the preload bolt 234 can be rotated to disengage it from the outer ring surface of bearing 432, releasing the fixation of bearing 432. Under the elastic push of spring 233, bearing 432 and worm gear 13 are preloaded in the meshing direction, pushing worm gear 13 to feed axially and compensate for the gap in real time. Limit block 235 slides in limit groove 234 to ensure that the axial movement of bearing 432 is smooth, without deflection or shaking. Then, the preload bolt 234 is rotated to make one end of the outer ring surface of bearing 432 in close contact, fixing bearing 432. Then, the fixing bolt 235 is rotated to push the shaft seat 231 to move, so that the shaft seat 231 and bearing 432 come into contact and abut together, completing the gap compensation and locking. During this process, spring 233 is compressed.

[0051] Specifically, the housing 11 has a threaded hole 1 that mates with the preload bolt 24 and a threaded hole 2 that mates with the preload bolt 34; the bearing seat 231 has a mounting hole 1 that mates with the fixing bolt 25; the bearing seat 331 has a mounting hole 2 that mates with the fixing bolt 35; and the housing 11 has a threaded groove 1 that mates with the fixing bolt 25 and a threaded groove 2 that mates with the fixing bolt 35.

[0052] The bearing seat 231 has three mounting holes 1, and the bearing seat 331 has three mounting holes 2. The preload bolts 24 and 34 rotate in the threaded holes 1 and 2 to achieve high-precision axial feed. The fixing bolts 25 and 35 rotate in the threaded grooves 1 and 2 to push the bearing seat 231 and 331 to feed, and then abut against the bearing 22 and bearing 32 for limiting and locking.

[0053] Example 3, referring to Figures 2 to 13 This is the third embodiment of the present invention, which is based on the first two embodiments.

[0054] Specifically, the lubrication assembly 4 includes: a liquid outlet pipe 41, installed on the housing 11, with one end extending into the inner cavity of the housing 11; a groove 111 is provided inside the housing 11; an opening / closing member 42, installed in the groove 111, passing through the liquid outlet pipe 41 and cooperating with it; and a driving member 43, disposed in the groove 111, and installed on the opening / closing member 42 and the housing 11. The driving member 43 cooperates with the pre-tightening bolt 24 and the opening / closing member 42 respectively. When the bolt 24 is loosened or when the clearance compensation of the worm gear 12 is adjusted, the oil circuit is briefly opened when the preload bolt 24 is loosened and tightened. The trigger element 44 is set on the housing 11, the drive motor 14 and the opening and closing element 42, and cooperates with the drive element 43 and the opening and closing element 42. The opening and closing element 42 controls the opening and closing of the oil circuit. The trigger element 44 is heated and moves to trigger intermittent lubrication. The lubricating oil tank 45 is fixed on the surface of the housing 11 and one end of the outlet pipe 41 is connected to it. The lubricating oil tank 45 is used to store lubricating oil.

[0055] During the installation of the pre-tightening bolt 24, the pre-tightening bolt 24 presses down on the drive stop 43, pushing the opening and closing part 42 to briefly open the oil circuit. As the opening and closing part 42 is pressed down, it closes again. The lubricant flows to the meshing area through the outlet pipe 41, achieving lubrication upon installation without waste. At the same time, during the adjustment of the worm gear 12 clearance compensation, the pre-tightening bolt 24 and the bearing 22 need to be loosened and then tightened. During this process, the drive stop 43 resets part of its position and is then pressed down by the pre-tightening bolt 24, causing the opening and closing part 42 to open the oil circuit and then close, achieving lubrication during adjustment.

[0056] Specifically, the opening and closing component 42 includes: a round rod 421 that slides within the tank 111 and passes through the outlet pipe 41, with a seal between the round rod 421 and the outlet pipe 41; a first through hole 422 that is formed on the surface of the round rod 421 and cooperates with the outlet pipe 41; a second through hole 423 that is formed on the surface of the round rod 421 and cooperates with the outlet pipe 41; a square groove 424 that is formed on the inner wall of the tank 111; and a square block 425 that is fixed to the surface of the round rod 421 and slides within the square groove 424. The first through hole 422 and the second through hole 423 cooperate with the outlet pipe 41 to control the opening and closing. The square groove 424 and the square block 425 limit the movement of the round rod 421, ensuring that the round rod 421 can only slide and cannot rotate, thus ensuring accurate alignment and no deviation of the through hole when the passage is open.

[0057] During the process of the drive stop 43 being acted upon by the pre-tightening bolt 24, when the opening and closing part 42 opens the outlet pipe 41, the round rod 421 moves to align the through hole 422 with the outlet pipe 41, opening the oil passage and allowing the lubricant to flow. After the pre-tightening bolt 24 is tightened and abuts against the bearing 22, the round rod 421 moves to the rod wall to block the outlet pipe 41, closing the oil passage.

[0058] Specifically, the driving component 43 includes: a trigger block 431, which slides within the groove 111 and is fixed to one end of the round rod 421; a driving block 432, which slides on the housing 11, with one end engaging with the pre-tightening bolt 24 nut and the other end engaging with the trigger block 431; the driving block 432 is convex in shape, and the larger end of the driving block 432 is provided with an inclined surface; a slide groove 433, which is formed on the inner wall of the groove 111; a slider 434, which is fixed to the surface of the trigger block 431 and slides within the slide groove 433; and a spring 435, which is disposed within the slide groove 433, with its two ends respectively fixed to the inner wall of the slide groove 433 and the slider 434. Between surfaces 434, a second slide groove 436 is formed on the inner wall of the groove 111. A second slider 437 is fixed to the surface of the drive block 432 and slides within the second slide groove 436. A fourth spring 438 is disposed within the second slide groove 436, with its two ends fixed between the inner wall of the second slide groove 436 and the surface of the second slider 437, respectively. The first slide groove 433 and the first slider 434 guide and limit the trigger block 431. The third spring 435 provides a reset force for the movement of the trigger block 431. The second slide groove 436 and the second slider 437 guide and limit the drive block 432. The fourth spring 438 provides a reset force for the movement of the drive block 432.

[0059] Tighten the preload bolt 24, press the nut down on the drive block 432, and the inclined surface on the drive block 432 presses against the trigger block 431, causing the trigger block 431 to move. This, in turn, moves the round rod 421, causing the through hole 422 to gradually align with and offset the outlet pipe 41, thus achieving a brief opening and closing of the oil circuit. This lubricates the worm gear 12 and the worm wheel 13. After tightening, the inclined surface on the drive block 432 has detached from the surface of the trigger block 431, and the rod wall of the round rod 421 has blocked the oil circuit of the outlet pipe 41. When adjusting the clearance of the worm gear 12 in the future, the preload bolt 24 needs to be loosened and tightened again. Lubrication can be performed during this process.

[0060] Specifically, the trigger 44 includes: a cavity 441, which is opened inside the housing 11; a piston 442, which slides inside the cavity 441; and the space formed by the cavity 441 and one side of the piston 442 is filled with molten metal. The piston 442 and the cavity 441 are sealed. The molten metal is mercury or a mercury-like heat-sensitive substance, such as gallium and its alloys. It expands when heated and contracts when cooled, which is existing technology and will not be described in detail here. A heat-conducting ring 443 is installed on the surface of the housing 11 and sleeved on the surface of the drive motor 14. A heat-conducting rod 444 is fixed to the surface of the heat-conducting ring 443, and one end of the rod penetrates the housing 11 and extends into the cavity 441. The heat-conducting rod 444 is fixedly connected to the housing 11. The heat-conducting ring 443 is sleeved on the surface of the drive motor 14 to absorb heat. The heat-conducting rod 444 transfers heat to the cavity 441, and the molten metal expands to push the piston 442.

[0061] A toothed plate 445 slides on the housing 11 and is fixed at one end to the surface of the piston 442. A rotating column 446 rotates on the inner wall of the groove 111 and is rotatably connected to the inner wall of the groove 111 via a damping bearing. A ratchet 447 has its inner ring fixedly fitted onto the surface of the rotating column 446. The ratchet 447 provides unidirectional intermittent drive and prevents reverse rotation. A gear 448 is fixedly fitted onto the outer ring surface of the ratchet 447 and meshes with the toothed plate 445. A ring 449 is fixedly fitted onto the outer ring surface of the ratchet 447. Cam 4410 is fixed to the surface of ring 449. Roller 4411 rotates at one end of round rod 421 and cooperates with cam 4410. Cam 4410 pushes roller 4411, causing round rod 421 to move and gradually align through hole 423 with liquid outlet pipe 41, opening the oil circuit once. L-shaped rod 4412 is sealed with housing 11. L-shaped rod 4412 and spring 4413 provide the drive motor 14 and the piston 442 and toothed plate 445 to reset after the molten metal is cooled.

[0062] The drive motor 14 generates heat during operation → the heat-conducting ring 443 absorbs heat → the molten metal expands thermally → pushing the piston 442 and the toothed plate 445 to move. The toothed plate 445 drives the gear 448, ratchet 447 and cam 4410 to rotate → the cam 4410 pushes the roller 4411 → the round rod 421 moves to open the oil circuit once and gradually closes it. If the drive motor 14 generates heat during operation and does not trigger the oil circuit to open once, the toothed plate 445 will reset under the action of the ratchet 447, but the rotation angle of the cam 4410 will not change, preparing for the next operation of the drive motor 14 to quickly trigger the oil circuit to open. The drive motor 14 cools down → the spring 4413 pulls the piston 442 to reset → the inner ring of the ratchet 447 remains stationary, realizing temperature sensing and automatic intermittent lubrication, without waste or over-lubrication.

[0063] Specifically, the L-shaped rod 4412 slides on the housing 11, and one end is fixed to the surface of the piston 442. The spring 4413 is sleeved on the surface of the L-shaped rod 4412, and both ends are fixed to the surface of the housing 11 and the surface of the L-shaped rod 4412, respectively. The heat-conducting plate 4414 is fixed to one end of the heat-conducting rod 444 located in the cavity 441. The handle 4415 is fixed to one end of the L-shaped rod 4412. The heat-conducting plate 4414 plays a better role in dispersing the heat transferred by the heat-conducting rod 444 into the molten metal. The operating handle 4415 can manually push the L-shaped rod 4412, the piston 442 and the toothed plate 445 to move, so as to manually open and close the oil circuit for lubrication.

[0064] The trigger block 431 has a trigger hole 4311 and a square hole 4312, which are interconnected. The trigger hole 4311 mates with one end of the drive block 432, and the square hole 4312 mates with the other end of the drive block 432. The trigger hole 4311 has a bevel, which, in conjunction with the bevel on the drive block 432, allows the trigger block 431 to move more smoothly when the drive block 432 presses against it. 1. The larger end of the drive block 432 is engaged with the smaller end of the drive block 432. When the pre-tightening bolt 24 is tightened and the nut applies pressure to the drive block 432, the drive block 432 stops pressing the trigger block 431 to move. At this time, the smaller end of the drive block 432 corresponds to the square hole 4312. When the cam 4410 acts on the roller 4411, the round rod 421 and the trigger block 431 can move normally to realize the opening and closing of the oil circuit.

[0065] During use, the clearance elastic preload compensation is provided: after long-term wear of the worm 12 / worm wheel 13 and the occurrence of side clearance, the preload bolt is loosened, and the spring automatically pushes the bearing and the worm 12 / worm wheel 13 to make a slight axial floating, and the double lead tooth surface automatically eliminates the clearance; after adjustment, the preload bolt and the fixing bolt are tightened to achieve rigid locking, and the compensation is accurate, without loosening or jerking.

[0066] The worm 12 and worm wheel 13 work together to achieve axial preload compensation through elastic element 23 on the worm 12 side; and axial auxiliary compensation through elastic element 33 on the worm wheel 13 side. The cooperation between the two sides can eliminate the gap of the full meshing surface, which is more accurate and more rigid than the traditional single-sided compensation.

[0067] Adjustment linkage lubrication: When loosening / tightening the preload bolt 24 for clearance compensation, the drive stop 43 will be automatically triggered, pushing the opening and closing part 42 to open the oil circuit instantly, supplying oil to the meshing surface once and then automatically closing, realizing lubrication while adjusting the clearance, and avoiding tooth surface damage.

[0068] Temperature-triggered automatic intermittent lubrication: The drive motor 14 generates heat during operation, and the heat causes the molten metal in the cavity 441 to expand through the heat conduction ring 443, pushing the piston 442 and the gear plate 445 to move, causing the gear 448, ratchet 447, and cam 4410 to rotate, pushing the roller 4411 and the round rod 421 to open the oil circuit for oil supply and close the oil circuit; after the machine stops and cools down, it automatically resets, realizing temperature-triggered intermittent lubrication, no lubrication, no waste, and long-term stability.

[0069] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all such modifications or substitutions should be covered within the scope of the claims of the present invention.

Claims

1. A gap compensation device for a double lead worm gear pair, characterized by: include, The reducer body (1) includes a housing (11) and a worm (12) and a worm wheel (13) disposed in the housing (11), wherein the worm (12) and the worm wheel (13) mesh with each other; A worm gear clearance compensation component (2) is installed on the housing (11) and the worm (12) to compensate for and adjust the clearance between the worm (12) and the worm wheel (13). The worm gear clearance compensation component (2) includes: a bearing (21) whose inner ring is rotatably sleeved on one end surface of the worm (12) and whose outer ring is fixed to the inner wall of the housing (11); a bearing (22) whose inner ring is fixedly sleeved on the other end surface of the worm (12); and an elastic element (23) installed on the housing (11), with the outer ring of the bearing (22) sliding inside it, to provide continuous clearance between the worm (12) and the worm wheel (13) during the initial adjustment. 2) Axial preload, automatically compensating for tooth backlash caused by meshing wear. Preload bolt 1 (24) is threaded onto the housing (11) and engages with the outer ring of bearing 1 (21). It is used to adjust the position of bearing 2 (22) and worm (12) after the elastic element 1 (23) adjusts the position of bearing 2 (22) and worm (12) in the initial stage. Fixing bolt 1 (25) has one end that passes through elastic element 1 (23) and is threaded onto the housing (11). It is used to apply pressure to elastic element 1 (23) to lock the axial position of bearing 2 (22) and worm (12). Worm gear clearance compensation component (3) is installed on the housing (11) and worm gear (13) to compensate, adjust and fix the clearance between worm gear (13) and worm (12); The lubrication assembly (4) is mounted on the housing (11) and cooperates with the preload bolt (24) for lubrication protection between the worm (12) and the worm wheel (13).

2. The dual lead worm gear wheel and pinion pair gap compensation device of claim 1, wherein: The worm gear clearance compensation component (3) includes: bearing three (31), whose inner ring is rotatably sleeved on one end surface of the worm gear (13), and whose outer ring is fixed to the inner wall of the housing (11); bearing four (32), whose inner ring is fixedly sleeved on the other end surface of the worm gear (13); elastic component two (33), which is installed on the housing (11), and the outer ring of bearing four (32) slides inside it, used to provide continuous axial preload of the worm gear (13) in the initial adjustment, automatically compensating for the tooth backlash caused by meshing wear; and preload screw. Bolt 2 (34) is threaded onto the housing (11) and engages with the outer ring of bearing 4 (32). It is used to adjust the position of bearing 4 (32) and worm gear (12) after the elastic element 2 (33) adjusts the position of bearing 4 (32) and worm gear (12) in the initial stage. Bolt 2 (35) is used to fix bearing 4 (32) by one end passing through elastic element 2 (33) and threaded onto the housing (11). It is used to apply pressure to elastic element 2 (33) and lock the axial position of bearing 4 (32) and worm gear (13).

3. The dual lead worm gear wheel and pinion pair gap compensation device of claim 2, wherein: The reducer body (1) also includes a drive motor (14) fixed on the housing (11), and a docking groove is provided at one end of the worm (12), and the docking groove is matched with the output shaft of the drive motor (14).

4. A gap compensation device for a double lead worm gear pair according to any one of claims 1, 2 or 3, characterized in that: The elastic element one (23) includes: a bearing seat one (231), which is disposed on the housing (11) and one end of which extends into the housing (11); a bearing two (22), which is disposed in the bearing seat one (231) and the outer ring of the bearing two (22) slides on the inner wall of the bearing seat one (231); an annular plate one (232), which is fixed on the surface of the outer ring of the bearing two (22); a spring one (233), which is disposed in the inner cavity of the bearing seat one (231) and its two ends respectively abut against the inner wall of the bearing seat one (231) and the surface of the annular plate one (232); a limiting groove one (234), which is arranged in a circumferential array on the inner wall of the bearing seat one (231); and a limiting block one (235), which is arranged in a circumferential array and fixed on the surface of the outer ring of the bearing two (22) and slides in the limiting groove one (234).

5. The backlash compensation device for a dual-lead worm gear pair as described in claim 2, characterized in that: The elastic element two (33) includes: a bearing seat two (331), which is disposed on the housing (11) and one end of which extends into the housing (11); a bearing four (32), which is disposed in the bearing seat two (331) and the outer ring of the bearing four (32) slides on the inner wall of the bearing seat two (331); an annular plate two (332), which is fixed on the surface of the outer ring of the bearing four (32); a spring two (333), which is disposed in the inner cavity of the bearing seat two (331) and its two ends respectively abut against the inner wall of the bearing seat two (331) and the surface of the annular plate two (332); a limiting groove two (334), which is arranged in a circumferential array on the inner wall of the bearing seat two (331); and a limiting block two (335), which is arranged in a circumferential array and fixed on the surface of the outer ring of the bearing four (32) and slides in the limiting groove two (334).

6. The backlash compensation device for a dual-lead worm gear pair as described in claim 5, characterized in that: The housing (11) has a threaded hole 1 that mates with the pre-tightening bolt 1 (24) and a threaded hole 2 that mates with the pre-tightening bolt 2 (34). The bearing seat 1 (231) has a mounting hole 1 that mates with the fixing bolt 1 (25). The bearing seat 2 (331) has a mounting hole 2 that mates with the fixing bolt 2 (35). The housing (11) has a threaded groove 1 that mates with the fixing bolt 1 (25) and a threaded groove 2 that mates with the fixing bolt 2 (35).

7. The backlash compensation device for a double-lead worm gear pair as described in any one of claims 1, 2, 3, 5, and 6, characterized in that: The lubrication assembly (4) includes: an outlet pipe (41) installed on the housing (11) with one end extending into the inner cavity of the housing (11), a groove (111) provided in the housing (11), an opening and closing element (42) installed in the groove (111), passing through the outlet pipe (41) and cooperating with the outlet pipe (41), a drive element (43) set in the groove (111) and installed on the opening and closing element (42) and the housing (11), the drive element (43) cooperating with the pre-tightening bolt (24) and the opening and closing element (42) respectively, a trigger element (44) set on the housing (11), the drive motor (14) and the opening and closing element (42), and cooperating with the drive element (43) and the opening and closing element (42), and a lubricating fluid tank (45) fixed on the surface of the housing (11), with one end of the outlet pipe (41) connected to it.

8. The backlash compensation device for a dual-lead worm gear pair as described in claim 7, characterized in that: The opening and closing component (42) includes: a round rod (421) that slides inside the tank (111) and passes through the liquid outlet pipe (41); a first through hole (422) that is opened on the surface of the round rod (421) and cooperates with the liquid outlet pipe (41); a second through hole (423) that is opened on the surface of the round rod (421) and cooperates with the liquid outlet pipe (41); a square groove (424) that is opened on the inner wall of the tank (111); and a square block (425) that is fixed on the surface of the round rod (421) and slides inside the square groove (424).

9. The backlash compensation device for a dual-lead worm gear pair as described in claim 8, characterized in that: The driving component (43) includes: a trigger block (431), which slides within the groove (111) and is fixed to one end of a round rod (421); a driving block (432), which slides on the housing (11), with one end engaging with the nut of a pre-tightening bolt (24) and the other end engaging with the trigger block (431); a sliding groove (433), which is formed on the inner wall of the groove (111); and a slider (434), which is fixed to the surface of the trigger block (431) and slides within the sliding groove (433). Spring 3 (435) is located in slide groove 1 (433), with its two ends fixed between the inner wall of slide groove 1 (433) and the surface of slider 1 (434). Slide groove 2 (436) is located on the inner wall of groove body (111). Slider 2 (437) is fixed on the surface of drive block (432) and slides in slide groove 2 (436). Spring 4 (438) is located in slide groove 2 (436), with its two ends fixed between the inner wall of slide groove 2 (436) and the surface of slider 2 (437).

10. The backlash compensation device for a dual-lead worm gear pair as described in claim 9, characterized in that: The trigger (44) includes: a cavity (441) formed inside the housing (11); a piston (442) sliding inside the cavity (441), with the space formed by the cavity (441) and one side of the piston (442) filled with molten metal; a heat-conducting ring (443) mounted on the surface of the housing (11) and sleeved on the surface of the drive motor (14); a heat-conducting rod (444) fixed to the surface of the heat-conducting ring (443), with one end penetrating the housing (11) and extending into the cavity (441); and a toothed plate (445) sliding on the housing (11). One end is fixed to the surface of the piston (442), the rotating column (446) rotates on the inner wall of the groove (111), the ratchet (447) has its inner ring fixedly sleeved on the surface of the rotating column (446), the gear (448) is fixedly sleeved on the outer ring surface of the ratchet (447) and meshes with the toothed plate (445), the ring (449) is fixed on the outer ring surface of the ratchet (447), the cam (4410) is fixed on the surface of the ring (449), and the roller (4411) rotates on one end of the round rod (421) and cooperates with the cam (4410).

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