DE112007001043T5 - Multi-row rolling bearing arrangement - Google Patents

Abstract

Multi-row rolling bearing assembly comprising:
a plurality of rolling bearing units arranged relative to each other;
a pair of bearing grease spacers interposed between respective outer races of the adjacent rolling bearing units, each of the bearing lubricating spacers having a nozzle for discharging a lubricating oil onto an inner race of the adjacent rolling bearing unit and a collar disposed on an outer diametrical side of the nozzle and covering an outer periphery of the inner race ; and
an oil discharge space communicating with a space in each of the adjacent rolling bearing units into which the lubricating oil discharged from the nozzle is discharged, the oil discharge space being provided with one of the following structures (A) and (B):
(A) the structure in which a single intermediate outer ring spacer is interposed between the bearing lubricating spacers and the oil discharge space is defined between each of the bearing lubricating spacers and the intermediate outer ring spacer;
(B) The structure in which an inner ring spacer is inserted between the respective inner rings of the adjacent rolling bearing units, wherein Ölauslassausnehmungen, which towards an inner periphery ...

Description

BACKGROUND OF THE INVENTION

The The present invention relates to a multi-row roller bearing assembly, which a juxtaposed arrangement of a variety of Includes bearing units that support a used in a machine tool main shaft is used and in particular relates to the lubrication of the ultra-high speed rotating bearing assembly when such bearing units in a back-to-back Combination can be used while attached to a solid Position are biased.

Around the machining efficiency of a main shaft of a machine tool increase, there is a tendency to increase the Speed out. When a main shaft is operating at high speed will increase the torque and that in a main shaft bearing developed amount of heat. In view of this, beam lubrication and Air oil lubrication widely used to lubricate the main shaft bearing used to work around this problem.

The Jet lubrication is of a type in which a significant amount of oil is blasted into the bearing, at the same time the bearing lubrication and bearing cooling, but this lubrication method has an increase in the resistance to movement of the lubricating oil result (essentially proportional to the square of the speed) when the bearing is operated at high speed, and therefore increased a loss of performance of the bearing, resulting in a problem, which with the need for a high power drive motor is linked.

Further, the air oil lubrication is of a type in which a lubricating oil is mixed with a carrier air and the oil is sprayed into the bearing through a nozzle, and to reduce the resistance to movement of the oil in the bearing, it has been suggested that a small amount of the oil is brought to an outer diametrical surface of an inner ring so that it can be supplied to a raceway section by utilizing a centrifugal force and a surface tension (see, for example, FIGS Japanese Laid-Open Patent Publication No. 2001-012481 , No. 2002-54643 ).

The conventional lubricating apparatus utilizing air-oil lubrication is insufficient for providing a bearing cooling effect, and therefore has a problem associated with heat generation of the bearing when used in an environment where ultra-high speed is applied. As a lubricating device which is effective in avoiding such a cooling problem and effective in ultra high-speed rotation operation, the applicant has the Japanese Laid-Open Patent Publication No. 2006-118525 proposed. When this proposal is made as a multi-row rolling bearing assembly which is used, for example, in a main shaft front side in a back-to-back combination biased at a fixed position, such a multi-row rolling bearing assembly takes such a construction as shown in FIG 13 is shown.

This multi-row rolling bearing assembly has a shape in which an outer ring spacer as Lagerschmierabstandshalter 58 is executed and the lubricating oil from nozzles 59 the bearing lubricant spacer 58 in circumferentially extending grooves 57 in respective end surfaces of the bearing inner rings 53 is discharged, so that the lubricating oil by the action of a centrifugal force and a surface tension in the direction of raceway surfaces 53a the inner rings 53 along oblique surface sections 53b in associated outer diametrical surfaces of the inner rings 53 can be performed. Further, a collar-like section 61 provided, which the respective inclined surface portion 53b covered with an intermediate gap, so that from the gap in the direction of the adjacent raceway surface 53a flowing lubricating oil can be performed.

• [Patentdokument 1] Japanische offengelegte Patentpublikation Nr. 2001-012481
• [Patentdokument 2] Japanische offengelegte Patentpublikation Nr. 2002-54643
• [Patentdokument 3] Japanische offengelegte Patentpublikation Nr. 2006-118525

From that of each of the nozzles 59 discharged lubricating oil, a part of the lubricating oil except that which flows in the very small gap dissipates heat, which is then developed in the inner ring as a result of the operation, and then goes outside through a lubricating oil outlet passage 62 dissipated. The lubricating oil outlet passage 62 is through the use of an annular cover element 60 formed with a generally U-shaped cross-section, which in an inner diametrical surface of each bearing lubricating spacer 58 is fitted. In other words, the lubricating oil outlet passage 62 from a shoulder surface 58a that has a large diameter in one half of an axially projecting side of the collar 61 has, ie in an axial half next to the storage unit 52 , except a point where the respective nozzle 59 is formed, and from an inner wall surface of the annular cover member 60 with a generally U-shaped cross-section, which in the remaining half, that of the axially projecting side of the collar 61 opposite, ie in the remaining axially of the respective storage unit 52 distant half, with a shoulder surface 58b with a large diameter over its entire circumference is engaged, and from a Ölauslassraum 64 passing through an outer diametral surface of the inner ring spacer 67 is limited, which is in contact with the end surface of the associated inner ring 53 is kept, and from egg an oil outlet passage 63 who with this oil outlet 64 connected to the outside, manufactured. The oil outlet passage 63 is formed at a location spaced from a location where the nozzle is located 59 in a circumferential direction of the bearing grease spacer 58 is formed by a radial through hole from the bearing liner spacer 58 to the annular cover element 60 is.

• [Patent Document 1] Japanese Laid-Open Patent Publication No. 2001-012481
• [Patent Document 2] Japanese Laid-Open Patent Publication No. 2002-54643
• [Patent Document 3] Japanese Laid-Open Patent Publication No. 2006-118525

However, it has been found that with the in 13 shown construction, in which two rolling bearing units 52 and 52 in a back-to-back combination which is biased at a fixed position, as shown therein, a pair of bearing lubrication spacers 58 and 58 axially adjacent to each other with respect to each other for the two rolling bearing units 52 and 52 be used. In such a case, such a construction is assumed in which the two annular cover elements 60 and 60 which are held in a back-to-back relationship to each other between the pair of lubricating oil outlet passages 62 and 62 to step. Therefore, there are problems not only in that the axial dimension of each of the bearing grease spacers 58 is increased, but increases the number of component parts, resulting in an increase in the number of processing steps, which is associated with an increase in cost.

Further, in the main shaft bearing, the axial inner gap is set in a range of a few micrometers to accompany the high-speed rotation and rigidity, but when the rolling bearings employing the above construction in a back-to-back combination are used Position is biased, as in 13 As shown above, there is a problem that, as discussed above, difficulties are encountered in adjusting the axial inner gap.

In other words, in the case of in 13 shown construction of the axial inner gap by processing respective end faces of the bearing lubricant spacers 58 and 58 or the inner ring spacer 67 with respect to each axial gap between the inner ring and the outer ring in the left and right rolling bearing unit 52 and 52 set. However, since the bearing grease spacer 58 a shape in which the collar 61 axially projecting from one end side, the processing of the corresponding end surface is difficult to achieve. Accordingly, the axial inner gap is formed by machining the end surface of the inner ring spacer 67 but if this inner gap is made too small compared to the desired one, there is no way other than the inner ring spacer 67 re-fabricate or the end face of each bearing grease spacer 58 to edit.

on the other hand it is necessary, the main shaft used in the machine tool in its axial dimension because of the compactness of a machine to reduce, and because of this is the reduction of the axial Dimensions of each grease bearing spacer adjacent to the main shaft be installed, desired.

SUMMARY OF THE INVENTION

A Object of the present invention is a multi-row rolling bearing assembly to provide in which an oil outlet passage ensured can be, and therefore allows the cooling of the bearing assembly in which a reduction in the number of component parts, a reduction in the number of production steps, a cost reduction and a reduction of the axial dimension can be achieved while it has a construction which is for a high-speed rotation can be used, and in which the axial inner gap easy can be adjusted.

A Another object of the present invention is to provide a mainshaft spindle and to make a machine more compact in itself when the bearing assembly used for supporting a main shaft of the machine tool becomes.

• (A) Der Aufbau, in welchem ein einzelner Zwischenaußenringabstandshalter zwischen die Lagerschmierabstandshalter eingefügt ist und der Ölauslassraum zwischen jedem der Lagerschmierabstandshalter und dem Zwischenaußenringabstandshalter definiert ist.
• (B) Der Aufbau, in welchem ein Innenringabstandshalter zwischen die jeweiligen Innenringe der benachbarten Wälzlagereinheiten eingefügt ist, wobei Ölauslassausnehmungen, welche in Richtung einer Innenperipherie geöffnet sind, in jeweiligen Seitenflächen der Lagerschmierabstandshalter gebildet sind, welche in Kontakt miteinander gehalten sind, und der Ölauslassraum zwischen Innenflächen der Ölauslassausnehmungen in den Lagerschmierabstandshaltern und einer äußeren Diametralfläche des Innenringabstandshalters gebildet ist.

A multi-row rolling bearing assembly comprising a plurality of rolling bearing units disposed relative to each other; a pair of bearing grease spacers interposed between respective outer races of the adjacent rolling bearing units, each of the bearing lubricating spacers having a nozzle for discharging a lubricating oil onto an inner race of the adjacent rolling bearing unit and a collar disposed on an outer diametrical side of the nozzle and covering an outer periphery of the inner race ; and an oil discharge space communicating with a space in each of the adjacent rolling bearing units into which the lubricating oil discharged from the nozzle is discharged, the oil discharge space being provided with one of the following structures (A) and (B):

• (A) The construction in which a single Zwi is inserted between the Lagerschmierabstandshalter and the Ölauslassraum between each of the Lagerschmierabstandshalter and the Zwischenaußenringabstandshalter is defined.
• (B) The structure in which an inner ring spacer is interposed between the respective inner rings of the adjacent rolling bearing units, wherein Ölauslassausnehmungen which are open towards an inner periphery, formed in respective side surfaces of the Lagerschmierabstandshalter, which are held in contact with each other, and the Ölauslassraum between Inner surfaces of the Ölauslassausnehmungen is formed in the Lagerschmierabstandshaltern and an outer diametrical surface of the inner ring spacer.

According to the the above structure (A), the supply of the lubricating oil in the Rolling bearing units performed with the lubricating oil which are from the nozzles in the bearing grease spacers is dissipated. Since the oil outlet between the single intermediate outer ring spacer and each of the pairwise Lagerschmierabstandshalter is formed, may further the oil outlet passage for that of the nozzles discharged lubricating oil can be ensured and the cooling of the bearing units with the lubricating oil can be achieved, what the use for a high-speed rotation and allows ultra-high speed rotation. As to ensure this Ölauslassraums such Structure is used, in which the individual Zwischenaußenringabstandshalter provided between the Lagerschmierabstandshaltern on both sides there is no need, an additional annular Cover element for each of the bearing grease spacers add as suggested in the previously described Example is required. Accordingly, the width the arrangement of the bearing grease spacers and the axial dimension the multi-row rolling bearing assembly can be reduced.

There there is no need for an additional annular Cover element for each of the bearing grease spacers In addition, the structure can be simplified, the number of component parts can be reduced and the reduction the number of assembly steps and the cost can be achieved.

There the single intermediate outer ring spacer and the pairwise Bearing lubricant spacers, between which this Zwischenaußenringabstandshalter is inserted between the respective outer rings of the adjacent Rolling bearing units occur, is additionally the just setting the dimensions between the end faces the Zwischenaußenringabstandshalters sufficient to the Adjustment of the axial inner gap to facilitate. The above oil outlet space may be a type of temporary retention the lubricating oil is opened to the outside, or a type containing the retained lubricating oil can hold.

There the oil outlet space between the bearing grease spacers is formed, as in the case of the structure (A) discussed above, even with the above construction (B), the oil outlet passage for that of the nozzles in the bearing grease spacers discharged lubricating oil can be ensured, and the cooling of the bearing units with the lubricating oil can be achieved, which makes it possible for a high-speed rotation and an ultrahigh-speed rotation to be used. Because while ensuring this Ölauslassraums Such a structure is used, in which the on the inner peripheral surface open Ölauslassausnehmungen in each Side surfaces of the bearing lubricant spacers on their Contact sides are formed, and the space through respective inner surfaces the Ölauslassausnehmungen in these bearing lubricating spacers is surrounded and the outer diametrical surface of the inner ring spacer designed as the Ölauslassraum there is no need, an additional annular Cover element for each of the bearing grease spacers add as suggested in the previously described Example is required. For this reason, the construction in the Bearing Grease Spacers, which are used to remove the oil necessary, simplifies the number of component parts can be reduced and reducing the number of assembly steps and the cost can be achieved. Furthermore, the width of the Arrangement of the spacers are narrowed and the axial dimension the multi-row rolling bearing assembly can be reduced.

If the Ölauslassraum with the structure discussed above (A) is provided, the Zwischenaußenringabstandshalter have a Ölauslassausnehmung, which in each of its is defined opposite surfaces, and the Ölauslassraum can between the Ölauslassausnehmung and the side surface of the bearing grease spacer be. With such a simplified structure, the oil outlet passage for the lubricant discharged from the nozzle be ensured.

Further, when the oil discharge space having the structure (A) discussed above is provided, an inner ring spacer may be interposed between the respective inner rings of the adjacent rolling bearing units, and the oil discharge space may be interposed between side surfaces of the bearing grease spacers facing side surfaces from which the respective collars protrude ren diametrical surface of the Zwischenaußenringabstandshalters and an outer diametrical surface of the inner ring spacer may be formed. Even in this case, with a simplified structure, the oil discharge passage for the lubricant discharged from the nozzle can be ensured. The Zwischenaußenringabstandshalter preferably has a ring shape with a rectangular section.

If the Ölauslassraum with the structure discussed above (A) is provided, the pair of Lagerschmierabstandshalter than be used inserted into respective annular shoulders, which on inner peripheral sides of axially opposite ends are formed of the Zwischenaußenring spacers, the Zwischenaußenringabstandshalter can Ölauslassausnehmung which are in each of its opposite surfaces is defined, and the Ölauslassraum can between the Ölauslassausnehmung and the side surface of the bearing grease spacer be.

In in such a case, using each of the bearing grease spacers and the outer ring spacer, which are separate from each other Elements are it does that make editing (for example loops) axially opposite end surfaces (width surfaces) the intermediate ring spacer is possible, adjusting the dimension of the width surfaces thereof simplify. Thereafter, the Lagerschmierabstandshalter in the corresponding annular shoulder of the Zwischenaußenringabstandshalters used. In other words, although a build-up of the bearing grease spacer occurs, wherein the collar axially from one of its side surfaces protrudes, the width surfaces of this Zwischenaußenring spacers be processed in a state in which the Lagerschmierabstandshalter from the Zwischenaußenringabstandshalter are removed. Accordingly, the Wide surfaces of the Zwischenaußenringabstandshalters easy to work without being obstructed by the collar. Therefore, by merely setting the dimensions between the width surfaces of the Zwischenaußenringabstandhalters the axial inner gap can be easily adjusted. By the bearing grease spacers and the Zwischenaußenringabstandshalter separated from each other Furthermore, the back (which is each of the Ring shoulders opposite side) of the bearing grease spacer be edited and set. Accordingly, can the gap between the outer diametrical section the inner ring and the collar are precisely controlled. With a so precisely controlled gap there is no way that the lubricating oil in the bearing units in a higher flows as the required amount. Consequently, it is possible an increase in the resistance to movement of the lubricating oil to prevent and also a drive loss of the storage unit to prevent. Therefore, for example, the need for a drive motor can be avoided with high performance and the manufacturing cost be reduced. It is also possible to have a disability between the outer diametrical portion of the inner ring and to avoid the collar, which as a result of too small Crevices could occur, and which by assembly conditions the bearing units or by an extension of the inner ring below the influence of heat and centrifugal force can be caused.

Further even in this case, the supply of lubricating oil in the rolling bearing units with one of the nozzles oil drained in the bearing grease spacers and, since the oil outlet space between each of the oil outlet recesses in opposite surfaces of the outer ring spacer and each of the side surfaces of the bearing grease spacers is formed, the Ölauslassdurchgang for the lubricant be ensured and the cooling with the lubricating oil can be achieved, which makes it possible for a high-speed rotation and an ultrahigh-speed rotation to be used. Because this oil outlet between each of the Ölauslassausnehmungen in the opposite Surfaces of the intermediate outer ring spacer and each of the side faces of the paired bearing grease spacers is formed, there is no need, an additional annular cover element for each of the bearing grease spacers to add and accordingly, the axial dimension in which the Lagerschmierabstandshalter are arranged to be reduced. Since there is no need, an additional annular Add cover element for each of the bearing grease spacers, Further, the structure may be simple, the number of component parts can be reduced and a reduction in the number of assembly steps and the cost can be achieved.

If the annular shoulder in an inner peripheral side of each of the opposite Axialenden of the Zwischenaußenring spacers is formed, For example, as described hereinabove, an outer diametral section may be provided of the inner ring provided with an inner sloping portion whose diameter is from one side next to an end surface of the inner ring to a side adjacent to a raceway surface of the Inner ring increases, and the bearing spacer can in each annular shoulder in the outer ring spacer by one Einstellabstandshalter be provided, which has a gap between adjust the inner race angled section and the collar can.

According to this construction, the adjustment spacers present between each of the bearing lubricating spacers and the intermediate outer ring spacer can be machined and adjusted after the finished dimensions each of the rolling bearing units, the Zwischenaußenring spacers and others have been determined to be determined. In this way, the gap between the inner ring inclined portion and the collar can be accurately and easily controlled.

In The present invention can be the multi-row rolling bearing assembly be used to support a main shaft of a machine tool, in which case the adjacent storage units with the in between inserted Lagerschmierabstandshalter in a back-to-back combination can be used while at one fixed position are biased, as described later becomes.

in the Case of this construction may be the axial dimension of each of the bearing grease spacers can be reduced, and therefore the main shaft and the Machine tool to be made more compact in itself.

BRIEF DESCRIPTION OF THE DRAWINGS

On In any case, the present invention will become apparent from the following description their preferred embodiments clearly understood when used in conjunction with the accompanying drawings is taken. The embodiments and the drawings however, are for the purpose of illustration and explanation only given and are not intended to limit the scope of the present Invention, in whatever way, to use, with this Scope determined by the appended claims becomes. In the accompanying drawings, the same reference numerals used to designate like parts throughout several views and:

1 (A) Fig. 10 is a sectional view showing a multi-row rolling bearing assembly according to a first preferred embodiment of the present invention;

1 (B) is an enlarged view of an area shown by the symbol A of 1 (A) ;

2 FIG. 10 is a sectional view showing a spindle device connected to the in FIG 1 (A) shown multi-row rolling bearing assembly is equipped;

3 Fig. 10 is a sectional view showing the multi-row rolling bearing assembly according to a second preferred embodiment of the present invention;

4 FIG. 10 is a sectional view showing the spindle device associated with the in FIG 3 shown multi-row rolling bearing assembly is equipped;

5 Fig. 10 is a sectional view showing the multi-row rolling bearing assembly according to a third preferred embodiment of the present invention;

6 is a sectional view showing an important portion of the in 5 shown multi-row rolling bearing assembly shows;

7 FIG. 10 is a sectional view showing the spindle device associated with the in FIG 5 shown multi-row rolling bearing assembly is equipped;

8th Fig. 10 is a sectional view showing the multi-row rolling bearing assembly according to a fourth preferred embodiment of the present invention provided with a setting spacer;

9 is a sectional view showing an important portion of the in 8th shown multi-row rolling bearing assembly shows;

10 FIG. 10 is a sectional view showing the spindle device associated with the in FIG 8th shown multi-row rolling bearing assembly is equipped;

11 (A) Fig. 10 is a sectional view showing a multi-row rolling bearing assembly according to a fifth preferred embodiment of the present invention;

11 (B) FIG. 10 is an enlarged view of a portion of FIG 11 (A) ;

12 FIG. 10 is a sectional view showing the spindle device associated with the in FIG 11 (A) shown multi-row rolling bearing assembly is equipped; and

13 is a sectional view showing the proposed example.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

A first preferred embodiment of the present invention will be described in detail with particular reference to 1 described. 1 (A) FIG. 11 illustrates a sectional view of a multi-row rolling bearing assembly according to this embodiment. FIG. The illustrated multi-row rolling bearing assembly 1 is from a variety of (in the case shown two) rolling bearing units 2 built, which are juxtaposed relative to each other. Each of the rolling bearing units 2 is designed in the form of an angular ball bearing and is designed as a back-to-back combination and is used under bias condition at a fixed position. Each of the rolling bearing units 2 contains a variety of rolling elements 5 in the form of balls, which between a raceway surface 3a an inner ring 3 and a track surface 4a an outer ring 4 are inserted, wherein the rolling elements 5 through a holder 6 being held. Between the respective outer rings 4 and 4 the juxtaposed rolling bearing units 2 and 2 are an intermediate outer ring spacer 13 and a pair of bearing grease spacers 8th and 8th on each side of the intermediate outer ring spacer 13 inserted. Further, an inner ring spacer 17 between the respective inner rings 3 and 3 the juxtaposed rolling bearing units 2 and 2 inserted. Each of the bearing grease spacers 8th serves for discharging a cooling oil, of which a part of the corres-ring rolling bearing unit 2 is fed to the spacer 8th faces.

The holders 6 are of the outer race type and are preferably made of a phenol resin, PEEK, PPS, a polyamide resin, a C / C composite, an aluminum alloy or a Ti alloy (increase in strength during high-speed operation). The inner rings 3 are made, for example, from a carburized steel in view of a significantly increasing hoop stress during high speed operation. The rolling elements are preferably made of a ceramic material with a view to reducing the centrifugal force.

One of the opposite end surfaces of the inner ring 3 , which in each of the rolling bearing units 2 which is on a non-load side (on a bearing rear side) is provided with a circumferentially extending groove 7 formed, which is excluded axially inwardly. Further, an outer diametrical surface of the inner ring 3 on one side next to the circumferential groove 7 and continuously to the corresponding raceway surface 3a as an inclined surface section 3b with a large diameter next to the track surface 3a executed. In other words, a portion of the outer diametrical surface of the inner ring 3 where a stepped surface is provided as the inclined surface portion 3b executed.

When in contact with an end face of the outer ring 4 The bearing grease spacer forms 8th an annular outer ring spacer which is axially close to the rolling bearing unit 2 is provided. This bearing lubricant spacer 8th has a nozzle 9 extending in the direction of a portion of the end surface of the inner ring where the circumferential groove 7 is defined, open, and one with the nozzle 9 related oil feed passage 10 on, and is with a collar 11 Mistake. A cooling oil leading to the oil supply passage 10 fed and from the nozzle 9 is discharged, is in the circumferential groove 7 in the inner ring 3 a part of which is sprayed by utilizing a centrifugal force and a surface tension of an inner diametrical surface of the circumferential groove 7 along the inclined surface portion 3b and then along the track surface 3a of the inner ring 3 as lubricating oil flows.

The collar 11 extends from a side surface of the bearing grease spacer 8th in the direction of the adjacent storage unit 2 in an axial direction and superimposed on the inclined surface portion 3b with a gap δ ( 1 (B) ), which between it and the inclined surface section 3b is defined by the gap δ in the direction of the raceway surface 3a to lead flowing lubricating oil. The collar 11 is designed so that it becomes an inner diametrical side of the holder 6 extends. An angular portion at which the end surface of the inner ring 3 to which the nozzle 9 facing, and the inclined surface portion 3b cutting is considered a curved edge 3ba a bent configuration executed to separate the lubricating oil away from the inner ring 3 by preventing the angled edge under the influence of a centrifugal force.

One of the opposite side surfaces of each of the bearing grease spacers 8th , which the Zwischenaußenringabstandshalter 13 touched, is with a Ölauslassausnehmung 8a formed, which is open towards an inner periphery thereof. Furthermore, the Zwischenaußenringabstandshalter 13 an annular Ölauslassausnehmung 13a which is defined in its opposite surfaces, and oil discharge spaces 14 are each between the Ölauslassausnehmungen 13a and the Ölauslassausnehmungen 8a in the side surfaces of the bearing grease spacers 8th educated. These oil outlet spaces 14 stand with respective rooms 18 in connection, which ever Weil in the rolling bearing units 2 and 2 are formed, being in the rooms 18 the lubricating oil is removed. Respective sections of the opposite surfaces of the Zwischenaußenring spacers 13 which the associated bearing lubricant spacers 8th touch, are with groove-like Ölauslassdurchgängen 15 formed, which extends from the Ölauslassausnehmung 13a extend radially toward an outer peripheral surface. Further, a portion of one of the opposite side surfaces of each of the bearing grease spacers 8th which is in contact with an end face of the outer ring 4 is held with a radially extending groove-like Ölauslassdurchgang 16 educated. It should be noted that each of the Lagerschmierab spacers 8th preferably quench hardened to prevent squeezing and further to facilitate its handling.

From the nozzle 9 A discharged lubricating oil, a part of the lubricating oil, except the lubricating oil, which flows in the small gap δ, heat from the inner ring, which is then heated as a result of the operation, and then from the lubricating oil outlet passage 12 discharged to the outside. This lubricating oil outlet passage 12 is from the oil outlet room 14 including the recess 8a located in the side surface of each of the bearing grease spacers 8th is formed, and the Ölauslassausnehmung 13a , which in each of the opposite side surfaces of the Zwischenaußenring spacers 13 is formed, and from the above groove-like Ölauslassdurchgängen 15 and 16 built up. It should be noted that a plurality of the groove-like oil outlet passages 15 and 16 can be distributed in a circumferential direction. For the cooling oil used, in view of reducing drive loss and increasing the cooling efficiency, it is preferable to use a cooling oil of a kind having such a viscosity not higher than VG 10, VG 2 as determined according to ISO. Further, to further reduce the drive loss and increase the cooling efficiency, the use of a water-soluble hydraulic oil having a low viscosity and a high coefficient of thermal conductivity as the cooling oil, and the use of stainless steel with a low linear expansion coefficient as material for each of the bearing lubricating spacers 8th prefers.

The operation for lubricating the multi-row rolling bearing assembly 1 of the construction described hereinabove will now be described. The under pressure in the respective oil supply passages 10 in the bearing grease spacers 8th supplied cooling oil is from the nozzles 9 sprayed on places where the circumferential grooves 7 in the respective end surfaces of the inner rings 3 are formed in a related relationship. Part of the in the circumferential grooves 7 sprayed cooling oil flows under the influence of a surface tension and a centrifugal force acting on the cooling oil as a result of rotation of the inner ring 3 is developed in the raceway surfaces 3a as lubricating oil, from respective inner wall surfaces of the circumferential grooves 7 in the inner rings 3 on an outer diametrical side along the inclined surface sections 3b to flow. Because of the nozzles 9 discharged cooling oil in the circumferential grooves 7 is collected and then partially from the inclined surface sections 3b the inner rings 3 into the respective raceway surfaces 3a In this way, the lubricating oil can uniformly over the entire circumference of each of the raceway surfaces 3a be supplied. The flow of the lubricating oil from the respective inner wall surfaces of the circumferential grooves 7 to the respective inclined surface sections 3b can be done easily when the surface tension of the lubricating oil, the centrifugal force acting on the lubricating oil and the inclination angle of each of the inclined surface portions 3b are exactly balanced with each other. Because an intersection between the end face of each of the inner rings 3 and the associated inclined surface portion 3b as the curved edge 3ba is executed, in the gezeig th case, the flow of the lubricating oil in the direction of the inclined surface portion 3b run smoothly.

The inclined surface section 3b of the corresponding inner ring 3 gets through the collar 11 of the bearing grease spacer 8th covered with the intervening gap δ, and that of this gap δ in the direction of the raceway surface 3a flowing lubricating oil gets through this collar 11 guided. It may happen that the lubricating oil flowing in the gap δ does not form an adhering flow, which at the inclined surface section 3b adheres, and by the action of centrifugal force in a against an inner diametrical surface of the collar 11 forced way flows. The lubricating oil flowing under such a condition is released by the action of the centrifugal force, soon after it comes from a tip of the collar 11 emerges, driven radially outward. However, since the collar 11 to a radially inner position of the holder 6 extends, so from the top of the collar 11 radially outwardly driven lubricating oil through an inner diametrical surface of the holder 6 and then gets in the direction of the rolling elements 5 fed. For this reason, this can be in the gap δ between the inclined surface portion 3b of the inner ring 3 and the collar 11 of the bearing grease spacer 8th supplied lubricating oil without unnecessary waste of it to be used for lubrication.

It should be noted that, when the gap δ is a minute gap having a smaller size than an oil film of the along the inclined surface portion 3b is designed so that the flow of lubricating oil can be adjusted by this gap δ, and therefore the amount of lubricating oil flowing through the very small gap δ can be easily adjusted without an external adjustment of the direction of the oil supply passage 10 To require to be supplied flow of the cooling oil.

The lubricating oil except for the amount thereof flowing into the minute gap δ is passed through the lubricating oil outlet passage through an oil discharge pump (not shown) 12 which is from the oil outlet space 14 which passes through the Ölauslassausnehmung 13a in the side surface of the Zwischenaußenring spacers 13 and the oil outlet recess 8a in the side surface of the bearing grease spacer 8th is limited, from the groove-like Ölauslassdurchgang 15 in the side surface of the Zwi rule the outer ring spacer 13 , and from the groove-like Ölauslassdurchgang 16 in the side surface of the bearing grease spacer 8th constructed, discharged to the outside. By the action of the lubricating oil provided by the cooling oil discharged through such a circuit, the multi-row rolling bearing assembly can 1 be effectively cooled.

In this multi-row rolling bearing assembly 1 are the intermediate outer ring spacers 13 and the paired bearing grease spacers 8th and 8th between which the intermediate outer ring spacer 13 is inserted between the adjacent rolling bearing units 2 and 2 inserted, and the oil outlet 14 is through each of the Ölauslassausnehmungen 13a in the opposite surfaces of the Zwischenaußenring spacers 13 and the side surface (at which the Ölauslassausnehmung 8a is formed) each of the Lagerschmierabstandshalter 8th and 8th , which the Ölauslassausnehmung 13a faced, defined. The oil outlet room 14 again stands with a room 18 in connection with that of the nozzle 9 in each of the rolling bearing units 2 and 2 discharged lubricating oil flows, thereby the lubricating oil outlet passage 12 to build. Accordingly, there is no need to add an additional annular lid member to each of the bearing lubricating spacers as required in the previously described proposed example to ensure the lubricating oil outlet passage, and hence the axial dimension of each of the bearing lubricating spacers 8th be reduced by an amount that would be claimed by the additional annular cover element.

Since there is no need, the additional annular lid member for each of the Lagerschmierabstandshalter 8th In addition, the number of component parts can be reduced, and a reduction in the number of manufacturing steps and the cost can be achieved.

Since the Zwischenaußenringabstandshalter 13 and the paired bearing grease spacers 8th and 8th between which the intermediate outer ring spacer 13 is inserted between the respective outer rings 4 and 4 the adjacent rolling bearing units 2 and 2 In addition, the axial inner gap can be simply adjusted by merely adjusting the dimensions between the end surfaces of the intermediate outer ring spacer 13 be set.

2 illustrates an example of a spindle device, which with the multi-row rolling bearing assemblies 1 of the herein in connection with the first embodiment with reference to 1 described construction is equipped. This spindle device 24 is used in a machine tool, and a jig for holding a tool or a workpiece is for fitting to a free end (as shown, a left end) of a main shaft 25 customized. This main shaft 25 is by a plurality (in the case shown, for example, two) of the multi-row rolling bearing assemblies 1 supported, which are axially spaced from each other. In those multi-row rolling bearing arrangements 1 become the adjacent rolling bearing units 2 and 2 , which respectively the Zwischenaußenringabstandshalter 13 and the paired bearing grease spacers 8th and 8th used in a back-to-back combination while biased at a fixed position, as described later.

The inner rings 3 the rolling bearing units 2 in each of the multi-row rolling bearing assemblies 1 are on an outer peripheral surface of the main shaft 25 attached and their outer rings 4 are on an inner diametrical surface of a housing 26 built-in. An engine 30 for driving the main shaft 25 is at one between the multi-row rolling bearing assemblies 1 and 1 inserted axial intermediate position in the housing 26 arranged. Its motor rotor 31 is at the main shaft 25 attached and a motor stator 32 in the case 26 attached.

The inner and outer rings 3 and 4 one of the rolling bearing units 2 each of the multi-row rolling bearing assemblies 1 , which is next to the free end of the main shaft 25 are arranged, each by an inner ring holder 27 and an outer ring holder 28 fixed in place, with the inner and outer rings 3 and 4 between shoulders 25a and 26a are inserted, which in an axial direction of the main shaft 25 and the housing 26 are oriented. A bearing fixing nut 33 for pressing and fixing the multi-row rolling bearing assembly 1 against the inner ring holder 27 is threaded on an end portion of the main shaft 25 appropriate. At respective positions of the main shaft 25 become those shoulders 25a and 26a the main shaft 25 and the housing 26 and bearing support surfaces of the inner and outer ring holder 27 and 28 set to predetermined positions and then the bearing fixing nut 33 attached, the two juxtaposed rolling bearing units 2 can be biased at a fixed position.

The housing 26 has one of an inner peripheral housing 26A and an outer peripheral housing 26B constructed double construction. The inner peripheral housing 26A is with a lubricating oil feed passage 34 that with the each in the Lagerschmierabstandshaltern 8th defined oil supply passages 10 communicates, a recovery passage for discharged oil 35 and a case cooling oil supply passage 36 Mistake. The lubricating oil supply passage 34 and the Recovery passage for discharged oil 35 extend axially through the outer ring holder 28 , The recovery passage for discharged oil 35 stands with that in each of the bearing grease spacers 8th defined oil outlet passage 12 ( 1 ) in connection.

That in the recovery passage for drained oil 35 flowing discharged oil is recovered by an oil discharge pump (not shown) into an oil recovery tank (also not shown), and is then returned to a cooling oil supply device (not shown), from which device the oil is re-introduced into the oil supply passage as cooling oil 10 can be supplied. Further, the cooling oil from the cooling oil supply device into the oil supply passage 36 for cooling the housing 26 fed. The cooling oil is used after to cool the housing 26 is recovered in the oil recovery tank and is returned to the cooling oil supply device.

When using the multi-row rolling bearing assemblies 1 for supporting the main shaft 25 the spindle device 24 the machine tool are the juxtaposed rolling bearing units 2 and 2 with the intermediate outer ring spacer 13 and the intervening bearing lubricant spacers 8th used in a back-to-back combination with a preload applied to the fixed position, the axial dimension of the bearing lubrication spacers 8th can be reduced, and therefore the spindle device 24 and the machine tool itself can be made more compact.

3 Fig. 11 illustrates a sectional view showing a second preferred embodiment of the multi-row rolling bearing assembly of the present invention. This multi-row rolling bearing assembly 1A is similar to that in 1 shown and described in connection with the first embodiment, but differs in that instead of the Zwischenaußenringabstandhalters 13 with the oil outlet recesses 13a and 13a which are defined in its opposite surfaces, an annular Zwischenaußenringabstandshalter 13A is inserted with a simple rectangular sectional shape and between respective side surface outer peripheral portions of the paired bearing lubricant spacers 8th and 8th is inserted. Accordingly, an oil discharge space 14A between side faces of the paired bearing grease spacers 8th and 8th which are opposite to those of which the respective collar 11 project, an inner diametrical surface of the Zwischenaußenring spacers 13A and an outer diametral surface of the inner ring spacer 17 which is between the inner rings 3 and 3 the juxtaposed rolling bearing units 2 and 2 is inserted, limited and stands with respective rooms 18 and 18 in connection, in which of the nozzles 9 in the adjacent rolling bearing units 2 and 2 discharged lubricating oil is discharged. Other construction features than those described above are similar to those shown and described in connection with the first embodiment.

Even in this second embodiment, there is no need to add an additional annular lid member to each of the bearing lubricating spacers as required in the previously described proposed example to ensure the lubricating oil outlet passage, and hence the axial dimension of each of the bearing lubricating spacers 8th be reduced by an amount that would be taken by the additional annular cover element to complete.

Since there is no need, an additional annular cover member for each of the Lagerschmierabstandshalter 8th In addition, the number of component parts can be reduced, and a reduction in the number of manufacturing steps and the cost can be achieved.

Since the Zwischenaußenringabstandshalter 13A and the paired bearing grease spacers 8th and 8th between which the intermediate ring spacer 13A is inserted between the respective outer rings 4 and 4 the adjacent rolling bearing units 2 and 2 are inserted, the axial inner gap can be easily adjusted merely by adjusting the dimensions between the end surfaces of the Zwischenaußenringabstandshalters 13A be set.

4 illustrates an example of a spindle device, which with the multi-row rolling bearing assemblies 1A of the herein in connection with the second embodiment with reference to 3 described construction is equipped. This spindle device 24A is used in a machine tool, and a jig for holding a tool or a workpiece is for mounting to a free end of a main shaft 25 customized. This main shaft 25 is by a plurality (in the case shown, for example, two) of the multi-row rolling bearing assemblies 1A supported, which are axially spaced from each other. In those multi-row rolling bearing arrangements 1A become the adjacent rolling bearing units 2 and 2 each including the intermediate outer ring spacer 13A and the paired bearing grease spacers 8th and 8th contains used in a back-to-back combination while biased at a fixed position. Other construction features than those described above are similar to those used in the spindle device 24 be used with respect to 2 described and shown. Even in this spindle device 24A can the axial Di dimension of the bearing lubricant spacers 8th can be reduced and accordingly, the spindle device 24A and the machine tool itself be made more compact.

5 FIG. 10 illustrates a sectional view showing the multi-row rolling bearing assembly according to a third preferred embodiment of the present invention. 6 Figure 11 is a sectional view showing an important section of the multi-row rolling bearing assembly. In the following description, component parts similar to those in the previous embodiment will be shown by the same reference numerals, and their details will not be repeated for the sake of brevity. If only portions of the structure are described, portions other than those described are considered to be similar to those in the above embodiment.

The multi-row rolling bearing assembly shown therein 1B used a plurality of (in the illustrated case, for example, two) juxtaposed rolling bearing units 2 , Each of the rolling bearing units 2 is designed in the form of an angular contact ball bearing and the rolling bearing units 2 are used in a back-to-back combination while biased at a fixed position. An outer ring spacer 37 which forms an outer ring spacer at an intermediate portion is between the respective outer rings 4 and 4 the adjacent rolling bearing units 2 and 2 inserted, and an inner ring spacer 17 is between the respective inner rings 3 and 3 the adjacent rolling bearing units 2 and 2 inserted.

annular shoulders 38 are in respective inner peripheries of axially opposite ends of the outer ring spacer 37 educated. At the ring shoulders 38 and 38 are the recess h1 from the axial end of the first annular shoulder 38 and the recess h2 from the opposite axial end of the second annular shoulder 38 essentially the same size. The first and the second ring shoulder 38 and 38 have diameters d1 and d2, which are formed substantially equal in size. The diameter of each of the ring shoulders 38 is larger than the inner diameter of the outer ring of each of the adjacent rolling bearing units 2 and 2 , It can happen that the respective recesses h1 and h2 of the ring shoulders 38 and 38 not substantially equal in size. It may also happen that the respective diametral dimensions d1 and d2 of the annular shoulders 38 and 38 not substantially equal in size.

The paired bearing grease spacers 8A and 8A are each in the ring shoulders 38 and 38 of the outer ring spacer 37 arranged and are in position by means of a plurality of corresponding bolts 39 fixed. Each of the bearing grease spacers 8A is with a variety of bolt holes 8 aa formed axially thereof at intervals, for example, a predetermined (or non-predetermined) distance in a circumferential direction thereof, and a plurality of internal threads (screw nuts) corresponding to those bolt holes 8 aa are in the outer ring spacers 37 educated. Each of the bolt holes 8 aa is with the corresponding bolt 39 provided and is screwed into the associated internal thread. It should be noted that one head of each threaded bolt in the annular shoulder 38 is included and not with the adjacent storage unit 2 will hamper. At the outer ring spacer 37 is the radius of curvature of a corner section 38R each of the shoulders chosen smaller than the chamfer dimension of an assembly area 40 as will be described later, so that respective mating surfaces of the annular shoulders 38 and the bearing grease spacer 8A be kept in close contact with each other. It should be noted, however, that the present invention is not always limited to such a construction and the corner portion of each annular shoulder 38 With a compensation processing can be worked to a disability between the respective ring shoulder 38 and the bearing grease spacer 8A to avoid. The on the respective ring shoulders 38 of the outer ring spacer 37 mounted bearing grease spacers 8A have a shape in which one axial portion and the opposite axial portion have the same symmetrical construction, and accordingly, only one axial portion is referred to, and it may happen that the description of the other axial portion is not repeated, although like reference numerals are used therefor ,

An axial end of the bearing grease spacer 8A is with the bolt holes 8 aa formed and contains the in the ring shoulder 38 introduced assembly area 40 pointing in the direction of a side to which the circumferential groove 7 in the end face of the inner ring 3 is provided, open nozzle 9 , and a first oil supply passage 10a , which with this nozzle 9 communicates, and also the collar 11 , The first oil feed passage 10a is formed so as to extend in a radial direction perpendicular to the axial direction and then in a direction radially outward from the mounting area 40 opens. The outer ring spacer 37 has a second oil supply passage 10b which communicates with the first oil supply passage therein 10a is defined for supplying the cooling oil. The cooling oil leading to the second oil feed passage 10b is fed and then from the nozzle 9 is discharged, is on the circumferential groove 7 in the inner ring 3 sprayed, part of it subsequently as lubricating oil by the action of centrifugal force and the surface tension of the inner diametrical surface of the circumferential groove 7 and along the inclined surface portion 3b in the direction of the raceway surface 3a of the inner ring 3 flows.

The collar 11 extends axially from a side surface of the bearing grease spacer 8A towards the next adjacent storage unit 2 and then dominates the inclined surface section 3b of the inner ring 3 with the gap δ (see 1 (B) ), so that the lubricating oil can be guided to the gap δ in the direction of the raceway surface 3a to flow. This collar 11 is on an outer diametrical side of the nozzle 9 arranged and extends to a radially inner position of the holder 6 , In each of the bearing grease spacers 8A is a Ölauslassausnehmung open towards an inner periphery 8 ab in a side surface of the outer ring spacer 37 formed, which the ring shoulder 38 faces. The outer ring spacer 37 has an annular Ölauslassausnehmung 37b on which in each of opposite surfaces of a wall 37a is defined on an inner diametrical side of the annular shoulder 38 and substantially in the width center of the outer ring spacer 37 is arranged. Between each of the annular oil outlet recesses 37b and 37b and the Ölauslassausnehmung 8 ab in each of the opposite side surfaces of the opposing bearing grease spacer 8A is an oil outlet room 41 educated.

These oil outlet spaces 41 and 41 stand each with rooms 18 in connection, in which of the nozzle 9 in the rolling bearing units 2 and 2 discharged lubricating oil is discharged. A partial endface 37c that are flush with a stepped surface 38a is what the ring shoulder 38 in the outer ring spacer 37 defined, is formed by cutting. However, it should be noted that this Teilendfläche 37c not flush with the stepped surface 38a can be. This partial end surface 37c extends radially outward from a portion of the stepped surface 38a on the circumference thereof to thereby form a groove-like oil outlet passage 42 to build. This groove-like oil outlet passage 42 stands with a radially outer space 43 of the assembly area 40 in communication which is in phase with the above peripheral portion is tuned. The groove-like oil outlet passage 42 also stands with the radially outer space 43 of the assembly area 40 and an annulus 40a of the assembly area 40 communicating with an inner diametrical portion or the like of the end surface of the outer ring 4 faces. It should be noted that the bearing grease spacer 8A preferably quench hardened to avoid crushing and further to facilitate its handling.

Part of the of the nozzle 9 discharged lubricating oil, except the running in the very small gap δ lubricating oil, and then removes heat from the heated because of the operation inner ring 3 and is discharged to the outside from a lubricating oil outlet passage. This lubricating oil outlet passage is out of the annulus 40a of the assembly area 40 , the radially outer space 43 of the assembly area 40 , the oil outlet recess 8 ab in the side surface of the bearing grease spacer 8A , the annular Ölauslassausnehmung 37b of the outer ring spacer 37 etc. built up. The radially outer space 43 of the assembly area 40 and the oil outlet recess 8 ab in the side surface of the bearing grease spacer 8A may be distributed in a plurality in a circumferential direction.

The lubricating operation of the multi-row rolling bearing assembly 1B The structure described above will now be described.

The cooling oil is pressurized in the direction of the second oil supply passages 10b supplied in the outer ring spacers and then the respective first oil supply passages 10a in the first and second bearing lubricant spacers 8A and 8A fed and is from the nozzle 9 dissipated and then in the direction of the points of the end face of the inner ring 3 sprayed on which the circumferential grooves 7 are each formed and which the nozzles 9 are opposite. A part of the thus sprayed cooling oil flows as lubricating oil in the raceway surfaces 3a the inner rings 3 from inner wall surfaces to an outer diametrical side of the circumferential grooves 7 in the inner rings 3 and along the inclined surface portions 3b by the action of a surface tension and a centrifugal force acting on the cooling oil due to the rotation of the inner rings 2 acts. In this way, the cooling oil discharged from the nozzles becomes the respective circumferential grooves 7 collected, a part of which from the inclined surface sections 3b in the inner rings 3 in the raceway areas 3a flows, and accordingly, the lubricating oil uniformly over the entire periphery of the raceway surfaces 3a be supplied. The flow of the lubricating oil from the inner wall surface of each circumferential groove 7 in the direction of the associated inclined surface portion 3b runs smoothly when the surface tension of the lubricating oil, the centrifugal force acting on the lubricating oil and the inclination angle of the inclined surface portion 3b are precisely tuned, whereby a sputtering of the lubricating oil is avoided under the influence of centrifugal force. As in the case shown, the intersection between the end surface of each inner ring 3 and the associated bevel section 3b the curved edge 3ba is, the flow of lubricating oil runs in the direction of the inclined surface portion 3b easily.

The lubricating oil, which from the gap δ, wel cher between the inclined surface portion 3b of the inner ring 3 and the collar 11 is limited, in the direction of the associated raceway surface 3a flows through the collar 11 guided. It may happen that, depending on various conditions including, for example, the rotational speed and the inclination angle, the lubricating oil flowing in the gap δ does not exist on the inclined surface portion 3b adherent adhesive flow forms and by the action of centrifugal force in an against an inner diametrical surface of the collar 11 forced way flows. The lubricating oil flowing under such a condition is released by the action of the centrifugal force, shortly after it comes from a tip of the collar 11 emerges, driven radially outward. However, since the collar 11 to a radially inner position of the holder 6 extends, so from the top of the collar 11 Lube oil driven radially outward is trapped by an inner diametral surface of the holder and is then moved in the direction of the rolling elements 5 fed. For this reason, this can be in the gap δ between the inclined surface portion 3b of the inner ring 3 and the collar 11 of the bearing grease spacer 8A supplied lubricating oil without unnecessary waste of it to be used for lubrication. The lubricating oil except for the amount thereof flowing into the minute gap δ is discharged to the outside through an oil discharge pump (not shown) through the lubricating oil outlet passage. By discharged through such a passage lubricating oil as a cooling oil, the multi-row rolling bearing assembly 1B be effectively cooled.

According to the multi-row rolling bearing assembly 1B of the type described above is the outer ring spacer 37 between the respective outer rings 4 and 4 the adjacent rolling bearing units 2 and 2 inserted. The ring shoulders 38 are on respective inner peripheral sides of the axially opposite ends of the outer ring spacer 37 formed and the paired bearing grease spacers 8A and 8A are in those ring shoulders 38 and 38 used. When respective end faces of the outer ring spacer 37 For example, the end face dimension can be 37h (Dimensions between the end faces) can be easily adjusted. However, it should be noted that a machining process of the end faces of the outer ring spacer 37 is not limited to grinding, but any other machining process, such as turning or microfinishing, can be used if necessary.

Thereafter, the mounting section 40 each bearing grease spacer 8A in the corresponding ring shoulder 38 in the outer ring spacer 37 introduced. In other words, the Lageschmierabstandshalter 8A a structure in which the collar 11 protrudes in an axial direction of one side surface thereof, but each of the end surfaces of this outer ring spacer 37 can be processed in a state in which the respective Lagerschmierabstandshalter 8A from the outer ring spacer 37 is removed. Accordingly, the working of each of the end surfaces of the outer ring spacer 37 Easy to run without going through the collar 11 to be disabled. By merely adjusting the endface dimension 37h of the outer ring spacer 37 etc., the axial inner gap in each of the bearing units 2 and 2 easy to set.

Using any bearing grease spacer 8A and the outer ring spacer 37 , which are separate elements, may be a back of the bearing grease spacer 8A (on one of the adjacent ring shoulders 38 opposite side) or the annular shoulder 38 in the outer ring spacer 37 be edited and set. Accordingly, the gap δ between the inner ring inclined portion 3b limited, which in an outer diametrical portion of the inner ring 3 is formed and whose diameter extends from one side adjacent to the end surface of the inner ring 3 in the direction of the opposite side next to the raceway surface of the inner ring 3 enlarged, and the collar 11 can be controlled exactly. In the multi-row rolling bearing assembly 1B According to this third embodiment, the number of processing steps can be reduced as compared to the case where the axial inner gap and the above gap are realized substantially simultaneously, because the adjustment of the axial inner gap and the adjustment of the gap δ between the inner ring inclined portion 3b and the collar 11 be realized independently of each other.

When the gap δ between the inner ring inclined portion 3b and the collar 11 is accurately controlled, a flow of excessive amount of lubricating oil can be avoided in the bearing assembly. The remaining lubricating oil which does not flow into the bearing assembly is passed through the lubricating oil outlet passage (the annular space 40a , the radially outer space 43 , the oil outlet recess 8 ab and the annular Ölauslassausnehmung 37b and others) discharged to the outside to thereby the multi-row roller bearing assembly 1B effective to cool. Since, by accurately controlling the gap δ, a lubricating oil amount exceeding the required amount does not flow into the bearing assembly, it is possible to prevent an increase in the moving resistance of the lubricating oil, and further a drive loss of the bearing units 2 and 2 to prevent. Accordingly, a large power drive motor or the like is no longer required, and a reduction in manufacturing cost can be achieved. It is also possible, the possibility To avoid that due to a small gap δ, the inclined surface portion 3b of the outer ring 3 and the collar 11 mutually under the influence of a mounting condition at the time of installation of the bearing units and / or caused by heat and / or centrifugal expansion of the inner ring 3 hinder.

For example, in the conventional technique of substantially simultaneously adjusting the axial inner gap and the gap δ, adjustment of either the axial gap or the gap δ will be insufficient so that the number of process steps such as replacement of a spacer will be required Such a number of process steps can be reduced. Accordingly, it is possible to reduce the manufacturing cost of the multi-row rolling bearing assembly 1B to reduce. If the back of the bearing grease spacer 8A or the ring shoulder 38 of the outer ring spacer 37 can be edited and adjusted, based on their processing amount, each offset between the first oil passage 10a and the second oil passage 10b be avoided when the second oil passage 10b in the outer ring spacer 37 is formed. The first and second oil passages 10a and 10b can after editing and adjusting the ring shoulder 38 and others are formed. Even in such a case, any offset between the first and second oil passages 10a and 10b safely prevented. Therefore, the lubricating oil can be easily used for the first and second oil passages 10a and 10b be supplied.

As the bearing grease spacer 8A introduced and thus in the radially inward outer ring spacers 37 formed annular shoulder 38 is provided, the following effects can be achieved. Compared with the structure in which the Zwischenaußenringabstandshalter 13 between the first and second bearing grease spacers 8th and 8th is inserted, as is the case with the in 1 shown and described in connection with the first embodiment, multi-row rolling bearing assembly, the axial dimension of the spacer can be significantly reduced as a whole.

The partial end surface 37c of the outer ring spacer 37 is made by cutting out a peripheral portion of the stepped surface 38a formed, which the ring shoulder 38 forms to assume a shape flush with the stepped surface 38a is. Since the Teilendfläche 37a with the stepped surface 38a For example, taken as a processing reference surface, can be processed quickly, the number of processing steps can be reduced accordingly. Because the outer ring spacers 37 , the radially outer space 43 of the assembly area 40 and the groove-like oil outlet passage 42 can be simultaneously processed, for example by means of a milling, the number of steps required to change the configuration can be reduced. The formation of the radially outer space 43 is effective for reducing the weight of the outer ring spacer 37 and further for smoothly discharging the discharged oil from the radially outer space 43 and others.

The outer ring spacer 37 has an annular Ölauslassausnehmung 37b in each opposite side surface of the wall section 37a at an axial center thereof. Because this annular Ölauslassausnehmung 37b is formed, the wall section 37a at the axial center of the outer ring spacer 37 have a thin-walled construction. The outer ring spacer 37 can be reduced in weight and have easy handling when the radially outer space 43 is formed, and further, when the wall portion 37a is designed at the axial center with a thin-walled construction.

Further, the oil outlet space 41 for the lubricant between the Ölauslassausnehmung 37b in each of the opposite side surfaces of the outer ring spacer 37 and the side surface of the bearing grease spacer 8A ensured, wherein the cooling can be realized with the lubricating oil, and an application for a high-speed rotation and an ultra-high-speed rotation can be achieved. Because of this oil outlet 41 between the Ölauslassausnehmung 37b in each of the opposite surfaces of the outer ring spacer 37 and the side surface of the bearing grease spacer 8A is formed, there is no need, an additional annular cover member for each of the Lagerschmierabstandshalter 8A and, consequently, the axial dimension of each bearing lubrication spacer 8th measured in a direction in which the bearing grease spacers 8th are arranged to be reduced.

7 illustrates an example of a spindle device 24B that with the multi-row rolling bearing arrangements 1B equipped in connection with the third embodiment with respect to the 5 and 6 shown and described. This spindle device 24B is used in a machine tool, and a jig for holding a tool or a workpiece is for fitting to a free end (a left end in the drawing) of the main shaft 25 customized. This main shaft 25 is by a plurality (in the case shown, for example, two) of the multi-row rolling bearing assemblies 1B supported, which axially spaced from each other. In those multi-row rolling bearing arrangements 1B become the adjacent rolling bearing units 2 and 2 with the intermediate outer ring spacer 37 used in a back-to-back combination while being biased at a fixed position.

The inner rings 3 those rows are on an outer diametrical surface of the main shaft 25 attached and the outer rings 4 are in an inner diametrical surface of the housing 26 appropriate. A drive motor 30 for driving the main shaft 25 is at an axial center position between the multi-row rolling bearing assemblies 2 and 2 in the case 26 arranged inlaid. Its motor rotor 21 is at the main shaft 25 attached and a motor stator 32 is on the case 26 attached.

The inner and outer rings 3 and 4 one of the rolling bearing units 2 which is arranged adjacent to the free end of the main shaft, each of the multi-row rolling bearing assemblies 1B are each through the inner ring holder 27 and the outer ring holder 28 fixed in position, between which the inner and outer rings 3 and 4 with the shoulders 25a and 26a are inserted, in an axial direction of the main shaft 25 and the housing 26 are oriented. The bearing mounting nuts 33 for pressing and fastening the multi-row rolling bearing assembly 1B against the inner ring holder 27 is threaded onto an end portion of the main shaft 25 appropriate. If respective positions of the main shaft 25 , those shoulders 25a and 26a of the housing 26 and bearing support surfaces of the inner and outer ring holder 27 and 28 are set at predetermined positions, and the bearing fixing nut 33 then tightened, the two adjacent rolling bearing units can 2 be biased at a fixed position.

When using the multi-row rolling bearing assemblies 1B for supporting the main shaft 25 the spindle device 24 the machine tool with the juxtaposed rolling bearing units 2 and 2 with the inserted between them outer ring spacers 37 In a back-to-back combination and with the bias applied at a fixed position, the axial dimension of the spacer as a whole can be reduced and therefore the spindle device can 24 and the machine tool itself be made more compact, since the bearing lubricant spacer 8A in the ring shoulder 37 of the outer ring spacer 37 is introduced.

8th FIG. 11 illustrates a sectional view showing the multi-row rolling bearing assembly according to a fourth preferred embodiment of the present invention. 9 Fig. 11 illustrates a sectional view showing an important portion of the multi-row rolling bearing assembly. This multi-row rolling bearing assembly 1C is similar to that used in connection with the third embodiment with particular reference to 5 and 6 is shown and described, but differs in that each of the bearing grease spacers 8A in the corresponding ring shoulder 38 of the outer ring spacer 37 by a Einstellabstandshalter 44 is provided, which the very small gap δ between the inner ring inclined portion 3b and the collar 11 can adjust. In other words, in this construction, the adjustment spacer is 44 added. The setting spacer 44 is with a through hole 44a formed, which extends axially thereof, and a bolt 39 is in this through hole 44a introduced. It should be noted that a head of such a screwed bolt in the annular shoulder 38 is included and not with the adjacent storage unit 2 with special needs.

In the multi-row rolling bearing assembly 1C According to the fourth embodiment, at least one of the opposite surface portions of the Einstellabstandshalters 44 which is between a back surface 8ac of the bearing grease spacer 8A and the ring shoulder 38 of the outer ring spacer 37 is provided, edited and adjusted by grinding. In this way, the very small gap δ between the inner ring inclined portion 3b and the collar 11 be controlled precisely and easily. In particular, after the finished dimensions of the outer ring spacer 37 , every bearing grease spacer 8A and the two rows of rolling bearing units 2 and 2 The setting spacer may be used 44 be edited and set. In this way, the very small gap δ can be accurately and easily controlled. If a plurality of Einstellabstandshaltern 44 with a plurality of setting widths prepared in advance, the setting of the very small gap δ can be quickly achieved, and thus the number of assembling steps can be reduced. Because the preparation of a variety of Einstellabstandshaltern 44 with a plurality of setting widths in advance effective for facilitating the setting of the very small gap δ, the versatility and multi-purpose usability of the bearing lubricating spacer can 8A increase. Accordingly, the manufacturing cost of the multi-row rolling bearing assembly can be achieved. Structural features other than those described above are similar to those used in the multi-row rolling bearing assembly 1B be used, with particular reference to the 5 and 6 is shown and described, and therefore functions and effects similar to those achieved by such a multi-row rolling bearing assembly can be achieved 1B be enabled.

10 illustrates an example of the spindle device 24C , which with the multi-row rolling bearing assembly 10 equipped with special reference to the 8th and 9 shown and described. This spindle device 24C is used in a machine tool, and a jig for holding a tool or a workpiece is for fitting to a free end (a left end in the drawing) of the main shaft 25 customized. This main shaft 25 is by a plurality (in the case shown, for example, two) of the multi-row rolling bearing assemblies 1C supported, which are axially spaced from each other. In those multi-row rolling bearing arrangements 10 become the adjacent rolling bearing units 2 and 2 with the intermediate outer ring spacer 37 used in a back-to-back combination while being biased at a fixed position. Other construction features than those described above are similar to those in the spindle device 24B are used, with particular reference to 7 shown and described. As the bearing grease spacer 8A in the ring shoulder 38 of the outer ring spacer 37 can be introduced even in this spindle device 24C the axial dimension of the spacer as a whole can be reduced, and therefore the spindle device can 24C and the machine tool itself be made more compact.

A fifth preferred embodiment of the present invention will now be described with particular reference to 11 described. 11 (A) FIG. 10 illustrates a sectional view of the multi-row rolling bearing assembly according to this embodiment. FIG. This multi-row rolling bearing assembly shown therein 1D uses a plurality (in the illustrated case, for example, two) of juxtaposed rolling bearing units 2 , Each of the rolling bearing units 2 is designed in the form of an angular contact ball bearing and the rolling bearing units 2 are used in a back-to-back combination while biased at a fixed position. Each of the rolling bearing arrangements 2 is of a type which has a variety of rolling bearing elements 5 contains, between the respective raceway surfaces 3a and 4a the inner and outer rings 3 and 4 are inserted, wherein the rolling elements 5 through a respective holder 6 being held.

Between the respective outer rings 4 and 4 the juxtaposed rolling bearing units 2 and 2 is a pair of bearing grease spacers 8th and 8th inserted. Between the respective inner rings 3 and 3 is the inner ring spacer 17 inserted. Each bearing lubricant spacer 8th serves for discharging a cooling oil, of which a part in the corresponding rolling bearing unit 2 is supplied.

The holders 6 are an outer race type and are preferably made of a phenol resin, PEEK, PPS, a polyamide resin, a C / C composite, an aluminum alloy, or a Ti alloy (increase in strength during a high-speed operation). The inner rings 3 are z. B. made of a carburized steel in view of a considerably increasing hoop stress during high-speed operation. The rolling elements 5 are preferably made of a ceramic material with a view to reducing the centrifugal force.

One of opposite end faces of the in each of the rolling bearing units 2 inserted inner ring 3 which is on a non-load side (on a bearing rear side) is with a circumferentially extending groove 7 formed, which is excepted axially inward. Further, an outer diametrical surface of the inner ring 3 on one side next to the circumferential groove 7 and continuously to the corresponding raceway surface 3a as an oblique section 3b with a large diameter next to the track surface 3a executed. In other words, a portion of the outer diametrical surface of the inner ring 3 on which a stepped surface is provided, as the inclined portion 3b executed.

When in contact with an end face of the outer ring 4 The bearing grease spacer forms 8th a ring-shaped outer ring spacer axially close to the rolling bearing unit 2 is provided. This bearing lubricant spacer 8th has a nozzle 9 which is opened toward a portion of the end surface of the inner ring where the circumferential groove 7 is defined, and one with the nozzle 9 related oil feed passage 10 is with a collar 11 Mistake. A cooling oil that goes to the oil supply passage 10 fed and from the nozzle 9 is discharged, is in the circumferential groove 7 in the inner ring 3 sprayed, part of which as a lubricating oil from an inner diametrical surface of the circumferential groove 7 along the sloping section 3b and then along the track surface 3a of the inner ring 3 flows.

The collar 11 extends from a side surface of the bearing grease spacer 8th in the direction of the adjacent storage unit 2 in an axial direction and superimposed on the inclined portion 3b with a gap δ ( 11 (B) ), which between him and the oblique section 3b for guiding the lubricating oil flowing through the gap δ in the direction of the raceway surface 3a is defined. The collar 11 extends to an inner diametrical side of the holder 6 , An angled section at which the end face of the inner ring 3 , which is the nozzle 9 facing, and the inclined portion 3b cutting is as a curved edge 3ba with a curved cut configuration to separate the lubricating oil away from the inner ring 3 through the angled edge under the influence of a zen to avoid centrifugal force.

One of the opposite side surfaces of each of the bearing grease spacers 8th , which is the nearest adjacent bearing grease spacer 8th touched, is with a Ölauslassausnehmung 8a formed open toward an inner periphery thereof, and an oil discharge space 14B is between inner surfaces of the Ölauslassausnehmungen 8a and 8a and an outer diametral surface of the inner ring spacer 17 educated. Those oil outlet rooms 14b stand with respective rooms 18 in connection, which in the rolling bearing units 2 and 2 are defined, in which the lubricating oil is discharged.

Further, respective side surfaces of the bearing lubricating spacers 8th which are kept in contact with each other, with groove-like Ölauslassdurchgängen 8b formed, extending radially outward from the associated Ölauslassausnehmungen 8a extend. In addition, a portion of one of the opposite side surfaces of each of the bearing grease spacers 8th , which are in contact with an end face of the outer ring 4 is held with a radially extending groove-like Ölauslassdurchgang 16 educated. It should be noted that each of the bearing grease spacers 8th preferably quench hardened to avoid squeezing and further to facilitate its handling.

From the nozzle 9 discharged lubricating oil, a part of the lubricating oil, except for the flowing into the very small gap δ lubricating oil from the lubricating oil outlet passage 12 discharged to the outside. This lubricating oil outlet passage 12 is from an oil outlet room 14B which is the one in each of the bearing grease spacers 8th defined Ölauslassausnehmung 8a contains, and the groove-like Ölauslassdurchgängen 8b and 16 built up. It should be noted that the groove-like oil outlet passages 8b and 16 may be distributed in a plurality in a circumferential direction. For the cooling oil used, from the viewpoint of reducing drive loss and increasing the cooling efficiency, it is preferable to use a cooling oil of a kind having a viscosity not higher than VG 10, VG 2 as determined according to ISO. Further, to reduce the drive loss and increase the cooling efficiency, there is the use of a water-soluble hydraulic oil having a low viscosity and a high heat transfer coefficient as a cooling oil and the use of stainless steel having a low linear expansion coefficient as the material for each of the bearing lubricating spacers 8th prefers.

The lubricating operation of the multi-row rolling bearing assembly 1D of the construction described above will now be described. The under pressure in the respective oil supply passages 10 in the bearing grease spacers 8th supplied cooling oil is discharged and then from the nozzles 9 sprayed on places where the circumferential grooves 7 in the respective opposite end surfaces of the inner rings 3 are formed. Part of the in the circumferential grooves 7 sprayed cooling oil flows as a lubricating oil under the influence of a surface tension and a centrifugal force acting on the cooling oil as a result of the rotation of the inner rings 3 is developed in the raceway surfaces 3a to from respective inner wall surfaces of the circumferential grooves 7 in the inner rings 3 on an outer diametrical side along the inclined surface portion 3b to flow. Because of the nozzles 9 discharged cooling oil in the circumferential grooves 7 is collected and then partially from the inclined surface sections 3b the inner rings 3 into the respective raceway surfaces 3a flows, the lubricating oil in this way uniform over the entire circumference of each of the raceway surfaces 3a be supplied. The flow of the lubricating oil from the respective inner wall surfaces of the circumferential grooves 7 in the direction of the inclined surface sections 3b can be done easily when the surface tension of the lubricating oil, the centrifugal force acting on the lubricating oil and the inclination angle of each of the inclined surface portions 3b are matched with each other, and accordingly, any possible sputtering of the lubricating oil under the influence of the centrifugal force can be avoided. As an intersection between the end face of each inner ring 3 and the associated inclined surface portion 3b as the curved edge 3ba is executed, in the case shown, the flow of the lubricating oil in the direction of the inclined surface portion 3b run smoothly.

The inclined surface section 3b of the inner ring 3 is through the collar 11 of the bearing grease spacer 8th covered with the intervening gap δ and that of this gap δ in the direction of the raceway surface 3a flowing lubricating oil gets through this collar 11 guided. It may happen that the lubricating oil flowing in the gap δ does not form an adhering flow, which at the inclined surface section 3b adheres, and by the action of centrifugal force in a against an inner diametrical surface of the collar 11 forced way flows. The lubricating oil flowing under such a condition is released by the action of the centrifugal force soon after it comes from a tip of the collar 11 emerges, driven radially outward. However, since the collar 11 to a radially inner position of the holder 6 extends, so from the top of the collar 11 Lube oil driven radially outward is trapped by an inner diametral surface of the holder and is then moved in the direction of the rolling elements 5 fed. For this reason, this can be in the gap δ between the inclined surface portion 3b of the inner ring 3 and the collar 11 of the bearing grease spacer 8th supplied lubricating oil without unnecessary waste of it used for lubrication become.

It should be noted that when the gap δ is a minute gap δ having a smaller size than an oil film along the inclined surface portion 3b is designed so that the flow of lubricating oil can be adjusted by this gap δ, and therefore, the amount of lubricating oil flowing through the very small gap δ can be easily adjusted without an external adjustment of the flow of the oil supply passage 10 to require supplied cooling oil.

The lubricating oil except for the amount thereof flowing in the minute gap δ is passed through the oil discharge space through an oil discharge pump (not shown) 14B by the respective inner surfaces of the Ölauslassausnehmungen 8a and 8a in the bearing lubricant spacer 8th and the outer diametrical surface of the inner ring spacer 17 is surrounded, and then through the groove-like Ölauslassdurchgang 8b and 16 in the bearing lubricant spacer 8th discharged to the outside, leaving the room 14B and the passages 8b and 16 the lubricating oil outlet circuit 12 form. By provided by the cooling oil, which is discharged through such a circuit, provided effect of the lubricating oil, the multi-row rolling bearing assembly 1D be effectively cooled.

Since the Ölauslassausnehmungen open in the direction of the inner peripheral surface 8a in the respective side surfaces of the bearing grease spacers held in contact with each other 8th and 8th are formed, and there through the respective inner surfaces of these Ölauslassausnehmungen 8a and 8a and the outer diametrical surface of the inner ring spacer 17 surrounded space as the oil outlet space 14B is executed, and there this Ölauslassraum 14B with the room 18 communicates in which of the nozzles 9 in the rolling bearing units 2 and 2 discharged lubricating oil is discharged, thereby the lubricating oil outlet circuit 12 to form, consists in this multi-row rolling bearing assembly 1D There is no need to add an additional annular cover member for each of the bearing lubrication spacers as required in the previously described proposed example to ensure the lubricating oil outlet passage, and hence the axial dimension of each bearing lubrication spacer 8th be reduced by an amount that would be claimed by the additional annular cover element.

There is no need for an additional annular element for each bearing lubrication spacer 8th In addition, the number of component parts can be reduced, and a reduction in the number of manufacturing processing steps and the cost can be achieved.

12 illustrates an example of the spindle device, which with the multi-row rolling bearing assemblies 1D in connection with the fifth embodiment with particular reference to 11 shown and described. This spindle device 24D is used in a machine tool, and a jig for holding a tool or a workpiece is for fitting to a free end (a left end as shown) of a main shaft 25 customized. This main shaft 25 is by a plurality (in ge case, for example, two) of the multi-row rolling bearing assemblies 1D supported, which are axially spaced from each other. In those multi-row rolling bearing arrangements 1D become the adjacent rolling bearing units 2 and 2 each of which is the partial bearing lubricant spacer 8th and 8th used in a back-to-back combination while biased at a fixed position, as will be described later.

The rolling bearing units 2 in each of the multi-row rolling bearing assemblies 1D are on an outer peripheral surface of the main shaft 25 with an inner diametrical surface of a housing 26 built-in outer rings 4 appropriate. An engine 30 for driving the main shaft 25 is as an axial center position between the multi-row rolling bearing assemblies 1D and 1D inserted, inside the case 26 arranged. Its motor rotor 31 is at the main shaft 25 attached and a motor stator 32 is on the case 26 attached.

The inner and outer rings 3 and 4 one of the rolling bearing units 2 each of the multi-row rolling bearing assemblies 1D , which is next to the free end of the main shaft 25 are arranged, each by an inner ring holder 27 and an outer ring holder 28 fastened in position, with the inner and outer rings 3 and 4 with shoulders 25a and 25a in an axial direction of the main shaft 25 and the housing 26 are oriented, are inserted in between. A bearing nut 33 for pressing against the inner ring holder 27 and securing the multi-row rolling bearing assembly 1D it is threaded onto an end portion of the main shaft 25 appropriate. At respective positions of the main shaft 25 become those shoulders 25a and 26a of the housing 26 and bearing support surfaces of the inner and outer ring holder 27 and 28 set to predetermined positions and then the bearing mounting nut 33 attracted, with the two adjacent rolling bearing units 2 can be biased at a fixed position.

The housing 26 has a double construction, which consists of an inner circumferential housing 26A and an outer peripheral housing 26B is constructed. The inner circumferential housing 26A is with a lubricating oil feed passage 34 who with each in the bearing lubricant spacers 8th defined oil supply passages 10 communicating, a recovery passage for discharged oil 35 and a case cooling oil supply passage 36 Mistake. The lubricating oil supply passage 34 extends axially and is at opposite end surfaces of the inner peripheral housing 26A open. The recovery passage for discharged oil 35 extends axially through the outer ring holder 28 , The recovery passage for discharged oil 35 stands with the lubricating oil outlet passage 12 ( 1 ) associated with each of the bearing grease spacers 8th is defined.

That in the recovery passage for discharged oil 35 flowing discharged oil is recovered by an oil discharge pump (not shown) into an oil recovery tank (also not shown), is then returned to a return oil supply device (not shown), the oil from this device again as a cooling oil in the oil supply passage 10 can be supplied. The cooling oil is further from the cooling oil supply device in the oil supply passage 36 for cooling the housing 26 fed. The cooling oil is used after to cool the housing 26 has been recovered into the oil recovery tank, from which it is returned to the cooling oil supply device.

When using the multi-row rolling bearing assemblies 1D for supporting the main shaft 25 the spindle device 24D the machine tool are the juxtaposed rolling bearing units 2 and 2 with the bearing grease spacers inserted between them 8th used in a back-to-back combination and with a preload applied to the fixed position, the axial dimension of the bearing lubrication spacers 8th can be reduced, and therefore the spindle device 24D and the machine tool itself can be made more compact.

Summary

Multi-row Rolling bearing assembly in which a plurality of rolling bearing units juxtaposed with a pair of bearing spacers are, which between respective outer rings of the adjacent Rolling bearing units are inserted, each the bearing grease spacer a nozzle for discharging a lubricating oil in the direction of an inner ring of the adjacent Rolling bearing unit and having a collar which on an outer diametrical side of the nozzle is arranged and an outer periphery of the inner ring covered. An oil outlet, which has one room in each the adjacent rolling bearing units, in which the of the Nozzle discharged lubricating oil dissipated is associated with, wherein a single Zwischenaußenringabstandshalter between the bearing grease spacers and the oil outlet space is inserted between each of the bearing grease spacers and defined the intermediate outer ring spacers.

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - JP 2001-012481 [0004, 0007]
• - JP 2002-54643 [0004, 0007]
• - JP 2006-118525 [0005, 0007]

Claims (7)

Multi-row rolling bearing assembly, which includes: a plurality of rolling bearing units arranged relative to each other; one A pair of bearing grease spacers interposed between respective outer races inserted the adjacent rolling bearing units wherein each of the bearing lubrication spacers is a nozzle for discharging a lubricating oil on an inner ring the adjacent rolling bearing unit and a collar which has on an outer diametrical side the nozzle is arranged and an outer periphery covered by the inner ring; and an oil outlet space, which with a space in each of the adjacent rolling bearing units is in communication, in which the discharged from the nozzle lubricating oil is discharged, wherein the Ölauslassraum with a the following structures (A) and (B) is provided: (A) the structure, in which a single intermediate outer ring spacer is inserted between the bearing grease spacers and the oil discharge space between each of the bearing grease spacers and the intermediate outer ring spacer is defined; (B) the structure in which an inner ring spacer between the respective inner rings of the adjacent rolling bearing units is inserted, wherein Ölauslassausnehmungen, which in the direction of an inner periphery are open, in respective Side surfaces of the bearing lubricant spacers are formed, which held in contact with each other, and wherein the Ölauslassraum between inner surfaces of the Ölauslassausnehmungen in the bearing grease spacers and an outer Diametralfläche the inner ring spacer is formed. Multi-row rolling bearing arrangement according to claim 1, wherein the Ölauslassraum provided with the structure (A) is, wherein the Zwischenaußenringabstandshalter an Ölauslassausnehmung in has each of its opposite surfaces, and wherein the oil outlet space between the Ölauslassausnehmung and the side surface of the bearing grease spacer is. Multi-row rolling bearing arrangement according to claim 1, wherein the Ölauslassraum provided with the structure (A) is, wherein an inner ring spacers between respective inner rings inserted the adjacent rolling bearing units is, and wherein the Ölauslassraum between side surfaces the bearing lubrication spacers, which face each other, from which project the respective collar, an inner diametrical surface the intermediate outer ring spacer and an outer diametral surface the inner ring spacer is formed. Multi-row rolling bearing arrangement according to claim 1, wherein the Ölauslassraum provided with the structure (A) with the pair of bearing grease spacers as in respective ones Ring shoulders is provided inserted, which on inner peripheral sides axially opposite ends of the Zwischenaußenringabstandshalters are formed, wherein the Zwischenaußenringabstandshalter one in each of its opposite surfaces having defined Ölauslassausnehmung, and wherein the Ölauslassraum between the oil outlet recess and the side surface the bearing lubricating spacer is formed. Multi-row rolling bearing arrangement according to claim 4, wherein an outer diametral portion of the inner ring is provided with an inner annular inclined portion, whose Diameter extending from one beside an end surface of the inner ring lying side to a next to a raceway surface of the Inner ring lying side enlarged, and where the bearing grease spacer in each annular shoulder in the outer ring spacer is provided by a Einstellabstandshalter, with a gap adjustable between the inner ring inclined portion and the collar is. Multi-row rolling bearing arrangement according to claim 3, wherein the Zwischenaußenringabstandshalter a ring shape having a rectangular section. Multi-row rolling bearing arrangement according to claim 1, which for supporting a main shaft of a machine tool is used, and in which the adjacent storage units with the bearing grease spacers inserted between them be used in a back-to-back combination, while they are biased at a fixed position.