TW202144690A - Gear reducer lubricating structure - Google Patents

Abstract

The present disclosure provides a gear reducer lubricating structure including a carrier, a planetary gear and a spacer. The carrier includes a frame body and a pivotal shaft disposed at the frame body. The planetary gear is pivotally disposed at the carrier and includes a main body, a bore and an oil groove. The main body includes an end surface. The bore penetrates the main body and allows the pivotal shaft to insert thereinto. The oil groove is disposed at the end surface and communicates with the bore. The spacer is located between the frame body and the end surface. When the planetary gear relative to the spacer and the carrier is turning, it will cause changes of an overlapped range between the spacer and the oil groove and enable to pump the lubricating oil into the oil groove. Hence, the lubricating oil is actively pumped into the oil groove, thereby flowing into the bore, and the lubricating effect is highly increased.

Description

Gear reducer lubrication structure

The present invention relates to a lubricating structure, and more particularly, to a lubricating structure for a gear reducer.

The advancement of science and technology has led to the development of technology. Various machines that use power or automation have replaced traditional human tools and are widely used in life, which has improved the convenience of human society. Motors are the most common source of power.

Generally speaking, the speed of the motor is fast. Therefore, in the structural configuration, a reducer will be used to reduce the speed of the driven components, especially the gear reducer, which changes the speed ratio through the configuration of the tooth pitch, which can reduce the speed. effect. In order to reduce the wear and tear of the gear reducer and increase its service life, the industry will add lubricating oil to the gear reducer, and open a thin groove connected with the shaft hole on the end face of the gear, so that the lubricating oil can flow into the shaft hole, Improve lubrication effect. However, the viscosity of lubricating oil is high, and it is not easy to flow into the shaft hole from the fine groove, resulting in poor lubrication effect, so there is still room for improvement.

In view of this, how to improve the lubrication structure of the gear reducer and improve its lubrication effect has become the goal of the relevant industry.

In order to solve the above problems, the present invention provides a lubricating structure for a gear reducer, through which the lubricating effect can be improved.

According to an embodiment of the present invention, a lubricating structure for a gear reducer is provided, which includes a planet carrier, at least one planet gear and at least one washer. The planet carrier includes a frame body and at least one pivot shaft, and the at least one pivot shaft is disposed on the frame body. The at least one planetary gear is pivoted on the planet carrier and includes a body, a shaft hole and at least one oil replenishing groove. The main body includes an end surface, the shaft hole penetrates through the main body and is provided for the pivot shaft to pass through, and the at least one oil replenishing groove is arranged on the end surface and communicates with the shaft hole. The at least one spacer is located between the frame body and the end surface of the at least one planetary gear. Wherein, the at least one planetary gear rotates relative to the at least one spacer and the planet carrier to change an overlapping range of the at least one spacer and the at least one oil supply groove, so as to press a lubricating oil into the at least one oil supply groove.

In this way, the lubricating oil can be actively pressed into the oil replenishment groove, and then flow into the shaft hole, which can improve the lubricating effect.

According to a plurality of embodiments of the aforementioned gear reducer lubricating structure, wherein the at least one oil supply groove can be arc-shaped and has a center, and the center of the at least one oil supply groove and a central axis of the shaft hole of the at least one planetary gear dislocation.

According to a plurality of embodiments of the aforementioned lubricating structure for the gear reducer, the at least one spacer can be roughly in the shape of a truncated triangle.

According to several embodiments of the aforementioned lubricating structure of the gear reducer, the at least one gasket can be roughly oval.

According to several embodiments of the aforementioned lubricating structure of the gear reducer, the at least one gasket can be roughly in the shape of a notch disk.

According to various embodiments of the aforementioned lubricating structure for the gear reducer, the body may include a convex ring located on the end face and surrounding the shaft hole, and the convex ring is partially cut to form the at least one oil replenishing groove.

According to multiple embodiments of the aforementioned gear reducer lubrication structure, a first radial length of the at least one gasket can be approximately equal to an outer edge radius of the convex ring, and the first radial length is the peripheral edge of the at least one gasket The maximum vertical distance from a central axis of the shaft hole.

According to a plurality of embodiments of the aforementioned lubricating structure for the gear reducer, the planet carrier may further include at least one concave portion located in the frame body, wherein the at least one gasket is located in the at least one concave portion.

According to a plurality of embodiments of the aforementioned gear reducer lubricating structure, a depth of the at least one concave portion can be smaller than a thickness of the at least one gasket.

According to multiple embodiments of the aforementioned gear reducer lubrication structure, a first radial length of the at least one gasket can be greater than or equal to a second radial length of the at least one oil supply groove, and the first radial length is The maximum vertical distance between the peripheral edge of the at least one gasket and a central axis of the shaft hole, and the second radial length is the maximum vertical distance between the peripheral edge of the at least one oil supply groove and the central axis.

Embodiments of the present invention will be described below with reference to the drawings. For the sake of clarity, many practical details are set forth in the following description. The reader should understand, however, that these practical details should not be used to limit the invention. That is, in some embodiments of the present invention, these practical details are unnecessary. In addition, to simplify the drawings, some well-known and conventional structures and elements will be shown in a simplified and schematic manner in the drawings; and repeated elements may be denoted by the same or similar numerals.

In addition, when a certain element (or mechanism or module, etc.) is "connected", "arranged" or "coupled" to another element herein, it may mean that the element is directly connected, directly arranged or directly coupled to another element , can also mean that an element is indirectly connected, indirectly arranged or indirectly coupled to another element, that is, there are other elements interposed between the element and the other element. When it is expressly stated that an element is "directly connected", "directly arranged" or "directly coupled" to another element, it means that no other element is interposed between the said element and the other element. The terms first, second, and third are only used to describe different elements or components, and do not limit the elements/components themselves. Therefore, the first element/component may also be renamed as the second element/component. Moreover, the combination of elements/components/mechanisms/modules in this article is not a generally known, conventional or conventional combination in this field, and whether the components/components/mechanisms/modules themselves are known to determine whether their combination relationship is not Easily accomplished by those of ordinary knowledge in the technical field.

Please refer to Figures 1, 2 and 3, wherein Figure 1 is a schematic perspective view of a gear reducer lubrication structure 10 according to a first embodiment of the present invention, Figure 2 is the first A partial perspective view of the lubricating structure 10 of the gear reducer of the embodiment, FIG. 3 is a schematic diagram of the pivot 120 , the roller 500 , the planetary gear 200 and the spacer 300 of the first embodiment of FIG. 1 . The gear reducer lubricating structure 10 includes a planet carrier 100 , at least one planetary gear 200 and at least one washer 300 .

The planet carrier 100 includes a frame body 110 and at least one pivot shaft 120 . The at least one pivot shaft 120 is disposed on the frame body 110 . The aforementioned at least one planetary gear 200 is pivoted on the planet carrier 100 and includes a body 210 , a shaft hole 230 and at least one oil replenishing groove 220 . The main body 210 includes an end surface 211 , the shaft hole 230 penetrates through the main body 210 and allows the pivot shaft 120 to pass through. The at least one spacer 300 is located between the frame body 110 and the end surface 211 of the at least one planetary gear 200 . The at least one planetary gear 200 rotates relative to the at least one spacer 300 and the planet carrier 100 to change an overlapping range A1 between the at least one spacer 300 and the at least one oil replenishing groove 220 (shown in FIGS. 5 and 6 ). ) to press a lubricating oil into the aforementioned at least one oil replenishing groove 220 .

In this way, the lubricating oil can be actively pressed into the oil replenishing groove 220, and then flow into the shaft hole 230, so that the lubricating effect can be improved. Details of the gear reducer lubrication structure 10 will be described later.

The gear reducer lubricating structure 10 may further include a casing 400 and a sun gear shaft 600 . The casing 400 includes a plurality of internal teeth (not shown), and the planetary carrier 100 may be a cage-type planetary carrier, so the carrier body 110 may include a The cage portion 111 and an output shaft 112 , the cage portion 111 is located in the casing 400 , and the output shaft 112 is connected to the cage portion 111 and protrudes toward the outside of the casing 400 . The cage portion 111 includes a first setting surface 1111 and a second setting surface 1112 which are arranged at intervals and are opposite to each other. The number of at least one pivot shaft 120 in the front can be three and the first setting surface 1111 and the second setting surface are arranged at intervals. Between 1112 and 1112 , the number of the aforementioned at least one planetary gear 200 is also three and is respectively pivoted on the three pivot shafts 120 and located between the first setting surface 1111 and a second setting surface 1112 , and the three planetary gears 200 are engaged with each other. on the inner teeth. The sun gear shaft 600 can be located in the cage portion 111 and engage with the three planetary gears 200 , so when the motor (not shown) drives the sun gear shaft 600 , the planetary gears 200 are linked to rotate to drive the planet carrier 100 to rotate relative to the housing 400 .

The gear reducer lubricating structure 10 may further include a plurality of rollers 500 , and the rollers 500 may be disposed between each shaft hole 230 and each pivot shaft 120 to reduce friction between the planetary gear 200 and the pivot shaft 120 .

Please refer to FIG. 4 , and please refer to FIGS. 2 and 3 together, wherein FIG. 4 is a partial cross-sectional schematic diagram of the lubricating structure 10 of the gear reducer according to the first embodiment of FIG. 1 . The body 210 of the planetary gear 200 may include a plurality of helical teeth (not shown) to engage with the sun gear shaft 600 and the internal teeth of the housing 400 , and the planetary gear 200 may include two oil supply grooves 220 on the end faces 211 on both sides, respectively corresponding to the first One setting surface 1111 and the second setting surface 1112, however, the number of the oil supply grooves 220 on one end surface 211 may be more than one, which is not intended to limit the present invention. The body 210 may further include a convex ring 240 located on the end face 211 and surrounding the shaft hole 230 . The convex ring 240 may be partially cut to form an oil supply groove 220 . As shown in FIG. 3 , only one oil supply groove 220 is located on the same end surface 211 . superior. The oil replenishment groove 220 is arc-shaped and has a center C1 , and the center C1 of the oil replenishment groove 220 is misaligned with a central axis I1 of the shaft hole 230 of the planetary gear 200 . The periphery of the oil replenishment groove 220 can be an arc with a center C1, so the oil replenishment groove 220 is actually an eccentric circle eccentric to the shaft hole 230. The oil replenishment groove 220 of this shape has the advantages of easy processing and short process time. In other embodiments, the oil replenishing groove may also have other shapes, which is not intended to limit the present invention.

When the planetary gear 200 is installed on the planet carrier 100, since the spacer 300 is located between the planetary gear 200 and the first setting surface 1111 or the second setting surface 1112, an oil-accommodating space S1 can be generated to accommodate lubricating oil. In order to increase the oil accommodating space S1, the planet carrier 100 may further include at least one recess 130 located in the carrier body 110, and in the first embodiment, the number of recesses 130 may be six, wherein three recesses 130 are arranged at intervals in the first setting On the surface 1111 , the other three recesses 130 are arranged at intervals on the second setting surface 1112 , the number of the aforementioned at least one spacer 300 is six, and each spacer 300 is located in each recess 130 . The area of the concave portion 130 is larger than that of the spacer 300 , and a depth D1 of the concave portion 130 may be smaller than a thickness D2 of the spacer 300 . In other words, when the spacer 300 is located on the concave portion 130 , the spacer 300 will protrude out of the concave portion. 130. A first radial length L1 (marked in FIG. 5 ) of the gasket 300 may be approximately equal to an outer radius of the convex ring 240 , and the first radial length L1 is the distance between the peripheral edge of the gasket 300 and the central axis I1 of the shaft hole 230 . Maximum vertical distance. Under this structure, the oil accommodating space S1 between the end surface 211 and the concave portion 130 can be enlarged, which is helpful for accommodating more lubricating oil.

In the first embodiment, the gasket 300 may be fixed on the first setting surface 1111 and the second setting surface 1112, but in other embodiments, the gasket 300 may also be fitted on the first setting surface and the second setting surface grooves for the gasket to fit, but not limited to this.

Please refer to Fig. 5 and Fig. 6, wherein Fig. 5 shows a schematic front view of the planetary gear 200 and the spacer 300 of the first embodiment of Fig. 1, and Fig. 6 shows the planet of the first embodiment of Fig. 1 Another schematic front view of the gear 200 and the spacer 300 . Initially, the overlapping range A1 of the planetary gear 200 and the gasket 300 is as shown in FIG. 5 . At this time, the gasket 300 is exposed from the arc top of the oil supply groove 220 , and the lubricating oil can flow into the oil supply tank 220 from the arc top, but is limited by Due to the viscous force of the lubricating oil, it is difficult for the lubricating oil to penetrate into the interior of the oil replenishing groove 220 . When the planetary gear 200 rotates in the direction R1 relative to the washer 300, the overlapping range A1 of the planetary gear 200 and the washer 300 is changed as shown in FIG. The pressure, thereby pressing the lubricating oil into the oil replenishing groove 220 , can help to allow the lubricating oil to penetrate deep into the oil replenishing groove 220 and flow into the shaft hole 230 . It should be noted here that, because the planetary gear 200 is a helical gear structure, an axial thrust can be generated to squeeze the lubricating oil and the gasket 300 during rotation, which can further help improve the oil replenishment capacity.

In addition, as shown in FIG. 5 and FIG. 6, the gasket 300 may be approximately a truncated triangle, the first radial length L1 of the gasket 300 may be greater than or equal to the second radial length L2 of the oil supply groove 220, and the second radial length L1 of the gasket 300 The radial length L2 is the maximum vertical distance between the periphery of the oil replenishing groove 220 and the central axis I1 of the shaft hole 230 . In this configuration, the ability of the gasket 300 to press lubricating oil into the oil charge sump 220 can be improved.

Please refer to FIG. 7 and FIG. 8, wherein FIG. 7 shows a schematic front view of the planetary gear 200a and the washer 300a of a lubricating structure of a gear reducer according to a second embodiment of the present invention, and FIG. 8 shows the first 7 is another schematic front view of the planetary gear 200a and the spacer 300a of the second embodiment. The planetary gear 200a includes an oil replenishment groove 220a, and the structure of the oil replenishment groove 220a is the same as that of the oil replenishment groove 220 in FIGS. 2 to 6, and will not be described again. The gasket 300a can be roughly in the shape of a notched disc and includes three notches 310a. The notches 310a are matched with the oil replenishing groove 220a to produce the oil replenishing effect.

Please refer to FIG. 9, wherein FIG. 9 is a schematic front view of the planetary gear 200b and the washer 300b of a lubricating structure of a gear reducer according to a third embodiment of the present invention. The planetary gear 200b includes an oil supply groove 220b, and the spacer 300b can also be generally elliptical.

Please refer to FIG. 10. FIG. 10 is a schematic front view of a planetary gear 200c and a gasket 300c of a lubricating structure for a gear reducer according to a fourth embodiment of the present invention. The planetary gear 200c includes two oil supply grooves 220c arranged symmetrically, and the gasket 300c can also be roughly rectangular with arc edges on both sides.

It should be noted here that the above-mentioned gaskets 300, 300a, 300b, 300c can be made by stamping and forming, and can be configured in any shape, and the gaskets 300, 300a, 300b, 300c can be made of wear-resistant materials , in order to increase the lifespan, but the above description is only one of the possible implementations, and does not limit the present invention.

Although the present invention has been disclosed as above with examples, it is not intended to limit the present invention. Anyone skilled in the art can make various changes and modifications without departing from the spirit and scope of the present invention. Therefore, the protection of the present invention The scope shall be determined by the scope of the appended patent application.

10: Gear reducer lubrication structure 100: Planet carrier 110: Frame 111: Cage Department 1111: The first setting surface 1112: Second setting surface 112: output shaft 120: Pivot 130: Recess 200, 200a, 200b, 200c: Planetary gears 210: Ontology 211: End face 220, 220a, 220b, 220c: Refill tank 230: Shaft hole 240: convex ring 300, 300a, 300b, 300c: Gaskets 400: Shell 500: Roller 600: sun gear shaft 310a: Notch A1: Overlap range C1: center of circle D1: depth D2: Thickness I1: central axis L1: first radial length L2: Second radial length R1: Direction S1: oil storage space

FIG. 1 is a three-dimensional schematic view of a lubricating structure of a gear reducer according to a first embodiment of the present invention; FIG. 2 is a partial perspective view of the lubrication structure of the gear reducer according to the first embodiment of FIG. 1; FIG. 3 is a schematic diagram of the pivot, rollers, planetary gears and spacers according to the first embodiment of FIG. 1; FIG. 4 is a schematic partial cross-sectional view of the lubrication structure of the gear reducer according to the first embodiment of FIG. 1; FIG. 5 is a schematic front view of the planetary gear and the washer according to the first embodiment of FIG. 1; Fig. 6 is another schematic front view of the planetary gear and the spacer of the first embodiment of Fig. 1; FIG. 7 is a schematic front view of a planetary gear and a washer of a lubricating structure for a gear reducer according to a second embodiment of the present invention; Fig. 8 shows another schematic front view of the planetary gear and the spacer of the second embodiment of Fig. 7; FIG. 9 is a schematic front view of a planetary gear and a spacer of a lubricating structure for a gear reducer according to a third embodiment of the present invention; and FIG. 10 is a schematic front view of a planetary gear and a washer of a lubricating structure for a gear reducer according to a fourth embodiment of the present invention.

120: Pivot

200: Planetary gear

210: Ontology

211: End face

220: Oil replenishment tank

230: Shaft hole

240: convex ring

300: Gasket

500: Roller

Claims (10)

A gear reducer lubrication structure, comprising: a planetary carrier, containing: a body; and at least one pivot is arranged on the frame body; At least one planetary gear, pivoted on the planetary carrier and including: a body, including one end face; a shaft hole, penetrating through the body and allowing the at least one pivot shaft to pass through; and at least one oil replenishing groove, disposed on the end face and communicating with the shaft hole; and at least one washer located between the frame body and the end face of the at least one planetary gear; Wherein, the at least one planetary gear rotates relative to the at least one gasket and the planet carrier to change an overlapping range of the at least one gasket and the at least one oil replenishment groove, so as to press a lubricating oil into the at least one oil replenishment groove. The lubricating structure of the gear reducer according to claim 1, wherein the at least one oil supply groove is arc-shaped and has a center, and the center of the at least one oil supply groove and a center of the shaft hole of the at least one planetary gear Axial misalignment. The lubricating structure of the gear reducer according to claim 1, wherein the at least one spacer is approximately in the shape of a truncated triangle. The lubricating structure of the gear reducer according to claim 1, wherein the at least one spacer is generally oval. The lubricating structure of the gear reducer according to claim 1, wherein the at least one spacer is generally in the shape of a notched disc. The lubricating structure of the gear reducer according to claim 1, wherein the main body further comprises a convex ring located on the end face and surrounding the shaft hole, the convex ring is partially cut to form the at least one oil supply groove. The lubricating structure of the gear reducer according to claim 6, wherein a first radial length of the at least one washer is approximately equal to an outer edge radius of the convex ring, and the first radial length is equal to the at least one washer The maximum vertical distance between the peripheral edge and a central axis of the shaft hole. The lubricating structure of the gear reducer according to claim 1, wherein the planet carrier further comprises: at least one recess located on the frame body; Wherein, the at least one gasket is located in the at least one recess. The lubricating structure of the gear reducer according to claim 8, wherein a depth of the at least one recess is smaller than a thickness of the at least one gasket. The lubricating structure of the gear reducer according to claim 1, wherein a first radial length of the at least one gasket is greater than or equal to a second radial length of the at least one oil supply groove, and the first radial length is The maximum vertical distance between the peripheral edge of the at least one gasket and a central axis of the shaft hole, and the second radial length is the maximum vertical distance between the peripheral edge of the at least one oil supply groove and the central axis.

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