JP2015117820A - Cooling structure of bearing device - Google Patents

Cooling structure of bearing device Download PDF

Info

Publication number
JP2015117820A
JP2015117820A JP2014059360A JP2014059360A JP2015117820A JP 2015117820 A JP2015117820 A JP 2015117820A JP 2014059360 A JP2014059360 A JP 2014059360A JP 2014059360 A JP2014059360 A JP 2014059360A JP 2015117820 A JP2015117820 A JP 2015117820A
Authority
JP
Japan
Prior art keywords
ring spacer
cold air
bearing device
nozzles
cooling structure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP2014059360A
Other languages
Japanese (ja)
Inventor
水谷　守
Mamoru Mizutani
守 水谷
森　正継
Masatsugu Mori
正継 森
裕士 恩田
Yuji Onda
裕士 恩田
真人 吉野
Masato Yoshino
真人 吉野
鈴木　康介
Kosuke Suzuki
康介 鈴木
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Priority to JP2014059360A priority Critical patent/JP2015117820A/en
Priority to PCT/JP2014/079406 priority patent/WO2015072383A1/en
Priority to TW103139787A priority patent/TW201540977A/en
Publication of JP2015117820A publication Critical patent/JP2015117820A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
    • B23Q1/70—Stationary or movable members for carrying working-spindles for attachment of tools or work
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/007—Cooling of bearings of rolling bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)
  • Auxiliary Devices For Machine Tools (AREA)
  • Turning (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a cooling structure of a bearing device which can equally cool rolling bearings in a circumferential direction, and can efficiently cool an inner ring spacer which is interposed between inner rings of the rolling bearings, in the bearing device having a plurality of the rolling bearings which are aligned in an axial direction.SOLUTION: In a bearing device J, an outer ring spacer 4 and an inner ring spacer 5 are interposed between outer rings 2 and between inner rings 3 of a plurality of rolling bearings 1 which are aligned in an axial direction, the outer rings 2 and the inner rings 4 are arranged in a housing, and the inner rings 3 and an inner ring spacer 5 are fit to a shaft. A plurality of nozzles 12 for blowing cooling winds to an external peripheral face of the inner ring spacer 5 are arranged at the outer ring spacer 4. For example, the nozzles 12 are arranged in a plurality of aligning rows at the outer ring spacer 4 in an axial direction and a circumferential direction, respectively.

Description

この発明は、軸受装置の冷却構造に関し、例えば、工作機械の主軸および主軸に組み込まれる軸受装置の冷却構造に関する。   The present invention relates to a cooling structure for a bearing device, for example, a main shaft of a machine tool and a cooling structure for a bearing device incorporated in the main shaft.

工作機械の主軸装置では、加工精度を確保するために、装置の温度上昇を小さく抑える必要がある。しかし、最近の工作機械では、加工能率を向上させるため高速化の傾向にあり、主軸を支持する軸受からの発熱も高速化と共に大きくなってきている。また、装置内部に駆動用のモータを組み込んだいわゆるモータビルトインタイプが多くなってきており、装置の発熱要因となってきている。   In a spindle device of a machine tool, in order to ensure machining accuracy, it is necessary to suppress a temperature rise of the device. However, recent machine tools have a tendency to increase the speed in order to improve the processing efficiency, and the heat generated from the bearing supporting the main shaft is also increasing as the speed increases. In addition, so-called motor built-in type in which a driving motor is incorporated in the apparatus is becoming more and more a cause of heat generation of the apparatus.

発熱による軸受の温度上昇は、予圧の増加をもたらす結果となり、主軸の高速化、高精度化を考えると極力抑えたい。軸受の温度上昇を抑える方法として、軸受に冷風を送り、軸と軸受の冷却を行う方法がある（例えば特許文献１）。特許文献１では、冷風を、軸の回転方向に角度を付けて噴射して旋回流とすることで、冷却効果を高めている。   The rise in the temperature of the bearing due to heat generation results in an increase in preload, and we want to suppress it as much as possible in consideration of higher speed and higher accuracy of the spindle. As a method of suppressing the temperature rise of the bearing, there is a method of cooling the shaft and the bearing by sending cold air to the bearing (for example, Patent Document 1). In patent document 1, the cooling effect is heightened by injecting cold wind at an angle in the rotational direction of the shaft to form a swirling flow.

特開２０００−１６１３７５号公報JP 2000-161375 A

上記冷風による冷却方法は、冷却効果が高いので、軸受の温度上昇を効果的に抑えることが期待できる。しかし、特許文献１に記載の冷却構造は、冷風を噴射する冷風注入パイプが１箇所（図示例の場合）にしか設けられていないので、軸受が均等に冷却されず、温度むらによる弊害が起こり得る。   Since the cooling method using the cold air has a high cooling effect, it can be expected to effectively suppress the temperature rise of the bearing. However, since the cooling structure described in Patent Document 1 is provided with only one cold air injection pipe for injecting cold air (in the illustrated example), the bearings are not cooled uniformly, and a problem due to temperature unevenness occurs. obtain.

軸方向に並ぶ複数の軸受を冷却する場合、特許文献１にも図示されているように、主軸装置の構造上、装置外部から供給される冷風を、外径側から複数の軸受間の空間に導入し、前記空間を経由して各軸受に送るのが現実的である。その場合、各軸受の内輪間に介在する内輪間座を効率良く冷却することが重要となる。その理由は、冷風で直接軸受を冷却するだけでなく、冷風により冷却された内輪間座でこの内輪間座に接する軸受の内輪を冷却することで、軸受の温度上昇をより一層効果的に抑えることができるからである。   When cooling a plurality of bearings arranged in the axial direction, as shown in Patent Document 1, due to the structure of the spindle device, cool air supplied from the outside of the device is introduced into the space between the plurality of bearings from the outer diameter side. It is realistic to introduce and send to each bearing via the space. In that case, it is important to efficiently cool the inner ring spacer interposed between the inner rings of the bearings. The reason for this is not only cooling the bearing directly with cold air, but also cooling the inner ring of the bearing that is in contact with the inner ring spacer with the inner ring spacer cooled by cold air, thereby further suppressing the temperature rise of the bearing. Because it can.

また、ノズルが一つだけであると、次のような問題がある。すなわち、一つのノズルから多量の冷風を内輪間座に向けて吐出すると、ノズルの吐出口で流速が最大速度（例えば音速）となる。ノズルの吐出口と内輪間座の間のすきまが狭い場合、このすきまの圧力が高くなりやすく、圧縮波が発生する。圧縮波が発生すると、ノズルから吐出される冷風の直進流れが阻害され、軸方向に拡散する。それにより、冷風が内輪間座の外周面と接する時間が短くなり、内輪間座と内輪を十分に冷却しないまま排気されて、冷却効果が低下する。   Further, when there is only one nozzle, there is the following problem. That is, when a large amount of cold air is discharged from one nozzle toward the inner ring spacer, the flow velocity becomes the maximum speed (for example, the speed of sound) at the discharge port of the nozzle. If the clearance between the nozzle outlet and the inner ring spacer is narrow, the pressure in this clearance tends to increase, and a compression wave is generated. When the compression wave is generated, the straight flow of the cold air discharged from the nozzle is inhibited and diffused in the axial direction. As a result, the time during which the cool air contacts the outer peripheral surface of the inner ring spacer is shortened, and the inner ring spacer and the inner ring are exhausted without being sufficiently cooled, thereby reducing the cooling effect.

この発明の目的は、軸方向に並ぶ複数の転がり軸受を有する軸受装置において、各転がり軸受の内輪間に介在する内輪間座を均等に冷却して、転がり軸受および軸を効率良く冷却することができ、さらに冷風を吐出するノズルの吐出口と内輪間座の間のすきまでの圧縮波の発生を抑制して冷却効果をより一層高めることができる軸受装置の冷却構造を提供することである。   An object of the present invention is to efficiently cool the rolling bearing and the shaft by uniformly cooling the inner ring spacer interposed between the inner rings of each rolling bearing in a bearing device having a plurality of rolling bearings arranged in the axial direction. It is also possible to provide a cooling structure for a bearing device that can further enhance the cooling effect by suppressing the generation of compression waves up to the gap between the discharge port of the nozzle that discharges cold air and the inner ring spacer.

この発明の軸受装置の冷却構造は、軸方向に並ぶ複数の転がり軸受の外輪間および内輪間に外輪間座および内輪間座をそれぞれ介在させ、前記外輪および外輪間座がハウジングに設置され、前記内輪および内輪間座が軸に嵌合される軸受装置において、前記外輪間座に、前記内輪間座の外周面に対して冷風を吹き付けるノズルを複数設けたことを特徴とする。前記ノズルは、軸方向に並べて複数設けても良いし、周方向に並べて複数設けても良い。また、前記ノズルは、軸方向および周方向にそれぞれ複数配列で設けても良い。   According to the cooling structure of the bearing device of the present invention, an outer ring spacer and an inner ring spacer are respectively interposed between outer rings and inner rings of a plurality of rolling bearings arranged in the axial direction, and the outer ring and the outer ring spacer are installed in a housing, In the bearing device in which the inner ring and the inner ring spacer are fitted to the shaft, the outer ring spacer is provided with a plurality of nozzles that blow cool air against the outer peripheral surface of the inner ring spacer. A plurality of the nozzles may be provided side by side in the axial direction, or a plurality of nozzles may be provided side by side in the circumferential direction. The nozzles may be provided in a plurality of arrays in the axial direction and the circumferential direction.

この構成によると、外輪間座に設けられたノズルより、冷風を内輪間座の外周面に吹き付けて、内輪間座を冷却する。そして、冷却された内輪間座により、この内輪間座に接する転がり軸受の内輪を冷却する。また、冷風は、内輪間座の外周面に吹き付けられた後、内輪間座と外輪間座のすきまを通って転がり軸受内に送られ、転がり軸受を直接冷却する。これら冷却された内輪間座および内輪により、軸も冷却される。このように、冷風で転がり軸受を直接冷却するだけでなく、冷風により冷却された内輪間座で転がり軸受の内輪を冷却することで、転がり軸受および軸の温度上昇をより一層効果的に抑えることができる。   According to this configuration, cool air is blown from the nozzle provided in the outer ring spacer to the outer peripheral surface of the inner ring spacer to cool the inner ring spacer. And the inner ring | wheel of the rolling bearing which contact | connects this inner ring | wheel spacer is cooled with the cooled inner ring | wheel spacer. The cold air is blown onto the outer peripheral surface of the inner ring spacer, and then sent through the clearance between the inner ring spacer and the outer ring spacer into the rolling bearing to directly cool the rolling bearing. The shaft is also cooled by the cooled inner ring spacer and inner ring. In this way, not only the rolling bearing is directly cooled by cold air, but also the inner ring of the rolling bearing is cooled by the inner ring spacer cooled by the cold air, so that the temperature rise of the rolling bearing and the shaft can be further effectively suppressed. Can do.

ノズルが複数設けられているため、内輪間座を軸方向および周方向のいずれか、または両方の方向にほぼ均等に冷却することが可能である。具体的には、ノズルを周方向に並べて複数設けた場合は、内輪間座を周方向にほぼ均等に効率良く冷却することができる。ノズルを軸方向に並べて複数設けた場合は、内輪間座を軸方向にほぼ均等に効率良く冷却することができる。ノズルを軸方向および周方向にそれぞれ複数配列で設けた場合は、内輪間座を軸方向および周方向の両方の方向にほぼ均等に冷却することができる。内輪間座が均等に冷却されると、転がり軸受および軸も均等に冷却され、温度むらによる弊害を排除することができる。   Since a plurality of nozzles are provided, it is possible to cool the inner ring spacer substantially uniformly in either or both of the axial direction and the circumferential direction. Specifically, when a plurality of nozzles are provided side by side in the circumferential direction, the inner ring spacer can be efficiently cooled substantially uniformly in the circumferential direction. When a plurality of nozzles are provided side by side in the axial direction, the inner ring spacer can be cooled almost uniformly and efficiently in the axial direction. When a plurality of nozzles are provided in the axial direction and the circumferential direction, the inner ring spacer can be cooled substantially uniformly in both the axial direction and the circumferential direction. When the inner ring spacer is cooled evenly, the rolling bearing and the shaft are also cooled uniformly, and the adverse effects due to temperature unevenness can be eliminated.

また、ノズルが複数設けられていると、一つのノズルから吐出される冷風の流量が少なくて済む。それにより、ノズルの吐出口と内輪間座の間のすきまが狭くても、このすきまの圧力が高くなり難く、前記すきまにおけるノズルの吐出口付近で発生する圧縮波の強度が低く抑えられる。その結果、ノズルから吐出された冷風がまっすぐに進んで直接に内輪間座の外周面に吹き付けられる。そのため、冷風が圧縮波に遮られて軸方向に拡散される場合と比べて、冷風が内輪間座の外周面と接する時間が長くなり、冷却効果が向上する。   Further, when a plurality of nozzles are provided, the flow rate of the cold air discharged from one nozzle can be reduced. As a result, even if the clearance between the nozzle outlet and the inner ring spacer is narrow, the pressure of this clearance is unlikely to increase, and the strength of the compression wave generated in the vicinity of the nozzle outlet in the clearance can be kept low. As a result, the cool air discharged from the nozzle advances straight and is blown directly onto the outer peripheral surface of the inner ring spacer. Therefore, compared with the case where the cold air is blocked by the compression wave and diffused in the axial direction, the time during which the cold air contacts the outer peripheral surface of the inner ring spacer is increased, and the cooling effect is improved.

前記外輪間座に、前記ノズルを軸方向および周方向にそれぞれ複数配列で設ける場合、前記ノズルがそれぞれ周方向に複数並んだノズル列を軸方向に複数組有し、互いに隣り合う２組の前記ノズル列間で、各ノズルの周方向位置を互いにずらせても良い。
ノズルから吐出された冷風は、ノズル吐出口付近では流速が速く（圧力が低い）、かつ周方向への直進性も強い。しかし、ノズル吐出口から離れると、流速が遅くなり、軸方向へ流れて拡散しやすくなる。互いに隣り合う２組の前記ノズル列間で、各ノズルの周方向位置が互いにずれていると、流速が遅くなる付近に隣のノズル列のノズル吐出口が位置し、その付近が低圧域となっている。この低圧域に引き込まれて、冷風が軸方向に拡散するのが抑制されるため、ノズルから吐出される冷風の直進性が良くなる。それにより、冷却効果がより一層高まる。 When the outer ring spacer is provided with a plurality of nozzles in the axial direction and the circumferential direction, the nozzle has a plurality of nozzle rows in which the nozzles are arranged in the circumferential direction in the axial direction, and the two sets of the nozzles adjacent to each other. You may shift the circumferential direction position of each nozzle mutually between nozzle rows.
The cold air discharged from the nozzle has a high flow velocity (low pressure) in the vicinity of the nozzle discharge port, and has a strong straightness in the circumferential direction. However, when it leaves | separates from a nozzle discharge port, a flow velocity becomes slow and it becomes easy to spread | diffuse by flowing to an axial direction. If the circumferential positions of the nozzles are shifted from each other between the two sets of nozzle rows adjacent to each other, the nozzle discharge port of the adjacent nozzle row is located in the vicinity where the flow velocity becomes slow, and the vicinity thereof is a low pressure region. ing. Since the cold air is suppressed from being diffused in the axial direction by being drawn into the low pressure region, the straightness of the cold air discharged from the nozzle is improved. Thereby, the cooling effect is further enhanced.

この発明の軸受装置の冷却構造において、前記外輪間座における、前記ノズルの吐出口がある内周面と、前記ノズルに対向する前記内輪間座の外周面とのすきま寸法が前記ノズルの口径の１／２以下で、かつ前記吐出口から前記内輪間座の外周面における冷風が当る箇所までの距離が０．７ｍｍ以上であるのが良い。   In the cooling structure for a bearing device according to the present invention, the clearance between the inner peripheral surface of the outer ring spacer where the nozzle discharge port is located and the outer peripheral surface of the inner ring spacer facing the nozzle is the diameter of the nozzle. It is preferable that the distance from the discharge port to the location where the cold air hits on the outer peripheral surface of the inner ring spacer is 0.7 mm or more.

前記すきま寸法をノズルの口径の１／２以下にすることで、ノズルの吐出口の圧力が高くなり、冷風の急激な膨張が抑えられる。これにより、冷風の噴射音を低減することができる。すきま寸法の上限は、運転中に生じる内輪間座の温度上昇と遠心力による膨張で内輪間座が、外輪間座に接触しないように設定する。
吐出口から前記内輪間座の外周面における冷風が当る箇所までの距離を０．７ｍｍ以上とすることで、冷却効果を維持しつつ騒音の低減効果を併せて持つことを試験で見出した。軸受サイズ（間座の径）にかかわらず、前記距離を０．７ｍｍ以上に確保することで、このような冷却効果を維持しつつ騒音の低減効果を併せて持つ効果が得られる。 By setting the clearance size to ½ or less of the nozzle diameter, the pressure of the nozzle outlet increases, and rapid expansion of cold air is suppressed. Thereby, the injection sound of cold wind can be reduced. The upper limit of the clearance dimension is set so that the inner ring spacer does not contact the outer ring spacer due to the temperature rise of the inner ring spacer that occurs during operation and expansion due to centrifugal force.
Tests have found that the distance from the discharge port to the location where the cold air hits the outer peripheral surface of the inner ring spacer is 0.7 mm or more, and the noise reduction effect is maintained while maintaining the cooling effect. Regardless of the bearing size (spacer diameter), by securing the distance to 0.7 mm or more, it is possible to obtain the effect of having a noise reduction effect while maintaining such a cooling effect.

この発明の軸受装置の冷却構造において、前記外輪間座は、内部にこの外輪間座の円周方向に沿って形成された環状空間と、この環状空間に繋がり装置外部から冷風が供給される冷風供給口と、前記環状空間と内周面間を連通する前記複数のノズルとを有し、前記外輪間座は、前記環状空間となる円周溝および前記冷風供給口を有する外径側部品と、前記複数のノズルを有する内径側部品とを互いに接合したものであっても良い。   In the cooling structure of the bearing device according to the present invention, the outer ring spacer includes an annular space formed along a circumferential direction of the outer ring spacer, and cold air connected to the annular space and supplied with cold air from the outside of the device. An outer diameter side component having a supply port and the plurality of nozzles communicating between the annular space and an inner peripheral surface, the outer ring spacer having a circumferential groove serving as the annular space and the cold air supply port; The inner diameter part having the plurality of nozzles may be joined to each other.

この構成であると、装置外部から供給される冷風が、冷風供給口から環状空間に入り、さらに環状空間から各ノズルを通って内輪間座の外周面に吹き付けられる。少なくとも１箇所の冷風供給口に冷風を供給するだけで、軸方向および周方向にそれぞれ複数配列で設けたノズルから冷風を吹き出すことができるため、装置外からの冷風の供給経路を簡略にすることができる。
外輪間座を、環状空間となる円周溝および冷風供給口を有する外径側部品と、複数のノズルを有する内径側部品とに分割し、両部材を互いに接合した構成とすると、外輪間座に前記環状空間、冷風供給口、および複数のノズルを容易に形成することができる。 With this configuration, cold air supplied from the outside of the apparatus enters the annular space from the cold air supply port, and further blows from the annular space through the nozzles to the outer peripheral surface of the inner ring spacer. By simply supplying cold air to at least one cold air supply port, it is possible to blow out cold air from a plurality of nozzles provided in a plurality of arrays in the axial direction and circumferential direction, thereby simplifying the supply path of the cold air from the outside of the apparatus. Can do.
The outer ring spacer is divided into an outer diameter side part having a circumferential groove and a cold air supply port that forms an annular space, and an inner diameter side part having a plurality of nozzles, and both members are joined to each other. Further, the annular space, the cold air supply port, and the plurality of nozzles can be easily formed.

この発明の軸受装置の冷却構造において、前記複数のノズルを、回転方向の前方へ傾斜させて設けても良い。
この構成であると、ノズルから吹き出された冷風が、内輪間座の外周面に沿う旋回流となって軸の回転方向に安定して流れる。それにより、内輪間座の表面の熱を奪って、効果的に冷却することが期待できる。 In the cooling structure for a bearing device according to the present invention, the plurality of nozzles may be provided to be inclined forward in the rotational direction.
With this configuration, the cool air blown from the nozzle becomes a swirl flow along the outer peripheral surface of the inner ring spacer and flows stably in the rotational direction of the shaft. Thereby, it can be expected that the surface of the inner ring spacer is deprived of heat and effectively cooled.

また、この発明の軸受装置の冷却構造において、前記外輪間座は、前記環状空間、冷風供給口、および複数のノズルの組合せからなる冷風流路を複数組有し、これら複数組の冷風流路のうち少なくとも１つの冷風流路の前記ノズルは、前記軸が正転方向に回転するときにその回転方向の前方へ傾斜させて設けられ、他の冷風流路の前記ノズルは、前記軸が逆転方向に回転するときにその回転方向の前方へ傾斜させて設けられ、かつ前記各冷風流路への冷風の供給を個別にＯＮ・ＯＦＦ切換え可能な冷風切換手段を設けても良い。   Further, in the cooling structure for a bearing device of the present invention, the outer ring spacer has a plurality of sets of cold air passages composed of a combination of the annular space, the cold air supply port, and a plurality of nozzles, and the plurality of sets of cold air passages. The nozzles of at least one of the cool air flow paths are provided so as to be inclined forward in the rotation direction when the shaft rotates in the forward rotation direction, and the nozzles of the other cool air flow paths are rotated in the reverse direction. It is also possible to provide a cold air switching means that is provided so as to incline forward in the direction of rotation when rotating in the direction and can individually switch ON / OFF the supply of the cold air to each of the cold air flow paths.

この場合、軸の回転方向に応じて冷風切換手段により各冷風流路への冷風の供給を適宜ＯＮ・ＯＦＦ切り換えることで、軸が正転方向に回転するときは、ノズルから吹き出される冷風が正転方向の旋回流となる冷風流路だけをＯＮにし、軸が逆転方向に回転するときは、ノズルから吹き出される冷風が逆転方向の旋回流となる冷風流路だけをＯＮにする。これにより、軸が正逆いずれの方向に回転する場合でも、冷風により内輪間座の表面の熱を奪って、内輪間座および内輪を効果的に冷却することができる。   In this case, by appropriately switching ON / OFF the supply of the cold air to each cold air flow path by the cold air switching means according to the rotation direction of the shaft, when the shaft rotates in the forward rotation direction, the cold air blown from the nozzle is When only the cool air flow path that becomes the swirl flow in the forward rotation direction is turned ON and the shaft rotates in the reverse rotation direction, only the cold air flow path that turns the cold air blown from the nozzle in the reverse rotation direction is turned ON. Thereby, even when the shaft rotates in either the forward or reverse direction, the inner ring spacer and the inner ring can be effectively cooled by taking the heat of the surface of the inner ring spacer with the cold air.

この発明の軸受装置の冷却構造は、特に、前記各ノズルが冷風を音速程度の流速で吐出することを可能とする形状である場合に有効である。
この場合、ノズルから音速程度の高速の冷風が吐出され圧縮波が発生しやすいが、この発明の軸受装置の冷却構造とすることで、強い圧縮波が発生することを防ぐことができる。 The cooling structure for a bearing device according to the present invention is particularly effective when each of the nozzles has a shape capable of discharging cold air at a flow velocity about the speed of sound.
In this case, a high-speed cold wind of about the speed of sound is discharged from the nozzle and a compression wave is likely to be generated. However, by using the cooling structure of the bearing device of the present invention, it is possible to prevent a strong compression wave from being generated.

この発明の軸受装置の冷却構造は、工作機械の主軸の支持に好適に用いることができる。その場合、転がり軸受を円周方向均等に冷却することができ、かつ各転がり軸受の内輪間に介在する内輪間座を効率良く冷却できるので、高速な領域での運転が可能となる。   The cooling structure for a bearing device according to the present invention can be suitably used for supporting the spindle of a machine tool. In this case, the rolling bearing can be cooled evenly in the circumferential direction, and the inner ring spacer interposed between the inner rings of the respective rolling bearings can be efficiently cooled, so that operation in a high speed region is possible.

この発明の軸受装置の冷却構造は、軸方向に並ぶ複数の転がり軸受の外輪間および内輪間に外輪間座および内輪間座をそれぞれ介在させ、前記外輪および外輪間座がハウジングに設置され、前記内輪および内輪間座が軸に嵌合される軸受装置において、前記外輪間座に、前記内輪間座の外周面に対して冷風を吹き付けるノズルを複数設けたため、各転がり軸受の内輪間に介在する内輪間座を均等に冷却して、転がり軸受および軸を効率良く冷却することができ、さらに冷風を吐出するノズルの吐出口と内輪間座の間のすきまでの圧縮波の発生を抑制して冷却効果をより一層高めることができる。   According to the cooling structure of the bearing device of the present invention, an outer ring spacer and an inner ring spacer are respectively interposed between outer rings and inner rings of a plurality of rolling bearings arranged in the axial direction, and the outer ring and the outer ring spacer are installed in a housing, In the bearing device in which the inner ring and the inner ring spacer are fitted to the shaft, the outer ring spacer is provided with a plurality of nozzles that blow cool air against the outer peripheral surface of the inner ring spacer, and therefore is interposed between the inner rings of the respective rolling bearings. The inner ring spacer can be cooled evenly, rolling bearings and shafts can be cooled efficiently, and the generation of compression waves up to the gap between the nozzle outlet that discharges cold air and the inner ring spacer is suppressed. The cooling effect can be further enhanced.

この発明の一実施形態に係る冷却構造を備えた軸受装置が組み込まれた主軸装置の断面図である。It is sectional drawing of the main axis | shaft apparatus incorporating the bearing apparatus provided with the cooling structure which concerns on one Embodiment of this invention. 同軸受装置の断面図である。It is sectional drawing of the bearing apparatus. 図２のIII−III断面図である。FIG. 3 is a sectional view taken along line III-III in FIG. 2. 図３の部分拡大図である。FIG. 4 is a partially enlarged view of FIG. 3. 同軸受装置の外輪間座の分解断面図である。It is an exploded sectional view of the outer ring spacer of the bearing device. 同外輪間座の外径側部品および内径側部品の接合方法の一例を示す断面図である。It is sectional drawing which shows an example of the joining method of the outer diameter side components and inner diameter side components of the outer ring spacer. この発明の異なる実施形態に係る冷却構造を備えた軸受装置の断面図である。It is sectional drawing of the bearing apparatus provided with the cooling structure which concerns on different embodiment of this invention. 図７のVIII−VIII断面図である。It is VIII-VIII sectional drawing of FIG. 図７のIX−IX断面図である。It is IX-IX sectional drawing of FIG. この発明のさらに異なる実施形態に係る冷却構造を備えた軸受装置の断面図である。It is sectional drawing of the bearing apparatus provided with the cooling structure which concerns on further different embodiment of this invention. 同軸受装置の外輪間座を内周側から見た部分展開図である。It is the partial expanded view which looked at the outer ring spacer of the bearing device from the inner peripheral side. 同軸受装置のノズルの吐出口の周辺部を軸方向から見た図である。It is the figure which looked at the peripheral part of the discharge outlet of the nozzle of the bearing apparatus from the axial direction. 圧縮波が発生している状態におけるノズルの吐出口付近の圧力分布を示す図である。It is a figure which shows the pressure distribution near the discharge outlet of a nozzle in the state in which the compression wave has generate | occur | produced. 圧縮波が発生している状態におけるノズルの吐出口付近に温度分布を示す図である。It is a figure which shows temperature distribution near the discharge outlet of a nozzle in the state in which the compression wave has generate | occur | produced. （Ａ），（Ｂ）はいずれもノズルの吐出口近傍の横断面形状と質量流量との関係を示す図であり、（Ａ）はノズルが１個である場合を示し、（Ｂ）はノズルを周方向に並べて複数設けた場合を示す。(A), (B) is a figure which shows the relationship between the cross-sectional shape near the discharge outlet of a nozzle, and a mass flow rate, (A) shows the case where there is one nozzle, (B) is a nozzle. A case is shown in which a plurality of are arranged in the circumferential direction. （Ａ），（Ｂ）はいずれもノズルの吐出口近傍の横断面形状と質量流量との関係を示す図であり、（Ａ）はノズルが１個である場合を示し、（Ｂ）はノズルを軸方向に並べて複数設けた場合を示す。(A), (B) is a figure which shows the relationship between the cross-sectional shape near the discharge outlet of a nozzle, and a mass flow rate, (A) shows the case where there is one nozzle, (B) is a nozzle. A case is shown in which a plurality of are arranged in the axial direction. 他の形状をしたノズルの断面図である。It is sectional drawing of the nozzle which carried out the other shape.

この発明の一実施形態に係る軸受装置の冷却構造を図１ないし図４と共に説明する。
図２に示すように、この軸受装置Ｊは、軸方向に並ぶ２つの転がり軸受１，１を備え、各転がり軸受１，１の外輪２，２間および内輪３，３間に、外輪間座４および内輪間座５がそれぞれ介在されている。転がり軸受１はアンギュラ玉軸受であり、内外輪３，２の軌道面間に複数の転動体８が介在されている。各転動体８は、保持器９により円周等配に保持される。２つの転がり軸受１，１は互いに背面組合せで配置されており、外輪間座４と内輪間座５の幅寸法差により、各転がり軸受１，１の初期予圧を設定して使用される。 A cooling structure for a bearing device according to an embodiment of the present invention will be described with reference to FIGS.
As shown in FIG. 2, this bearing device J includes two rolling bearings 1, 1 arranged in the axial direction, and an outer ring spacer between the outer rings 2, 2 and between the inner rings 3, 3 of each rolling bearing 1, 1. 4 and an inner ring spacer 5 are interposed. The rolling bearing 1 is an angular ball bearing, and a plurality of rolling elements 8 are interposed between the raceway surfaces of the inner and outer rings 3 and 2. The rolling elements 8 are held by the cage 9 at an equal circumference. The two rolling bearings 1 and 1 are arranged in combination with each other on the back surface, and are used by setting the initial preload of each rolling bearing 1 and 1 depending on the width dimension difference between the outer ring spacer 4 and the inner ring spacer 5.

図１は、前記軸受装置Ｊを工作機械の主軸の支持に用いた状態を示す。転がり軸受１，１の外輪２，２および外輪間座４がハウジング６の内周面に嵌合し、転がり軸受１，１の内輪３，３および内輪間座５が主軸７の外周面に嵌合している。主軸７は、請求項で言う「軸」である。外輪２，２および外輪間座４は、例えばハウジング６に対してすきま嵌めとされ、ハウジング６の段部６ａと端面蓋２０とにより軸方向の位置決めがされる。また、内輪３，３および内輪間座５は、例えば主軸７に対して締まり嵌めとされ、両側の位置決め間座２１，２２により軸方向の位置決めがされる。なお、図の左側の位置決め間座２２は、主軸７に螺着させたナット２３により固定されている。   FIG. 1 shows a state in which the bearing device J is used for supporting a spindle of a machine tool. The outer rings 2 and 2 and the outer ring spacer 4 of the rolling bearings 1 and 1 are fitted to the inner peripheral surface of the housing 6, and the inner rings 3 and 3 and the inner ring spacer 5 of the rolling bearings 1 and 1 are fitted to the outer peripheral surface of the main shaft 7. Match. The main shaft 7 is an “axis” in the claims. The outer rings 2 and 2 and the outer ring spacer 4 are, for example, a clearance fit with respect to the housing 6, and are positioned in the axial direction by the step portion 6 a of the housing 6 and the end surface lid 20. The inner rings 3 and 3 and the inner ring spacer 5 are, for example, an interference fit with respect to the main shaft 7 and are positioned in the axial direction by the positioning spacers 21 and 22 on both sides. Note that the positioning spacer 22 on the left side of the figure is fixed by a nut 23 screwed onto the main shaft 7.

図２、図３に示すように、前記外輪間座４は、内部にこの外輪間座４の円周方向に沿って形成された環状空間１０と、この環状空間１０に繋がり装置外部から冷風が供給される冷風供給口１１と、前記環状空間１０と内周面間を連通する複数のノズル１２とを有する。これら冷風供給口１１、環状空間１０、および複数のノズル１２で、外輪間座４内の冷風流路１３が構成される。複数のノズル１２は、軸方向および周方向にそれぞれ複数配列で設けられている。図の例では、各ノズル１２は外径端から内径端へ至るまで口径が一定であるが、内周端の吐出口１２ａ側へ行くほど先細りの形状としても良い。冷風供給口１１の断面積をＳ、各ノズル１２の吐出口１２ａの断面積の合計をＳ’totalとした場合、Ｓ’total＞Ｓの関係が成り立つようにする。これにより、ノズル１２の吐出口１２ａから吐出される冷風の圧力が下がり、冷風が内輪間座５の外周面に衝突するときに生じる衝突音を小さくすることができる。   As shown in FIGS. 2 and 3, the outer ring spacer 4 includes an annular space 10 formed along the circumferential direction of the outer ring spacer 4, and cold air from the outside of the apparatus connected to the annular space 10. The cool air supply port 11 to be supplied and a plurality of nozzles 12 communicating between the annular space 10 and the inner peripheral surface are provided. The cold air supply port 11, the annular space 10, and the plurality of nozzles 12 constitute a cold air flow path 13 in the outer ring spacer 4. The plurality of nozzles 12 are provided in a plurality of arrays in the axial direction and the circumferential direction, respectively. In the illustrated example, each nozzle 12 has a constant diameter from the outer diameter end to the inner diameter end, but may have a tapered shape toward the discharge port 12a side at the inner peripheral end. When the cross-sectional area of the cold air supply port 11 is S and the sum of the cross-sectional areas of the discharge ports 12a of the nozzles 12 is S'total, the relationship S'total> S is established. Thereby, the pressure of the cold air discharged from the discharge port 12a of the nozzle 12 is lowered, and the collision sound generated when the cold air collides with the outer peripheral surface of the inner ring spacer 5 can be reduced.

各ノズル１２は直線状であって、吐出口１２ａ側を主軸７の回転方向（図３に矢印で示す）の前方へ傾斜させてある。つまり、各ノズル１２は、外輪間座４の軸心に垂直な断面における任意の半径方向の直線から、この直線と直交する方向にオフセットした位置にある。ノズル１２をオフセットさせる理由は、ノズル１２から噴射された冷風を主軸７の回転方向に旋回流として作用させて、冷却効果を高めるためである。   Each nozzle 12 is linear, and the discharge port 12a side is inclined forward in the rotation direction of the main shaft 7 (indicated by an arrow in FIG. 3). That is, each nozzle 12 is at a position offset from an arbitrary straight line in a cross section perpendicular to the axis of the outer ring spacer 4 in a direction perpendicular to the straight line. The reason for offsetting the nozzle 12 is to increase the cooling effect by causing the cold air jetted from the nozzle 12 to act as a swirling flow in the rotation direction of the main shaft 7.

ノズル１２の吐出口１２ａは、内輪間座５の外周面に対して、すきま１５を介して対向している。図３の部分拡大図である図４に示すように、前記すきま１５のすきま寸法δａは、ノズル１２の口径Ｄの１／２以下としている。このようにすきま寸法δａを定めることで、ノズル１２の吐出口１２ａの圧力が高くなり、冷風の急激な膨張が抑えられる。これにより、冷風の噴射音を低減することができる。すきま寸法δの上限は、運転中に生じる内輪間座５の温度上昇と遠心力による膨張で内輪間座５が外輪間座４に接触しないように設定する。   The discharge port 12 a of the nozzle 12 faces the outer peripheral surface of the inner ring spacer 5 via a gap 15. As shown in FIG. 4, which is a partially enlarged view of FIG. 3, the clearance dimension δa of the clearance 15 is set to ½ or less of the diameter D of the nozzle 12. By determining the clearance dimension δa in this way, the pressure at the discharge port 12a of the nozzle 12 is increased, and rapid expansion of cold air is suppressed. Thereby, the injection sound of cold wind can be reduced. The upper limit of the clearance dimension δ is set so that the inner ring spacer 5 does not come into contact with the outer ring spacer 4 due to the temperature rise of the inner ring spacer 5 that occurs during operation and expansion due to centrifugal force.

また、吐出口１２ａから内輪間座５の外周面における冷風が当る箇所Ｐまでの距離Ｌは、０．７ｍｍ以上としている。前記距離Ｌを上記のように定めることで、内輪間座５に対する冷却効果を維持しつつ騒音の低減効果を併せて持つことを試験で見出した。軸受サイズ（間座の径）にかかわらず、前記距離Ｌを０．７ｍｍ以上に確保することで、このような冷却効果を維持しつつ騒音の低減効果を併せて持つ効果が得られる。   Moreover, the distance L from the discharge port 12a to the location P where the cool air hits on the outer peripheral surface of the inner ring spacer 5 is 0.7 mm or more. By determining the distance L as described above, it has been found through tests that the cooling effect on the inner ring spacer 5 is maintained and the noise reduction effect is also achieved. Regardless of the bearing size (spacer diameter), by securing the distance L to 0.7 mm or more, it is possible to obtain the effect of reducing the noise while maintaining such a cooling effect.

図５に示すように、前記外輪間座４は、それぞれ環状の外径側部品４Ａおよび内径側部品４Ｂからなる。外径側部品４Ａは、内周面に形成されて前記環状空間１０となる円周溝１６と、この円周溝１６の溝底面と外周面とを互いに連通する前記冷風供給口１１とを有する。内径側部品４Ｂは、前記複数のノズル１２を有する。これら外径側部品４Ａおよび内径側部品４Ｂを互いにすきま無く接合することで、外輪間座４が組み立てられる。外径側部品４Ａおよび内径側部品４Ｂの接合は、例えば圧入、接着剤を用いた接着、図６のようにピン１７を用いた固定等により行われる。   As shown in FIG. 5, the outer ring spacer 4 includes an annular outer diameter side component 4A and an inner diameter side component 4B, respectively. 4A of outer diameter side parts have the circumferential groove | channel 16 which is formed in an internal peripheral surface and becomes the said annular space 10, and the said cold wind supply port 11 which connects the groove bottom face and outer peripheral surface of this circumferential groove 16 mutually. . The inner diameter side component 4 </ b> B includes the plurality of nozzles 12. The outer ring spacer 4 is assembled by joining the outer diameter side part 4A and the inner diameter side part 4B without gaps. The outer diameter side component 4A and the inner diameter side component 4B are joined by, for example, press fitting, bonding using an adhesive, fixing using a pin 17 as shown in FIG.

図１において、主軸装置の外部に冷風供給装置２５が設けられており、この冷風供給装置２５から送り出される冷風Ａが、端面蓋２０の供給口２６およびハウジング６内の供給孔２７を通って、外輪間座４の前記冷風供給口１１に供給される。図の左側の転がり軸受１は、端面蓋２０に設けられた排気孔２８を介して装置外部と連通している。また、図の右側の転がり軸受１は、ハウジング６に設けられた接続孔２９および排気孔３０を介して装置外部と連通している。   In FIG. 1, a cold air supply device 25 is provided outside the spindle device, and the cold air A fed from the cold air supply device 25 passes through the supply port 26 of the end cover 20 and the supply hole 27 in the housing 6, It is supplied to the cold air supply port 11 of the outer ring spacer 4. The rolling bearing 1 on the left side of the figure communicates with the outside of the apparatus through an exhaust hole 28 provided in the end surface lid 20. Further, the rolling bearing 1 on the right side of the figure communicates with the outside of the apparatus through a connection hole 29 and an exhaust hole 30 provided in the housing 6.

この構成の軸受装置Ｊは、冷風供給装置２５より供給される冷風が、外輪間座４の冷風供給孔１１、環状空間１０を通って各ノズル１２から吐出される。吐出された冷風は、内輪間座５の外周面に吹き付けられて、内輪間座５を冷却する。ノズル１２は吐出口１２ａ側を主軸７の回転方向の前方へ傾斜させてあるため、冷風が内輪３の外周面に沿う旋回流となって主軸７の回転方向に安定して流れる。それにより、内輪３の表面の熱を奪って、効果的に冷却することが期待できる。   In the bearing device J having this configuration, the cold air supplied from the cold air supply device 25 is discharged from each nozzle 12 through the cold air supply hole 11 and the annular space 10 of the outer ring spacer 4. The discharged cool air is blown to the outer peripheral surface of the inner ring spacer 5 to cool the inner ring spacer 5. Since the nozzle 12 has the discharge port 12a side inclined forward in the rotation direction of the main shaft 7, the cool air flows as a swirl flow along the outer peripheral surface of the inner ring 3 and flows stably in the rotation direction of the main shaft 7. Thereby, it can be expected that the surface of the inner ring 3 is deprived of heat and effectively cooled.

そして、冷却された内輪間座５により、この内輪間座５に接する転がり軸受１の内輪３が冷却される。また、冷風は、内輪間座５の外周面に吹き付けられた後、内輪間座５と外輪間座４のすきま１５を通って転がり軸受１内に送られ、転がり軸受１を直接冷却する。これら冷却された内輪間座５および内輪３により、主軸７も冷却される。このように、冷風で転がり軸受１を直接冷却するだけでなく、冷風により冷却された内輪間座５で転がり軸受１の内輪３を冷却することで、転がり軸受１および主軸７の温度上昇をより一層効果的に抑えることができる。転がり軸受１を通過した冷風は、排気孔２８、接続孔２９、および排気孔３０を介して装置外部へ排出される。   The cooled inner ring spacer 5 cools the inner ring 3 of the rolling bearing 1 in contact with the inner ring spacer 5. The cold air is blown to the outer peripheral surface of the inner ring spacer 5 and then sent through the clearance 15 between the inner ring spacer 5 and the outer ring spacer 4 into the rolling bearing 1 to directly cool the rolling bearing 1. The main shaft 7 is also cooled by the cooled inner ring spacer 5 and inner ring 3. Thus, not only the rolling bearing 1 is directly cooled by the cold air, but also the inner ring 3 of the rolling bearing 1 is cooled by the inner ring spacer 5 cooled by the cold air, thereby further increasing the temperature rise of the rolling bearing 1 and the main shaft 7. It can be suppressed more effectively. The cold air that has passed through the rolling bearing 1 is discharged to the outside of the apparatus through the exhaust hole 28, the connection hole 29, and the exhaust hole 30.

ノズル１２は軸方向および周方向にそれぞれ複数配列で設けられているため、内輪間座５が軸方向および周方向にほぼ均等に効率良く冷却される。また、冷風が転がり軸受１内に周方向均等に送られるため、冷風による直接的な転がり軸受１の冷却も周方向均等に行われる。これらのことから、転がり軸受１および主軸７が周方向均等に冷却され、温度むらによる弊害を排除することができる。   Since the nozzles 12 are provided in a plurality of arrays in the axial direction and in the circumferential direction, the inner ring spacer 5 is cooled substantially uniformly and efficiently in the axial direction and the circumferential direction. Further, since the cool air is sent uniformly in the circumferential direction into the rolling bearing 1, the direct cooling of the rolling bearing 1 by the cool air is also performed uniformly in the circumferential direction. For these reasons, the rolling bearing 1 and the main shaft 7 are cooled uniformly in the circumferential direction, and adverse effects due to temperature unevenness can be eliminated.

外輪間座４の内周面と内輪間座５の外周面とのすきま１５のすきま寸法δをノズル１２の口径の１／２以下としたことにより、ノズル１２の吐出口１２ａの圧力が高くなり、冷風の急激な膨張が抑えられる。これにより、冷風の噴射音を低減することができる。また、各ノズル１２の吐出口１２ａの断面積の合計Ｓ’totalを冷風供給口１１の断面積Ｓよりも大きくしたため、ノズル１２の吐出口１２ａから吐出される冷風の圧力が下がり、冷風が内輪間座５の外周面に衝突するときに生じる衝突音を小さくすることができる。さらに、ノズル１２の吐出口１２ａから内輪間座５の外周面における冷風が当る箇所Ｐまでの距離Ｌを０．７ｍｍ以上としたため、冷却効果を維持しつつ騒音の低減効果を併せて持つことができる。   By setting the clearance dimension δ of the clearance 15 between the inner peripheral surface of the outer ring spacer 4 and the outer peripheral surface of the inner ring spacer 5 to be 1/2 or less of the diameter of the nozzle 12, the pressure at the discharge port 12a of the nozzle 12 increases. The rapid expansion of cold air is suppressed. Thereby, the injection sound of cold wind can be reduced. Further, since the total cross-sectional area S'total of the discharge ports 12a of the nozzles 12 is made larger than the cross-sectional area S of the cold air supply port 11, the pressure of the cold air discharged from the discharge ports 12a of the nozzles 12 decreases, It is possible to reduce a collision sound that occurs when the outer surface of the spacer 5 collides. Furthermore, since the distance L from the discharge port 12a of the nozzle 12 to the location P where the cool air hits on the outer peripheral surface of the inner ring spacer 5 is 0.7 mm or more, it has a noise reduction effect while maintaining the cooling effect. it can.

外輪間座４は、１つの冷風供給口１１から冷風を導入し、環状空間１０を介して各ノズル１２に冷風を送る構成とした。これにより、各ノズル１２に冷風を均等に分配することができ、かつハウジング６内における冷風供給装置４５から外輪間座５までの冷風の供給経路を簡略にすることができる。また、外輪間座４は外径側部品４Ａと内径側部品４Ｂを互いに接合した構成としたことにより、外輪間座４に前記環状空間１０、冷風供給口１１、および複数のノズル１２を容易に形成することができる。   The outer ring spacer 4 is configured to introduce cold air from one cold air supply port 11 and send the cold air to each nozzle 12 via the annular space 10. Accordingly, the cool air can be evenly distributed to the nozzles 12 and the supply path of the cool air from the cool air supply device 45 to the outer ring spacer 5 in the housing 6 can be simplified. Further, the outer ring spacer 4 has a configuration in which the outer diameter side component 4A and the inner diameter side component 4B are joined to each other, so that the annular space 10, the cold air supply port 11, and the plurality of nozzles 12 are easily provided in the outer ring spacer 4. Can be formed.

図７〜図９は、この発明の異なる実施形態に係る軸受装置の冷却構造を示す。図７に示すように、この軸装置Ｊの外輪間座４は、冷風供給口１１、環状空間１０、および複数のノズル１２の組合せからなる冷風流路１３Ｆ，１３Ｒ，１３Ｆが、軸方向に配列させて３組設けられている。図８に示すように、両側の２組の冷風流路１３Ｆの各ノズル１２は、主軸７が正転方向（矢印の方向）に回転するときにその回転方向の前方へ傾斜させて設けられている。また、図９に示すように、中央の冷風流路１３Ｒの各ノズル１２は、主軸７が逆転方向（矢印の方向）に回転するときにその回転方向の前方へ傾斜させて設けられている。図７に示すように、冷風供給装置４５から外輪間座４までの冷風の経路中に、各冷風流路１３Ｆ，１３Ｒ，１３Ｆへの冷風の供給を個別にＯＮ・ＯＦＦ切換え可能な冷風切換手段３２が設けられている。   7 to 9 show a cooling structure for a bearing device according to another embodiment of the present invention. As shown in FIG. 7, the outer ring spacer 4 of the shaft device J has cold air flow paths 13F, 13R, and 13F formed by combinations of a cold air supply port 11, an annular space 10, and a plurality of nozzles 12 arranged in the axial direction. Three sets are provided. As shown in FIG. 8, each nozzle 12 of the two sets of cold air flow paths 13F on both sides is provided to be inclined forward in the rotation direction when the main shaft 7 rotates in the normal rotation direction (the direction of the arrow). Yes. Further, as shown in FIG. 9, each nozzle 12 of the central cool air flow path 13 </ b> R is provided to be inclined forward in the rotation direction when the main shaft 7 rotates in the reverse rotation direction (the direction of the arrow). As shown in FIG. 7, in the path of cold air from the cold air supply device 45 to the outer ring spacer 4, cold air switching means that can individually switch ON / OFF the supply of cold air to each of the cold air flow paths 13F, 13R, 13F. 32 is provided.

この軸受装置の冷却構造によると、主軸７の回転方向に応じて冷風切換手段３２により各冷風流路１３Ｆ，１３Ｒ，１３Ｆへの冷風の供給を適宜ＯＮ・ＯＦＦ切り換えることで、主軸７が正転方向に回転するときは、ノズル１２から吹き出される冷風が正転方向の旋回流となる冷風流路１３ＦだけをＯＮにし、主軸７が逆転方向に回転するときは、ノズル１２から吹き出される冷風が逆転方向の旋回流となる冷風流路１３ＲだけをＯＮにする。これにより、主軸７が正逆いずれの方向に回転する場合でも、冷風により内輪間座５の表面の熱を奪って、内輪間座５および内輪３を効果的に冷却することができる。   According to the cooling structure of the bearing device, the main shaft 7 rotates in the forward direction by appropriately switching ON / OFF the supply of the cold air to the cold air flow paths 13F, 13R, 13F by the cold air switching means 32 according to the rotation direction of the main shaft 7. When rotating in the direction, only the cool air flow path 13F in which the cool air blown from the nozzle 12 becomes a swirl flow in the forward rotation direction is turned ON, and when the main shaft 7 rotates in the reverse rotation direction, the cool air blown from the nozzle 12 Only the cool air flow path 13 </ b> R that becomes a swirling flow in the reverse direction is turned ON. Thereby, even when the main shaft 7 rotates in either the forward or reverse direction, the inner ring spacer 5 and the inner ring 3 can be effectively cooled by removing the heat of the surface of the inner ring spacer 5 by the cold air.

図１０および図１１は、この発明のさらに異なる実施形態に係る軸受装置の冷却構造を示す。この軸受装置の冷却構造も、前記各軸受装置の冷却構造と同様に、外輪間座４にノズル１２が軸方向および周方向にそれぞれ複数配列で設けられている。図１１に示すように、ノズル１２がそれぞれ周方向に複数並んだノズル列１２Ａ，１２Ｂ，１２Ｃを軸方向に複数組（この例では３組）有し、互いに隣り合う２組のノズル列間で、各ノズル１２の周方向位置を互いにずらせてある。つまり、各ノズル１２が千鳥状に配置されている。   10 and 11 show a cooling structure for a bearing device according to still another embodiment of the present invention. In the cooling structure of the bearing device, a plurality of nozzles 12 are provided in the outer ring spacer 4 in the axial direction and the circumferential direction, respectively, in the same manner as the cooling structure of each bearing device. As shown in FIG. 11, a plurality of nozzle rows 12A, 12B, 12C each having a plurality of nozzles 12 arranged in the circumferential direction are provided in the axial direction (three sets in this example), and between two adjacent nozzle rows. The circumferential positions of the nozzles 12 are shifted from each other. That is, the nozzles 12 are arranged in a staggered manner.

この軸受の冷却構造では、外輪間座４は一つの部品からなり、ノズル列１２Ａ，１２Ｂ，１２Ｃ毎に外輪間座４内の冷風流路１３が設けられている。冷風流路１３は、外輪間座４の外周部に形成された環状溝４０と、この環状溝４０の底部から内径側に向けて、主軸７の回転方向の前方側へ傾斜して設けられた複数の導入孔４１と、これら導入孔４１の先端から同軸上に延び外輪間座４の内周面に吐出口１２ａが開口するノズル１２とで構成される。外輪間座４の内周面と、内輪間座５の外周面とは、微小な径方向のすきま４３を介して対向している。   In this bearing cooling structure, the outer ring spacer 4 is composed of a single component, and the cool air flow path 13 in the outer ring spacer 4 is provided for each of the nozzle rows 12A, 12B, and 12C. The cold air flow path 13 is provided with an annular groove 40 formed in the outer peripheral portion of the outer ring spacer 4 and an inclination toward the front side in the rotation direction of the main shaft 7 from the bottom of the annular groove 40 toward the inner diameter side. A plurality of introduction holes 41 and a nozzle 12 extending coaxially from the leading ends of the introduction holes 41 and having an outlet 12a open on the inner peripheral surface of the outer ring spacer 4 are configured. The inner peripheral surface of the outer ring spacer 4 and the outer peripheral surface of the inner ring spacer 5 are opposed to each other through a minute radial gap 43.

前記各軸受装置の冷却構造が、内輪間座５を均等に冷却することを主眼としているのに対し、図１０、図１１の軸受装置の冷却構造は、ノズル１２の吐出口１２ａ付近で発生する圧縮波の強度を低く抑えることで、冷却効果を高めることを主眼としている。ただし、前記各軸受装置の冷却構造および図１０、図１１の軸受装置の冷却構造は共に、外輪間座４にノズル１２が軸方向および周方向にそれぞれ複数配列で設けられているため、前記各軸受装置の冷却構造も、圧縮波の強度を低く抑えることが可能であり、図１０、図１１の軸受装置の冷却構造も、内輪間座５を均等に冷却することが可能である。   The cooling structure of each bearing device is intended to cool the inner ring spacer 5 evenly, whereas the cooling structure of the bearing device of FIGS. 10 and 11 occurs near the discharge port 12a of the nozzle 12. The main purpose is to enhance the cooling effect by keeping the intensity of the compression wave low. However, since both the cooling structure of each bearing device and the cooling structure of the bearing device of FIGS. 10 and 11 are provided with a plurality of nozzles 12 in the outer ring spacer 4 in the axial direction and in the circumferential direction, The cooling structure of the bearing device can also suppress the strength of the compression wave, and the cooling structure of the bearing device of FIGS. 10 and 11 can cool the inner ring spacer 5 evenly.

圧縮波について説明する。図１２のように、多量の冷風Ａをノズル１２から内輪間座５に向けて吐出すると、冷風Ａはノズル１２の吐出口１２ａで流速が最大速度（例えば音速）となる。外輪間座４と回転間座５の間のすきま４３が狭い場合、すきま４３の圧力が高くなりやすく、すきま４３における吐出口１２ａ付近Ｃで圧縮波が発生する。このとき、冷風Ａの供給量が多いほど、強い圧縮波が発生する。圧縮波が発生すると、ノズル１２から吐出される冷風Ａの直進流れが阻害され、図１３、図１４のように、軸方向に拡散する。それにより、冷風Ａが内輪間座５の外周面と接する時間が短くなり、冷却効果が低下する。図１３は、圧縮波が発生している状態における吐出口１２ａ付近の圧力分布を示し、図１４は、圧縮波が発生している状態における吐出口１２ａ付近に温度分布を示す。   The compression wave will be described. As shown in FIG. 12, when a large amount of cold air A is discharged from the nozzle 12 toward the inner ring spacer 5, the cold air A has a maximum velocity (for example, sound velocity) at the discharge port 12 a of the nozzle 12. When the gap 43 between the outer ring spacer 4 and the rotation spacer 5 is narrow, the pressure of the gap 43 tends to increase, and a compression wave is generated in the gap 43 near the discharge port 12a. At this time, the greater the supply amount of the cold air A, the stronger the compression wave is generated. When the compression wave is generated, the straight flow of the cold air A discharged from the nozzle 12 is inhibited and diffused in the axial direction as shown in FIGS. Thereby, the time for which the cool air A contacts the outer peripheral surface of the inner ring spacer 5 is shortened, and the cooling effect is reduced. FIG. 13 shows the pressure distribution in the vicinity of the discharge port 12a when the compression wave is generated, and FIG. 14 shows the temperature distribution in the vicinity of the discharge port 12a when the compression wave is generated.

ノズル１２を複数設けることで、一つのノズル１２から吐出される冷風Ａの流量が少なくなる。それにより、外輪間座４と内輪間座５の間のすきま４３が狭くても、このすきま４３で局所的に圧力が高くなり難く、ノズル１２の吐出口１２ａ付近Ｃで発生する圧縮波の強度が低く抑えられる。図１５は、（Ａ）ノズル１２が１個である場合、および（Ｂ）ノズル１２を軸方向に複数並べた場合の質量流量および圧縮波強度を比較した図である。また、図１６は、（Ａ）ノズル１２が１個である場合、および（Ｂ）ノズル１２を周方向に複数並べた場合の質量流量および圧縮波強度を比較した図である。いずれについても、ノズル１２を複数設けることで、質量流量および圧縮波強度が小さくなることが分かる。
このように、圧縮波の強度が小さくなることにより、ノズル１２から吐出された冷風Ａがまっすぐに進んで直接に内輪間座５の外周面に吹き付けられる。そのため、冷風Ａが圧縮波に遮られて軸方向に拡散される場合と比べて、冷風Ａが内輪間座５の外周面と接する時間が長くなり、冷却効果が向上する。 By providing a plurality of nozzles 12, the flow rate of the cold air A discharged from one nozzle 12 is reduced. As a result, even if the gap 43 between the outer ring spacer 4 and the inner ring spacer 5 is narrow, the pressure hardly increases locally in the gap 43, and the strength of the compression wave generated near the discharge port 12a of the nozzle 12 is strong. Is kept low. FIG. 15 is a diagram comparing mass flow rate and compression wave intensity when (A) one nozzle 12 is used and (B) a plurality of nozzles 12 are arranged in the axial direction. FIG. 16 is a diagram comparing the mass flow rate and the compression wave intensity when (A) there is one nozzle 12 and (B) a plurality of nozzles 12 are arranged in the circumferential direction. In any case, it is understood that the mass flow rate and the compression wave intensity are reduced by providing a plurality of nozzles 12.
As described above, the intensity of the compression wave is reduced, so that the cold air A discharged from the nozzle 12 advances straight and is directly blown onto the outer peripheral surface of the inner ring spacer 5. Therefore, as compared with the case where the cold air A is blocked by the compression wave and diffused in the axial direction, the time for the cold air A to contact the outer peripheral surface of the inner ring spacer 5 becomes longer, and the cooling effect is improved.

また、図１１のように各ノズル１２が千鳥状に配置されていると、下記の理由により、ノズル１２から吐出される冷風の直進性が良くなる。そのため、ノズルから吐出される冷風の直進性が良くなり、冷却効果がより一層高まる。
直進性が良くなる理由を説明する。ノズル１２から吐出された冷風は、吐出口１２ａ付近では流速が速く（圧力が低い）、かつ周方向への直進性も強い。しかし、吐出口１２ａから離れると、流速が遅くなり、軸方向へ流れて拡散しやすくなる。各ノズル１２が千鳥状に配置されていると、流速が遅くなる付近に隣のノズル列のノズル１２の吐出口１２ａが位置し、その付近が低圧域５０となっている。そのため、図１１に点線で示すように、冷風が低圧域５０に引き込まれて、軸方向に拡散するのが抑制される。図では、低圧域５０による引き込みを誇張して図示してあるが、実際には少しだけ直進性が良くことで、その分だけ冷風が内輪間座５の外周面と接する時間が長くなると考えられる。 In addition, when the nozzles 12 are arranged in a staggered manner as shown in FIG. 11, the straightness of the cold air discharged from the nozzles 12 is improved for the following reason. Therefore, the straightness of the cool air discharged from the nozzle is improved, and the cooling effect is further enhanced.
Explain why the straightness improves. The cold air discharged from the nozzle 12 has a high flow velocity (low pressure) in the vicinity of the discharge port 12a and a strong straightness in the circumferential direction. However, if it leaves | separates from the discharge outlet 12a, a flow rate will become slow, and it will become easy to spread | diffuse by flowing to an axial direction. When the nozzles 12 are arranged in a staggered manner, the discharge ports 12a of the nozzles 12 in the adjacent nozzle row are located in the vicinity where the flow velocity becomes slow, and the vicinity thereof is the low pressure region 50. Therefore, as shown by a dotted line in FIG. 11, the cold air is prevented from being drawn into the low pressure region 50 and diffusing in the axial direction. Although the drawing by the low pressure region 50 is exaggerated in the figure, it is considered that the time for which the cool air is in contact with the outer peripheral surface of the inner ring spacer 5 is increased by the fact that the straightness is actually slightly improved. .

ノズル１２は、図１７に示すような超音速ノズル、例えばラバール・ノズルの形状としても良い。この超音速ノズルは、長さ方向の中間部が狭くなっていて、冷風Ａを超音速で吐出することが可能である。このような超音速ノズルをノズル１２に用いた場合、特に、この軸受装置の冷却構造により圧縮波の強度を小さくする効果が発揮される。   The nozzle 12 may be in the form of a supersonic nozzle as shown in FIG. 17, for example, a Laval nozzle. The supersonic nozzle has a narrow middle portion in the length direction, and can discharge the cold air A at supersonic speed. When such a supersonic nozzle is used for the nozzle 12, the effect of reducing the strength of the compression wave is particularly exerted by the cooling structure of the bearing device.

この発明の軸受装置の冷却構造は、各実施形態で説明したように内輪間座５および内輪３の冷却効果が高いので、主軸装置を高速な領域で運転させることが可能となる。このため、この軸受装置を、工作機械の主軸の支持に好適に用いることができる。   Since the cooling structure of the bearing device according to the present invention has a high cooling effect on the inner ring spacer 5 and the inner ring 3 as described in the respective embodiments, the spindle device can be operated in a high speed region. For this reason, this bearing apparatus can be used suitably for support of the spindle of a machine tool.

１…転がり軸受
２…外輪
３…内輪
４…外輪間座
４Ａ…外径側部品
４Ｂ…内径側部品
５…内輪間座
６…ハウジング
７…主軸（軸）
１０…環状空間
１１…冷風供給口
１２…ノズル
１２Ａ，１２Ｂ，１２Ｃ…ノズル列
１２ａ…吐出口
１３，１３Ｆ，１３Ｒ…冷風流路
１５…すきま
１６…円周溝
３２…冷風切換手段
Ｊ…軸受装置 DESCRIPTION OF SYMBOLS 1 ... Rolling bearing 2 ... Outer ring 3 ... Inner ring 4 ... Outer ring spacer 4A ... Outer diameter side part 4B ... Inner diameter side part 5 ... Inner ring spacer 6 ... Housing 7 ... Main shaft (shaft)
DESCRIPTION OF SYMBOLS 10 ... Annular space 11 ... Cold air supply port 12 ... Nozzle 12A, 12B, 12C ... Nozzle row 12a ... Discharge port 13, 13F, 13R ... Cold air flow path 15 ... Clearance 16 ... Circumferential groove 32 ... Cold air switching means J ... Bearing device

Claims (11)

軸方向に並ぶ複数の転がり軸受の外輪間および内輪間に外輪間座および内輪間座をそれぞれ介在させ、前記外輪および外輪間座がハウジングに設置され、前記内輪および内輪間座が軸に嵌合される軸受装置において、
前記外輪間座に、前記内輪間座の外周面に対して冷風を吹き付けるノズルを複数設けたことを特徴とする軸受装置の冷却構造。 An outer ring spacer and an inner ring spacer are interposed between outer rings and inner rings of a plurality of rolling bearings arranged in the axial direction. The outer ring and outer ring spacers are installed in a housing, and the inner ring and inner ring spacers are fitted to the shaft. Bearing device,
A cooling structure for a bearing device, wherein the outer ring spacer is provided with a plurality of nozzles for blowing cool air to the outer peripheral surface of the inner ring spacer. 請求項１に記載の軸受装置の冷却構造において、前記外輪間座に、前記ノズルを周方向に並べて複数設けた軸受装置の冷却構造。   The bearing structure cooling structure according to claim 1, wherein a plurality of the nozzles are arranged in the outer ring spacer in a circumferential direction. 請求項１に記載の軸受装置の冷却構造において、前記外輪間座に、前記ノズルを軸方向に並べて複数設けた軸受装置の冷却構造。   2. The cooling structure for a bearing device according to claim 1, wherein a plurality of the nozzles are arranged in the outer ring spacer in the axial direction. 請求項１に記載の軸受装置の冷却構造において、前記外輪間座に、前記ノズルを軸方向および周方向にそれぞれ複数配列で設けた軸受装置の冷却構造。   2. The cooling structure for a bearing device according to claim 1, wherein a plurality of the nozzles are provided in the outer ring spacer in the axial direction and the circumferential direction. 請求項４に記載の軸受装置の冷却構造において、前記ノズルがそれぞれ周方向に複数並んだノズル列を軸方向に複数組有し、互いに隣り合う２組の前記ノズル列間で、各ノズルの周方向位置を互いにずらせた軸受装置の冷却構造。   5. The cooling structure for a bearing device according to claim 4, wherein a plurality of nozzle rows each having a plurality of nozzles arranged in the circumferential direction are provided in the axial direction, and the circumference of each nozzle is set between two nozzle rows adjacent to each other. A cooling structure for a bearing device in which the directional positions are shifted from each other. 請求項１ないし請求項５のいずれか１項に記載の軸受装置の冷却構造において、前記外輪間座における、前記ノズルの吐出口がある内周面と、前記ノズルに対向する前記内輪間座の外周面とのすきま寸法が前記ノズルの口径の１／２以下で、かつ前記吐出口から前記内輪間座の外周面における冷風が当る箇所までの距離が０．７ｍｍ以上である軸受装置の冷却構造。   6. The cooling structure for a bearing device according to claim 1, wherein an inner peripheral surface of the outer ring spacer having an outlet of the nozzle and an inner ring spacer facing the nozzle are disposed. A cooling structure for a bearing device, in which a clearance between the outer peripheral surface and the outer diameter of the nozzle is 1/2 or less, and a distance from the discharge port to a location where the cold air hits the outer peripheral surface of the inner ring spacer is 0.7 mm or more . 請求項１ないし請求項６のいずれか１項に記載の軸受装置の冷却構造において、前記外輪間座は、内部にこの外輪間座の円周方向に沿って形成された環状空間と、この環状空間に繋がり装置外部から冷風が供給される冷風供給口と、前記環状空間と内周面間を連通する前記複数のノズルとを有し、前記外輪間座は、前記環状空間となる円周溝および前記冷風供給口を有する外径側部品と、前記複数のノズルを有する内径側部品とを互いに接合したものである軸受装置の冷却構造。   The cooling structure for a bearing device according to any one of claims 1 to 6, wherein the outer ring spacer includes an annular space formed along a circumferential direction of the outer ring spacer, and an annular space. A cold air supply port connected to the space and supplied with cold air from the outside of the device; and the plurality of nozzles communicating between the annular space and the inner peripheral surface, and the outer ring spacer is a circumferential groove serving as the annular space And a cooling structure for a bearing device in which an outer diameter side component having the cold air supply port and an inner diameter side component having the plurality of nozzles are joined to each other. 請求項１ないし請求項７のいずれか１項に記載の軸受装置の冷却構造において、前記複数のノズルを、回転方向の前方へ傾斜させて設けた軸受装置の冷却構造。   The cooling structure for a bearing device according to any one of claims 1 to 7, wherein the plurality of nozzles are provided to be inclined forward in the rotational direction. 請求項１ないし請求項８のいずれか１項に記載の軸受装置の冷却構造において、前記外輪間座は、前記環状空間、冷風供給口、および複数のノズルの組合せからなる冷風流路を複数組有し、これら複数組の冷風流路のうち少なくとも１つの冷風流路の前記ノズルは、前記軸が正転方向に回転するときにその回転方向の前方へ傾斜させて設けられ、他の冷風流路の前記ノズルは、前記軸が逆転方向に回転するときにその回転方向の前方へ傾斜させて設けられ、かつ前記各冷風流路への冷風の供給を個別にＯＮ・ＯＦＦ切換え可能な冷風切換手段を設けた軸受装置の冷却構造。   9. The cooling structure for a bearing device according to claim 1, wherein the outer ring spacer includes a plurality of sets of cold air flow paths including a combination of the annular space, a cold air supply port, and a plurality of nozzles. The nozzles of at least one of the plurality of sets of cold air flow paths are provided so as to be inclined forward in the rotation direction when the shaft rotates in the normal rotation direction. The nozzle of the passage is provided to be inclined forward in the rotation direction when the shaft rotates in the reverse direction, and the cold air supply to each cold air flow path can be individually switched ON / OFF A cooling structure of a bearing device provided with means. 請求項１ないし請求項９のいずれか１項に記載の軸受装置の冷却構造において、前記各ノズルは、冷風を音速程度の流速で吐出することを可能とする形状である軸受装置の冷却構造。   10. The cooling structure for a bearing device according to claim 1, wherein each of the nozzles has a shape capable of discharging cold air at a flow rate of about sonic speed. 11. 工作機械の主軸の支持に用いられる請求項１ないし請求項１０のいずれか１項に記載の軸受装置の冷却構造。   The cooling structure for a bearing device according to any one of claims 1 to 10, which is used for supporting a main shaft of a machine tool.
JP2014059360A 2013-11-18 2014-03-22 Cooling structure of bearing device Pending JP2015117820A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2014059360A JP2015117820A (en) 2013-11-18 2014-03-22 Cooling structure of bearing device
PCT/JP2014/079406 WO2015072383A1 (en) 2013-11-18 2014-11-06 Cooling structure for bearing device
TW103139787A TW201540977A (en) 2013-11-18 2014-11-17 Cooling structure for bearing assembly

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2013237558 2013-11-18
JP2013237558 2013-11-18
JP2014059360A JP2015117820A (en) 2013-11-18 2014-03-22 Cooling structure of bearing device

Publications (1)

Publication Number Publication Date
JP2015117820A true JP2015117820A (en) 2015-06-25

Family

ID=53057319

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2014059360A Pending JP2015117820A (en) 2013-11-18 2014-03-22 Cooling structure of bearing device

Country Status (3)

Country Link
JP (1) JP2015117820A (en)
TW (1) TW201540977A (en)
WO (1) WO2015072383A1 (en)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018074375A1 (en) * 2016-10-17 2018-04-26 Ntn株式会社 Cooling structure for bearing device
WO2018181032A1 (en) * 2017-03-29 2018-10-04 Ntn株式会社 Cooling structure for bearing device
CN110036215A (en) * 2016-11-10 2019-07-19 Ntn株式会社 The cooling structure of bearing arrangement
WO2020054661A1 (en) * 2018-09-13 2020-03-19 Ntn株式会社 Bearing device cooling structure, and main spindle device of machine tool
JP2020041647A (en) * 2018-09-13 2020-03-19 Ntn株式会社 Structure for cooling bearing device
JP2020128760A (en) * 2019-02-07 2020-08-27 Ntn株式会社 Cooling structure of bearing device and main shaft device of machine tool
KR20220071603A (en) * 2020-11-24 2022-05-31 김대식 Air cooling type spindle structure

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107812962A (en) * 2017-11-21 2018-03-20 黄石百斯特智能科技有限公司 A kind of machine tool chief axis with annular spray formula cooling device
CN108097986B (en) * 2017-12-12 2020-01-14 广州市昊志机电股份有限公司 Lathe spindle air cooling structure
JP6946224B2 (en) * 2018-03-29 2021-10-06 Ntn株式会社 Bearing device cooling structure
WO2019188621A1 (en) * 2018-03-29 2019-10-03 Ntn株式会社 Cooling structure for bearing device
JP7164962B2 (en) * 2018-03-29 2022-11-02 Ntn株式会社 Cooling structure of bearing device
CN117124132B (en) * 2023-10-20 2024-02-09 常州克迈特数控科技有限公司 High-precision numerical control machine tool with main shaft cooling structure

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000055063A (en) * 1998-08-11 2000-02-22 Nippon Seiko Kk Lubricating device for bearing
JP2000161375A (en) * 1998-11-26 2000-06-13 Matsuura Machinery Corp Rotary main spindle cooling structure
JP2000291674A (en) * 1999-04-07 2000-10-20 Isuzu Motors Ltd Bearing cooling device
JP2001153144A (en) * 1999-09-13 2001-06-08 Nsk Ltd Angular ball bearing

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007010017A (en) * 2005-06-30 2007-01-18 Ntn Corp Air oil lubricating device for ball bearing

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000055063A (en) * 1998-08-11 2000-02-22 Nippon Seiko Kk Lubricating device for bearing
JP2000161375A (en) * 1998-11-26 2000-06-13 Matsuura Machinery Corp Rotary main spindle cooling structure
JP2000291674A (en) * 1999-04-07 2000-10-20 Isuzu Motors Ltd Bearing cooling device
JP2001153144A (en) * 1999-09-13 2001-06-08 Nsk Ltd Angular ball bearing

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018074375A1 (en) * 2016-10-17 2018-04-26 Ntn株式会社 Cooling structure for bearing device
CN110036215B (en) * 2016-11-10 2021-03-09 Ntn株式会社 Cooling structure of bearing device
CN110036215A (en) * 2016-11-10 2019-07-19 Ntn株式会社 The cooling structure of bearing arrangement
WO2018181032A1 (en) * 2017-03-29 2018-10-04 Ntn株式会社 Cooling structure for bearing device
WO2020054661A1 (en) * 2018-09-13 2020-03-19 Ntn株式会社 Bearing device cooling structure, and main spindle device of machine tool
JP2020041647A (en) * 2018-09-13 2020-03-19 Ntn株式会社 Structure for cooling bearing device
CN112673186A (en) * 2018-09-13 2021-04-16 Ntn株式会社 Cooling structure for bearing device and spindle device for machine tool
EP3851692A4 (en) * 2018-09-13 2022-05-25 NTN Corporation Bearing device cooling structure, and main spindle device of machine tool
JP7096742B2 (en) 2018-09-13 2022-07-06 Ntn株式会社 Bearing device cooling structure
TWI821394B (en) * 2018-09-13 2023-11-11 日商Ｎｔｎ股份有限公司 Cooling structure for bearing device, and spindle device for machine tool
JP2020128760A (en) * 2019-02-07 2020-08-27 Ntn株式会社 Cooling structure of bearing device and main shaft device of machine tool
JP7185546B2 (en) 2019-02-07 2022-12-07 Ntn株式会社 Cooling structure of bearing unit and spindle unit of machine tool
KR20220071603A (en) * 2020-11-24 2022-05-31 김대식 Air cooling type spindle structure
KR102515080B1 (en) * 2020-11-24 2023-03-27 김대식 Air cooling type spindle structure

Also Published As

Publication number Publication date
TW201540977A (en) 2015-11-01
WO2015072383A1 (en) 2015-05-21

Similar Documents

Publication Publication Date Title
JP2015117820A (en) Cooling structure of bearing device
US10428875B2 (en) Cooling structure for bearing device
KR20150058493A (en) Cooling structure for bearing device
JP6013112B2 (en) Cooling structure of bearing device
US10001170B2 (en) Rolling bearing
WO2016072309A1 (en) Cooling structure for bearing device
JP2014062616A (en) Cooling structure of bearing device
JP2018076923A (en) Cooling structure of bearing device
JP6385089B2 (en) Cooling structure of bearing device
KR102448407B1 (en) Cooling structure of bearing device
JP6609003B2 (en) Cooling structure of bearing device
JP6385090B2 (en) Cooling structure of bearing device
JPH08270660A (en) Conical roller bearing device
JP4891947B2 (en) fan
JP6899306B2 (en) Bearing device cooling structure
WO2018074375A1 (en) Cooling structure for bearing device
TWI821394B (en) Cooling structure for bearing device, and spindle device for machine tool
JP7185546B2 (en) Cooling structure of bearing unit and spindle unit of machine tool
JP6946224B2 (en) Bearing device cooling structure
JP7096742B2 (en) Bearing device cooling structure
WO2018181032A1 (en) Cooling structure for bearing device

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20170227

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20170822

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20180306