JP2010230025A - Lubricating structure of bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubricating structure of a bearing, in which a lubricating life can be simply extended, thus attaining labor saving in maintenance with the bearing unassembled. <P>SOLUTION: As shown in (A), in an initial status, a fluid pressure cylinder part 21 is closely filled up with operation grease G<SB>H</SB>. When the operation grease G<SB>H</SB>flows into a fluid pressure cylinder part 21, the internal pressure in a cylinder chamber 21b increases, and also fluid pressure applied to a receiving part 21d of a piston part 21c increases. Therefore, the piston part 21c starts to advance into the cylinder chamber 21b, the piston part 21c presses an extension part 19e to transmit driving force, and the movable member 19 starts to move in a direction separating from the bearing 12. As a result, as shown in (B), grease G<SB>O</SB>after deterioration moves together with the movable member 19 in a state retained in a retainer 19a, and a gap between the tip surface of the retainer 19a and the end surface of the bearing 12 is gradually filled up with non-deteriorated grease G<SB>N</SB>. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a lubricating structure of a bearing that lubricates the bearing with a semi-solid lubricant.

  Conventionally, in order to lubricate the bearing, in addition to sealing the grease inside the bearing, a grease reservoir is provided in the vicinity of the bearing, and this grease reservoir is filled with grease. Since the maintenance of the bearings of the main motor of a railway vehicle is very troublesome, it is desired to save labor. In general, since the bearing of the main motor is often used at high rotation and high temperature, the deterioration of grease (lubricant) is promoted, and the lubrication life is reached relatively early due to wear of the bearing. Therefore, in the initial stage, the grease reservoir is filled with grease leaving a certain amount of space, and an intermediate greasing that additionally fills this space with grease after a certain amount of time has elapsed (for example, when traveling for 600,000 km) The method called is being implemented.

  The conventional lubrication structure of the bearing is a movable structure that moves in the filling chamber in a direction away from the bearing in order to form a space for filling undegraded grease between the deteriorated grease in the filling chamber and the bearing. A plate is provided (see, for example, Patent Document 1). In such a conventional bearing lubrication structure, for example, a structure in which the bag body is contracted by fluid pressure in the filling chamber to move the movable plate, or the movable plate is moved by manually or automatically rotating the feed screw mechanism. A structure in which the movable plate is moved by the biasing force of the spring after releasing the stopper, a structure in which the movable plate is moved by pulling a string, or the like is used.

JP 2007-285517 A

  In the conventional bearing lubrication structure, when the movable plate is moved manually, an operation part for opening and closing the discharge port for discharging the fluid from the bag body, an operation part for operating the feed screw mechanism part, An operation part for releasing the spring stopper, an operation part for pulling the string, and the like need to be provided outside the bearing lid, and the operation part needs to be manually operated from the outside of the bearing lid. Further, in the conventional bearing lubrication structure, when the movable plate is automatically moved, it is necessary to provide a motor for rotationally driving the feed screw mechanism on the outside of the bearing lid. However, with the conventional bearing lubrication structure, when it is difficult to secure sufficient working space or installation space outside the bearing lid, intermediate lubrication is easily performed with the main motor bearing remaining in a non-disassembled state. There was a problem that could not be done. For example, in a conventional bearing lubrication structure, there is only a slight gap outside the bearing lid with the main motor mounted on the carriage, and even if the operation portion of the feed screw mechanism is rotated by a tool, the outside of the bearing lid It was impossible to insert a tool into the gap. In the conventional bearing lubrication structure, for example, when the movable plate is driven by the feed screw mechanism, the operating portion is passed through the through hole of the bearing lid, and a seal material or the like is provided between the through hole and the operating portion. To prevent the grease from leaking between them. However, in such a conventional bearing lubrication structure, there is a problem that if the forgetting to seal with the sealing material before and after the intermediate lubrication work, the grease leaks out from the bearing lid and causes a problem in lubrication. .

  An object of the present invention is to provide a lubrication structure for a bearing that can easily extend the lubrication life in a non-disassembled state and save labor for maintenance.

The present invention solves the above-mentioned problems by the solving means described below.
In addition, although the code | symbol corresponding to embodiment of this invention is attached | subjected and demonstrated, it is not limited to this embodiment.
As shown in FIGS. 4 and 10, the invention of claim 1 is a bearing lubrication structure for lubricating a bearing (12, 13) with a semi-solid lubricant (G), and the semi-solid lubricant is A driving force is generated by the movable part (19; 19A, 19B) moving in the filling chamber (14a) to be filled and the fluid pressure of the working fluid ( _GH ), and this driving force is transmitted to the movable part. The bearing lubrication structure (18) includes a fluid pressure cylinder portion (21; 21A, 21B) for driving the movable portion.

According to a second aspect of the present invention, there is provided a lubricating structure for a bearing according to the first aspect, wherein the movable portion separates the deteriorated semi-solid lubricant (G _O ) from the bearing. It is.

According to a third aspect of the present invention, there is provided a lubricating structure for a bearing according to the first or second aspect, wherein the movable part moves in the filling chamber, thereby causing semi-solid lubrication after deterioration on the side close to the bearing. The bearing lubrication structure is characterized in that the agent (G _O ) is separated from the bearing and the undegraded semi-solid lubricant (G _N ) on the side far from the bearing is brought close to the bearing.

  According to a fourth aspect of the present invention, in the lubricating structure for a bearing according to any one of the first to third aspects, the fluid pressure cylinder portion generates the driving force outside the filling chamber, and from the outside of the filling chamber. The bearing lubricating structure is characterized in that the driving force is transmitted to the movable part.

  According to a fifth aspect of the present invention, in the lubrication structure for a bearing according to any one of the first to fourth aspects, the fluid pressure cylinder portion receives a fluid pressure of the working fluid and receives a cylinder chamber (21a). The bearing lubrication structure is characterized in that the driving force is transmitted to the movable part through a piston part (21c) driven inside.

  According to a sixth aspect of the present invention, in the lubrication structure for a bearing according to any one of the first to fifth aspects, the fluid pressure cylinder portion is formed of the movable portion as shown in FIGS. The bearing lubrication structure includes a cylinder side fitting portion (21e) fitted to the movable portion side fitting portion (19f).

According to a seventh aspect of the present invention, in the lubricating structure of the bearing according to the sixth aspect, the fluid pressure cylinder portion is a gap portion (Δ ₁₁ ) between the movable portion side fitting portion and the cylinder side fitting portion. A lubricating structure for a bearing, characterized by comprising:

  According to an eighth aspect of the present invention, in the lubricating structure for a bearing according to the sixth or seventh aspect, as shown in FIG. 9, the cylinder side fitting portion has a convex or concave tapered surface (21g). The movable portion side fitting portion has a concave or convex tapered surface (19h) that fits with the tapered surface of the cylinder side fitting portion.

  According to a ninth aspect of the present invention, in the lubricating structure for a bearing according to any one of the first to eighth aspects, the movable portion has a central axis of the movable portion as shown in FIG. The bearing lubrication structure is characterized in that a plurality of the fluid pressure cylinder portions are arranged so that the driving force acts on the movable portion at a plurality of locations. It is.

  A tenth aspect of the present invention is the bearing lubrication structure according to any one of the first to ninth aspects, wherein the fluid pressure cylinder portion is configured such that the driving force acts equally on the movable portion at a plurality of locations. Thus, the bearing lubrication structure is characterized in that the movable part is driven.

  An eleventh aspect of the present invention is the bearing lubrication structure according to any one of the first to tenth aspects, wherein the fluid pressure cylinder portion has the driving force at equal intervals in the circumferential direction of the movable portion. A bearing lubrication structure is characterized in that the movable part is driven to act.

  A twelfth aspect of the present invention is the bearing lubrication structure according to any one of the first to eleventh aspects, wherein the fluid pressure cylinder portion is point-symmetrical with respect to a central axis of the movable portion. In this bearing lubrication structure, the movable portion is driven so that the driving force acts on the movable portion.

  According to a thirteenth aspect of the present invention, in the lubricating structure for a bearing according to any one of the first to eleventh aspects, as shown in FIGS. 4 and 10, the filling chamber is located outside the filling chamber. The outer filling chamber (14c) formed in an enlarged manner is provided, the movable part is provided with an extension part (19e) extending from the outer peripheral part of the movable part into the outer filling chamber, and the fluid pressure cylinder part is provided with the extension. The lubricating structure of the bearing is characterized in that the movable part is driven by driving the part.

  According to a fourteenth aspect of the present invention, in the lubricating structure for a bearing according to any one of the first to thirteenth aspects, as shown in FIG. 10, the movable portion is formed from the one end face side of the bearing. A first movable part (19A) that moves in the filling chamber for supplying the semisolid lubricant, and a second movable part that moves in the filling chamber for supplying the semisolid lubricant from the other end face side of the bearing. (19B), and the fluid pressure cylinder part includes a first fluid pressure cylinder part (21A) for driving the first movable part and a second fluid pressure cylinder for driving the second movable part. A bearing lubrication structure comprising: a portion (21B).

  According to a fifteenth aspect of the present invention, in the lubricating structure for a bearing according to the fourteenth aspect, a supply flow path for supplying the working fluid from the outside to the first fluid pressure cylinder portion and the second fluid pressure cylinder portion ( 22) a lubricating structure for a bearing.

  According to a sixteenth aspect of the present invention, in the lubricating structure for a bearing according to the fourteenth or fifteenth aspect, as shown in FIG. 11, the pressure receiving portions (21d) of the first and second fluid pressure cylinder portions are provided with the pressure receiving portions (21d). A contact prevention portion (23) is provided that forms a predetermined gap portion between these pressure receiving portions to prevent the pressure receiving portions from coming into close contact so that the fluid pressure of the working fluid acts. It is a lubrication structure of a bearing.

  According to a seventeenth aspect of the present invention, in the lubrication structure for a bearing according to the fifteenth aspect, as shown in FIGS. 12 and 13, the first and second fluid pressure cylinder portions have a pressure receiving portion (21d having the same area). And a fluid pressure acting part (24A to 24C) for simultaneously acting the working fluid on the pressure receiving parts of the first and second fluid pressure cylinder parts. .

According to an eighteenth aspect of the present invention, in the lubrication structure for a bearing according to the seventeenth aspect, the fluid pressure acting portion is a pressure receiving portion on the first fluid pressure cylinder portion side and a pressure receiving portion on the second fluid pressure cylinder portion side. A lubricating structure for a bearing, wherein a predetermined gap (Δ ₁₂ ) is formed between the first and second portions.

  According to a nineteenth aspect of the present invention, in the lubricating structure for a bearing according to any one of the first to eighteenth aspects, the fluid pressure cylinder portion operates in the same type as the semi-solid lubricant in the filling chamber. A lubrication structure for a bearing, wherein the movable part is driven by fluid pressure of fluid.

  According to the present invention, it is possible to easily extend the lubrication life in a non-decomposed state and save labor for maintenance.

It is sectional drawing of an electric motor frame provided with the lubricating structure of the bearing which concerns on 1st Embodiment of this invention, and a shaft. It is a top view of the bearing cover provided with the lubricating structure of the bearing which concerns on 1st Embodiment of this invention, (A) is the top view seen from the IIA direction of FIG. 1, (B) is from the IIB direction of FIG. It is the top view seen, (C) is the top view seen from the IIC direction of FIG. 1, (D) is the top view seen from the IID direction of FIG. BRIEF DESCRIPTION OF THE DRAWINGS It is an external view of the bearing cover provided with the lubricating structure of the bearing which concerns on 1st Embodiment of this invention, (A) is a top view, (B) (C) is the III-IIIB line | wire of FIG. 3 (A). It is sectional drawing which shows the state cut | disconnected. It is sectional drawing which expands and shows IV part of FIG. 3 (B), (A) is sectional drawing of an initial state, (B) is sectional drawing after replacement | exchange lubrication. It is sectional drawing which expands and shows the V section of FIG. 4, (A) is sectional drawing of an initial state, (B) is sectional drawing after replacement | exchange grease. It is sectional drawing which shows the state cut | disconnected by the VI-VI line of FIG. 3 (A). It is sectional drawing which shows the state cut | disconnected by the VII-VII line of FIG. It is a perspective view which shows typically the flow path of the working fluid of the lubricating structure of the bearing which concerns on 1st Embodiment of this invention. It is sectional drawing of the fluid pressure cylinder part of the lubricating structure of the bearing which concerns on 2nd Embodiment of this invention, (A) is sectional drawing which shows a fitting state when a movable part is displaced below, B) is a cross-sectional view showing a fitting state when the movable portion is displaced upward. It is sectional drawing of the fluid pressure cylinder part of the lubricating structure of the bearing which concerns on 3rd Embodiment of this invention, (A) is sectional drawing of an initial state, (B) is sectional drawing after replacement | exchange lubrication. It is sectional drawing which expands and shows the XI part of FIG. 10, (A) is sectional drawing of an initial state, (B) is sectional drawing after replacement | exchange lubrication. It is sectional drawing of the fluid pressure cylinder part of the lubricating structure of the bearing which concerns on 4th Embodiment of this invention, (A) is sectional drawing in case a fluid pressure action part is cylindrical, (B) is fluid pressure. It is sectional drawing in case an action part is conical. It is sectional drawing of the fluid pressure cylinder part of the lubricating structure of the bearing which concerns on 5th Embodiment of this invention, (A) is sectional drawing in case a fluid pressure action part is conical, (B) is fluid pressure. It is sectional drawing in case an action part is planar. It is sectional drawing of an electric motor frame provided with the lubricating structure of the bearing which concerns on 6th Embodiment of this invention, and a shaft.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a cross-sectional view of an electric motor frame body and shaft provided with a bearing lubrication structure according to a first embodiment of the present invention.
The shaft 1 is a member that transmits the power of the main motor to the wheels via a gear and an axle (not shown). The motor frame 2 is a frame (housing) that fixes and supports the stator of the main motor and rotatably supports the rotor of the main motor. The frame 3, the brackets 4 and 5, and the greasing plug 6, 7, collars 8 to 11, bearings 12 and 13, bearing lids (end lids) 14 to 17, and the like.

The frame 3 is a member that fixes and supports the stator of the electric motor, and flange portions 3a and 3b are formed at both ends. The bracket 4 is a member that connects the frame 3 and the bearing lid 16, and a flange portion 4 a that is joined to the flange portion 3 a and a flow path through which the operating grease _GH flows when the operating grease _GH is filled. 4b and the like. The bracket 5 is a member that connects the frame 3 and the bearing lid 17 and includes a flange portion 5a that is joined to the flange portion 3b. The greasing plugs 6 and 7 are members that are screwed into the inflow ports of the flow paths 4b and 17d, respectively, so as to close the inflow ports. The greasing plugs 6 and 7 are formed inside these inflow ports. A male screw portion that meshes with the female screw portion thus formed is formed. The collars 8 to 11 are annular members that are fitted into both end portions of the shaft 1. The bearings 12 and 13 are rolling bearings that rotatably support the shaft 1, the bearing 12 is a ball bearing, and the bearing 13 is a roller bearing. The bearings 12 and 13 include rolling elements 12a and 13a, retainers 12b and 13b that hold the rolling elements 12a and 13a at equal intervals, outer rings 12c and 13c that rotate outside the retainers 12b and 13b, Inner rings 12d and 13d rotating inside the cages 12b and 13b are provided. Since the bearings 12 and 13 generate heat due to the heat of stirring of the grease G when the grease G is excessively packed therein, the grease G is generally packed about 1/3 of the space volume in the initial state.

  FIG. 2 is a plan view of a bearing lid provided with the bearing lubrication structure according to the first embodiment of the present invention, and FIG. 2 (A) is a plan view seen from the IIA direction of FIG. ) Is a plan view seen from the IIB direction in FIG. 1, FIG. 2C is a plan view seen from the IIC direction in FIG. 1, and FIG. 2D is a plan view seen from the IID direction in FIG. It is. FIG. 3 is an external view of a bearing lid having a bearing lubrication structure according to the first embodiment of the present invention, FIG. 3 (A) is a plan view, and FIGS. 3 (B) and 3 (C) are FIG. It is sectional drawing which shows the state cut | disconnected by the III-IIIB line of A). 4 is an enlarged cross-sectional view of the IV portion of FIG. 3B, FIG. 4A is a cross-sectional view in an initial state, and FIG. 4B is a cross-sectional view after replacement lubrication. is there. FIG. 5 is an enlarged cross-sectional view showing a portion V in FIG. 4, FIG. 5 (A) is a cross-sectional view in an initial state, and FIG. 5 (B) is a cross-sectional view after replacement lubrication. FIG. 6 is a cross-sectional view showing a state cut along line VI-VI in FIG. 7 is a cross-sectional view showing a state cut along line VII-VII in FIG. FIG. 8 is a perspective view schematically showing the flow path of the working fluid in the lubricating structure of the bearing according to the first embodiment of the present invention.

  The bearing lids 14 and 16 shown in FIG. 1 are members for fixing the bearing 12, and the bearing lids 15 and 17 are members for fixing the bearing 13. The bearing lids 14 and 15 are cast or machined parts made of aluminum, iron, or the like. The bearing lids 14 and 15 are attached to the outside of the electric motor frame 2, and the bearing lids 16 and 17 are attached to the inner side of the electric motor frame 2. Has been. The bearing lid 14 is fixed to the bearing lid 16 with bolts so as to sandwich the bearing 12 between the bearing lid 16 and the bearing lid 15 is fixed to the bearing lid 17 with bolts so as to sandwich the bearing 13. The bearing lids 14 to 17 include a lubrication structure 18. The bearing lids 14 and 15 have substantially the same structure as shown in FIGS. 2A and 2D, and the bearing lids 16 and 17 have substantially the same shapes as shown in FIGS. It is the same structure. The bearing lid 14 includes a filling chamber 14a shown in FIGS. 1 and 3B, 3C, a holding portion 14d shown in FIGS. 2A and 3A, through holes 14e and 14f, and FIG. 14g, the escape part 14h, etc. are provided. Hereinafter, the bearing lids 14 and 16 side will be described, and the bearing lids 15 and 17 side portions will be denoted by reference numerals corresponding to the bearing lid 14 and 16 side portions, and detailed description thereof will be omitted.

  The filling chamber 14a shown in FIGS. 3B and 3C is a portion filled with grease G for lubricating the bearing 12, and includes an annular filling chamber (first grease reservoir) 14b and an outer filling chamber (second grease). (Reservoir) 14c and the like. As shown in FIGS. 3B and 3C, the filling chamber 14 a has a quadrangular cross-sectional shape when cut in the radial direction of the bearing lid 14.

The annular filling chamber 14 b is a portion that is filled with grease G for lubricating the bearing 12. The annular filling chamber 14b is formed along the gap (bearing opening) between the outer ring 12c and the inner ring 12d shown in FIG. 1, and is filled as shown in FIGS. 2 (A) and 3 (A). It is a concave groove portion formed in an annular shape so as to surround the through hole 14e in the chamber 14a. Annular plenum 14b, as shown in FIG. 4, in the grease filling chamber of the piston system capable replacement grease after deterioration (grease after use) G _O and undegraded grease and (unused grease) G _N is there. As shown in FIGS. 3B and 3C, the annular filling chamber 14 b has an opening on the end face side of the bearing 12. As shown in FIG. 3A, the outer filling chamber 14c is formed to extend outside the annular filling chamber 14b along the annular filling chamber 14b, and is coupled to a part of the annular filling chamber 14b. It is a concave groove. As shown in FIGS. 3B and 3C, the outer filling chamber 14c has an opening on the end face side of the bearing 12 like the annular filling chamber 14b. The holding part 14d shown in FIGS. 2 (A) and 3 (A) is a part that holds down the end face of the outer ring 12c, and is spaced from the outer peripheral part of the annular filling chamber 14b along the circumferential direction of the annular filling chamber 14b. Four are formed. A through hole 14e shown in FIGS. 2A and 3A is an insertion hole for inserting the collar 8 shown in FIG. 1, and the through hole 14f is a bolt for fixing the bearing lid 14 to the bearing lid 16. An insertion hole to be inserted. 4 is a portion formed between the annular filling chamber 14b and the outer filling chamber 14c, partitions the annular filling chamber 14b and the outer filling chamber 14c, and allows the movable portion 19 to move freely. To guide. The escape portion 14h is a portion that prevents the wall portion 14g and the reinforcing portion 19g from interfering with each other, and two escape portions 14h are formed corresponding to the extension portion 19e so as to cut out the end portion of the wall portion 14g.

The bearing lid 16 includes an annular filling chamber 16a shown in FIG. 2B, a restraining portion 16b, a through hole 16c, a flow path 16f, and the like. The annular filling chamber 16 a is a portion that is filled with grease G for lubricating the bearing 12. The annular filling chamber 16a is a recess formed in an annular shape so as to surround the through hole 16c, which is formed along the gap between the outer ring 12c and the inner ring 12d. 2B is a portion that suppresses the end face of the outer ring 12c of the bearing 12, and the through hole 16c is an insertion hole into which the collar 9 shown in FIG. 1 is inserted. The flow path 16f is a portion into which the working grease _GH flows when the working grease _GH is filled, and one end (upstream side) is connected to the flow path 4c of the bracket 4 and the other end. The part (downstream side) is connected to the flow path 22.

The lubrication structure 18 shown in FIG. 1 is a structure that lubricates the bearings 12 and 13 with grease G. The lubrication structure 18 lubricates the bearings 12 and 13 by supplying the grease G sealed in the annular filling chambers 14b and 15b to the bearings 12 and 13, and in the annular filling chambers 14b and 15b as shown in FIG. grease G _O after the deterioration of the interchanged with grease G _N of the non-deteriorated lubricating the grease G _N of the non-deteriorated. The lubrication structure 18 includes a movable portion 19 shown in FIG. 4, a discharge portion 20, a fluid pressure cylinder portion 21, a flow path 22 shown in FIGS. 7 and 8, and the like.

The movable part 19 shown in FIGS. 4 and 6 is a part that moves in the filling chamber 14a in which the grease G is filled. The movable portion 19, by moving in the filling chamber 14a, the grease G _O after side degradation near the bearing 12 away from the bearing 12, the bearing 12 of the grease G _N of undegraded remote from the bearing 12 close to, replacing the grease G _N of the grease G _O and undegraded after deterioration in charging chamber 14a. The movable part 19 is an annular member whose central axis is the same as the central axis of the bearing 12. In the initial state shown in FIGS. 4 (A) and 6 (A), the movable portion 19 divides the annular filling chamber 14b into two regions, a side closer to the bearing 12 and a side far from the bearing 12, and FIG. 4 (B) and FIG. 6 (B) and 6 (C) are partition plates that move in the annular filling chamber 14b during replacement lubrication. As shown in FIG. 4, the movable portion 19 is fitted between the outer inner peripheral surface and the inner inner peripheral surface of the annular filling chamber 14 b, and is movably guided by these. The movable portion 19 is in the initial state shown in FIGS. 4 (A) and FIG. 6 (A), the a region for accommodating the grease G _O after deterioration, the annular packing chamber 14b in the area that houses the grease G _N of undegraded Is partitioned. The movable portion 19 is formed in an annular shape from a synthetic resin or metal material such as polyamide resin having heat resistance and oil resistance, fiber reinforced plastic, or the like, and the movable portion 19 is cut in the radial direction. It is a movable plate with a groove whose cross-sectional shape is concave. As shown in FIGS. 4 (B), 6 (B), and 6 (C), the movable portion 19 is not deteriorated by the surface (back surface) opposite to the bearing 12 side by moving away from the bearing 12. the grease G _N pressurized to fat feeding replacement extruded grease G _N of the non-deteriorated between the tip surface and the end face of the bearing 12 of the holding portion 19a. The movable portion 19 includes a holding portion 19a shown in FIGS. 4 and 6, a passage portion 19b shown in FIG. 3, guide portions 19c and 19d shown in FIGS. 4 and 6, an extension portion 19e shown in FIG. 4 and FIG. 5 includes a movable portion side fitting portion 19f and a reinforcing portion 19g shown in FIG.

Holding portion 19a shown in FIGS. 4 and 6, a part for holding the grease G _O after degradation. Holding portion 19a holds so as to sandwich the grease G _O after degradation between the inner and outer circumferential surfaces of the guide portion 19d of the guide portion 19c, FIG. 4 (B) and FIG. 6 (B) ( It moves away from the bearing 12 in a state in holding the grease G _O after the degradation as shown in C). The holding portion 19a has an opening on the bearing 12 side, and a cross-sectional shape when the movable portion 19 is cut in the radial direction is formed in a substantially U shape.

  The passage portion 19b shown in FIG. 3 is a portion connecting the outer filling chamber 14c and the annular filling chamber 14b. The passage portion 19b allows the grease G or the lubricating oil to pass through so that the grease G or the lubricating oil that has exuded from the grease G can move from the outer filling chamber 14c to the annular filling chamber 14b. As shown in FIG. 3 (A), the passage portion 19b is formed at four locations in the circumferential direction of the guide portion 20b corresponding to the outer filling chamber 14c, and as shown in FIGS. 3 (B) and (C). It is a notch part formed in the edge part of the guide part 20b.

  Guide portions 19c and 19d shown in FIG. 4 are portions that guide the movable portion 19 to be movable. The guide portion 19c is movably guided to the outer peripheral portion of the annular filling chamber 14b and the inner peripheral portion of the wall portion 14g, and the guide portion 19d is movably guided to the inner peripheral portion of the annular filling chamber 14b. Has been. The guide portions 19c and 19d are cylindrical guide surfaces that are centered on the central axis of the bearing lid 14 so that the movable portion 19 moves in the central axis direction of the bearing lid 14. The guide portions 19c and 19d prevent the movable portion 19 from being inclined when the movable portion 19 moves in the annular filling chamber 14b. The guide portion 19c is formed so as to always be in surface contact with the outer peripheral surface of the annular filling chamber 14b, and the guide portion 19d is always in surface contact with the inner peripheral surface of the annular filling chamber 14b. It is formed with the same length. The outer peripheral surface of the guide portion 19c is fitted to the outer peripheral surface of the annular filling chamber 14b so as to be in close contact with the outer inner peripheral surface of the annular filling chamber 14b, and the inner peripheral surface of the guide portion 19d is the annular filling chamber 14b. The annular filling chamber 14b is fitted to the outer peripheral surface so as to be in close contact with the outer inner peripheral surface.

  The extension portion 19e is a portion that extends outward from the outer peripheral portion of the movable portion 19. The thickness of the extension 19e is preferably as thin as possible within a range in which the strength of the extension 19e can be ensured so that the amount of grease in the outer filling chamber 14c does not decrease. As shown in FIG. 3A, for example, two extension portions 19e are arranged at equal intervals in the circumferential direction of the filling chamber 14a (point symmetry with respect to the central axis of the movable portion 19). 14c is extended. As shown in FIG. 4, the extension portion 19e is connected to the outer peripheral portion of the holding portion 19a near the bearing 12 (near the substantially U-shaped opening of the holding portion 19a) so as not to interfere with the wall portion 14g as much as possible. Has been.

The movable portion side fitting portion 19 f shown in FIG. 5 is a portion that fits with the cylinder side fitting portion 21 e of the fluid pressure cylinder portion 21. The movable portion side fitting portion 19f is a recess (through hole) formed in the extension portion 19e, and as shown in FIG. 5, the inner peripheral portion of the movable portion side fitting portion 19f and the outer periphery of the cylinder side fitting portion 21e. as predetermined gap delta ₁₁ is formed between the parts, the inner diameter of the movable portion engaging portions 19f is formed larger than the outer diameter of the cylinder-side engaging portion 21e.

  The reinforcement part 19g shown in FIG. 4 is a part which reinforces the connection part of the holding | maintenance part 19a and the extension part 19e. The reinforcing portion 19g is a rib or the like that reinforces the connection portion between the outer peripheral portion of the holding portion 19a and the base portion of the extension portion 19e, and the extension portion 19e bends when the fluid pressure cylinder portion 21 drives the extension portion 19e. Rigidity is given to the base part of the extension part 19e so that there is no. As shown in FIG. 4 (A), the reinforcing portion 19g is formed to face the end of the wall portion 14g. As shown in FIG. 4 (B), the movable portion 19 is provided at the bottom of the annular filling chamber 14b. When it moves, it contacts the escape portion 14h.

Figure 4 and the discharge unit 20 shown in FIG. 6, when the movable portion 19 moves in a direction away from the bearing 12, and the grease G _N of the non-deteriorated part to discharge toward the bearing 12, the movable portion 19 and the annular discharging the grease G _N of undegraded pressurized between the filling chamber 14b. Discharge unit 20, as shown in FIG. 6 (B), a flow path grease G _N of the non-deteriorated flows, grease G _N of the non-deteriorated discharges between the grease G _O and the bearing 12 after degradation . Discharge unit 20, when the movable portion 19 in a direction away from the bearing 12 has moved, the grease G _N of undegraded pressurized between the bottom surface of the rear annular chamber filled 14b of the movable portion 19 to the bearing 12 Discharge as shown by the two-dot chain line. As shown in FIG. 3 (A), the discharge portion 20 is disposed on the inner peripheral portion of the movable portion 19 with an interval in the circumferential direction of the movable portion 19, and a bearing as shown in FIG. 6 (B). discharging the grease G _N of the non-deteriorated toward the gap S ₁₁ between the retainer 12b and the inner ring 12d 12. For example, as shown in FIG. 3A, eight discharge units 20 are arranged at equal intervals in the circumferential direction of the movable unit 19 so as to be equidistant from the central axis of the bearing lid 14. As shown in FIGS. 4 and 6, the discharge unit 20 includes an inflow port 20a, a guide unit 20b, a discharge port 20c, and the like.

Inlet 20a is a portion which the grease G _N of the non-deteriorated flows, as the cross-sectional shape in the circumferential direction of the edge portion of the movable portion 19 (hole shape) is substantially rectangular, cutting out the movable portion 19 Is formed. As shown in FIG. 6B, when the movable part 19 moves in the direction away from the bearing 12 as shown in FIG. 6B, the inflow port 20a is undegraded under pressure between the movable part 19 and the annular filling chamber 14b. grease G _N flows.

Guide portion 20b shown in FIGS. 4 and 6, the grease G _N of the non-deteriorated a portion for guiding the grease G _N of the non-deteriorated to move toward the bearing 12, the wall portions raised toward the bearing 12 It is. As shown in FIGS. 4A and 6A, the guide portion 20b is formed at such a height that the position of the discharge port 20c and the end surface of the bearing 12 substantially coincide with each other in the initial state. ing. Guide portion 20b, as shown in FIG. 3 (A), the cross-sectional shape (hole shape) is long radially in the circumferential direction of the movable portion 19 when cut by a plane perpendicular to the direction of movement of the grease G _N of undegraded The guide portion 20b is formed in the same size from the inflow port 20a toward the discharge port 20c. As shown in FIGS. 4 and 6, the guide portion 20 b is formed perpendicular (straight) to the surface of the movable portion 19 on the bearing 12 side, and is cut in the radial direction and the circumferential direction of the movable portion 19. The cross section at the time is linear.

Outlet 20c is a portion for discharging the grease G _N of the non-deteriorated at a position opposite to the bearing 12, forms a slight gap between the retainer 12b of the bearing 12 as shown in FIGS. 4 and 6 As shown, the cage 12b faces the cage 12b. As shown in FIG. 3A, the discharge port 20c is formed in a substantially rectangular shape like the inflow port 20a.

The fluid pressure cylinder portion 21 shown in FIGS. 4 and 5 is a portion that generates a driving force by the fluid pressure of the working grease _GH and transmits the driving force to the movable portion 19 to drive the movable portion 19. . The fluid pressure cylinder part 21 prevents the working grease _GH from leaking from the fluid pressure cylinder part 21 to the filling chamber 14a and prevents the grease G from leaking from the filling chamber 14a to the fluid pressure cylinder part 21. For this purpose, as shown in FIG. 4, a driving force is generated outside the filling chamber 14a, and this driving force is transmitted from the outside of the filling chamber 14a to the movable portion 19. The fluid pressure cylinder portion 21 includes a cylinder body portion 21a, a cylinder chamber 21b, a piston portion 21c, a pressure receiving portion 21d, a cylinder side fitting portion 21e shown in FIG. .

The fluid pressure cylinder portion 21 transmits a driving force to the movable portion 19 through the piston portion 21c, and drives the movable portion 19 by driving the extension portion 19e. As shown in FIG. 4, the fluid pressure cylinder portion 21 is arranged outside the filling chamber 14a and separated from the filling chamber 14a, and the driving force acts on the movable portion 19 at a plurality of locations as shown in FIG. A plurality are arranged. As shown in FIGS. 7 and 8, the fluid pressure cylinder portion 21 is arranged so that the distance from the connection portion between the flow path 16 f and the flow path 22 to each fluid pressure cylinder portion 21 is equal, and is movable. The movable part 19 is driven so that the driving force acts equally on the part 19 at two locations. In the fluid pressure cylinder portion 21, a driving force is applied at equal intervals in the circumferential direction of the movable portion 19 in order to prevent the central axis of the movable portion 19 from being inclined with respect to the central axis of the bearing lid 14 during replacement lubrication. The movable part 19 is driven as described above. When the number of installed fluid pressure cylinder parts 21 is an even number, the fluid pressure cylinder part 21 is configured such that a driving force acts on the movable part 19 at a plurality of points symmetrical with respect to the central axis of the movable part 19. The movable part 19 is driven. The fluid pressure cylinder portion 21 drives the movable portion 19 by the fluid pressure of the same type of working grease _GH as the grease G in the filling chamber 14a. In the fluid pressure cylinder portion 21, for example, as shown in FIG. 8, the pressure receiving portion 21d of one piston portion 21c and the pressure receiving portion 21d of the other piston portion 21c are substantially in the same position in the axial direction of the piston portion 21c. Thus, the two piston portions 21c are arranged symmetrically with respect to the central axis of the cylinder body portion 21a.

  The cylinder body 21a shown in FIGS. 4 and 5 is a part constituting the body of the fluid pressure cylinder 21. The cylinder body 21a is formed in an annular shape from a synthetic resin or metal material such as polyamide resin having heat resistance and oil resistance, fiber reinforced plastic, or the like. As shown in FIG. 4, the cylinder body 21 a includes a through hole 21 f that fits with the outer ring 12 c of the bearing 12 and accommodates the bearing 12. As shown in FIG. 4, the cylinder body 21a is formed to have a thickness substantially the same as the thickness of the bearing 12. As shown in FIG. 1, both end faces of the cylinder body 21a are connected to the end face of the bearing lid 14 and the bearing. The cylinder body 21 a is sandwiched between the end surface of the lid 16 and the outer peripheral surface of the cylinder body 21 a is fitted to the inner peripheral surface of the bearing lid 16.

The cylinder chamber 21b shown in FIG.4 and FIG.5 is a part which accommodates the piston part 21c so that a movement is possible. As shown in FIG. 7, the cylinder chamber 21b is arranged point-symmetrically with respect to the central axis of the cylinder main body 21a, and on the end surface of the cylinder main body 21a on the bearing 12 side as shown in FIGS. It is a recess formed at a predetermined depth. The cylinder chamber 21b forms a fluid pressure working chamber into which the working grease _GH flows into a space (head side chamber) between the piston portion 21c and the pressure receiving portion 21d.

The piston portion 21c is a member that moves in the cylinder chamber 21b under the fluid pressure of the working grease _GH . The piston portion 21c is formed with a predetermined length so as to always come into surface contact with the inner peripheral surface of the cylinder chamber 21b within the movable range of the piston portion 21c when moving in the cylinder chamber 21b. The outer peripheral surface of the piston portion 21c is slidably in close contact with the inner peripheral surface of the cylinder chamber 21b to prevent the operating grease _GH from leaking from the cylinder chamber 21b to the filling chamber 14a and from the filling chamber 14a. The grease G is prevented from leaking into the cylinder chamber 21b. The piston portion 21c has an outer diameter of a portion corresponding to a piston rod of a normal cylinder mechanism such that the space between the outer peripheral surface of the piston portion 21c and the inner peripheral surface of the cylinder chamber 21b is sealed over a wide range. It is formed integrally with the piston rod so as to have the same outer diameter.

The pressure receiving portion 21d is a portion that receives the fluid pressure of the working grease _GH . The pressure receiving portion 21d is formed at the rear end portion (bottom portion) of the piston portion 21c so that the piston portion 21c moves forward when the fluid pressure of the working grease _GH is applied. The pressure receiving portion 21d is a planar pressure receiving surface formed perpendicular to the central axis of the bearing 12 (the central axis of the shaft 1).

The cylinder side fitting portion 21e shown in FIG. 5 is a portion that fits with the movable portion side fitting portion 19f of the extension portion 19e. The cylinder side fitting part 21e is a convex part (projection part) formed at the tip part of the piston part 21c, and when the fluid pressure of the working grease _GH acts on the pressure receiving part 21d, it presses the extension part 19e. The movable part 19 is moved.

The flow path 22 shown in FIG.7 and FIG.8 is a part which supplies the working grease _GH to the fluid pressure cylinder part 21 from the outside. As shown in FIG. 7, the flow path 22 is formed in the outer peripheral surface of the cylinder body 21 a along the circumferential direction, and an arc-shaped groove whose opening is closed by the inner peripheral surface of the bearing lid 16. And a linear through hole formed from the downstream side to the cylinder chamber 21b. As shown in FIGS. 1 and 8, one end (upstream side) of the flow path 22 is connected to the flow path 16f of the bearing lid 16, and the other end (downstream) as shown in FIGS. Side) is connected to the fluid pressure cylinder portion 21, and is open to the cylinder chamber 21 b of the fluid pressure cylinder portion 21. The flow path 22 is connected to the two fluid pressure cylinders from the connection portion between the flow path 16f and the flow path 22 so that the fluid pressure of the working grease _GH acts equally on the pressure receiving portions 21d of the two fluid pressure cylinder sections 21. It is formed so that the distances of the part 21 to the pressure receiving part 21d are equal and the flow rates of the working grease _GH flowing into the two fluid pressure cylinder parts 21 are equal.

Next, the operation of the bearing lubrication structure according to the first embodiment of the present invention will be described.
As shown in FIG. 2A, in an initial state, the annular filling chamber 14b is filled with grease G without any gap. Further, as shown in FIGS. 4A and 6A, grease G is filled between the movable portion 19 and the bearing 12, between the annular filling chamber 14b and the movable portion 19, and also in the outer filling chamber 14c. Has been. When air is sealed in the fluid pressure cylinder portion 21 shown in FIGS. 4 and 5 and the flow paths 4b, 16f, 17d, and 22 shown in FIG. 1, the working grease _GH is replaced at the time of replacement lubrication (maintenance). Movement may be hindered. For this reason, as shown in FIGS. 4A and 6A, in the initial state, the hydraulic cylinder portion 21 is filled with the working grease _GH without any gaps. The working grease _GH is also filled in the flow paths 4b, 16f, 17d, and 22 up to the tips of the grease filler plugs 6 and 7 shown in FIG. When the bearing 12 rotates in this state, the grease G in the vicinity of the end surface of the bearing 12 gradually deteriorates, and as shown in FIGS. 4 (A) and 6 (A), the grease G in the vicinity of the end surface of the bearing 12 Is mixed. As shown in FIGS. 4 (B) and 6 (B), at the time of replacement lubrication, the greasing plug 6 shown in FIG. 1 is removed from the inlet so that the movable part 19 moves in a direction away from the bearing 12. The working grease _GH is injected into the passage 4b. As a result, the operating grease _GH passes through the flow paths 4b, 16f, and 22, and the operating grease _GH flows into the fluid pressure cylinder portion 21 as shown in FIGS. 4 (A) and 5 (A). .

When the operating grease _GH flows into the fluid pressure cylinder portion 21, the internal pressure in the cylinder chamber 21b increases as the amount of operating grease _GH injected increases, and the fluid pressure applied to the pressure receiving portion 21d of the piston portion 21c also increases. To do. For this reason, when the piston portion 21c starts moving forward in the cylinder chamber 21b, the piston portion 21c presses the extension portion 19e to transmit a driving force, and the movable portion 19 starts moving in a direction away from the bearing 12. As a result, it moves the movable portion 19 while the grease G _O after degradation is held by the holding portion 19a, the grease G _N is pressed in the non-deteriorated between the bottom of the bottom and the annular packing chamber 14b of the movable portion 19 Is done. Therefore, as shown by the two-dot chain line in FIG. 6 (B), while the grease G _N of the non-deteriorated is guided by the guide portion 20b from the inlet 20a ejecting from the outlet 20c, the holding portion 19a front end surface and the bearing 12 This undegraded grease _GN is gradually filled between the two end faces. Figure 4 (B) and as shown in FIG. 6 (C), when the movable portion 19 until it contacts the bottom of the annular filling chamber 14b is moved, the non-deteriorated between the grease G _O and the bearing 12 after degradation grease G _N is fully replacement greasing, the bearing 12 is newly lubricated by grease G _N of the non-deteriorated. Replacement grease is also supplied to the annular filling chamber 15b on the bearing lid 15 side by the same method.

The bearing lubrication structure according to the first embodiment of the present invention has the following effects.
(1) In the first embodiment, the fluid pressure cylinder portion 21 generates a driving force by the fluid pressure of the working grease _GH , and the fluid pressure cylinder portion 21 transmits the driving force to the movable portion 19 to move the movable force cylinder 19. The part 19 is driven in the filling chamber 14a. For this reason, even if it is difficult to secure a sufficient working space or installation space outside the bearing lids 14 and 15 shown in FIG. 1, it is possible to secure a sufficient working space and fluid from any place where the work is easy. The movable part 19 can be easily driven by applying a pressure to the fluid pressure cylinder part 21. As a result, the work place at the time of replacing the grease can be changed to an arbitrary position according to the situation around the electric motor frame 2, and the space necessary for the work can be saved. In addition, such a conventional lubrication structure as a conventional bearing is complicated such that the gap between the operation portion of the feed screw mechanism that drives the movable portion and the through hole of the bearing lid is sealed with a sealant before and after the intermediate lubrication operation. Since the work can be omitted, the work load at the time of replacement lubrication can be reduced.

(2) In the first embodiment, by the movable portion 19 moves in the filling chamber 14a, the grease G _O after side degradation near the bearing 12 away from the bearing 12, remote from the bearing 12 Not closer grease G _N deterioration in the bearing 12. Thus, for example, the bearing 12 of the main motor of the railway vehicle in a non-decomposed state, can swap the grease G _N of the grease G _O and undegraded after deterioration, stretching the lubrication life achieving lubricating effect sufficiently Can be made. Further, since a sufficient amount of grease G can be filled in the vicinity of the bearing 12 in the initial state, it is possible to prevent poor lubrication before replacement lubrication. Furthermore, it is possible to forcibly away grease G _O after degradation such as abrasion powder is mixed from the vicinity of the bearing 12.

(3) In the first embodiment, the fluid pressure cylinder portion 21 generates a driving force outside the filling chamber 14a and transmits this driving force from the outside of the filling chamber 14a to the movable portion 19. For this reason, as shown in FIGS. 4 and 5, the fluid pressure of the working grease _GH can be applied to the fluid pressure cylinder portion 21 in a state where the fluid pressure cylinder portion 21 is separated from the filling chamber 14a. As a result, it is possible to prevent the working grease _GH from flowing out from the fluid pressure cylinder portion 21 into the filling chamber 14a, and to prevent the grease G from flowing out from the filling chamber 14a into the fluid pressure cylinder portion 21. You can also.

(4) In the first embodiment, the fluid pressure cylinder part 21 transmits the driving force to the movable part 19 through the piston part 21c that receives the fluid pressure of the working grease _GH and drives in the cylinder chamber 21b. For this reason, it is possible to easily move the movable portion 19 by easily driving the piston portion 21c with the fluid pressure of the working grease _GH .

(5) In the first embodiment, the fluid pressure cylinder portion 21 includes a cylinder side fitting portion 21e that fits with the movable portion side fitting portion 19f of the movable portion 19. For this reason, the movable portion side fitting portion 19f and the cylinder side fitting portion 21e can be easily joined and separated, and the bearing lid 14 and the cylinder body portion 21a can be easily assembled or disassembled. .

(6) In the first embodiment, a gap portion delta ₁₁ between the movable portion engaging portions 19f and the cylinder-side engaging portion 21e. For example, the fitting portion between the guide portions 19c and 19d of the movable portion 19 and the annular filling chamber 14b of the bearing lid 14 is manufactured with a predetermined dimensional tolerance so that relative movement is possible, and there is a minute gap between them. There is (gat). Further, the fitting portion between the outer ring 12c of the bearing 12 and the through hole 21f of the cylinder main body 21a is also manufactured with a predetermined dimensional tolerance, and there is a minute gap between them. In the first embodiment, a predetermined gap portion Δ ₁₁ is formed in the radial direction of the movable portion 19 and the cylinder body portion 21 a between the movable portion side fitting portion 19 f and the cylinder side fitting portion 21 e. . For this reason, even if there is a minute gap in the fitting portion between the guide portions 19c, 19d and the annular filling chamber 14b or the fitting portion between the outer ring 12c and the through hole 21f, the movable portion side fitting portion 19f and the cylinder side fitting are provided. The mating portion 21e can be easily fitted.

(7) In the first embodiment, the central axis of the movable portion 19 is the same as the central axis of the bearing 12 and the movable portion 19 is an annular member, and the driving force acts on the movable portion 19 at a plurality of locations. Thus, a plurality of fluid pressure cylinder portions 21 are arranged. For this reason, a plurality of small fluid pressure cylinder portions 21 can be efficiently arranged to transmit the driving force from a plurality of locations in a well-balanced manner to the movable portion 19, and the movable portion 19 can be easily moved during replacement lubrication.

(8) In the first embodiment, the fluid pressure cylinder portion 21 drives the movable portion 19 so that the driving force acts on the movable portion 19 evenly at a plurality of locations. For this reason, the driving force generated by the fluid pressure cylinder portion 21 acts evenly at a plurality of locations of the movable portion 19, and the movable portion moves relative to the central axis of the bearing lid 14 when moving the movable portion 19 during replacement lubrication. It is possible to prevent the 19 central axis from being inclined.

(9) In the first embodiment, the fluid pressure cylinder portion 21 drives the movable portion 19 so that the driving force acts at equal intervals in the circumferential direction of the movable portion 19. For this reason, it is possible to prevent a driving force that tilts the central axis of the movable portion 19 from acting on the movable portion 19 with respect to the central axis of the bearing lid 14. As a result, since it is possible to prevent an excessive frictional force from being generated between the guide portions 19c and 19d of the movable portion 19 and the annular filling chamber 14b of the bearing lid 14, the movable portion 19 can be smoothly smoothed during the replacement lubrication. Can be moved to.

(10) In the first embodiment, the fluid pressure cylinder portion 21 drives the movable portion 19 so that the driving force acts on the movable portion 19 at a plurality of points symmetrical with respect to the central axis of the movable portion 19. . For this reason, since the symmetrical position with respect to the center of the movable part 19 is simultaneously pressed by the driving force generated by the fluid pressure cylinder part 21, it is possible to prevent the driving force from tilting the movable part 19 from acting. Can do.

(11) In the first embodiment, the outer filling chamber 14c is formed to be expanded outside the filling chamber 14a, and the extension portion 19e extends from the outer peripheral portion of the movable portion 19 into the outer filling chamber 14c. The fluid pressure cylinder part 21 drives the movable part 19 by driving the extension part 19e. For example, when the extension portion 19e shown in FIG. 4 does not exist, it is necessary to drive the movable portion 19 by disposing the fluid pressure cylinder portion 21 outside the bearing lid 14, but there is a space outside the bearing lid 14. In reality, it is difficult to dispose the fluid pressure cylinder portion 21. In the first embodiment, the extension portion 19e is protruded into the outer filling chamber 14c, and the extension portion 19e can be driven by the fluid pressure cylinder portion 21 disposed outside the bearing 12. The movable portion 19 can be easily driven even if there is no room on the outside.

(12) In the first embodiment, the fluid pressure cylinder portion 21 drives the movable portion 19 with the same type of operating grease _{GH as} the grease G in the filling chamber 14a. Therefore, even when the working grease _GH leaks from the fluid pressure cylinder portion 21 to the annular filling chamber 14b and is mixed with the grease G in the annular filling chamber 14b, the grease G in the annular filling chamber 14b is mixed. It is possible to prevent the lubrication performance from being deteriorated due to changes in the components.

(Second Embodiment)
FIG. 9 is a cross-sectional view of the fluid pressure cylinder portion of the lubricating structure of the bearing according to the second embodiment of the present invention, and FIG. 9 (A) shows a fitting state when the movable portion is displaced downward. FIG. 9B is a cross-sectional view illustrating a fitting state when the movable portion is displaced upward. In the following, the same parts as those shown in FIGS. 1 to 8 are denoted by the same reference numerals and detailed description thereof is omitted.
The movable part side fitting part 19f shown in FIG. 9 is a concave part fitted to the taper surface 21g of the cylinder side fitting part 21e. The taper surface 19h is a through hole formed so that the fluid pressure cylinder portion 21 side is wide and the bearing lid 14 side is narrow, and the surface of the taper surface 19h is conical. The cylinder side fitting portion 21e is a convex portion that fits with the tapered surface 19h of the movable portion side fitting portion 19f. The taper surface 21g is a projection formed so that the tip end side is thin and the rear end side is thick, and the surface of the taper surface 21g is formed in a conical shape at the same inclination angle as the taper surface 19h. The tapered surfaces 19h and 21g serve as a guide portion that guides the movable portion side fitting portion 19f and the cylinder side fitting portion 21e when the movable portion side fitting portion 19f and the cylinder side fitting portion 21e are fitted. Function. In the second embodiment, even if there is a relative position (displacement) between the movable portion side fitting portion 19f and the cylinder side fitting portion 21e, the taper surface 19h causes the piston portion 21c to move forward. The tapered surface 21g is guided. Therefore, the movable part 19 can be moved by easily fitting the movable part side fitting part 19f and the cylinder side fitting part 21e.

(Third embodiment)
FIG. 10 is a sectional view of a fluid pressure cylinder portion of a lubricating structure of a bearing according to a third embodiment of the present invention, FIG. 10 (A) is a sectional view in an initial state, and FIG. 10 (B) is a replacement supply. It is sectional drawing after fat. FIG. 11 is an enlarged cross-sectional view of the XI portion of FIG. 10, FIG. 11 (A) is a cross-sectional view in an initial state, and FIG. 11 (B) is a cross-sectional view after replacement lubrication.
A bearing lid 14A shown in FIG. 10 includes a filling chamber 14a for supplying grease G from one end face side of the bearing 12, and the bearing lid 14B is a filling chamber 14a for supplying grease G from the other end face side of the bearing 12. The bearing lids 14A and 14B have the same structure as the bearing lid 14 shown in FIG. The lubrication structure 18 shown in FIG. 10 is different from the lubrication structure 18 provided with the movable portion 19 on the outer side (bearing lid 14 side) of the bearing 12 as shown in FIG. The movable portions 19A and 19B are provided on the bearing lid 14B side, respectively. The lubrication structure 18 includes movable portions 19A and 19B shown in FIG. 10, discharge portions 20A and 20B, fluid pressure cylinder portions 21A and 21B shown in FIGS. 10 and 11, a flow path 22 shown in FIG. The adhesion prevention part 23 shown in FIG.

The movable portion 19A shown in FIG. 10 moves in the filling chamber 14a on the bearing lid 14A side, and the movable portion 19B moves in the filling chamber 14a on the bearing lid 14B side. Discharging portion 20A, 20B, when the movable portion 19A is moved in a direction away from the bearing 12, the grease G _N of the non-deteriorated discharged toward the bearing 12. The fluid pressure cylinder portions 21A and 21B drive the movable portions 19A and 19B, respectively, and include a pressure receiving portion 21d having the same area. The flow path 22 supplies the working grease _GH to the fluid pressure cylinder portions 21A and 21B. The adhesion preventing portion 23 shown in FIG. 11 forms a predetermined gap portion between the pressure receiving portions 21d so that the fluid pressure of the working grease _GH acts on the pressure receiving portions 21d of the fluid pressure cylinder portions 21A and 21B. Thus, it is a portion that prevents these pressure receiving portions 21d from coming into close contact with each other. The adhesion prevention part 23 is a protrusion formed on the inner peripheral surface of the cylinder chamber 21 b so as to partition the two cylinder chambers 21 b, and is disposed below the opening on the downstream side of the flow path 22. The adhesion prevention unit 23 forcibly separates the pressure receiving portions 21d so that the fluid pressure of the working grease _GH flowing from the flow path 22 acts on the pressure receiving portions 21d of the fluid pressure cylinder portions 21A and 21B. It functions as a stopper that prevents these pressure receiving portions 21d from coming into close contact with each other. The movable parts 19A and 19B, the discharge parts 20A and 20B, and the fluid pressure cylinder parts 21A and 21B have the same structure as the movable part 19 and the discharge part 20 shown in FIG. 4 and the fluid pressure cylinder part 21 shown in FIGS. 10 and 11, the same parts as those of the movable part 19, the discharge part 20, and the fluid pressure cylinder part 21 are denoted by the same reference numerals, and detailed description thereof is omitted.

Next, the operation of the bearing lubrication structure according to the third embodiment of the present invention will be described.
As shown in FIG. 10, during replacement lubrication, the greasing plug 6 shown in FIG. 1 is removed so that the movable parts 19A and 19B move away from the bearing 12, and the working grease G is transferred from the inlet to the flow path 4b. _{When H} is injected, the working grease _GH passes through the flow path 16 f and flows into the flow path 22. As shown in FIG. 11, in the opening of the downstream side of the flow path 22, divided into two flows of hydraulic grease G _H, operated grease G _H is the channel to the fluid pressure cylinder unit 21A side of the cylinder chamber 21b 22 and the operating grease _GH flows from the flow path 22 into the cylinder chamber 21b on the fluid pressure cylinder portion 21B side. As the amount of operating grease _GH injected increases, the internal pressures in the cylinder chambers 21b of the fluid pressure cylinder portions 21A and 21B increase simultaneously, and the fluid pressure applied to the pressure receiving portions 21d of the piston portions 21c also increases. Since the pressure receiving portions 21d of the piston portions 21c have the same area, fluid pressure of the same magnitude is simultaneously applied to the pressure receiving portions 21d of the piston portions 21c, and the piston portions 21c start to drive simultaneously. A driving force is applied to the movable portions 19A and 19B from the fluid pressure cylinder portions 21A and 21B at a point-symmetrical position with respect to the central axes of the movable portions 19A and 19B. As a result, the movable portions 19A and 19B start to move substantially simultaneously in the direction away from the bearing 12.

The bearing lubrication structure according to the third embodiment of the present invention has the following effects in addition to the effects of the first and second embodiments.
(1) In the third embodiment, the movable portion 19A moves within the filling chamber 14a on the bearing lid 14A side, and the fluid pressure cylinder portion 21A drives the movable portion 19A, and the filling chamber 14a on the bearing lid 14B side. The movable portion 19B moves within the fluid, and the fluid pressure cylinder portion 21B drives the movable portion 19B. As a result, the grease G can be supplied from one end face side and the other end face side of the bearing 12, so that the lubrication effect can be further enhanced and the lubrication life can be further extended.

(2) In the third embodiment, the flow channel 22 supplies the working grease _GH from the outside to the fluid pressure cylinder portion 21A and the fluid pressure cylinder portion 21B. For this reason, the working grease _GH can be simultaneously supplied from one flow path 22 to the fluid pressure cylinder portions 21A and 21B, and the movable portions 19A and 19B can be driven simultaneously. As a result, it is not necessary to construct complicated piping in order to drive the movable portions 19A and 19B independently of each other, and a simple and compact structure can be achieved. Further, if there is a difference in the deterioration state of the working grease _GH depending on the use state up to the replacement lubrication, the fluid pressure of the working grease _GH acting on the fluid pressure cylinder parts 21A and 21B is changed from the fluid pressure cylinder part 21A. It may be different from the fluid pressure cylinder portion 21B. In this case, for example, if one fluid pressure cylinder portion 21A is driven first at a lower fluid pressure, the pressure of the fluid pressure cylinder portions 21A and 21B increases when the fluid pressure cylinder portion 21A stops. When the fluid pressure sufficient to drive the other fluid pressure cylinder portion 21B is reached, the fluid pressure cylinder portion 21B starts driving. Thus, since the fluid pressure chambers of the fluid pressure cylinder portions 21A and 21B are communicated with each other by one cylinder chamber 21b, the fluid pressure cylinder portions 21A and 21B are driven both simultaneously or one by one. be able to.

(3) In the third embodiment, the adhesion preventing portion 23 is provided between the pressure receiving portions 21d so that the fluid pressure of the working grease _GH acts on the pressure receiving portions 21d of the fluid pressure cylinder portions 21A and 21B. The adhesion preventing portion 23 prevents the pressure receiving portions 21d from coming into close contact with each other. For this reason, the adhesion preventing portion 23 forcibly forms a gap between the pressure receiving portion 21d on the fluid pressure cylinder portion 21A side and the pressure receiving portion 21d on the fluid pressure cylinder portion 21B side, and these pressure receiving portions 21d are in close contact with each other. Thus, it is possible to prevent the movable portion 19 from becoming inoperable because the fluid pressure of the working grease _GH does not act.

(Fourth embodiment)
FIG. 12 is a cross-sectional view of a fluid pressure cylinder portion of a lubricating structure of a bearing according to a fourth embodiment of the present invention, and FIG. 12 (A) is a cross-sectional view when the fluid pressure acting portion is a columnar shape, FIG. 12B is a cross-sectional view when the fluid pressure acting portion is conical.
The lubrication structure 18 shown in FIG. 12 includes fluid pressure acting portions 24A and 24B. The fluid pressure acting portions 24A and 24B simultaneously actuate the working grease _GH on the pressure receiving portions 21d of the fluid pressure cylinder portions 21A and 21B. It is a part to be made. Fluid pressure acting portion 24A, 24B forms a predetermined gap delta ₁₂ between the pressure receiving portion 21d and the fluid pressure cylinder unit 21B side of the pressure receiving portion 21d of the hydraulic cylinder unit 21A side. The fluid pressure acting portion 24A is formed at the rear end portion of the piston portion 21c on the fluid pressure cylinder portion 21A side, and the fluid pressure acting portion 24B is formed at the rear end portion of the piston portion 21c on the fluid pressure cylinder portion 21B side. ing. The fluid pressure acting portions 24A and 24B are both convex portions having the same shape, and are accommodated in the cylinder chamber 21b in a state where the tip portions are butted together, and the butting position is substantially the same as the center line of the pipe line 22. I'm doing it. Fluid pressure acting portion 24A, 24B, as operated grease G _H flows into the gap portion delta _12, protrudes from the rear end face of the piston portion 21c (the bottom portion). For example, as shown in FIG. 12A, the fluid pressure cylinder portions 21A and 21B are formed as cylindrical projections having a smaller outer diameter than the piston portion 21c, or as shown in FIG. 12B. For example, a conical protrusion having the same diameter and the same bottom diameter. As shown in FIG. 12B, the fluid pressure cylinder portions 21A and 21B are formed in a rear end shape so that the contact area between the tip portions becomes small, and fluid pressure acting on the pressure receiving portion 21d is possible. It is preferable to make it as high as possible.

Next, the operation of the bearing lubrication structure according to the fourth embodiment of the present invention will be described.
As shown in FIG. 12, during replacement lubrication, the working grease _GH flows into the cylinder chamber 21b on the fluid pressure cylinder portion 21A side and the cylinder chamber 21b on the fluid pressure cylinder portion 21B side from the flow path 22. Since the gap delta ₁₂ is formed between the fluid pressure cylinder unit 21A side of the pressure receiving portion 21d and the fluid pressure cylinder unit 21B side of the pressure receiving portion 21d, hydraulic grease G _H flows into the gap portion delta ₁₂ The fluid pressure of the working grease _GH acts on the pressure receiving portion 21d. Since the pressure receiving portions 21d of the piston portions 21c have the same area, fluid pressure of the same magnitude is simultaneously applied to the pressure receiving portions 21d of the piston portions 21c, and the piston portions 21c start to drive simultaneously. As a result, as shown in FIG. 10, the movable portions 19 </ b> A and 19 </ b> B start moving substantially simultaneously in the direction away from the bearing 12.

In addition to the effects of the first to third embodiments, the bearing lubrication structure according to the fourth embodiment of the present invention has the following effects.
(1) In the fourth embodiment, the hydraulic pressure acting portions 24A and 24B simultaneously apply the working grease _GH to the pressure receiving portion 21d having the same area as the fluid pressure cylinder portions 21A and 21B. For this reason, since the driving force generated by the fluid pressure cylinder portions 21A and 21B can be applied to the movable portions 19A and 19B at the same time, the grease G is uniformly distributed from one end and the other end of the bearing 12 simultaneously. Can be supplied.

(2) In the fourth embodiment, the fluid pressure cylinder unit 21A side of the pressure receiving portion 21d and the fluid pressure cylinder unit 21B side of the fluid pressure acting portion 24A between the pressure receiving portion 21d, 24B is a predetermined gap delta ₁₂ Form. Therefore, the actuation grease G _H can be ingress easily the gap delta _12, reliably be driven to act in the movable portion 19A, the 19B in the pressure-receiving portion 21d of the fluid pressure of the hydraulic grease G _H Can do.

(Fifth embodiment)
FIG. 13 is a cross-sectional view of a fluid pressure cylinder portion of a lubricating structure of a bearing according to a fifth embodiment of the present invention, and FIG. 13 (A) is a cross-sectional view when the fluid pressure action portion is conical, FIG. 13B is a cross-sectional view when the fluid pressure acting portion is planar.
The lubrication structure 18 shown in FIG. 13 includes fluid pressure acting portions 24A to 24C. The fluid pressure acting portions 24A to 24C simultaneously actuate the working grease _GH on the pressure receiving portions 21d of the fluid pressure cylinder portions 21A and 21B. It is a part to be made. Fluid pressure acting portion 24A~24C forms a predetermined gap delta ₁₂ between the pressure receiving portion 21d and the fluid pressure cylinder unit 21B side of the pressure receiving portion 21d of the hydraulic cylinder unit 21A side. The fluid pressure acting parts 24A and 24B are accommodated in the cylinder chamber 21b in a state where the end part is in contact with the fluid pressure acting part 24C. For example, as shown in FIG. 13A, the fluid pressure acting parts 24A and 24B are conical protrusions having the same diameter as the piston part 21c and the diameter of the bottom surface, as shown in FIG. 13B. And a planar end surface portion perpendicular to the central axis of the piston portion 21c. The fluid pressure acting part 24C is sandwiched between the end of the fluid pressure acting part 24A and the end of the fluid pressure acting part 24B, and the cylinder chamber 21b on the fluid pressure cylinder part 21A side and the fluid pressure side cylinder part 21B It is a wall part formed in the internal peripheral surface of this cylinder chamber 21b so that it may divide into the cylinder chamber 21b. The fluid pressure acting part 24 </ b> C includes a flow dividing part 24 a, and is arranged such that the tip part bisects the cross section of the opening part on the downstream side of the flow path 22. As shown in FIG. 13 (A), the fluid pressure cylinder portions 21A to 21C are formed in end shapes so that the contact areas of the end surfaces that come into contact with each other are reduced, and the fluid pressure acting on the pressure receiving portion 21d is possible. It is preferable to make it as high as possible.

The flow dividing portion 24 a is a portion that divides the flow of the working grease _GH flowing from the flow path 22. The diverter 24a is located downstream of the flow path 22 so that the flow rate of the working grease _GH flowing into the fluid pressure cylinder portion 21A and the flow rate of the working grease _GH flowing into the fluid pressure cylinder portion 21B are the same. The flow of the working grease _GH flowing in from the side end is divided into two. The flow dividing portion 24a is a wall portion formed on the inner peripheral surface of the cylinder chamber 21b so as to divide the two cylinder chambers 21b, and the tip portion bisects the cross section of the opening on the downstream side of the flow path 22. It arrange | positions in the cylinder chamber 21b. In the flow dividing portion 24a, the cross-sectional shape of the tip portion is formed in a blade shape so as not to hinder the flow of the working grease _GH .

Next, a processing method of the fluid pressure cylinder portion of the bearing lubrication structure according to the fifth embodiment of the present invention will be described.
As shown in FIG. 13A, when the shape of the rear ends of the fluid pressure acting portions 24A and 24B is conical, a cutting edge shape is formed so that a wall portion remains between the two cylinder chambers 21b. The both ends of the cylinder body 21a are cut by a predetermined depth with a flat drill. Further, the outer peripheral surface of the cylinder body 21a is cut to a predetermined depth by a drill having a flat cutting edge shape so that the two cylinder chambers 21b and the flow path 22 communicate with each other. As a result, a plate-like fluid pressure acting portion 24C is formed between the two cylinder chambers 21b. On the other hand, as shown in FIG. 13B, when the shape of the rear end portion of the fluid pressure acting portions 24A, 24B is a flat shape, the cutting is performed so that the wall portion remains between the two cylinder chambers 21b. Both end surfaces of the cylinder body 21a are cut to a predetermined depth by a drill having a sharp blade shape. Similarly, the outer peripheral surface of the cylinder body 21a is cut to a predetermined depth by a drill having an acute cutting edge shape so that the two cylinder chambers 21b and the flow path 22 communicate with each other. As a result, a mountain-shaped fluid pressure acting portion 24C is formed between the two cylinder chambers 21b.

Next, the operation of the bearing lubrication structure according to the fifth embodiment of the present invention will be described.
When the grease filler plug 6 shown in FIG. 1 is removed and the operating grease _GH is injected into the channel 4b from the inlet, the operating grease _GH passes through the channel 16f and flows into the channel 22. As shown in FIG. 13, since the flow dividing portion 24a is disposed in the opening on the downstream side of the flow path 22, the flow of the working grease _GH is divided into two by the flow dividing portion 24a, and the fluid pressure cylinder portion 21A. with actuating grease G _H to the cylinder chamber 21b of the side flows from the channel 22, actuating the grease G _H flows from the channel 22 to the fluid pressure cylinder unit 21B side of the cylinder chamber 21b. As the amount of operating grease _GH injected increases, the internal pressures in the cylinder chambers 21b of the fluid pressure cylinder portions 21A and 21B increase simultaneously, and the fluid pressure applied to the pressure receiving portions 21d of the piston portions 21c also increases. Since the pressure receiving portions 21d of the piston portions 21c have the same area, fluid pressure of the same magnitude is simultaneously applied to the pressure receiving portions 21d of the piston portions 21c, and the piston portions 21c start to drive simultaneously. A driving force is applied to the movable portions 19A and 19B from the fluid pressure cylinder portions 21A and 21B at a point-symmetrical position with respect to the central axes of the movable portions 19A and 19B. As a result, the movable portions 19A and 19B start to move substantially simultaneously in the direction away from the bearing 12.

(Sixth embodiment)
FIG. 14 is a cross-sectional view of an electric motor frame body and shaft provided with a bearing lubrication structure according to a sixth embodiment of the present invention.
The bracket 4 shown in FIG. 14 includes a flow path 4c into which the grease G flows when the grease G is filled. The greasing plugs 6 and 7 are members that are screwed into the inlets of the flow paths 4c and 17f, respectively, so as to open and close the inlets, and the grease fillers 6 and 7 are formed inside these inlets. A male screw portion that meshes with the female screw portion thus formed is formed. The bearing lid 16 includes a flow path 16d and a supply port 16e. The flow path 16d is a portion into which the grease G flows when the grease G is filled. One end (upstream side) is connected to the flow path 4c of the bracket 4 and the other end (downstream side) is connected. It opens toward the bearing 12. The supply port 16e is an opening through which the grease G is supplied to the annular filling chamber 14b through the bearing 12. The bearing lid 17 includes a supply port 17e and a flow path 17f. The supply port 17e is an opening for supplying the grease G to the annular filling chamber 15b through the bearing 13. The flow path 17f is a portion into which the grease G flows when the grease G is filled, and one end portion (upstream side) is connected to an inflow port to which the greasing plug 7 is attached, and the other end portion (downstream side). Side) is open toward the bearing 13.

Next, the operation of the bearing lubrication structure according to the sixth embodiment of the present invention will be described.
In the initial state, the grease G is not sealed between the bottom of the movable portion 19 and the bottom of the annular filling chambers 14b and 15b. During replacement greasing the flow path 4b, when supplying hydraulic grease G _H to 17d, the movable portion 19 in a direction away from the bearing 12, 13 is moved together with the grease G _O after deterioration, and the movable portion 9 bearing 12 A gap is formed between the two. Thereafter, the flow path 4c, 16d, when injecting the grease G _N of the non-deteriorated from 17f, through the bearings 12 and 13 from the supply port 16e, 17e, the gap between the movable portion 9 and the bearing 12, 13 grease G _N of the non-deteriorated is filled.

In addition to the effects of the first to fifth embodiments, the bearing lubrication structure according to the sixth embodiment has the effects described below.
In the sixth embodiment, the movable portion 19 releases the grease G _O after deterioration from the bearing 12, 13. Therefore, to form a gap between the bearing 12 and 13 and the movable portion 19, the grease G _N of the non-deteriorated from the outside to the gap portion can be greasing.

(Other embodiments)
The present invention is not limited to the embodiment described above, and various modifications or changes can be made as described below, and these are also within the scope of the present invention.
(1) In this embodiment, the grease G is described as an example of the semi-solid lubricant. However, the present invention is not limited to the grease G, and a semi-solid gear compound, petrolatum (Vaseline), etc. The present invention can also be applied to other semi-solid lubricants. In this embodiment, the bearings 12 and 13 that support the shaft 1 of the main motor of the railway vehicle have been described as an example. However, the present invention is not limited to this, and a bearing that supports the shaft of a power plant turbine or the like. The present invention can also be applied to. Further, in this embodiment, the case where the bearings 12 and 13 are ball bearings or roller bearings has been described as an example, but the present invention can be applied to other types of rolling bearings. In particular, the present invention can be applied not only to a bearing of a main motor of a railway vehicle but also to a rolling bearing that is used for a long time without being disassembled and lubricated by grease G.

(2) In this embodiment, the case where the working fluid acting on the fluid pressure cylinder portions 21, 21A, 21B is the working grease _GH has been described as an example. However, in addition to the grease, a liquid such as oil, water, or the like A gas such as air can also be used as the working fluid. Moreover, in this embodiment, although the case where the recessed part was formed in the movable part side fitting part 19f and the convex part was formed in the cylinder side fitting part 21e was described as an example, the movable part side fitting part 19f A convex part can be formed and a concave part can also be formed in the cylinder side fitting part 21e.

(3) In this embodiment, the discharge section 20, 20A, 20B has been described as an example a case comprising a guide portion 20b, so as displace the grease G _O after deterioration by omitting the guide portion 20b undeteriorated grease G _N can be discharged from the inlet 20a of the. In this embodiment, the case where a plurality of discharge units 20, 20A, 20B are arranged has been described as an example. However, the number of installation units, the installation interval, the installation area, and the like of the discharge units 20, 20A, 20B are not limited. without movable parts 19, 19A, without interfering with the operation of 19B, and can the grease G _N of the non-deteriorated to arbitrarily change these installation conditions so as to be movable with a certain momentum. Furthermore, in this embodiment, the case where the front end surface of the guide portion 20b and the end surface of the bearing 12 are matched has been described as an example. You can also

(4) In this embodiment, a case where the gap S ₁₁ between the inner ring 12d and the cage 12b of bearing 12 positions the outlet 20c has been described as an example, depending on the format or type of the bearing 12 The position of the discharge port 20c can be arbitrarily changed. Further, in this embodiment, the case where the discharge portions 20, 20A, 20B are arranged at intervals in the circumferential direction of the inner peripheral portion of the movable portions 19, 19A, 19B has been described as an example, but the present invention is limited to this. is not. For example, the discharge portions 20, 20A, 20B are continuously arranged in the circumferential direction of the inner peripheral portion of the movable portions 19, 19A, 19B, or spaced in the circumferential direction of the central portion of the movable portions 19, 19A, 19B. The discharge parts 20, 20A, 20B can also be arranged. Furthermore, in this embodiment, the case where the cross-sectional shape of the guide portion 20b is substantially rectangular has been described as an example, but a circular shape, a polygonal shape, a triangular shape, an elliptical shape, or a cross-sectional shape that is an arbitrary combination thereof may be used. it can.

(5) In this embodiment, the case where two fluid pressure cylinder parts 21, 21A, and 21B are arranged has been described as an example. However, three or more fluid pressure cylinder parts 21, 21A, and 21B are arranged respectively. You can also For example, when an even number of fluid pressure cylinder parts 21, 21A, 21B are arranged, they are arranged symmetrically with respect to the central axis of the movable parts 19, 19A, 19B, and an odd number of fluid pressure cylinder parts 21, 21A, 21B. When arrange | positioning, it can arrange | position at equal intervals in the circumferential direction of movable part 19,19A, 19B. In the first embodiment, the pressure receiving portion 21d of one piston portion 21c of the fluid pressure cylinder portion 21 and the pressure receiving portion 21c of the other piston portion 21c are substantially in the same position in the axial direction of the piston portion 21c. In addition, the case where the two piston portions 21c are arranged symmetrically with respect to the central axis of the cylinder body portion 21a has been described as an example, but the present invention is not limited to such a case. For example, the pressure receiving portion 21d of the one piston portion 21c and the pressure receiving portion 21c of the other piston portion 21c may be shifted back and forth in the axial direction of the piston portion 21c.

(6) In the first and second embodiments, the case where the cross-sectional shapes of the movable portion side fitting portion 19f and the cylinder side fitting portion 21e are rectangular and triangular has been described as an example. The shape is not limited to other shapes, and other shapes can be used. In the first and second embodiments, the case where the lubrication structure 18 is applied to the bearing lids 14 and 15 has been described as an example. However, the present invention is also applied to the bearing lids 16 and 17 side. be able to. Further, in the third to fifth embodiments, the case where the bearing lids 14A and 14B are disposed at both ends of the bearing 12 has been described as an example. However, the bearing lids 14A and 14B are disposed at both ends of the bearing 13, respectively. A bearing lid having the same structure can also be arranged.

DESCRIPTION OF SYMBOLS 1 Shaft 2 Electric motor frame 6, 7 Greasing plug 12, 13 Bearing 14-17, 14A, 14B Bearing lid 14a, 15a Filling chamber 14b, 15b Annular filling chamber 14c, 15c Outer filling chamber 18 Lubrication structure 19, 19A, 19B Movable part 19a Holding part 19e Extension part 19f Movable part side fitting part 19h Tapered surface 20, 20A, 20B Discharge part 21, 21A, 21B Fluid pressure cylinder part 21a Cylinder body part 21b Cylinder chamber 21c Piston part 21e Cylinder side fitting part 21g taper surface 22 flow path (supply flow path)
23 Contact prevention part 24A, 24B, 24C Fluid pressure action part 24a Splitting part G Grease (semi-solid lubricant)
G _O Degraded grease (degraded semi-solid lubricant)
G _N undegraded grease (semisolid lubricant undeteriorated)
_GH operating grease (working fluid)
S ₁₁ gap Δ ₁₁ , Δ ₁₂ gap

Claims (19)

A bearing lubrication structure for lubricating a bearing with a semi-solid lubricant,
A movable part that moves in a filling chamber filled with the semi-solid lubricant;
A fluid pressure cylinder portion that generates a driving force by the fluid pressure of the working fluid, transmits the driving force to the movable portion, and drives the movable portion;
A lubricating structure for a bearing comprising: In the lubricating structure of the bearing according to claim 1,
The movable part separates the deteriorated semi-solid lubricant from the bearing,
Lubricating structure for bearings. The bearing lubricating structure according to claim 1 or 2,
The movable part moves in the filling chamber to separate the deteriorated semi-solid lubricant on the side close to the bearing from the bearing and to remove the undegraded semi-solid lubricant on the side far from the bearing. Close to the bearing,
Lubricating structure for bearings. In the lubricating structure of the bearing according to any one of claims 1 to 3,
The fluid pressure cylinder portion generates the driving force outside the filling chamber and transmits the driving force from the outside of the filling chamber to the movable portion;
Lubricating structure for bearings. In the lubricating structure of the bearing according to any one of claims 1 to 4,
The fluid pressure cylinder part receives the fluid pressure of the working fluid and transmits the driving force to the movable part through a piston part that is driven in a cylinder chamber;
Lubricating structure for bearings. In the lubricating structure of the bearing according to any one of claims 1 to 5,
The fluid pressure cylinder part includes a cylinder side fitting part that fits with a movable part side fitting part of the movable part;
Lubricating structure for bearings. In the lubricating structure of the bearing according to claim 6,
The fluid pressure cylinder part has a gap part between the movable part side fitting part and the cylinder side fitting part;
Lubricating structure for bearings. In the lubricating structure of the bearing according to claim 6 or 7,
The cylinder side fitting portion has a convex or concave tapered surface,
The movable portion side fitting portion has a concave or convex tapered surface that fits with the tapered surface of the cylinder side fitting portion;
Lubricating structure for bearings. In the lubricating structure of the bearing according to any one of claims 1 to 8,
The movable part is an annular member in which the central axis of the movable part is the same as the central axis of the bearing,
A plurality of the fluid pressure cylinder portions are arranged such that the driving force acts on the movable portion at a plurality of locations;
Lubricating structure for bearings. In the lubricating structure of the bearing according to any one of claims 1 to 9,
The fluid pressure cylinder portion drives the movable portion so that the driving force acts evenly on the movable portion at a plurality of locations;
Lubricating structure for bearings. In the lubricating structure of the bearing according to any one of claims 1 to 10,
The fluid pressure cylinder part drives the movable part so that the driving force acts at equal intervals in the circumferential direction of the movable part;
Lubricating structure for bearings. In the lubricating structure of the bearing according to any one of claims 1 to 11,
The fluid pressure cylinder portion drives the movable portion so that the driving force acts on the movable portion at a plurality of points symmetrical with respect to the central axis of the movable portion;
Lubricating structure for bearings. In the lubricating structure of the bearing according to any one of claims 1 to 11,
The filling chamber includes an outer filling chamber formed outside the filling chamber.
The movable part includes an extension extending from the outer peripheral part of the movable part into the outer filling chamber,
The fluid pressure cylinder part drives the movable part by driving the extension part;
Lubricating structure for bearings. In the lubricating structure of the bearing according to any one of claims 1 to 13,
The movable part is
A first movable part that moves in a filling chamber that supplies the semi-solid lubricant from one end face side of the bearing;
A second movable part that moves in a filling chamber that supplies the semi-solid lubricant from the other end face side of the bearing,
The fluid pressure cylinder part is
A first fluid pressure cylinder portion for driving the first movable portion;
A second fluid pressure cylinder portion for driving the second movable portion;
Lubricating structure for bearings. In the lubricating structure of the bearing according to claim 14,
A supply flow path for supplying the working fluid from the outside to the first fluid pressure cylinder part and the second fluid pressure cylinder part;
Lubricating structure for bearings. The bearing lubrication structure according to claim 14 or 15,
A predetermined gap portion is formed between the pressure receiving portions so that the pressure pressure of the working fluid acts on the pressure receiving portions of the first and second fluid pressure cylinder portions, and these pressure receiving portions are in close contact with each other. Providing an adhesion prevention part for preventing
Lubricating structure for bearings. The lubricating structure of the bearing according to claim 15,
The first and second fluid pressure cylinder portions have pressure receiving portions of the same area,
A fluid pressure acting part that simultaneously causes the working fluid to act on the pressure receiving parts of the first and second fluid pressure cylinder parts;
Lubricating structure for bearings. The lubricating structure of the bearing according to claim 17,
The fluid pressure acting portion forms a predetermined gap portion between the pressure receiving portion on the first fluid pressure cylinder portion side and the pressure receiving portion on the second fluid pressure cylinder portion side;
Lubricating structure for bearings. The bearing lubricating structure according to any one of claims 1 to 18,
The fluid pressure cylinder portion drives the movable portion by the fluid pressure of the same type of working fluid as the semi-solid lubricant in the filling chamber;
Lubricating structure for bearings.

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