JP5174001B2 - Two-speed switching speed reducer - Google Patents

Description

  The present invention relates to a two-speed switching speed reduction device that can be used as a speed reducer for a kneading extruder, continuous kneading machine, rolling mill, etc., and capable of switching a rotational speed.

  A kneading extruder or continuous kneading machine is an apparatus that kneads resin, rubber, or the like by rotating the rotor or screw shaft by increasing the torque by decelerating the rotation of the driving electric motor with a reduction gear. This kneading extruder and continuous kneading machine require adjustment of the throughput of the kneaded product, and this adjustment was made by making the rotational speed of the rotor and screw shaft variable. Also, in the rolling mill, in order to produce various types of rolled products, the rolling speed has been switched.

  For example, in a kneading extruder or continuous kneader, a variable speed drive device is required to adjust the rotational speed of the rotor and screw shaft, but variable speed operation by primary frequency control of an electric motor is not possible. This is disadvantageous in terms of cost. In the case of a large machine, the rotational speed of the input shaft is kept constant, and the rotational speed of the output shaft is switched between two speeds of low speed and high speed by a rotational speed switching device such as a clutch. In many cases, a speed switching speed reducer is used. Similarly, in a rolling mill, a two-speed switching reduction device is often used.

  FIG. 11 shows a two-speed switching reduction device conventionally used as a reduction gear for kneading extruders, continuous kneaders, rolling mills and the like. This two-speed switching reduction gear includes an input shaft 1 that is driven to rotate by an electric drive motor (not shown), in which a small gear 2 for low speed and a small gear 3 for high speed are fixed to the outer periphery at a predetermined interval. An output shaft 4 in which a low speed large gear 5 meshed with the low speed small gear 2 and a high speed large gear 6 meshed with the high speed small gear 3 are rotatably mounted on the outer periphery at a predetermined interval; A rotation speed switching device 7 for fixing one of the low speed large gear 5 and the high speed large gear 6 to the outer periphery of the output shaft 4 and rotating the output shaft 4 by switching between two low speed or high speed rotation speeds; It is comprised.

  The rotational speed switching device 7 includes an external spline 4a having a predetermined length formed in the center in the axial direction of the output shaft 4, a large low-speed gear 5 and a large high-speed gear that are externally fitted to the external spline 4a. A shifter 8 located between the gears 6 and an annular groove formed on the outer periphery of the intermediate part of the shifter 8 are moved to move the shifter 8 to the low speed large gear 5 side or the high speed large gear 6 side. The shifter 8 is composed of a cam follower 18 supported by a swingable clutch 16 that is connected to the low speed large gear 5 or the high speed large gear 6.

  FIG. 11 shows a neutral state in which the shifter 8 is not connected to either the low speed large gear 5 or the high speed large gear 6, but switching is not shown in either direction indicated by the double arrow in FIG. 11. The shifter 8 is moved to the high speed gear 5 side or the high speed gear 6 side by operating the lever and manually moving the clutch 16. In this state, the shifter 8 fitted on the external spline 4a of the output shaft 4 and the large gear 5 for low speed or the large gear 6 for high speed are connected.

  The rotation of the input shaft 1 that is rotationally driven by a drive electric motor (not shown) is rotated to the low speed large gear 5 via the low speed small gear 2 and to the high speed large gear 6 via the high speed small gear 3. However, since one of the low speed large gear 5 and the high speed large gear 6 is coupled to the output shaft 4 via the shifter 8, the output shaft 4 is coupled to the low speed large gear 5. Is a low speed and rotates at a high speed when it is connected to the large gear 6 for high speed. That is, the rotation speed of the output shaft 4 can be switched between two rotation speeds, low speed and high speed.

  However, when the shifter 8 is connected to the low speed large gear 5 or the high speed large gear 6, the shifter 8 is pressed by points or lines by the cam follower 18 supported by the clutch 16. When the switching speed reduction device is large, there is a possibility that the switching operation cannot be performed well, and with the increase in the size of the speed reduction device and the increase in transmission power, the allowable rotational speed, load capacity, and life of the cam follower 18 become problems.

  Moreover, there exists a technique of patent document 1 as a concrete proposal example of a two-speed switching reduction gear. The two-stage switching speed reducer described in Patent Document 1 includes a switching ring that is externally fitted to an input shaft and an output shaft, and the end of the U-shaped member is moved by operating the switching lever. The cylinder-shaped slider provided in the cylinder is configured to be able to perform switching by pressing the switching rings and sliding the switching rings along the input shaft and the output shaft. However, as the size of the reducer increases and the transmission power increases, the axial load applied to the switching ring tends to increase. With a slider that presses with a point or line as with a cam follower, the same as with a cam follower. The switching operation and its lifetime are considered to be a problem.

JP-A-10-110791

  The present invention has been made as a solution to the above-mentioned conventional problems, and can reliably switch the rotation speed of the output shaft between two rotation speeds, low speed and high speed, and the allowable rotation speed and load capacity of the parts. It is an object of the present invention to provide a two-speed switching speed reducer that is hardly affected by the life or the like.

According to the first aspect of the present invention, there is provided an input shaft for rotationally driving, wherein a low speed small gear and a high speed small gear are fixed to an outer periphery at a predetermined interval, and a low speed large gear meshing with the low speed small gear. A high-speed large gear meshing with the high-speed small gear has an output shaft that is freely mounted on the outer periphery at a predetermined interval, and one of the low-speed large gear and the high-speed large gear. A two-speed switching reduction device having a rotation speed switching device coupled to the outer periphery of the output shaft so as to rotate together with the output shaft and rotating the output shaft at a low speed or a high speed, the rotation speed switching device, An external spline having a predetermined length formed in the axial direction of the outer peripheral surface of the output shaft; and a shifter externally fitted to the external spline and positioned between the low speed large gear and the high speed large gear. Annular formed on the outer periphery of the intermediate part of the shifter It is composed of a plate-like bush provided inside and movable in the movement direction of the shifter, and is a pressing surface formed on both sides in the movement direction of the bush, and faces the opposed surface of the annular groove. The shifter is moved by pressing by contact to selectively connect the shifter and the large gear for low speed or the large gear for high speed, and the pressing surface of the bush and the annular groove of the shifter A lubricant supply unit that supplies a lubricant is provided between the pressing surface of the bush and the pressing surface of the bush is closer to the edge of the pressing surface positioned along the circumferential direction of the annular groove. The two-speed switching reduction device is characterized in that a taper is formed at an end so that a gap is formed so that a gap between the annular groove and the opposing surface is wide .

According to a second aspect of the invention, the bushing is a two-speed switching換減speed apparatus according to claim 1, characterized in that it is supported by a supporting portion provided closer to the rotational direction of the shifter.

The invention according to claim 3 is the two-speed switching reduction device according to claim 1 or 2 , wherein at least the pressing surface of the bush is formed of a non-ferrous metal or a resin material.

The invention according to claim 4 is the two-speed switching reduction gear according to any one of claims 1 to 3 , wherein the shape of the bush is an arc shape along the annular groove of the shifter.

The invention according to claim 5 is characterized in that the surface roughness of the pressing surface of the bush and the surface roughness of the facing surface of the annular groove of the shifter are 1.6a or less in arithmetic mean roughness, respectively. A two-speed switching reduction device according to any one of claims 1 to 4 .

The invention according to claim 6 is the two-speed switching deceleration according to any one of claims 1 to 5 , wherein the bush is supported by a support portion via a spherical bearing provided therein. Device.

  According to the two-speed switching reduction device of the first aspect of the present invention, the pressing surfaces formed on both sides of the bush are pressed against the opposed surfaces of the shifters facing each other, that is, the switching is performed by pressing the surfaces facing each other. In addition to a small two-speed switching speed reducer, it is easy to cope with an increase in size. Therefore, regardless of the size of the two-speed switching reduction device, the shifter can be reliably moved and connected to the low speed large gear or the high speed large gear, and the output shaft can be rotated at two speeds, low speed and high speed. It is possible to reliably switch to the rotation speed. Furthermore, since the pressing surface of the bush presses the opposing surface of the shifter, the allowable load capacity is large, and the life is long because it is not affected by the allowable rotational speed or life of the parts.

In addition, by supplying a lubricant between the pressing surface of the bush and the opposing surface of the annular groove of the shifter, heat generation and wear due to sliding between the pressing surface of the bush and the opposing surface of the annular groove of the shifter are also suppressed. be able to.

Furthermore, the lubricant can be reliably supplied from a gap formed between the pressing surface of the bush and the opposing surface of the annular groove of the shifter.

According to the two-speed switching換減speed apparatus according to a second aspect of the present invention, the gap between the pressing surface and the opposing surface of the side away from the support portion of the bush when the shifter is rotated (counter-rotational direction of the shifter) of the bushing It is possible to set wider than the gap on the side closer to the support portion (shifter rotation direction side), that is, to set the inclination of the bush. As a result, the wedge effect in the gap between the pressing surface and the opposing surface during rotation of the shifter can be enhanced, and the friction suppressing effect is enhanced.

According to the two-speed switching speed reduction device of the third aspect of the present invention, it is possible to suppress the shifter pressed by the bush from being worn or wrinkled.

According to the two-speed switching reduction gear device of the fourth aspect of the present invention, since the shape of the bush is an arc shape along with the shifter, the pressing of the shifter on the pressing surface of the bush becomes more stable. In the case of supplying the lubricant, the lubricant easily penetrates uniformly between the pressing surface of the bush and the opposing surface of the shifter, so that the allowable load can be easily increased and the wear suppression effect can be easily improved.

According to the two-speed switching reduction device of the fifth aspect of the present invention, when the lubricant permeates between the pressing surface of the bush and the opposing surface of the annular groove of the shifter, the flow of the lubricant is disturbed due to surface roughness. Can be suppressed.

According to the two-speed switching speed reducer of claim 6 of the present invention, since the pressing surface of the bush is reliably aligned with the opposing surface of the annular groove of the bush during rotation of the shifter, The surface pressure by the pressing surface becomes uniform at any position on the pressing surface, and the shifter pressing on the pressing surface of the bush is stabilized.

It is a longitudinal cross-sectional view which shows the two-speed switching speed reducer of one Embodiment of this invention. It is the sectional view on the AA line of FIG. 1 which shows the two-speed switching speed reducer of the embodiment. It is the BB sectional drawing of FIG. 2 which shows the two-speed switching speed reducer of the embodiment. An example of the bush used for the 2nd-speed switching speed reducer of a reference example is shown, (a) is a top view, (b) is a front view, (c) is a right view. An example of the bush used for the two-speed switching speed reducer of this invention is shown, (a) is a top view, (b) is a front view, (c) is a right view. The different example of the bush used for the two-speed switching speed reducer of this invention is shown, (a) is a top view, (b) is a front view, (c) is a right view. The different example of the bush used for the two-speed switching speed reducer of this invention is shown, (a) is a top view, (b) is a front view, (c) is a right view. The different example of the bush used for the two-speed switching speed reducer of this invention is shown, (a) is a top view, (b) is a front view, (c) is a right view. It is a longitudinal cross-sectional view in the position corresponding to FIG. 2 which shows the two-speed switching speed reducer of different embodiment of this invention. It is a longitudinal cross-sectional view in the position corresponding to FIG. 2 which shows the two-speed switching speed reducer of further different embodiment of this invention. It is a longitudinal cross-sectional view which shows the conventional two-speed switching speed reducer.

  Hereinafter, the present invention will be described in more detail based on embodiments shown in the accompanying drawings.

  1 to 3 are longitudinal sectional views showing a two-speed switching reduction device according to an embodiment of the present invention. FIG. 2 is a sectional view taken along the line AA in FIG. 1, and FIG. 3 is a sectional view taken along the line BB in FIG. It is sectional drawing.

For example, as shown in FIGS. 1 to 3, the two-speed switching reduction gear of the present invention includes a low-speed small gear 2 and a high-speed small gear 3 fixed to the outer periphery with a predetermined interval, not shown. An input shaft 1 that is rotationally driven by a driving electric motor, a low-speed large gear 5 that meshes with the low-speed small gear 2, and a high-speed large gear 6 that meshes with the high-speed small gear 3 are spaced apart from each other by a predetermined interval. The output shaft 4 is rotatably mounted on the outer periphery via a bearing 4b, and one of the low-speed large gear 5 and the high-speed large gear 6 is rotated with the output shaft 4 so that the output shaft is rotated. 4 is connected to the outer periphery, and is configured to have a rotational speed switching device 7 for rotating the output shaft 4 at a low speed or high speed, which are incorporated in all box-shaped housing 15.

  The low-speed small gear 2 and the high-speed small gear 3 are connected to or attached to the input shaft 1 and the low-speed large gear 5 and the high-speed large gear 6 are connected to the output shaft 4 with a predetermined interval, respectively. As described above, it is desirable that these intervals are the same, and at least such that the low speed small gear 2 and the low speed large gear 5 and the high speed small gear 3 and the high speed large gear 6 can mesh with each other. There must be. The gear fixed to the input shaft 1 has been described as a small gear, and the gear mounted on the output shaft 4 has been described as a large gear. This is because the rotational speed of the output shaft 4 is reduced from the rotational speed of the input shaft 1. This is because the diameter of the gear fixed to the input shaft 1 is smaller than the diameter of the gear mounted on the output shaft 4 so as to mesh with the gear. The gear fixed to the input shaft 1 is described as a small gear, and the gear mounted on the output shaft 4 is described as a large gear.

  Further, when comparing the low speed small gear 2 fixed to the input shaft 1 and the high speed small gear 3, the diameter of the low speed small gear 2 is smaller than the diameter of the high speed small gear 3. On the other hand, when comparing the low speed large gear 5 mounted on the output shaft 4 and the high speed large gear 6, the diameter of the low speed large gear 5 is larger than the diameter of the high speed large gear 6. Also, on the opposite surface sides of the low speed large gear 5 and the high speed large gear 6 mounted on the output shaft 4, annular spurs having the same shape and formed with internal splines 5b and 6b on the inner periphery, respectively. 5a and 6a are provided, respectively.

  The input shaft 1 is supported by a bearing 15 a provided in the housing 15, and has one end projecting outward from the housing 15, and is rotationally driven by an external driving electric motor (not shown).

  The output shaft 4 is also supported by a bearing 15 a provided in the housing 15 in a state parallel to the input shaft 1, and the side opposite to the input shaft 1 protrudes from the housing 15 to the outside. Note that the output shaft 4 may protrude outward from the housing 15 on the same side as the input shaft 1. An external spline 4 a having a predetermined length is formed in the axial direction of the outer peripheral surface of the output shaft 4. The position where the external spline 4 a is formed is a position between the mounted low speed large gear 5 and the high speed large gear 6, and both ends thereof are annular projecting portions 5 a of the low speed large gear 5. And the inner side of the annular projecting portion 6a of the high-speed large gear 6 respectively.

  A shifter 8 is fitted on the external spline 4 a of the output shaft 4. An inner tooth spline 8b is formed on the inner periphery of the shifter 8, and a pair of outer tooth splines 8c and 8c are formed on the outer periphery with an interval in the axial direction. By fitting the internal spline 8b of the shifter 8 to the external spline 4a of the output shaft 4, the shifter 8 is externally fitted to the output shaft 4 so as to be movable in the axial direction. The outer peripheral shape of the external spline 8c of the shifter 8 is the same as the inner peripheral shape of the annular projecting portion 5a of the large gear 5 for low speed and the inner peripheral shape of the annular projecting portion 6a of the large gear 6 for high speed. By moving the shifter 8 to the inside of these annular projecting portions 5a and 6a, the external splines 8c of the shifter 8 are moved to the inner tooth splines 5b of the annular projecting portions 5a and 6a. , 6b, and the shifter 8 is connected to the large gear 5 for low speed or the large gear 6 for high speed.

An annular groove 8d is formed on the outer periphery of the intermediate portion of the shifter 8 along the circumferential direction. Inside the annular groove 8d, an arc-shaped and plate-like bush 9 is provided along the shifter 8, and this bush 9 is at least around the axis centering on the radial direction of the shifter 8, It is supported by the support portion 13 by the clutch 16 so as to be swingable, and is configured to be movable in the moving direction of the shifter 8 between the opposing surfaces 8a, 8a on both sides of the annular groove 8d. The bush 9 needs to be plate-shaped, but the shape is not necessarily arcuate. In the present invention, both side surfaces of the bush 9 are referred to as a pressing surface 9a, and a surface of the shifter 8 that faces the pressing surface 9a of the bush 9 is referred to as an opposing surface 8a.

  The rotational speed switching device 7 includes the external spline 4a formed in the axial direction of the outer peripheral surface of the output shaft 4, the shifter 8 fitted on the external spline 4a, and the annular groove of the shifter 8 as described above. The bush 9 is movable along the moving direction of the shifter 8 provided inside 8d.

  Here, the operation of the two-speed switching reduction device of the present invention will be described. 1 and 3 show a neutral state in which the shifter 8 is not connected to either the low speed large gear 5 or the high speed large gear 6, but the clutch lever 16a shown in FIG. When the opposing surface 8a of the shifter 8 located on the side of the large-speed gear 5 facing each other is pressed by one pressing surface 9a of the bush 9, the shifter 8 has an annular projecting portion of the large-speed gear 5 It fits in 5a and is connected to the large gear 5 for low speed. Further, when the position of the clutch lever 16a is locked by a locking device (not shown) so that the clutch 16 does not return to the neutral state in the operating state of the clutch 16, the shifter 8 has its internal spline 8b connected to the external teeth of the output shaft 4. Returning to the neutral state is restricted by the pressing surface 9a of the bush 9 in a state of being fitted to the spline 4a. Therefore, the shifter 8 is fixed to the output shaft 4, and the low speed large gear 5 is fixed to the output shaft 4 via the shifter 8. Thus, preparation for rotating the output shaft 4 at a low rotation speed is completed.

  First, when an external drive electric motor (not shown) is operated to drive the input shaft 1 to rotate, the rotation of the input shaft 1 is transferred to the low speed large gear 5 via the low speed small gear 2 fixed to the outer periphery thereof. Communicated. As described above, since the low-speed large gear 5 is fixed to the output shaft 4 via the shifter 8, the output shaft 4 rotates at a low speed, and the connected rotor, screw shaft, and the like rotate at a low speed.

  On the other hand, when the clutch lever 16a shown in FIG. 2 is operated to actuate the clutch 16, and the other pressing surface 9a of the bush 9 presses the opposing surface 8a of the shifter 8 located on the high-speed large gear 6 side facing, The shifter 8 is fitted into the annular projecting portion 6 a of the high speed large gear 6 and is connected to the high speed large gear 6. Further, as described above in this state, when the position of the clutch lever 16a is locked by a lock device (not shown), the shifter 8 has the internal spline 8b fitted to the external spline 4a of the output shaft 4, and the bush The movement toward the low-speed large gear 5 side (return to the neutral state) is restricted by the pressing surface 9a. Therefore, the shifter 8 is fixed to the output shaft 4, and the high-speed large gear 5 is fixed to the output shaft 4 via the shifter 8. Thus, preparation for rotating the output shaft 4 at a high rotational speed is completed.

  First, when an external driving electric motor (not shown) is operated to rotate the input shaft 1, the rotation of the input shaft 1 is transferred to the high-speed large gear 6 via the high-speed small gear 3 fixed to the outer periphery thereof. Communicated. As described above, since the high-speed large gear 5 is fixed to the output shaft 4 via the shifter 8, the output shaft 4 rotates at high speed, and the connected rotor, screw shaft, and the like rotate at high speed.

  As described above, the rotational speed of the output shaft 4 can be easily and reliably switched between the low speed and the high speed only by operating the clutch lever 16a. In the above description, the rotation speed is distinguished from low speed and high speed. However, comparing both rotation speeds, only the low speed is described as low speed and the high speed is high speed. Since it is decelerated by the switching device 7, the output shaft 4 rotates at a rotational speed that is slower than the rotational speed of the input shaft 1.

  The above is the description of the basic configuration and the operation of the two-speed switching reduction device of the present invention. However, the two-speed switching reduction device of the present invention can have various configurations as described below.

  As shown in FIG. 2, a lubricant supply pipe 17 is provided outside the bush 9, and from the lubricant supply portion 10, between the pressing surface 9 a of the bush 9 and the opposing surface 8 a of the annular groove 8 d of the shifter 8. By supplying the lubricant, heat generation and wear between the pressing surface 9a of the bush 9 and the opposing surface 8a of the shifter 8 can be suppressed.

  The bush 9 shown in FIG. 4 reliably supplies the lubricant from the lubricant supply pipe 17 shown in FIG. 2 between the pressing surface 9a of the bush 9 and the opposing surface 8a of the annular groove 8d of the shifter 8. Further, the bush 9 is formed with a lubricant supply hole 11 and a lubricant supply groove 12. Thus, by forming the lubricant supply hole 11 and the lubricant supply groove 12 in the bush 9, the lubricant can be supplied more reliably. Note that the lubricant supply hole 11 and the lubricant supply groove 12 may be provided on a path different from the bush 9 shown in FIG.

  The bush 9 shown in FIG. 5 is a bush 9 in which a taper 9b (shown by a gap between arrows because it is slightly inclined in FIG. 5) is formed at the ends of the pressing surfaces 9a on both sides. Thus, by forming the taper 9 b at the end of the pressing surface 9 a of the bush 9, the supply of the lubricant can be ensured from the gap formed between the pressing surface 9 a of the bush 9 and the opposing surface 8 a of the shifter 8. It can be carried out. As shown in FIG. 5 (b), the bush 9 shown here has a taper 9b at both the upper and lower ends of the pressing surface 9a, and is a bush 9 considering versatility. The taper 9b may be formed only on one end side in consideration of the agent supply side and the rotational direction of the low speed large gear 5 and the high speed large gear 6.

  The bush 9 shown in FIG. 6 is provided with the support portion 13 supported by the clutch 16 close to the rotational direction side of the shifter 8. By configuring the bush 9 in this way, the gap between the pressing surface 9a and the opposing surface 8a on the side farther from the support portion 13 of the bush 9 when the shifter 8 rotates (on the side opposite to the rotation direction of the shifter 8) 9 can be set wider than the gap on the side closer to the support portion 13 (the rotation direction side of the shifter 8), that is, the inclination of the bush 9 can be set. Thereby, since the wedge effect in the clearance gap between the pressing surface 9a and the opposing surface 8a at the time of rotation of the shifter 8 can be enhanced, the friction suppressing effect is enhanced.

  The bush 9 according to the above embodiment is formed of an iron-based material, but the bush 9 shown in FIG. 7 is a bush 9 in which a portion including the pressing surface 9a is formed of a non-ferrous metal or a resin material. . In this embodiment, the part indicated by the symbol C is formed of a plate-like member made of a non-ferrous metal or resin material whose hardness is lower than that of the bush 9, and the remaining part including the support portion 13 is made of rolled steel. Yes. It is recommended to use a bronze-based material such as aluminum bronze or lead bronze as the non-ferrous metal, and to use a peak resin as the resin material. The entire bush 9 may be formed of such a non-ferrous metal or resin material as long as the desired strength can be ensured.

  A bush 9 shown in FIG. 8 is a bush 9 in which a spherical bearing 14 is incorporated and supported by a support portion 13 via the spherical bearing 14. When the spherical bearing 14 is provided in this way, when the shifter 8 fixed to the low speed large gear 5 or the high speed large gear 6 is rotated, the negative pressing surface 9a of the bush 9 is opposed to the opposing surface 8a of the shifter 8. And centered to hit the whole.

  As described above, the bush 9 shown in FIGS. 4 to 8 is the bush 9 provided with added value, but includes the bush 9 having a basic configuration that does not provide added value, and the pressing surface 9a of the bush 9 at the time of pressing, It is preferable that the surface roughness of the opposing surface 8a of the shifter 8 is 1.6a or less in terms of arithmetic average roughness (Ra). The arithmetic average roughness shown here is defined in JIS B 0601. The surface roughness is more preferably 0.8a or less in arithmetic average roughness, and is more preferably as close to 0 as possible.

  The embodiment shown in FIG. 2 is an embodiment in which a pair of left and right arc-shaped bushes 9 are provided. However, as shown in FIG. As shown in the figure, the substantially semicircular arc plate-like bushes 9 having the pressing surfaces 9a separated from each other may be provided on the left and right, and the number of the bushes 9 may be any number.

DESCRIPTION OF SYMBOLS 1 ... Input shaft 2 ... Small gear for low speed 3 ... Small gear for high speed 4 ... Output shaft, 4a ... External tooth spline, 4b ... Bearing 5 ... Large gear for low speed, 5a ... Circular projecting part, 5b ... Internal tooth spline 6 ... high gear for high speed, 6a ... annular protrusion, 6b ... internal spline 7 ... rotational speed switching device 8 ... shifter, 8a ... opposite surface, 8b ... internal spline, 8c ... external spline, 8d ... annular Groove 9 ... Bush, 9a ... Pressing surface, 9b ... Taper 10 ... Lubricant supply part 11 ... Lubricant supply hole 12 ... Lubricant supply groove 13 ... Support part 14 ... Spherical bearing 15 ... Housing, 15a ... Bearing 16 ... Clutch, 16a ... Clutch lever 17 ... Lubricant supply pipe 18 ... Cam follower

Claims (6)

A low-speed small gear and a high-speed small gear, which are rotationally driven and fixed to the outer periphery at a predetermined interval;
A low-speed large gear meshing with the low-speed small gear, and a high-speed large gear meshing with the high-speed small gear, an output shaft that is rotatably mounted on the outer periphery at a predetermined interval;
One of the large gear for low speed and the large gear for high speed is connected to the outer periphery of the output shaft so as to rotate together with the output shaft, and a rotational speed switching device for rotating the output shaft at low speed or high speed. A two-speed switching speed reducer comprising:
The rotational speed switching device includes an external spline having a predetermined length formed in the axial direction of the outer peripheral surface of the output shaft;
A shifter externally fitted to the external spline and positioned between the low speed large gear and the high speed large gear;
It is provided in an annular groove formed on the outer periphery of the intermediate portion of the shifter, and is configured by a plate-like bush that is movable in the movement direction of the shifter,
With the pressing surfaces formed on both sides in the movement direction of the bush, the opposing surfaces of the annular groove are pressed by surface contact to move the shifter, and the shifter and the low-speed large gear or the high-speed gear While selectively connecting with a large gear ,
A lubricant supply unit for supplying a lubricant is provided between the pressing surface of the bush and the opposing surface of the annular groove of the shifter;
On the pressing surface of the bush, a gap is formed such that the gap between the pressing surface and the opposing surface of the annular groove becomes wider toward the edge side located along the circumferential direction of the annular groove. Further, a two-speed switching speed reducer characterized in that a taper is formed at the end . The bush, the double-speed switching換減speed apparatus according to claim 1, characterized in that it is supported by a supporting portion provided closer to the rotational direction of the shifter. The bush, the double-speed switching換減speed apparatus according to claim 1 or 2, characterized in that at least the pressing surface is formed of a non-ferrous metal or a resin material. The shape of the bush, the double-speed switching換減speed apparatus according to any one of claims 1 to 3, characterized in that the arcuate shape along the annular groove of the shifter. And surface roughness of the pressing surface of the bush, the surface roughness of the opposed surfaces of the annular groove of the shifter, any one of claims 1 to 4, characterized in that it is 1.6a or less in each arithmetic average roughness The two-speed switching speed reducer described in 1. The two-speed switching reduction device according to any one of claims 1 to 5 , wherein the bush is supported by a support portion via a spherical bearing provided therein.

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