JPH08210592A - Solid lubricant and sliding machine element - Google Patents

Abstract

PURPOSE: To provide a solid lubricant and a sliding machine element, capable of securing those of superior lubricating performance, high strength and high tenacity, thereby conducible to the augmentation of applications. CONSTITUTION: A solid lubricant is made up of a compound sintered material containing a lubricating phase 1 sing a lubricator as the main ingredient, a binder phase 2 using a metal or alloy as the main ingredient, and a reinforced phase 3 consisting of at least one type of metals, seramics, glass, a fiber of carbon or wisker.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION This invention relates to self-lubricating solid lubricants and sliding mechanical elements.

[0002]

2. Description of the Related Art Many mechanical elements that move in the atmosphere can be lubricated with oil at their sliding parts. But,
With mechanical elements that operate in a high temperature / vacuum or mechanical elements that operate under low speed / high surface pressure conditions, the sliding parts cannot be lubricated with oil.

Typical examples of such mechanical elements include cages for rolling ball bearings incorporated in a rotary anode X-ray tube, cages for rolling ball bearings used in outer space, gears, and the like. You can

As described above, regarding mechanical elements that cannot be lubricated with oil, attempts have recently been made to form the mechanical elements themselves with a solid lubricant having a self-lubricating property.

As a solid lubricant, a metal-based composite material containing a solid lubricant such as tungsten disulfide or molybdenum disulfide is known. For example, Japanese Patent Publication Sho 58-17819
As shown in the publication, WS ₂ , MoS ₂ and C
A solid lubricating composite material composed of u, Fe, Ni and Co and a metal of group 4a, 5a, 6a of the periodic table is known. In addition, as disclosed in Japanese Patent Laid-Open No. 62-196351, W
S _2, MoS _2, a solid lubricating component such as graphite 30~1000μ
There is also known a solid lubricating composite material of the same kind in which a lump of m is formed and bonded by a mesh structure composed of a metal component.

However, the solid lubricant having the former composition has a problem that the brittle solid lubricant component is finely dispersed, so that it has low strength and is easily broken.
There is also a problem that abnormal wear occurs under high load conditions.

Further, even in the case of the solid lubricant having the latter composition, there is a problem that the strength is not sufficiently improved and the use is limited.

[0008]

As described above, the conventional solid lubricant has a problem that its use is limited to an extremely narrow range because of its low strength and poor toughness.

[0009] Therefore, an object of the present invention is to provide a solid lubricant and a sliding machine element which can obtain excellent lubrication performance, high strength and high toughness and thus contribute to the expansion of applications.

[0010]

In order to achieve the above object, a solid lubricant according to the present invention comprises a lubricating phase containing a solid lubricant as a main component and a bonding phase containing a metal or an alloy as a main component. It is formed of a composite sintered material containing a reinforcing phase made of at least one of metal, ceramics, glass, carbon fibers or whiskers.

Preferred materials for forming the lubricating phase include tungsten disulfide (WS ₂ ), molybdenum disulfide (MoS ₂ ), graphite, fluorinated graphite and boron nitride. In particular, WS ₂ has a small amount of reaction loss when a solid lubricant is produced by mixing, molding, and sintering a fiber that is a reinforcing phase forming material and a metal powder that is a binder phase constituent material, and has excellent lubricating characteristics. It is more preferable because it contributes to the realization of

Preferred materials for forming the binder phase include Cu, Ag, Mo, W, Co, Nb, Al,
Cu-Sn, Cu-Pb-Zn, Fe-Cu-Mn, N
Examples thereof include metals and alloys such as i-Cr, W-Cu, and Ta-Cu. If the volume ratio of the lubricating phase to the binder phase is less than 10/90, the lubricity is poor, and if it exceeds 90/10, it becomes difficult to retain the lubricating phase component and the amount of wear increases.

Preferred materials for forming the strengthening phase include W, Mo, Cr, Ta, Nb, Fe, Ni,
At least one metal fiber or whisker selected from Co and Cu, or alloy fiber or whisker containing these as the main components, or SiC, Si ₃ N ₄ , and Al
There may be mentioned ceramic fibers such as ₂ O ₃ or whiskers, or fibers such as glass and carbon.

Among these, W, Mo, Cr, Ta, N
At least one kind of metal fiber selected from b, Fe, Ni, Co, and Cu or an alloy fiber containing these as main components has strong bonding with the lubricating phase component and the binder phase component after sintering, It is more preferable because it can contribute to the improvement of strength and toughness. Especially, diameter of 5 to 200 μm and length of 0.1 mm
W fibers of up to 5 mm are more preferable because they have a large reinforcing effect and high strength at high temperature. If the content of this strengthening phase is less than 5 vol%, there is little improvement effect on strength and wear resistance.
If it exceeds 70 vol%, the components of the lubricating phase are relatively reduced and the lubricity is lowered. Therefore, the range of 5 to 70 vol% is preferable.

Since the strength of a solid lubricant containing fibers as a reinforcing phase largely depends on the orientation coefficient of the fibers, it is most preferable to orient one-dimensionally in the direction of action of force.

Further, in the sliding machine element according to the present invention, the element body has a lubricating functional component containing a solid lubricant as a main component, a coupling functional component containing a metal or an alloy as a main component, a metal, a ceramic, and a glass. , A composite sintered material containing a reinforcing functional component made of at least one kind of carbon fiber or whisker.

[0017]

The solid lubricant and the sliding machine element according to the present invention are composed of a lubricating phase containing a solid lubricant as a main component, a bonding phase containing a metal or an alloy as a main component, and fibers of metal, ceramics, glass and carbon. Alternatively, it is formed of a composite sintered material containing a reinforcing phase composed of at least one kind of whiskers.

Therefore, by appropriately setting the orientation coefficient of the fibers or whiskers in consideration of the action direction of force, the strength and toughness can be greatly improved as compared with the conventional solid lubricant.

That is, the solid lubricant according to the present invention is made by sintering. At this time, if the deterioration due to the diffusion of the mixed solid lubricant is taken into consideration, the sintering temperature cannot be set too high. Therefore, the strength of the binder phase cannot be increased so much. However, the fiber can have a sufficiently high sintering temperature. Therefore, the tensile strength of the fiber is much larger than the tensile strength of the binder phase. For example, taking the combination of tungsten fiber as the reinforcing phase and tungsten as the binder phase as an example, the tensile strength of the tungsten fiber is
It is 5 times the tensile strength of the tungsten metal binder phase obtained by sintering at 1000 ° C. Therefore, the strength can be significantly improved by incorporating the tungsten fiber into the solid lubricant composed of the tungsten metal binding phase and the lubricating phase. In addition, in the case of this combination, since the reinforcing phase and the binding phase are the same kind of metal, internal stress does not occur because the linear expansion coefficients are the same even if the temperature environment changes, and the bonding strength is improved. Can be higher.

[0020]

Embodiments will be described below with reference to the drawings.

FIG. 1 shows a sectional structure diagram of a solid lubricant according to an embodiment of the present invention.

This solid lubricant is W as a solid lubricant.
It is formed of a composite sintered material including a lubricating phase 1 made of S ₂ , a binder phase 2 made of a W—Cu alloy, and a reinforcing phase 3 made of long filaments of tungsten.

In the case of this example, the weight ratio of WS ₂ , W--Cu alloy and W long fiber is set to 40: 37.8: 16.2: 6. The W long fibers constituting the reinforcing phase 3 are oriented so as to extend in a state substantially parallel to the direction in which the force acts.

FIG. 2 shows a sectional structure diagram of a solid lubricant according to another embodiment of the present invention. This solid lubricant is
Lubricating phase 1 consisting of WS ₂ as a solid lubricant, and WC
It is formed of a composite sintered material containing a binder phase 2 made of a u alloy and a reinforcing phase 3a made of a tungsten short fiber.

In the case of this example, the weight ratio of WS ₂ , W--Cu alloy, and W short fibers is set to 30: 44.1: 18.9: 7. Then, the W short fibers constituting the reinforcing phase 3a are two-dimensionally oriented in a plane parallel to the direction in which the force acts.

Here, the orientation of the fibers constituting the reinforcing phase 3 (3a) will be described.

Now, assuming that the solid lubricant is broken by breaking the contained fiber, the tensile strength σc of the solid lubricant is σc = β · σf · Vf + σm ′ (1-V1-Vf) It can be expressed as (1).

In the formula (1), β: orientation coefficient σf: tensile strength of fiber σm ': tensile strength of binder phase Vf: volume content of fiber Vl: volume content of solid lubricant.

As can be seen from the equation (1), in order to improve the tensile strength σc of the solid lubricant without lowering the lubricating effect,
Tensile strength of binder phase σm 'and volume content of solid lubricant V
It is effective to make l constant and to contain a large amount of fibers having a tensile strength higher than that of the binder phase and to increase the orientation coefficient β.

Now, let us consider the orientation coefficient β.

Considering a coordinate system as shown in FIG. 3, the strength σc of the solid lubricant is taken as the strength in the X-axis direction.

First, when a total of n fibers are three-dimensionally randomly oriented, and the inclinations of the fibers in the xz plane, xy plane, and zy plane are θ, η, and ξ, respectively, the number of orientations is shown in FIG. As shown. Here, the slope ξ does not affect the strength in the x-axis direction. Therefore, its orientation coefficient β is

[Equation 1]

It becomes

When the fibers are oriented in the x-axis direction, xz
FIG. 5 shows the inclinations of the fibers in the plane, the xy plane, and the zy plane with respect to θ, η, and ξ.
Note that the solid line in the figure is the case where it is ideally oriented in the x-axis direction. In that case, the orientation coefficient β is 1. The broken line is x
This is the distribution when there is a tendency to be oriented in the axial direction.

Similarly, a case where two-dimensional random orientation in the xz plane is observed is as shown in FIG. The orientation coefficient β in that case is

[Equation 2]

It becomes

FIG. 7 shows the case of two-dimensional random orientation in the xy plane, and the orientation coefficient β is the same as in the case of the xz plane.

When the two-dimensional random orientation is made in the zy plane, the result is as shown in FIG. Since cos (π / 2) = 0, the orientation coefficient β becomes 0.

As can be seen from the equation (1), the strength σc increases as the orientation coefficient β increases. As described above, the value is 0 in the case of two-dimensional random orientation on a plane perpendicular to the force acting direction, and 0 in the case of three-dimensional random orientation.
405, 0.637 in the case of two-dimensional random orientation in the plane including the force action direction, and 1 in the case of ideal orientation in the force action direction.

Therefore, when the strength of the material is increased by incorporating fibers, the fibers are two-dimensionally orientated in a plane including the direction in which the force acts rather than the three-dimensional random orientation, or the force is It turns out that it is effective to orient one-dimensionally in the direction of action.

The composite sintered material is prepared by mixing the materials, molding under pressure,
It is manufactured by the procedure of sintering. In this series of procedures, pressure molding affects the orientation of the fibers it contains.

That is, when the pressing direction at the time of pressure molding is set as shown in FIG. 9 (a), FIG.
As shown in the observation image of the ABCD cross section of (a), the contained W short fibers, for example, tend to be two-dimensionally randomly oriented in a plane perpendicular to the pressing direction. Therefore, when processing this sintered material to manufacture a mechanical element, it is necessary to perform centering so that the direction of the force applied to the mechanical element and the orientation direction of the W short fibers coincide with each other. Here, the result of an experiment conducted to investigate the effectiveness of the solid lubricant shown in FIG. 2 will be described.

The materials used in this experiment are shown in Table 1. In addition, below, W powder is shown by Wp and W short fiber is shown by Wf. These materials were mixed in the composition ratio shown in Table 2 and 1000 ℃
Hot press sintering at No. The samples shown in 1 to 8 were manufactured. The pressing direction is from one direction as shown in FIG. These samples were evaluated in terms of strength and friction characteristics.

[0044]

[Table 1]

[0045]

[Table 2]

The strength of the sample was measured by a three-point bending test. In the test, it was bent in the pressing direction. Table 3 shows the results. In addition, a friction test was conducted under the sliding conditions shown in Table 4 in order to investigate the friction characteristics of the sample. The results are shown in Table 5. The friction surface corresponds to the ABCD surface shown in FIG. 9 (a), and the sliding direction is parallel to the lines AB and DC.

[0047]

[Table 3]

[0048]

[Table 4]

[0049]

[Table 5]

10 and 11 are graphs in which the results of Tables 3 and 5 are summarized by the composition ratio (vol%) of WS ₂ as a solid lubricant. 10 and 11, the W fiberization rate [Wf / (Wp + Wf)] is constant at 0.3.

As can be seen from FIG. 11, the tensile strength is improved when the amount of WS ₂ which is the solid lubricant is reduced. However, as can be seen from FIG. 10, when the amount of WS ₂ which is a solid lubricant is as small as 35 vol%, the lubricity is impaired, and the specific wear amount is an order of magnitude larger than that when WS ₂ is 50 vol% or more. Become. Therefore, the solid lubricant WS
It can be said that the amount of ₂ is required to be 50 vol% or more.

12 and 13 show WS which is a solid lubricant.
₂ is a graph summarizing the effects of the W fiberization rate on the specific wear amount and tensile strength when the amount of ₂ is kept constant at 60 vol%.

As can be seen from FIG. 13, the tensile strength is improved by increasing the W fiberization rate. Further, as can be seen from FIG. 12, by setting the W fiberization rate to 0.2 or more,
The specific wear amount is one digit smaller than that of the conventional one in which W fiber is not mixed (W fiberization rate 0).

A simple summary of the results of this experiment shows that sample N
o. Compared with the conventional solid lubricant containing no W fiber such as 1, the amount of solid lubricant WS ₂ is 50 vol%,
By mixing the same kind of W fiber as the base metal and making the fiberization rate 0.3 or more, the tensile strength is 2.4 times and the specific wear amount is 1
It can be made orders of magnitude smaller.

FIG. 14 shows a schematic sectional view of a sliding machine element formed of a solid lubricant according to the present invention, in which a rotary anode X-ray tube incorporating a cage for a rolling ball bearing is incorporated. There is. As shown in the figure, a cathode 11 that emits electrons and an anode target 14 that is integrally fixed to a rotor 13 on a rotating shaft 12 are arranged opposite to each other in a vacuum container 10. In this figure, a radiation window for guiding the X-rays emitted from the anode target 14 to the outside is omitted.

The rotary shaft 12 includes two ball bearings 15a, 15
It is rotatably supported by b. Ball bearing 15a,
15b is composed of an inner ring 17, an outer ring 18, and a plurality of balls 19 rotatably arranged between them. A magnetic field generator (not shown) is provided outside the vacuum container 10. The rotating magnetic field generated by the magnetic field generator causes the rotor 13 to rotate, whereby the rotating shaft 12 and the anode target 14 rotate together. It is supposed to do.

As shown in an enlarged view in FIG. 15, the ball bearing 15a incorporates a retainer 20 for holding the ball 19, and the retainer 20 is made of the solid lubricant according to the present invention. There is.

Before explaining the specific structure of the cage 20, let us consider what force acts on the cage 20.

FIG. 16 (a) shows a schematic sectional view of a rolling ball bearing. In the rolling ball bearing, the transfer surfaces of the inner ring 17 and the outer ring 18 are in contact with the sphere 19 at a contact angle α so as to support the axial force and the force in the direction orthogonal thereto. Further, when mounting the bearing, the inner ring 17 and the outer ring 18 of the bearing may be damaged due to poor machining accuracy of the shaft or the bearing housing and bearing mounting error.
An inclination θ between them occurs. At this time, the contact angle α is as shown in FIG.
It changes depending on the bearing rotation angle phase φ as shown in 6 (b). The contact angle α also changes depending on the main load p _i acting on the sphere 19. The main load p _i also changes depending on the bearing rotation angle phase φ.

Here, the revolution speed Vb of the sphere is geometrically Vb = πdm {1-Dacos (α) / dm} ni / 120 (4)

In the equation (4), dm is the sphere revolution diameter Da is the sphere diameter ni is the inner ring rotation speed (rpm).

Therefore, the equation (4) can be expressed as follows for the above reason.

Vb = πdm {1-Dacos (α (φ) / dm} ni / 120 (5) That is, it is understood that the revolution speed Vb of the sphere changes depending on the bearing rotation angle phase φ. .

Generally, the revolution speed Vr of the cage 20 is
It is considered that it corresponds to the average speed of the revolution speed Vb of the sphere shown in the equation (5) during one revolution. On the other hand, the revolution speed Vb of the ball is
As shown in equation (5), it changes depending on the bearing rotation angle phase φ. Now, let us consider a bearing in which a pure moment acts around an axis passing through the phases φ = 0 and π as shown in FIG. Revolution speed Vr of cage 20 and revolution speed V of ball 19
From the difference from b, the phases φ1 to φ2 and φ5 shown in FIG.
At φ6, the ball 19 comes into contact with the rear surface of the ball pocket of the cage 20, and at phases φ3 to φ4 and φ7 to φ8, the ball 19 comes into contact with the front surface of the ball pocket of the cage 20. As a result, as shown in FIG. 18, the cage 20 receives compressive stress near the phase φ = 0 and π and tensile stress near the phase φ = π / 2 and 3π / 2. In other words, when focusing on a part of the cage 20, the double-spinning repetitive stress acts twice per revolution of the cage. This is considered to be the cause of breaking the cage 20.

Therefore, in this embodiment, a lubricating functional component containing a solid lubricant as a main component, a bonding functional component containing a metal or an alloy as a main component, and at least one of metal, ceramics, glass and carbon fibers were used. Cage 2 formed of a solid lubricant made of a composite sintered material containing a strengthening functional component, that is, a solid lubricant whose strength is increased by adding fibers
It incorporates 0.

The cage 20 incorporated in this embodiment is
As shown in FIG. 19, the long fibers 21 as the reinforcing functional component are oriented in the circumferential direction in which the repeated stress that is considered to be the cause of the cage breakage acts, and the strength is further increased. Therefore, this cage 20 is excellent in lubricity and exhibits high strength characteristics. In the case of this example, the ball bearing 15a having the highest temperature among the plurality of ball bearings has the cage 20 made of a solid lubricant containing fibers, so that the degree of vacuum in the vacuum container 10 is lowered. And not
A low friction lubrication state can be maintained. In addition, in FIG.
Indicates a ball pocket.

In the above-mentioned embodiment, the long fibers are contained as the reinforcing functional component, but as shown in FIG. 20, the cage 20 in which the short fibers 21a as the reinforcing functional component are oriented in the circumferential direction, As shown in 21, a cage 20b in which short fibers as a reinforcing functional component are two-dimensionally randomly oriented may be incorporated in a surface 24 parallel to the cage cylindrical side surface 23. Further, as shown in FIG. 22, a cage 20c in which short fibers as a reinforcing functional component are two-dimensionally randomly oriented may be incorporated in a surface 25 perpendicular to the cage cylindrical side surface 23. The orientation of the fibers as shown in FIGS. 20 to 22 is such that after mixing the materials, a cylindrical solid lubricant is manufactured by hot press sintering while applying a force in the direction indicated by the solid arrow in FIGS. 23 to 25. It is obtained by doing.

FIG. 26 is a schematic sectional view of a sliding machine element formed of a solid lubricant according to the present invention, in which a rotary anode X-ray tube incorporating a pressure contact member of a rolling ball bearing is incorporated. There is.

The main part of this rotating anode X-ray tube has the same structure as that shown in FIG. Therefore, the same portions are denoted by the same reference numerals, and detailed description of overlapping portions will be omitted.

In this example, as shown in an enlarged view in FIG. 27, a pressure contact member 31 formed in a ring shape on the ball 19 mounted on one ball bearing 15a is pressed in the axial direction by the restoring force of the leaf spring 32. are doing. The pressure contact member 31 is formed of the solid lubricant according to the present invention.

Before explaining the specific structure of the pressure contact member 31, let us consider what kind of force acts on the pressure contact member 31.

In the pressure contact member 31 incorporated in the rolling ball bearing, as shown in FIGS. 27 and 28, one end face in the axial direction serves as a contact face in contact with the ball 19 of the rolling ball bearing 15a, and the other end face directly. Alternatively, the pressure receiving surface 33 receives a force from the leaf spring 32 via the plate.

Therefore, as shown in FIG. 29, in the A-direction viewing surface, compressive stress acts on the right side of the widthwise center of the pressure contact member 31, and tensile stress acts on the left side. Also,
The direction of this stress is the circumferential direction of the pressure contact member. This is considered to be the cause of breaking the press contact member 31.

Therefore, in this embodiment, a lubricating functional component containing a solid lubricant as a main component, a bonding functional component containing a metal or an alloy as a main component, and at least one of fibers of metal, ceramics, glass and carbon were used. A pressure contact member 31 formed of a solid lubricant made of a composite sintered material containing a strengthening functional component, that is, a solid lubricant whose strength is increased by adding fibers is incorporated.

The pressure contact member 31 incorporated in this embodiment.
As shown in FIG. 30, the long fibers 41 as a reinforcing functional component are oriented in the circumferential direction of the pressure contact member on which the compressive stress and the tensile stress, which are considered to be the cause of the pressure contact member rupture, act, and the strength is further increased. There is. Therefore, the pressure contact member 31 has excellent lubricity and exhibits high strength characteristics. Also in the case of this example, since the ball bearing 15a, which has the highest temperature among the plurality of ball bearings, has the pressure contact member 31 made of a solid lubricant containing fibers, the degree of vacuum in the vacuum container 10 is reduced. It is possible to maintain a low friction and low lubrication state.

In the above-mentioned embodiment, the long fibers are contained as the reinforcing functional component, but as shown in FIG. 31, the pressure contact member 31a in which the short fibers 41a as the reinforcing functional component are oriented in the circumferential direction, and As shown in 32, a cage 31b in which short fibers as a reinforcing functional component are two-dimensionally randomly oriented may be incorporated in a surface 43 parallel to the pressure contact member cylindrical side surface 42. Further, as shown in FIG. 33, a short pressure fiber serving as a reinforcing functional component may be incorporated in a surface 44 perpendicular to the side surface 42 of the pressure contact member, in which the pressure contact member 31c is randomly oriented in two dimensions.

The orientation of the fibers as shown in FIGS. 31 to 33 is obtained by mixing the materials and then applying a force in a direction indicated by a solid arrow in FIGS. 23 to 25 by hot press sintering to form a cylindrical solid. Obtained by manufacturing a lubricant.

FIG. 34 shows a sliding machine element made of the solid lubricant according to the present invention, here, a gear 51.

Before explaining the specific structure of the gear 51, let us consider what kind of force acts on the gear 51.

As shown in FIG. 35, when the gear 51 tries to transmit the rotational force Fa of the shaft to another gear, a force of Fb acts on its tooth surface as a reaction thereof. Therefore,
A bending stress Fc as shown in FIG. 36 acts on the tooth base.

The gear 51 according to this embodiment comprises a lubricating functional component containing a solid lubricant as a main component, a coupling functional component containing a metal or an alloy as a main component, metal, ceramics, glass,
It is formed of a solid lubricant made of a composite sintered material containing a reinforcing functional component made of at least one kind of carbon fiber, that is, a solid lubricant whose strength is increased by adding fibers.

As shown in FIG. 34, the gear 51 according to this embodiment has two fibers as a reinforcing functional component on the surface 52 perpendicular to the tooth surface on which the bending stress Fc, which is considered to be the cause of the gear 51 breaking, acts. Dimensionally oriented. Such fiber orientation can be obtained by mixing the materials and then producing a cylindrical solid lubricant by hot press sintering while applying a force in the direction indicated by the solid arrow in FIG.

Therefore, the gear 51 is excellent in lubricity and exhibits high strength characteristics.

[0084]

As described above, according to the present invention,
It is possible to provide a solid lubricant and a sliding machine element that can maintain a low-friction lubrication state even in high temperature and vacuum, and that are not easily damaged.

[Brief description of drawings]

FIG. 1 is a sectional structure diagram of a solid lubricant according to an embodiment of the present invention.

FIG. 2 is a sectional structure diagram of a solid lubricant according to another embodiment of the present invention.

FIG. 3 is a diagram for explaining the orientation of contained fibers.

FIG. 4 is a diagram for explaining the orientation of contained fibers.

FIG. 5 is a diagram for explaining the orientation of contained fibers.

FIG. 6 is a diagram for explaining the orientation of contained fibers.

FIG. 7 is a diagram for explaining the orientation of contained fibers.

FIG. 8 is a diagram for explaining the orientation of contained fibers.

FIG. 9 is a diagram for explaining the relationship between the pressing direction and the orientation of fibers.

FIG. 10 is a diagram showing a relationship between a solid lubricant amount and a specific wear amount characteristic of the solid lubricant according to the present invention.

FIG. 11 is a graph showing the relationship between the amount of solid lubricant and the tensile strength of the solid lubricant according to the present invention.

FIG. 12 is a diagram showing the relationship between the fiberization rate and the specific wear amount characteristic of the solid lubricant according to the present invention.

FIG. 13 is a diagram showing the relationship between the fiberization rate and the tensile strength of the solid lubricant according to the present invention.

FIG. 14 is a schematic cross-sectional view of a rotary anode X-ray tube incorporating a cage according to the present invention.

FIG. 15 is an enlarged sectional view showing a main part of the rotating anode X-ray tube.

FIG. 16 is a diagram for explaining a force that acts on a cage.

FIG. 17 is a view for explaining a force that acts on a cage.

FIG. 18 is a diagram for explaining a force that acts on a cage.

FIG. 19 is a perspective view of an assembled cage.

FIG. 20 is a perspective view showing a modified example of the cage.

FIG. 21 is a perspective view showing another modified example of the cage.

FIG. 22 is a perspective view showing still another modified example of the cage.

FIG. 23 is a diagram for explaining a cage manufacturing method in which the orientation of fibers is taken into consideration.

FIG. 24 is a diagram for explaining a cage manufacturing method in which the orientation of fibers is taken into consideration.

FIG. 25 is a diagram for explaining a cage manufacturing method in which the orientation of fibers is taken into consideration.

FIG. 26 is a rotary anode X incorporating a pressure contact member according to the present invention.
Schematic cross section of a wire tube

FIG. 27 is an enlarged sectional view showing a main part of the rotating anode X-ray tube.

FIG. 28 is a view for explaining a force that acts on the pressure contact member.

FIG. 29 is a view for explaining a force acting on the pressure contact member.

FIG. 30 is a perspective view of an assembled pressure contact member.

FIG. 31 is a perspective view showing a modified example of the pressure contact member.

FIG. 32 is a perspective view showing another modification of the pressure contact member.

FIG. 33 is a perspective view showing still another modified example of the pressure contact member.

FIG. 34 is a perspective view of a gear according to the present invention.

FIG. 35 is a diagram for explaining a force acting on a gear.

FIG. 36 is a diagram for explaining a force acting on a gear.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Lubrication phase 2 ... Bonding phase 3, 3a ... Reinforcement phase 10 ... Vacuum container 11 ... Cathode 12 ... Rotating shaft 14 ... Anode target 15a, 15b
... Ball bearing 17 ... Inner ring 18 ... Outer ring 19 ... Ball 20, 20a, 20b, 20c ... Retainer 31, 31a, 31b, 31c ... Pressure contact member 32 ... Leaf spring 41 ... Long fiber 41a ... Short fiber 51 ... Gear

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Naofumi Hiraoka, 1 Komukai Toshiba-cho, Sachi-ku, Kawasaki-shi, Kanagawa Incorporated, Toshiba Research and Development Center, Inc. No. 7 Higashi Shiba Tungaloy Co., Ltd.

Claims (7)

[Claims] 1. A lubricating phase containing a solid lubricant as a main component, a bonding phase containing a metal or an alloy as a main component, and a reinforcing phase containing at least one of metal, ceramics, glass, carbon fibers and whiskers. A solid lubricant, which is formed of a composite sintered material. 2. The solid lubricant according to claim 1, wherein the lubricating phase is at least one selected from tungsten disulfide, molybdenum disulfide, graphite, graphite fluoride, and boron nitride. . 3. The binder phase is Cu, Ag, Mo, W, C
o, Nb, Al, Cu-Sn, Cu-Pb-Zn, Fe
The solid lubricant according to claim 1, wherein the solid lubricant is at least one metal or alloy selected from -Cu-Mn, Ni-Cr, W-Cu, and Ta-Cu. 4. The strengthening phase is W, Mo, Cr, Ta, N.
2. At least one metal fiber selected from b, Fe, Ni, Co and Cu, or at least one alloy fiber selected from alloys containing these as main components. The solid lubricant described. 5. The lubricating phase is tungsten disulfide,
The binder phase is at least one selected from Cu, Ag, W, Mo and Ta, and the strengthening phase has a diameter of 5 to 200.
The solid lubricant according to claim 1, which is a tungsten fiber having a length of 0.1 μm and a length of 0.1 to 5 mm. 6. The element body comprises a lubricating functional component containing a solid lubricant as a main component, a bonding functional component containing a metal or an alloy as a main component, and at least one of metal, ceramics, glass, carbon fibers or whiskers. A sliding machine element, characterized in that it is formed of a composite sintered material containing a strengthening functional component. 7. The sliding machine element according to claim 6, wherein the element body is a cage or a pressure contact member of a rolling ball bearing, or a gear.