DE112017004530T5 - Cooling structure for a storage device - Google Patents

Abstract

The invention relates to a cooling structure for a bearing device (J), wherein the bearing device (J) comprises a rolling bearing (1) with a stationary side race (2) and a rotating side raceway (3) Side adjacent arranged spacer (4) of the stationary side and a rotor side (3) of the rotating side adjacent arranged spacer (5) of the rotating side. An annular recess (13) of the stationary side is provided on a peripheral surface of the spacer (4) of the stationary side and an annular recess (14) of the rotating side is the recess (13) of the stationary side in an axial position opposite to a peripheral surface of Spacer (5) of the rotating side provided. A nozzle port (15) adapted to receive pressurized air (A) from an outlet (15a) opened toward a lower surface of the stationary side recess (13) toward a lower surface of the recess (14) To eject rotating side is provided so that it is inclined in a direction of rotation of the spacer (5) of the rotating side forward.

Description

CROSS-REFERENCE TO THE RELATED APPLICATION

This application claims priority from September 9, 2016 Japanese Patent Application No. 2016 - 176547 the entire disclosure of which is incorporated by reference into this application.

BACKGROUND OF THE INVENTION

(Field of the Invention)

The present invention relates to a cooling structure for a bearing apparatus, and relates to, for example, a cooling structure for a spindle of a machine tool and a bearing attached to such a spindle.

(Description of the Related Art)

In spindle devices for machine tools, it is necessary to reduce a temperature rise in the devices to ensure the machining accuracy. However, newer machine tools often operate at higher speeds to improve machining efficiency, which, with increasing speed, results in increased heat generation from bearings supporting the spindles. In addition, more and more often so-called spindle devices are used with built-in motor having a built-in spindle drive motor, which also leads to heat generation in the devices.

In view of increasing the speed and the accuracy of the spindles, the temperature rise in the bearings caused by heat generation must be minimized, since otherwise it would lead to an increase in the preload. As a measure for reducing a temperature rise in a spindle device, a spindle and bearings are cooled by supplying the bearings with compressed air (see, for example, Patent Documents 1 and 2). In Patent Documents 1 and 2, cold air is blown into a space between two bearings at an angle relative to the rotational direction, so that a swirling flow is generated and the spindle and the bearings are thereby cooled.

[Related document]

[Patent Document]

• [Patent Document 1] Japanese Publication No. 2000-161375
• [Patent Document 2] Japanese Publication No. 2015-183738

In a machine tool, compressed air is used as an air seal to prevent the entry of foreign matter into a spindle and air oil or oil mist for lubricating bearings. The compressed air is generated by a compressor. Normally, a machine tool has a compressor. When compressed air is used to cool a bearing and a shaft, this compressed air is also generated by a compressor for cooling.

When cooling with compressed air as in Patent Document 1, a higher cooling effect is achieved because more compressed air is supplied. However, it is necessary for the supply of a larger amount of compressed air to use a compressor with a larger capacity. Therefore, an improvement in the cooling effect is accompanied by an increase in the size and the power consumption of a machine tool.

Patent Document 2 proposes a solution to the above problem: as in 12 is shown in this document, a storage device J proposed which between a pair of rolling bearings 101 . 101 with an outer spacer ring 104 and an inner spacer ring 105 is provided, wherein the outer spacer ring 104 one with an annular recess 113 having provided inner peripheral surface and compressed air A for cooling over a through the outer spacer ring 104 limited nozzle opening 115 towards an outer peripheral surface of the inner spacer ring 105 is blown. The compressed air A gets out of the nozzle opening with high force 115 into one mainly through the recess 113 formed big room 120 ejected, and the compressed air A is adiabatically expanded, causing a drop in temperature and an increase in the flow rate of the compressed air A causes. Because of the compressed air A on the inner spacer ring 105 blown, the inner spacer ring 105 and the rolling bearings 101 effectively cooled.

In this way, according to the configuration of Patent Document 2, due to the improved cooling effect, it is possible to reduce a temperature rise in bearings having a smaller amount of compressed air than in the embodiment of Patent Document 1. However, it is desirable to effectively cool bearings with even less compressed air.

SUMMARY OF THE INVENTION

An object of the present invention is to provide a cooling structure for a bearing apparatus, by which bearings can be effectively cooled with a small amount of compressed air and compressed air consumption can be reduced.

A cooling structure for a bearing apparatus according to the present invention is a cooling structure for a bearing apparatus, wherein the bearing apparatus adjoins a rolling bearing having a stationary side race and a rotating side race which are opposed inside and outside the rolling bearing adjacent to the stationary side race a stationary side spacer and a rotating side race disposed adjacent the rotating side spacer, wherein, in a stationary member and a rotating member, the stationary side race and the stationary side spacer are disposed in the stationary member, and the race of the rotating side and the spacer of the rotating side are arranged in the rotating element,
wherein the cooling structure is a stationary-side annular recess provided on a peripheral surface of the stationary-side spacer of the rotating-side spacer, an opposite-side circumferential surface of the stationary-side spacer of the rotating side of the stationary-side recess in an axial position provided annular recess of the rotating side and a nozzle opening, which is adapted to eject compressed air from an outlet, which is open towards a lower surface of the recess of the stationary side, towards a lower surface of the recess of the rotating side, wherein the nozzle opening in a direction of rotation of the spacer of the rotating side is inclined forward. For example, the stationary side race is an outer ring and the rotating side race is an inner ring. In such a case, the stationary member and the rotating member are, for example, a housing and a shaft, respectively.

According to this embodiment, the compressed air for cooling from the nozzle opening defined by the stationary side spacer is ejected toward the lower surface of the rotating side recess provided on the rotating side spacer. The compressed air is expelled from the narrow nozzle opening into a large space formed mainly by the recess of the stationary side and the recess of the rotating side, and the compressed air is adiabatically expanded. This adiabatic expansion leads to an increase in the flow velocity and a drop in temperature of the compressed air. As a result, the spacer of the rotating side is effectively cooled. Compared with a conventional configuration, the space into which the compressed air is ejected is increased since not only the stationary-side spacer is provided with a recess in a conventional manner, but also the spacer of the rotating side is provided with a spacer. In this way, the adiabatic expansion of the compressed air is increased, so that an increase in the flow velocity and a decrease in the temperature of the compressed air is further increased, whereby a further improvement in the cooling effect is achieved.

Further, since the nozzle opening defined by the stationary-side spacer is inclined forward in the rotational direction of the rotating-side spacer, the compressed-air ejected from the nozzle opening flows in the axial direction as it swirls along the peripheral surface of the rotating-side spacer and becomes the outer side blown out of the camp. The swirling flow allows the compressed air to contact the peripheral surface of the rotating side spacer for a longer period of time than when the compressed air is flowing straight in the axial direction. Thereby, the spacer of the rotating side can be cooled more effectively.

In this way, by effectively cooling the rotating-side spacer, the rotating-side race of the rolling bearing and the rotating shaft can be effectively cooled by the rotating-side spacer. As a result, the compressed air consumption can be reduced.

In the present invention, the recess of the rotating side preferably has an axial length that is twice or more than twice the opening diameter of the nozzle opening. When the axial length of the recess of the rotating side is smaller than twice the opening diameter of the nozzle opening, the compressed air can not adequately flow into the recess of the rotating side and the compressed air ejected from the nozzle opening can not be sufficiently adiabatically expanded.

In the present invention, the recess of the rotating side preferably has a radial depth within a range of 10% to 50% of a radial thickness of the rotating side spacer.
When the radial depth of the rotary-side recess is smaller than 10% of the radial thickness of the rotating-side spacer, the volume of the compressed air can not be increased sufficiently because the volume of the rotary-side recess is small. In contrast, if the radial depth is greater than 50%, there is a risk that the spacer of the rotating side will be damaged during assembly of the bearing on the shaft or due to an axial load acting during operation because the radial thickness of the spacer the rotating side is too low.

In the present invention, the lower surface of the rotating side recess may be formed with recesses formed like cross or rib grooves. In addition, the lower surface of the recess of the rotating side may be formed with a plurality of circumferential grooves.
In these cases, the lower surface of the rotating side recess is formed as a textured grooved surface, and the lower surface has a larger surface area. This enables effective heat exchange between the rotating side spacer and the compressed air, and the cooling effect is further improved.

When the stationary-side spacer in the present invention has a stationary-side spacer body formed with the nozzle hole and a lubricating-oil-hole forming member formed with a lubricating oil hole for supplying the rolling bearing with lubricating oil, it is preferable that a peripheral surface of the stationary-side spacer body be the lower surface of the Is the stationary side recess and that a side surface of the lubricating oil opening forming member is a side wall surface of the recess of the stationary side.
Thus, when the stationary side recess is formed with the peripheral surface of the stationary side spacer body and the lubricating oil hole forming member side surface, it is only necessary to connect the stationary side spacer body and the lubricating oil hole forming member to form the stationary side recess, so that the recess of the stationary side does not have to be produced by material processing.

A combination of at least two embodiments disclosed in the appended claims and / or the description and / or the accompanying drawings is to be understood as being within the scope of the present invention. Likewise, in particular, a combination of any two or more of the appended claims should be considered to be within the scope of the present invention.

list of figures

• 1: eine Schnittansicht einer Spindelvorrichtung einer Werkzeugmaschine, welche eine Kühlstruktur für eine Lagervorrichtung nach einer ersten Ausführungsform der vorliegenden Erfindung umfasst;
• 2: eine vergrößerte Schnittansicht eines Hauptteils der Kühlstruktur für eine Lagervorrichtung;
• 3: eine Schnittansicht entlang der Linie III-III in 1;
• 4A: eine erklärende Darstellung zum Vergleich der Größe eines Raumes, in welchen Druckluft ausgestoßen wird;
• 4B: eine weitere erklärende Darstellung zum Vergleich der Größe eines Raumes, in welchen Druckluft ausgestoßen wird;
• 5: eine Schnittansicht eines Hauptteils einer Kühlstruktur für eine Lagervorrichtung nach einer zweiten Ausführungsform der vorliegenden Erfindung;
• 6: eine Schnittansicht eines Hauptteils einer Kühlstruktur für eine Lagervorrichtung nach einer dritten Ausführungsform der vorliegenden Erfindung;
• 7: eine Schnittansicht eines Hauptteils einer Kühlstruktur für eine Lagervorrichtung nach einer vierten Ausführungsform der vorliegenden Erfindung;
• 8: eine Schnittansicht eines Hauptteils einer Kühlstruktur für eine Lagervorrichtung nach einer fünften Ausführungsform der vorliegenden Erfindung;
• 9: eine Schnittansicht eines Hauptteils einer Kühlstruktur für eine Lagervorrichtung als Vergleichsbeispiel;
• 10: eine Schnittansicht eines Hauptteils einer Kühlstruktur für eine Lagervorrichtung als ein weiteres Vergleichsbeispiel;
• 11: eine Schnittansicht eines Hauptteils einer Kühlstruktur für eine Lagervorrichtung als noch ein weiteres Vergleichsbeispiel;
• 12: eine Schnittansicht eines Hauptteils einer konventionellen Kühlstruktur einer Lagervorrichtung.

In any event, a more complete understanding of the present invention will become apparent from the following description of preferred embodiments of the invention taken in conjunction with the accompanying drawings. However, the embodiments and the drawings are merely illustrative and explanatory and are in no way intended to limit the scope of the present invention which is to be determined by the appended claims. In the accompanying drawings, like reference characters designate like parts throughout the several views. Show it:

• 1 FIG. 3 is a sectional view of a spindle device of a machine tool including a cooling structure for a bearing device according to a first embodiment of the present invention; FIG.
• 2 : An enlarged sectional view of a main part of the cooling structure for a bearing device;
• 3 a sectional view taken along the line III-III in 1 ;
• 4A : an explanatory diagram for comparing the size of a space in which compressed air is ejected;
• 4B : another explanatory diagram for comparing the size of a space in which compressed air is ejected;
• 5 FIG. 3 is a sectional view of a main part of a cooling structure for a bearing apparatus according to a second embodiment of the present invention; FIG.
• 6 FIG. 3 is a sectional view of a main part of a cooling structure for a bearing apparatus according to a third embodiment of the present invention; FIG.
• 7 FIG. 3 is a sectional view of a main part of a cooling structure for a bearing apparatus according to a fourth embodiment of the present invention; FIG.
• 8th FIG. 4 is a sectional view of a main part of a cooling structure for a bearing apparatus according to a fifth embodiment of the present invention; FIG.
• 9 FIG. 3 is a sectional view of a main part of a cooling structure for a bearing apparatus as a comparative example; FIG.
• 10 FIG. 3 is a sectional view of a main part of a cooling structure for a bearing apparatus as another comparative example; FIG.
• 11 Fig. 3 is a sectional view of a main part of a cooling structure for a bearing apparatus as still another comparative example;
• 12 FIG. 3 is a sectional view of a main part of a conventional cooling structure of a bearing apparatus. FIG.

DESCRIPTION OF THE EMBODIMENTS

Hereinafter, a cooling structure for a bearing apparatus according to a first embodiment of the present invention will be described with reference to FIG 1 to 4 described in more detail.
1 FIG. 10 is a sectional view of a spindle device of a machine tool including a cooling structure for a bearing device. FIG. The cooling structure is applied to a spindle device of a machine tool in this example, but the applicability of the cooling structure is not limited to spindle devices of a machine tool.

A storage device J comprises two arranged in the axial direction of rolling bearings 1 . 1 and an outer spacer ring 4 and an inner spacer ring 5 which are between outer rings 2 . 2 or between inner rings 3 . 3 the rolling bearing 1 . 1 are arranged. The outer rings 2 and the outer spacer ring 4 are in a housing 6 arranged and the inner rings 3 and the inner spacer ring 5 are on a spindle 7 appropriate. Each of the rolling bearings 1 is an angular contact ball bearing in which a plurality of rolling elements 8th between the respective raceway surfaces of the outer ring 2 and the inner ring 3 are arranged. The rolling elements 8th are uniformly spaced in a circumferential direction by a holding device 9 held. The two rolling bearings 1 . 1 are arranged in an O arrangement and are used with an initial preload that fits each of the rolling bearings 1 . 1 according to a width dimension difference between the outer spacer ring 4 and the inner spacer 5 is set.

In this embodiment, the rolling bearing 1 used with rotating inner ring. Accordingly, the outer ring 2 and the inner ring 3 Also referred to as a "stationary side race" or as a "rotating side race" and the outer spacer 4 and the inner spacer ring 5 are also referred to as a "spacer of the stationary side" or as a "spacer of the rotating side". The spindle 7 is also referred to as a "rotating element" and the housing 6 is also referred to as a "stationary element". The same applies to the other embodiments which will be described later.

The outer rings 2 . 2 and the outer spacer ring 4 For example, they are loose relative to the housing 6 attached and through a stepped section 6a of the housing 6 and an end surface cover 40 positioned axially. On the other hand, the inner rings are 3,3 and the inner spacer 5 for example with press fit against the spindle 7 attached and by positioning spacers 41 . 42 axially positioned on both sides. The positioning spacer 42 on the left side of the figure is through one with the spindle 7 screwed mother 43 attached.

The cooling structure will be described below. As in 2 is shown, the outer spacer ring 4 an outer spacer ring body 11 which is a spacer body of the stationary side, and lubricating oil hole forming members 12 . 12 in ring form, separated from the outer spacer ring body 11 are. The outer spacer ring body 11 is formed to have a substantially T-shaped cross section, and the lubricating oil opening forming elements 12 . 12 are symmetrically positioned and on both axial sides of the outer spacer ring body 11 attached. 2 is an extended partial view of 1 , It should be noted that 1 and 2 different cross sections for one of the rolling bearings 1 represent.

The outer spacer ring body 11 has a larger inside diameter than the lubricating oil opening forming elements 12 . 12 on. In this way, the outer spacer ring 4 an inner circumferential surface that with a recess 13 the stationary side is formed, which consists of an inner peripheral surface of the outer spacer ring body 11 and side surfaces of the inner peripheral surface of the outer spacer ring body 11 leading lube opening forming elements 12 . 12 is formed. The inner peripheral surface of the outer spacer ring body 11 is a lower surface of the recess 13 the stationary side and the side surfaces of the lubricating oil opening forming elements 12 . 12 are side wall surfaces of the recess 13 the stationary side. If the recess 13 the stationary side of the inner peripheral surface of the outer spacer ring body 11 and the side surfaces of the lubricating oil hole forming members 12 . 12 is formed, it is thus only necessary, the outer spacer ring body 11 and the lubricating oil opening forming elements 12 . 12 to connect to the recess 13 to form the stationary side, leaving the recess 13 the stationary side does not have to be produced by material processing.

The recess 13 the stationary side is an annular groove having a substantially rectangular cross-section. The side surfaces of the lubricating oil opening forming elements 12 . 12 have inner diameter end portions 12a . 12a which are cut obliquely to increase the distance between the end portions to the inner diameter side. The inner peripheral surface of the outer spacer ring 4 with the exception of the recess 13 the stationary side, so the inner peripheral surfaces of the lubricating oil opening forming elements 12 . 12 , Lies or lie the outer peripheral surface of the inner spacer ring 5 with a small radial gap δa opposite.

The outer peripheral surface of the inner spacer ring 5 is with one of the inner peripheral surface of the outer spacer ring body 11 opposite annular recess 14 the rotating side provided. The recess 14 the rotating side is an annular groove having a substantially rectangular cross section. The recess 14 the rotating side has an axial width Y which is equal to the axial width of the inner peripheral surface of the outer spacer ring body 11 is. The recess 14 The rotating side also has a depth Z within a range of 10% to 50% of a radial thickness T of the inner spacer ring 5 ,

The outer spacer ring body 11 is with a nozzle opening 15 provided, which is adapted to compressed air A for cooling in the direction of a lower surface of the recess 14 the rotating side of the inner spacer 5 eject. The nozzle opening 15 has an outlet 15a on, in the direction of the lower surface of the recess 13 the rotating side of the outer spacer 4 is open. In this example, a plurality of (for example, three) orifices are formed 15 set so that they are arranged at equal intervals in the circumferential direction.

As in 3 is shown, is each of the nozzle openings 15 in a direction of rotation of the inner spacer ring 5 tilted forward. D , that is, each nozzle opening is in a position that is from any radial straight line L at a section perpendicular to the axis of the outer spacer ring 4 is, in one to the straight line L orthogonal direction is offset. The nozzle opening 15 is offset for the reason that the compressed air A thereby in the direction of rotation of the inner spacer ring 5 how an eddy current acts, which allows an improvement in the cooling effect. It should be noted that the outer spacer ring 4 in 1 and 2 as a cross section showing the center line of the nozzle opening 15 includes.

The outer spacer ring body 11 has an outer peripheral surface which is provided with an insertion groove 16 for introducing the compressed air A from the outside of the bearing into the respective nozzle openings 15 is formed. The insertion groove 16 is in an intermediate portion in the axial direction on the outer peripheral surface of the outer spacer ring 4 provided and formed such that it has a shape of a circular arc, with the respective nozzle openings 15 connected is. The insertion groove 16 is on the outer peripheral surface of the outer spacer ring body 11 over an angular range α formed, which constitutes a major part in the circumferential direction, with the exception of a circumferential position in which a lubricating oil supply channel (not shown) is provided, which will be described later. As in 1 is shown is the housing 6 with a compressed air inlet duct 45 provided and the insertion groove 16 is formed such that it communicates with the compressed air inlet channel 45 connected is. The housing 6 is externally provided with an air supply device (not shown), which is adapted to the compressed air introduction channel 45 the compressed air A supply.

A lubricating structure will be described below. As in 1 is shown, the outer spacer ring 4 the lubricating oil opening forming elements 12 . 12 to supply the bearings with lubricating oil. In this example, air oil (air blended oil) is used as the lubricating oil. Each of the lubricating oil opening forming elements 12 consists of a base section 12b with an inner spacer ring 5 with the radial gap 8a opposite inner peripheral surface and a tip portion 30 with a collar shape extending from the base portion 12b protrudes outward in the axial direction, so that it is the outer peripheral surface of the inner ring 3 with an annular gap 8b for one between the tip section 30 and the outer peripheral surface of the inner ring 3 limited air duct opposite. In other words, the top section is formulated 30 the lubricating oil opening forming element 12 arranged so that it extends into the bearing and the outer peripheral surface of the inner ring 3 covered. The top section 30 the lubricating oil opening forming element 12 is radially inside the inner peripheral surface of the holding device 9 arranged.

As in 2 is shown, the lubricating oil opening forming element 12 with a lubricating oil opening 31 to supply the annular gap 8b between the lubricating oil opening forming element 12 and the outer peripheral surface of the inner ring 3 provided with air oil. The oil opening 31 is inclined so as to lead to the inner diameter side on the bearing side, and has a toward the inner peripheral side of the tip portion 30 open outlet on. The oil opening 31 the air oil gets through the housing 6 and in the outer spacer ring body 11 provided air supply passage (not shown) supplied. The inner ring 3 is at a location where the extension line of the lubricating oil opening 31 the outer peripheral surface of the inner ring 3 cuts, with an annular recess 3a Provided.
Oil from the lubricating oil opening forming element 12 discharged air oil accumulates in the annular recess 3a on and the oil is due to one with the rotation of the inner ring 3 continuous centrifugal force along the outer peripheral surface of the inner ring 3 , which is an inclined surface, guided in the direction of the bearing center.

An outlet structure will be described below. As in 1 is shown is the bearing device J with an outlet channel 46 for discharging the compressed air for cooling and the air oil for lubrication. The outlet channel 46 includes one in a portion of the outer spacer ring body 11 in the circumferential direction provided outlet groove 47 and a radial outlet opening 48 and an axial outlet opening 49 which are in the housing 6 are provided and with the outlet groove 47 are connected. The outlet groove 47 of the outer one Spacer body 11 is formed via a circumferential position, which is opposite to the position in which the lubricating oil supply channel is provided.

The effect of the cooling structure for a bearing device having the above-described configuration will be described below: The outer spacer ring 4 provided nozzle opening 15 allows the compressed air A for cooling in the direction of the lower surface of the recess 14 the rotating side of the inner spacer 5 can be blown. Here is the compressed air A from the narrow nozzle opening 15 into one mainly through the recess 13 the stationary side and the recess 14 the turning side formed large room 20 ejected and the compressed air A is extended adiabatically. Strictly speaking, the room points 20 a size up by adding the size of the recess 13 the stationary side, the size of the recess 14 the rotating side and the size of the between the recess 13 the stationary side and the recess 14 the rotating side arranged space with the width of the radial gap 8a is obtained.

When the compressed air A in the nozzle opening 15 a volume V1 and a temperature T1 and the compressed air in the room 20 a volume V2 and a temperature T2 According to the equation of state for gases (ideal gas thermal equation of state) and the first law of thermodynamics, the temperatures and volumes can be expressed as V1 <V2 or T1> T2. That is, the temperature of the compressed air A in the room 20 decreases as the volume of compressed air increases. An increase in the volume causes a higher flow velocity of the compressed air A , In this way, the inner spacer ring 5 be effectively cooled by compressed air A with a low temperature and a high speed on the inner spacer ring 5 is blown.

In a conventional cooling structure of a bearing device, which in 12 is shown, is the volume of a room 120 in which compressed air A is ejected, substantially equal to the volume of a recess 113 ( 4A) , In contrast, the volume of the room 20 ( 4B) in which the compressed air A is ejected in the cooling structure for a storage device in 2 essentially the same as adding up the volume of the recess 13 the stationary side and the volume of the recess 14 the size of the rotating page. If the volume of the recess 113 and the volume of the recess 13 the stationary side are the same, is the space 20 the cooling structure for a storage device in 2 around the volume of the recess 14 the rotating side is larger than the room 120 the cooling structure for a storage device in 12 , For this reason, the cooling structure for a bearing device in 2 a larger coefficient of expansion of the nozzle opening 15 discharged compressed air A on and thereby are a drop in temperature and an increase in the volume of compressed air A further increased, which improves the cooling effect.

In this embodiment, the axial width Y the recess 14 the rotating side equal to the axial width of the inner peripheral surface of the outer spacer ring body 11 but the axial width Y the recess 14 the rotating side may be different from that of the inner circumferential surface of the outer spacer ring body 11 differ. However, even in such a case, it is preferable that the recess 14 the rotating side of an axial length Y which is twice as large or more than twice as large as an opening diameter D the nozzle opening 15 is. When the axial length Y the recess 14 the rotating side is smaller than twice the opening diameter D the nozzle opening 15 as it is in 9 is shown, the compressed air A not appropriate in the recess 14 the rotating side and the flow out of the nozzle opening 15 expelled compressed air A can not be sufficiently adiabatically extended.

The recess 14 The rotating side has a radial depth for the following reason Z within a range of 10% to 50% of a radial thickness T of the spacer 5 the turning side: when the radial depth Z less than 10% of the thickness T is how in 10 shown, the volume of compressed air can A due to the small volume of the recess 14 The rotating side can not be enlarged enough. In contrast, when the radial depth is 50% of the thickness T exceeds, as in 11 shown a risk that the spacer is the rotating side 5 during assembly of the rolling bearing 1 at the spindle 7 or due to an axial load acting during operation, since the thickness ( T - Z ) at a location at which the recess 14 the rotating side is formed, is too low.

Because the nozzle opening 15 in the direction of rotation of the inner spacer ring 5 is inclined forward, which flows out of the nozzle opening 15 expelled compressed air A in the axial direction, while on the outer peripheral surface of the inner spacer ring 5 is moved along, and is via the outlet channel ( 46 ) are blown out to the outside of the bearing. While the compressed air A whirls, comes the compressed air A for a longer time with the outer peripheral surface of the inner spacer ring 5 in contact, as if the compressed air flows straight in the axial direction. This allows the inner spacer ring 5 be cooled more effectively.

In this way, the inner ring 3 of the rolling bearing 1 and the spindle 7 by effectively cooling the inner spacer ring 5 over the inner spacer ring 5 be effectively cooled. The cooling effect of this cooling structure can be improved by merely developing the structure in such a way that the outer spacer ring 4 and the inner spacer ring 5 with an annular recess 13 the stationary side or an annular recess 14 the rotating side be provided and that the nozzle opening 15 is inclined. Therefore, the air supply device for the supply of compressed air A do not have high throughput and energy consumption can be reduced.

In addition, the provision of the recess provides 13 the stationary side and the recess 14 the rotating side for the following effect: the in the room 20 between the outer spacer ring 4 and the inner spacer 5 expelled compressed air A is over the radial gap 8a between the outer spacer ring 4 and the inner spacer 5 blown out to the outside of the camp. During this process, at least part of the compressed air flows A in the warehouse. Because the radial gap 8a narrower than the room 20 is, the flow velocity through the radial gap 8a flowing compressed air A in each section in the circumferential direction uniformed, resulting in a uniform flow velocity of the compressed air flowing into the bearing A leads. In this way, during the rotation between the compressed air A and the rolling elements 8th generated collision noise can be reduced.

In the 2 illustrated storage device J has the inner spacer ring 5 on, with the recess 14 the rotating side is provided, which has a rectangular cross-section; the shape of the recess 14 The rotating side is not limited to this form. For example, the recess 14 the turning side, like an in 5 illustrated second embodiment, a corner portion 21 which is an inclined surface. Furthermore, the recess 14 the turning side, like an in 6 illustrated third embodiment, a lower surface having a circular arc-shaped cross-section.

In addition, the lower surface of the recess 14 the turning side, like an in 7 illustrated fourth embodiment, with recesses formed by corrugations or the like as cross or strip grooves 22 be trained; likewise, the lower surface 14 the recess of the rotating side, as in a 8th illustrated fifth embodiment, also with a plurality of circumferential grooves 23 be formed so that the recess 14 the rotating side has the lower surface shaped as a structured grooved surface and has a larger surface area on the lower surface. In this way, by enlarging the surface of the lower surface of the recess 14 the rotating side of the heat exchange between the inner spacer ring 5 and the compressed air A performed more effectively and the cooling effect is further improved.

Although the respective embodiments listed above are described for the case where the rolling bearing 1 is used with rotating inner ring, the present invention can also be applied to the case in which the bearing is used with rotating outer ring. In such a case, for example, one on the inner circumference of the inner ring 3 mounted shaft (not shown) the stationary element and one on the outer circumference of the outer ring 2 attached roller or roller (not shown) the rotating element.

Although the present invention has been described in detail in connection with the preferred embodiments thereof with reference to the accompanying drawings, many obvious changes and modifications will be apparent to those skilled in the art in view of the description. Accordingly, such changes and modifications are to be regarded as included in the scope of the present invention as defined by the appended claims.

LIST OF REFERENCE NUMBERS

1

Rolling

2

Outer ring (stationary side race)

3

Inner ring (rotating side race)

4

outer spacer (stationary side spacer)

5

inner spacer ring (spacer of the rotating side)

6

Housing (stationary element)

7

Spindle (rotating element)

11

Outer Spacer Body (Spacer Body of Stationary Side)

12

Oil port forming element

31

Oil Opening

13

Recess of the stationary side

14

Recess of the rotating side

15

nozzle opening

15a

outlet

22

groove-shaped recess

23

circumferential groove

A

compressed air

J

bearing device

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• JP 2016 [0001]
• JP 176547 [0001]

Claims (6)

A cooling structure for a bearing apparatus, the bearing apparatus comprising a rolling bearing having a stationary side race and a rotating side race which are opposed inside and outside the rolling bearing, a stationary side spacer adjacent to the stationary side race and a rotating side race Side disposed adjacent spacer of the rotating side, wherein in a stationary member and a rotating member, the stationary side of the stationary ring and the stationary side spacer are arranged in the stationary member and the rotating side race and the rotating side spacer in the rotating member are arranged, the cooling structure comprising: a ring-shaped recess of the stationary side, which is provided on a peripheral surface of the spacer of the rotating side opposite spacer of the stationary side, a ringför A rotary opening side recess provided on the stationary side recess in an axial position opposed to a peripheral surface of the rotating side spacer opposed to the stationary side spacer, and a nozzle opening adapted to receive pressurized air from an outlet formed in Direction of a lower surface of the recess of the stationary side is opened to eject toward a lower surface of the recess of the rotating side, wherein the nozzle opening is inclined in a rotational direction of the spacer of the rotating side forward. Cooling structure for a storage device according to Claim 1 wherein the recess of the rotating side has an axial length that is twice or more than twice the opening diameter of the nozzle opening. Cooling structure for a storage device according to Claim 1 or 2 wherein the recess of the rotating side has a radial depth within a range of 10% to 50% of a radial thickness of the rotating side spacer. Cooling structure for a bearing device according to one of Claims 1 to 3 wherein the lower surface of the recess of the rotating side is formed with recesses shaped like cross or strip grooves. Cooling structure for a bearing device according to one of Claims 1 to 3 wherein the lower surface of the recess of the rotating side is formed with a plurality of circumferential grooves. Cooling structure for a bearing device according to one of Claims 1 to 5 wherein the stationary side spacer comprises a stationary side spacer body formed with the nozzle opening and a lubricating oil hole forming member formed with a lubricating oil hole for supplying the rolling bearing with lubricating oil, a peripheral surface of the stationary side spacer body, the lower surface of the recess is the stationary side, and a side surface of the lubricating oil hole forming member is a side wall surface of the stationary side recess.

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