CN219994336U - Cycloidal pin gear speed reducer capable of bearing large axial thrust - Google Patents
Cycloidal pin gear speed reducer capable of bearing large axial thrust Download PDFInfo
- Publication number
- CN219994336U CN219994336U CN202321683067.0U CN202321683067U CN219994336U CN 219994336 U CN219994336 U CN 219994336U CN 202321683067 U CN202321683067 U CN 202321683067U CN 219994336 U CN219994336 U CN 219994336U
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- bearing
- speed reducer
- hole
- pressing plate
- gear speed
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- 239000003638 chemical reducing agent Substances 0.000 title claims abstract description 38
- 238000003825 pressing Methods 0.000 claims abstract description 34
- 238000000034 method Methods 0.000 claims 1
- 230000005540 biological transmission Effects 0.000 abstract description 4
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
Abstract
The utility model relates to the technical field of speed reducers, and discloses a cycloidal pin gear speed reducer capable of bearing larger axial thrust. The gap of the output end of the working equipment to be decelerated passes through the pressing plate and is matched in the inner hole of the shaft head of the output shaft, and a double flat key is arranged between the output end of the working equipment to be decelerated and the inner hole of the shaft head. The parts of axial force generated by rotation of the output shaft of the utility model are propped against the plane of the pressing plate, and the axial force transmission directions are as follows: pressing plate, thrust bearing, bearing seat, cushion block and machine base, and the final axial force is born by the machine base. The output shaft cannot axially float in the internal direction of the speed reducer, and the parts in the speed reducer cannot be blocked or damaged.
Description
Technical Field
The utility model relates to the technical field of speed reducers, in particular to a cycloidal pin gear speed reducer capable of bearing large axial thrust.
Background
In the structure of the conventional cycloidal pin gear speed reducer (see fig. 1), one end of the output shaft bearing 7 is fixed with a step of the output shaft 5, and the other end of the output shaft bearing 7 is limited by the fastening ring 8 to move axially, wherein the fastening ring 8 and the output shaft 5 are in interference fit, at this time, the fastening ring 8, the output shaft 5 and the output shaft bearing 7 can be regarded as an integral output shaft assembly, and when the output shaft 5 receives axial force, the output shaft assembly moves together in the direction of the axial force. The output end bearing of the general cycloidal pin gear reducer uses a bearing with a stop groove on the outer ring and is provided with a stop ring 9, and the axial movement of the output shaft bearing 7 is limited by a small end cover 10 and the machine base 6. Therefore, only the stop ring 9 ensures the axial movement of the output shaft assembly of the cycloidal pin gear speed reducer, if the axial force is too large, the stop ring 9 is easy to fail, and finally the output shaft assembly is axially moved towards the internal direction of the speed reducer, so that the internal parts of the speed reducer are easy to be blocked and damaged.
Chinese patent application No. CN202080020691.5 discloses a reduction gear and a method for producing a different reduction gear, in particular a reduction gear product family, having a first housing part, a further housing part connected to the first housing part and a bearing device received in the first housing part, by means of which the input shaft is rotatably supported, wherein the input shaft protrudes through an opening through a second housing part, the cover part being connected to the first housing part, in particular oil-tightly, the cover part or a flange part incorporated into the cover part receiving a sealing device sealed towards the input shaft, the second housing part having an inlet for lubricating oil, which opens into an axial bore opening towards the side of the first housing part facing the cover part and into a second annular space, the through bore of the axial bore facing the cover part being covered and/or closed by the cover part, the rolling bodies of the two bearing parts together with the first housing part also defining and/or enclosing at least a second annular space. The technical problems set forth above cannot be effectively solved.
Disclosure of Invention
Aiming at the defect that the existing cycloidal pin gear speed reducer only depends on a stop ring and cannot bear larger axial force, the utility model provides the cycloidal pin gear speed reducer capable of bearing larger axial thrust.
The technical scheme of the utility model is as follows:
the cycloidal pin gear speed reducer capable of bearing large axial thrust comprises a machine base and an output shaft, wherein the output shaft is connected with the output end of working equipment needing to be decelerated.
Still include cushion, clamp plate, bearing frame, frame fixed connection cushion, cushion fixed connection bearing frame the bearing hole has been seted up at the bearing frame center thrust bearing is installed to the bearing downthehole, the bearing hole is interference fit with thrust bearing, thrust bearing inner circle is fixed in the output shaft, the clamp plate is established to output shaft terminal surface cover, the terminal surface of clamp plate supports in thrust bearing's inner circle terminal surface.
One end of the pressing plate arranged on the output shaft sleeve is provided with a shaft head inner hole, an output end gap of the working equipment needing to be decelerated penetrates through the pressing plate to be matched in the shaft head inner hole, and a double flat key is arranged between the output end of the working equipment needing to be decelerated and the shaft head inner hole.
Further, the mounting holes and the inner hexagonal mounting holes are formed in the cushion block, the mounting holes are located in the inner ring of the inner hexagonal mounting holes, the number of the mounting holes and the number of the inner hexagonal mounting holes are multiple, and the mounting holes and the inner hexagonal mounting holes are uniformly distributed in the circumferential direction of the cushion block at equal intervals.
Further, a concave step-shaped mounting concave spigot is formed in the end face of one side of the bearing seat, and a concave second connecting convex spigot is formed in the end face of the other side of the bearing seat.
Further, the bearing seat is axially provided with a second inner hexagonal mounting hole and a threaded mounting hole which are communicated, and the second inner hexagonal mounting hole and the threaded mounting hole are alternately distributed in the circumferential direction of the bearing seat at equal intervals.
Further, a step-shaped bearing spigot is formed in the end face of one side of the cushion block, and a convex connecting convex spigot is formed in the end face of the other side of the cushion block. The connecting convex spigot and the second connecting convex spigot are mutually matched and positioned.
Further, the clamp plate is located the bearing hole of bearing frame, the clamp plate center is provided with the second mounting hole of two keyway in area that link up, the terminal surface of clamp plate is provided with sunken fastening tang, the clamp plate axial has been seted up and has been dismantled the screw hole, and the output clearance of the work equipment that needs to slow down passes the second mounting hole of clamp plate.
Further, the inner diameter of the fastening spigot is in interference fit with the output shaft, and a gap is reserved between the depth of the fastening spigot and the plane of the shaft head of the output shaft.
Compared with the prior art, the utility model has the following beneficial effects:
the thrust bearing is arranged in the bearing hole of the bearing seat, the bearing hole and the thrust bearing are in interference fit, the radial displacement of the thrust bearing is limited, one side of the thrust bearing is abutted against the bearing hole, the other side is abutted against the end face of the pressing plate, and the axial displacement of the thrust bearing is limited.
The output shaft of the speed reducer rotates by means of double flat keys to drive the output end of the working equipment to be decelerated to rotate, and at the moment, the output shaft of the speed reducer, the thrust bearing and the pressing plate rotate simultaneously. The parts of axial force generated by the rotation of the output shaft of the speed reducer are propped against the plane of the pressing plate, and the axial force transmission direction is as follows: pressing plate, thrust bearing, bearing seat, cushion block and machine base, and the final axial force is born by the machine base. The output shaft cannot axially float in the internal direction of the speed reducer, and the parts in the speed reducer cannot be blocked, damaged and the like.
Drawings
FIG. 1 is a schematic diagram of a conventional cycloidal pin gear speed reducer in the prior art;
FIG. 2 is a schematic cross-sectional view of the present utility model;
FIG. 3 is a schematic diagram of the front structure of a pad;
FIG. 4 is a schematic cross-sectional view of a spacer;
FIG. 5 is a schematic view of the front structure of a bearing housing;
FIG. 6 is a schematic view of a cross-sectional structure of the bearing housing in the direction of the arrow shown in FIG. 5;
FIG. 7 is a schematic view of the front structure of the platen;
FIG. 8 is a schematic cross-sectional view of a platen;
fig. 9 is a schematic view of the connection of the present utility model to an extruder.
In the figure: cushion block 1, mounting hole 101, inner hexagonal mounting hole 102, bearing spigot 103, connection male spigot 104, thrust bearing 2, pressing plate 3, second mounting hole 301, fastening spigot 302, dismounting threaded hole 303, bearing seat 4, second inner hexagonal mounting hole 401, threaded mounting hole 402, mounting female spigot 403, second connection male spigot 404, bearing hole 405, output shaft 5, spindle head inner hole 501, stand 6, output shaft bearing 7, fastening ring 8, stop ring 9, small end cover 10, output screw 11, box 12, ball bearing 13.
Detailed Description
The utility model will now be described in further detail with reference to the accompanying drawings. The drawings are simplified schematic representations which merely illustrate the basic structure of the utility model and therefore show only the structures which are relevant to the utility model.
Referring to fig. 2-9, the cycloidal pin gear speed reducer capable of bearing larger axial thrust of the utility model comprises a machine base 6, a cushion block 1, a thrust bearing 2, a pressing plate 3, a bearing seat 4 and an output shaft 5, wherein the machine base 6 is fixedly connected with the cushion block 1 through screws, the cushion block 1 is connected with the machine base 6 through mounting holes 101 through socket head cap screws, and the cushion block 1 is fixedly connected with the bearing seat 4 through screws.
The center of the bearing seat 4 is provided with a bearing hole 405, a thrust bearing 2 is arranged in the bearing hole 405, and the bearing hole 405 and the thrust bearing 2 are in interference fit to limit the radial displacement of the thrust bearing 2. The thrust bearing 2 inner ring is fixed in output shaft 5, and output shaft 5 terminal surface cover establishes clamp plate 3, and the terminal surface of clamp plate 3 supports in thrust bearing 2 inner ring terminal surface, and clamp plate 3 is located bearing hole 405 of bearing frame 4. The bearing hole 405 is a stepped hole, one side of the thrust bearing 2 abuts against the stepped surface of the bearing hole 405, and the other side abuts against the end surface of the pressing plate 3, so that the axial displacement of the thrust bearing 2 is limited.
The cushion block 1 is provided with a mounting hole 101 and an inner hexagonal mounting hole 102, the mounting hole 101 is positioned in the inner ring of the inner hexagonal mounting hole 102, the number of the mounting holes 101 and the inner hexagonal mounting holes 102 is multiple, and the plurality of mounting holes 101 and the inner hexagonal mounting holes 102 are uniformly distributed in the circumferential direction of the cushion block 1 at equal intervals. The mounting hole 101 is used for connecting the base 6, and the inner hexagonal mounting hole 102 is used for connecting the bearing seat 4.
The end face of one side of the cushion block 1 is provided with a step-shaped bearing spigot 103, and the end face of the other side of the cushion block 1 is provided with a convex connecting convex spigot 104. The male connection end 104 is cooperatively positioned with the second male connection end 404.
The bearing seat 4 is axially provided with a second inner hexagonal mounting hole 401 and a threaded mounting hole 402 which are communicated, and the second inner hexagonal mounting hole 401 and the threaded mounting hole 402 are alternately distributed in the circumferential direction of the bearing seat 4 at equal intervals. The socket-shaped mounting hole 102 is connected to the second socket-shaped mounting hole 401 by a socket-shaped screw, and the socket-shaped mounting hole 102 is provided with an internal thread.
The center of the pressing plate 3 is provided with a through second mounting hole 301 with double key grooves, the end face of the pressing plate 3 is provided with a concave fastening spigot 302, and the pressing plate 3 is axially provided with a dismounting threaded hole 303.
The end face of one side of the bearing seat 4 is provided with a concave step-shaped mounting concave spigot 403, and the end face of the other side of the bearing seat 4 is provided with a concave second connecting convex spigot 404.
A ball bearing 13 is also arranged between the output shaft 5 and the stand 6, and a bearing spigot 103 on the cushion block 1 is matched and positioned with the outer ring of the ball bearing 13. An oil seal is also arranged between the bearing seat 4 and the pressing plate 3.
The inner diameter of the fastening spigot 302 is in interference fit with the output shaft 5; the pressing plate 3 is provided with a disassembly threaded hole 303, and the fastening spigot 302 is in interference fit with the output shaft 5, so that when the pressing plate 3 is disassembled, a screw can be screwed into the disassembly threaded hole 303 to eject the pressing plate 3; the depth of the fastening spigot 302 is kept with a gap with the plane of the shaft head of the output shaft 5, so that the condition that the bottom surface of the fastening spigot 302 is contacted with the plane of the shaft head of the output shaft 5 and finally the axial force is born by the output shaft 5 due to the fact that the pressing plate 3 bears the axial force is prevented.
The working equipment to be decelerated in this embodiment is an extruder, that is, the embodiment is used for decelerating the extruder, the output screw 11 of the extruder is matched in the shaft head inner hole 501 of the output shaft 5 through the second mounting hole 301 of the pressing plate 3, the mounting concave spigot 403 of the bearing seat 4 is connected and positioned with the box 12 of the extruder, and the bearing seat 4 is connected and fixed with the box 12 of the extruder through the screw mounting hole 402.
The diameter of the second mounting hole 301 is larger than the diameter of the spindle head inner hole 501 of the output shaft 5, and the depth and width dimensions of the double-key groove of the second mounting hole 301 are respectively larger than those of the double-key groove of the spindle head inner hole 501 of the output shaft 5, so that the second mounting hole 301 avoids the force transmission of the output screw 11 of the extruder.
When the extruder is used, the output screw 11 of the extruder stretches into the output shaft 5, a double flat key is arranged between the shaft head inner hole 501 of the output shaft 5 and the output screw 11 of the extruder, the output screw 11 is driven to rotate by the double flat key through rotation of the speed reducer, and at the moment, the output shaft 5, the thrust bearing 2 and the pressing plate 3 of the speed reducer simultaneously rotate. The parts of axial force generated by the rotation of the reducer output shaft 5 are propped against the plane of the pressing plate 3, and the axial force transmission directions are as follows: the axial force is finally born by the base 6 from the pressing plate 3, the thrust bearing 2, the bearing seat 4, the cushion block 1 and the base 6.
The foregoing description is only illustrative of the utility model and is not to be construed as limiting the utility model. Various modifications and variations of the present utility model will be apparent to those skilled in the art. Any modification, equivalent replacement, improvement, or the like, which is within the spirit and principle of the present utility model, should be included in the scope of the claims of the present utility model.
Claims (7)
1. The cycloidal pin gear speed reducer capable of bearing large axial thrust comprises a base (6) and an output shaft (5), wherein the output shaft (5) is connected with the output end of working equipment needing speed reduction;
the method is characterized in that: the novel bearing structure is characterized by further comprising a cushion block (1), a pressing plate (3) and a bearing seat (4), wherein the base (6) is fixedly connected with the cushion block (1), the bearing seat (4) is fixedly connected with the bearing seat (4), a bearing hole (405) is formed in the center of the bearing seat (4), a thrust bearing (2) is arranged in the bearing hole (405), the bearing hole (405) and the thrust bearing (2) are in interference fit, the inner ring of the thrust bearing (2) is fixed on an output shaft (5), the pressing plate (3) is sleeved on the end face of the output shaft (5), and the end face of the pressing plate (3) abuts against the end face of the inner ring of the thrust bearing (2);
one end of a pressing plate (3) sleeved on the output shaft (5) is provided with a spindle head inner hole (501), the output end clearance of the working equipment needing to be decelerated penetrates through the pressing plate (3) to be matched in the spindle head inner hole (501), and a double flat key is arranged between the output end of the working equipment needing to be decelerated and the spindle head inner hole (501).
2. The cycloidal pin gear speed reducer capable of bearing large axial thrust according to claim 1, wherein the cycloidal pin gear speed reducer is characterized in that: the novel anti-collision device is characterized in that mounting holes (101) and inner hexagonal mounting holes (102) are formed in the cushion block (1), the mounting holes (101) are located in the inner ring of the inner hexagonal mounting holes (102), the number of the mounting holes (101) and the number of the inner hexagonal mounting holes (102) are multiple, and the mounting holes (101) and the inner hexagonal mounting holes (102) are uniformly distributed in the circumferential direction of the cushion block (1) at equal intervals.
3. The cycloidal pin gear speed reducer capable of bearing large axial thrust according to claim 1, wherein the cycloidal pin gear speed reducer is characterized in that: the end face of one side of the bearing seat (4) is provided with a concave step-shaped mounting concave spigot (403), and the end face of the other side of the bearing seat (4) is provided with a concave second connecting convex spigot (404).
4. The cycloidal pin gear speed reducer capable of bearing large axial thrust according to claim 1, wherein the cycloidal pin gear speed reducer is characterized in that: the bearing seat (4) is axially provided with a second through inner hexagonal mounting hole (401) and a threaded mounting hole (402), and the second inner hexagonal mounting hole (401) and the threaded mounting hole (402) are alternately distributed in the circumferential direction of the bearing seat (4) at equal intervals.
5. A cycloidal pin gear speed reducer capable of bearing large axial thrust according to claim 3, characterized in that: the end face of one side of the cushion block (1) is provided with a step-shaped bearing spigot (103), the end face of the other side of the cushion block (1) is provided with a convex connecting convex spigot (104), and the connecting convex spigot (104) and the second connecting convex spigot (404) are mutually matched and positioned.
6. The cycloidal pin gear speed reducer capable of bearing large axial thrust according to claim 4, wherein the cycloidal pin gear speed reducer is characterized in that: the pressing plate (3) is located in a bearing hole (405) of the bearing seat (4), a second through-hole with double key grooves (301) is formed in the center of the pressing plate (3), a concave fastening spigot (302) is formed in the end face of the pressing plate (3), a disassembly threaded hole (303) is formed in the axial direction of the pressing plate (3), and an output end gap of working equipment needing to be decelerated penetrates through the second through-hole (301) of the pressing plate (3).
7. The cycloidal pin gear speed reducer capable of bearing large axial thrust according to claim 6, wherein the cycloidal pin gear speed reducer is characterized in that: the inner diameter of the fastening spigot (302) is in interference fit with the output shaft (5), and a gap is reserved between the depth of the fastening spigot (302) and the plane of the shaft head of the output shaft (5).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321683067.0U CN219994336U (en) | 2023-06-29 | 2023-06-29 | Cycloidal pin gear speed reducer capable of bearing large axial thrust |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321683067.0U CN219994336U (en) | 2023-06-29 | 2023-06-29 | Cycloidal pin gear speed reducer capable of bearing large axial thrust |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN219994336U true CN219994336U (en) | 2023-11-10 |
Family
ID=88605714
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202321683067.0U Active CN219994336U (en) | 2023-06-29 | 2023-06-29 | Cycloidal pin gear speed reducer capable of bearing large axial thrust |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN219994336U (en) |
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2023
- 2023-06-29 CN CN202321683067.0U patent/CN219994336U/en active Active
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