WO2019098557A1 - Slide bearing for machine tool - Google Patents

Slide bearing for machine tool Download PDF

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Publication number
WO2019098557A1
WO2019098557A1 PCT/KR2018/012695 KR2018012695W WO2019098557A1 WO 2019098557 A1 WO2019098557 A1 WO 2019098557A1 KR 2018012695 W KR2018012695 W KR 2018012695W WO 2019098557 A1 WO2019098557 A1 WO 2019098557A1
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WO
WIPO (PCT)
Prior art keywords
slide bearing
friction surface
machine tool
groove
slide
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PCT/KR2018/012695
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French (fr)
Korean (ko)
Inventor
조영전
Original Assignee
두산공작기계 주식회사
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Publication of WO2019098557A1 publication Critical patent/WO2019098557A1/en

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    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/107—Grooves for generating pressure
    • 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
    • B23Q1/25—Movable or adjustable work or tool supports
    • B23Q1/26—Movable or adjustable work or tool supports characterised by constructional features relating to the co-operation of relatively movable members; Means for preventing relative movement of such members
    • B23Q1/38—Movable or adjustable work or tool supports characterised by constructional features relating to the co-operation of relatively movable members; Means for preventing relative movement of such members using fluid bearings or fluid cushion supports
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • 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 buildup of machine tools, e.g. spindles, slides, actuators

Definitions

  • the present invention relates to a slide bearing for a machine tool, and more particularly, to a friction surface shape of a slide bearing excellent in fine transfer and abrasion resistance.
  • a column of a machine tool, a spindle head, or the like is slidably moved relative to a mating member.
  • slide bearings with excellent lubrication performance should be installed in the transfer part.
  • various types of oil grooves are formed that contain lubricating oil on the friction surface of the slide bearing.
  • the shape of the oil groove is variously shaped such as a zigzag type, an X-axis type, and a continuous arc type.
  • the lowering of the lubrication performance lowers the accuracy of the fine feed of the machine tool and further promotes the wear of the slide bearing friction surface.
  • the present invention provides a slide bearing for a machine tool, which improves abrasion resistance and fine transfer performance of a friction surface of a machine tool slide bearing and further reduces a conveying load of the conveying member.
  • the present invention provides a slide bearing in which an oil groove is formed on a friction surface of the slide bearing.
  • the slide bearing has a friction surface on which a friction surface of the slide bearing is widened at regular intervals in the longitudinal direction to both edges of the friction surface of the slide bearing, Thereby forming a separation groove.
  • the separating groove has a shape of a circular arc in cross section and has a depth passing through the thickness of the friction surface of the slide bearing and being pierced to the base material of the friction surface of the slide bearing.
  • the separation groove may be inclined at an angle with respect to a direction perpendicular to the longitudinal direction of the slide bearing or a direction perpendicular to the longitudinal direction of the slide bearing.
  • the distance between the oil grooves formed on both sides of the separation groove with the separation groove therebetween is set within a range of 0.8 to 1.2 times the length of the oil groove in the transverse direction with respect to the friction surface.
  • the length of the oil groove in the transverse direction with respect to the friction surface is narrower than the width of the guide path of the counterpart in which friction occurs substantially in the friction surface.
  • the surface pressure of the slide bearings repeating the conveying operation in a high-load state is uniformly distributed over the entire friction surface of the slide bearings. Reduce friction resistance.
  • the friction surface of the slide bearing and the foreign material such as metal powder generated due to wear of the mating member are effectively discharged to minimize the abrasion of the friction surface and the mating member.
  • the load of the conveying motor can be reduced and the conveying error of the conveying member can be reduced.
  • Fig. 1 is a friction surface view of a slide bearing showing oil groove patterns of various shapes as a prior art example
  • FIG. 2 is a state-of-the-art pressure distribution diagram of a slide bearing as an example of the prior art.
  • Fig. 3 is an oil groove-like perspective view showing that the separation grooves are formed at regular intervals on the friction surfaces of the slide bearings according to the embodiment of the present invention.
  • FIG. 4 is a cross-sectional view taken along the line A-A in Fig. 3, showing the separation groove of the present invention.
  • FIG. 5 is an oil groove-shaped perspective view showing another embodiment of the present invention in which the separation groove is formed obliquely on the friction surface of the slide bearing.
  • FIG. 6 is a state pressure distribution diagram of a slide bearing as an embodiment of the present invention.
  • Fig. 7 is a load factor graph of a feed motor compared with the prior art, as an embodiment of the present invention.
  • FIG. 8 is a graph of wear rate compared to the prior art, according to an embodiment of the present invention.
  • the slide bearing 10 is constituted by a base material 50 serving as a base of the slide bearing 10 and a friction surface 40 having a relatively thin thickness and excellent abrasion resistance and lubricity on the base material 50 On the surface of the friction surface (40), a groove (20) capable of containing oil is formed.
  • the oil groove 20 is formed on the friction surface 40 of the slide bearing 10 with a predetermined pattern and a predetermined depth.
  • the friction surface 40 of the slide bearing 10 is provided with a plurality of separating grooves (not shown) extending to both edges of the friction surface 40 of the slide bearing 10 in the width direction of the slide bearing 10 at regular intervals 30).
  • the separation groove 30 extends from a counter member 60 (for example, a spindle head that slides up and down on the column or a table that horizontally slides on a bed of the machine tool) There is an effect of dispersing the surface pressure applied to the friction surface 40 of the rotor 10.
  • the separation groove 30 also discharges the generated metal abrasion powder when friction occurs with the mating member 60 slidably moving on the friction surface 40 of the slide bearing 10 to improve the abrasion resistance. More specific lubrication characteristics will be described in more detail through the following examples.
  • the depth of the separating groove 30 is greater than the thickness of the friction surface 40 of the slide bearing 10 so as to penetrate into the base material 50 of the slide bearing 10 to form a recessed shape. This is because, when the separating groove 30 is formed only on the friction surface 40 of the slide bearing 10, the friction surface 40 is thin and the sufficient depth can not be ensured. That is, to ensure an adequate depth of the separation groove 30.
  • the cross section of the separation groove 30 has an arc shape.
  • the separation groove 30 may be formed in a direction perpendicular to the longitudinal direction of the slide bearing 10, and may be formed at a predetermined angle? With respect to the direction perpendicular to the longitudinal direction of the slide bearing 10, The slide bearing 10 may be formed in the shape of a groove communicating with the edge of the slide bearing 10.
  • This shape serves to help the discharge of the metal wear powder generated when the slide bearing 10 is in friction with the mating member 60 and to improve the lubrication property.
  • the cross-section of the separation groove 30 may be a channel shape instead of an arc shape.
  • a load of 1 ton was applied to a conventional slide bearing having a zigzag pattern of an oil groove 20 pattern and a transporting member transported on the slide bearing 10 of the present invention, ⁇ m, 2 ⁇ m, and 3 ⁇ m.
  • the length a of the oil grooves 20 in the transverse direction (a) (B / a) of the distance b between the oil grooves 20 on both sides of the oil groove 10 between the oil groove 20 and the oil groove 20 of the oil groove 10 is varied.
  • the distance b between the oil grooves 20 is based on the oil grooves 20 on both sides of the separation groove 30 of the slide bearing 10.
  • the distance b between the most preferable oil grooves 20 having excellent abrasion resistance of the slide bearing 10 of the present invention is in the range of 0.8 to 1.2 times the transverse length a of the oil groove 20 appear.
  • the separation grooves 30 are formed at regular intervals on the friction surface 40 of the slide bearing 10, so that the surface pressure of the slide bearings 10 can be controlled by the slide bearings 10
  • the frictional resistance of the slide bearing 10 can be reduced.
  • the frictional resistance between the friction surface 40 of the slide bearing 10 and the mating member 60 is reduced and the metal wear generated by the friction bearing surface 40 and the mating member 60 can be effectively discharged.
  • the abrasion of the substrate can be minimized.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

A slide bearing has separation grooves formed on the friction surface thereof at regular intervals in the longitudinal direction and extending from one edge to the other edge of the friction surface. Each of the separation grooves has an arc-shaped section and is recessed to pass through the friction surface of the slide bearing and down to a base material of the slide bearing. Further, the separation grooves are formed in a direction perpendicular to the longitudinal direction of the slide bearing.

Description

공작 기계용 슬라이드 베어링Slide bearings for machine tools
본 발명은 공작기계용 슬라이드 베어링에 관한 것으로서, 보다 구체적으로는 미세이송과 내마모 성능이 우수한 슬라이드 베어링의 마찰면 형상에 관한 것이다.BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a slide bearing for a machine tool, and more particularly, to a friction surface shape of a slide bearing excellent in fine transfer and abrasion resistance.
공작기계의 컬럼이나 스핀들 헤드 등은 상대 부재에 대해 슬라이드 이송을 하게 된다. 이 때 이송부에는 윤활 성능이 우수한 슬라이드 베어링을 설치한다. 이러한 슬라이드 베어링은 윤활 성능을 높이기 위해 슬라이드 베어링의 마찰면 표면에 윤활유를 내포하는 다양한 형태의 오일 그루브가 형성된다. 이러한 오일 그루브의 형상은 도 1과 같이 지그재그(zigzag) 타입이나 엑스자(X) 타입, 연속된 원호 타입 등 다양한 형상이 있다. A column of a machine tool, a spindle head, or the like is slidably moved relative to a mating member. At this time, slide bearings with excellent lubrication performance should be installed in the transfer part. In order to improve the lubrication performance of these slide bearings, various types of oil grooves are formed that contain lubricating oil on the friction surface of the slide bearing. As shown in Fig. 1, the shape of the oil groove is variously shaped such as a zigzag type, an X-axis type, and a continuous arc type.
그러나 이러한 형상의 오일 그루브의 존재에도 불구하고, 공작기계가 고하중의 무게를 지탱하면서 장시간에 걸쳐 이송 동작을 반복하게 되면 도 2와 같이 슬라이드 베어링의 마찰면에 면압이 증가하여 윤활 성능이 저하되게 된다. However, in spite of the existence of such an oil groove, when the machine tool is repeatedly moved for a long time while supporting the weight of the heavy load, the surface pressure on the friction surface of the slide bearing increases, do.
윤활 성능의 저하는 공작기계의 미세 이송의 정확도를 떨어뜨리고, 나아가 슬라이드 베어링 마찰면의 마모를 촉진시키게 된다. The lowering of the lubrication performance lowers the accuracy of the fine feed of the machine tool and further promotes the wear of the slide bearing friction surface.
따라서, 슬라이드 베어링 마찰면의 내마모성과 미세 이송 정밀도를 향상시키는 윤활성이 높은 슬라이드 베어링의 개발이 필요하다. Therefore, it is necessary to develop a slide bearing with high lubricity which improves the abrasion resistance and the fine transfer accuracy of the slide bearing friction surface.
본 발명은 공작기계 슬라이드 베어링 마찰면의 내마모성과 미세 이송 성능을 향상시키고, 나아가 이송부재의 이송 부하가 줄어든 공작기계용 슬라이드 베어링을 제공한다.The present invention provides a slide bearing for a machine tool, which improves abrasion resistance and fine transfer performance of a friction surface of a machine tool slide bearing and further reduces a conveying load of the conveying member.
본 발명의 해결 수단은 마찰면에 오일 그루브가 형성된 슬라이드 베어링에 있어서, 상기 슬라이드 베어링의 마찰면에 길이 방향으로 일정한 간격 마다 상기 슬라이드 베어링의 폭 방향으로 상기 슬라이드 베어링의 마찰면의 양쪽 가장자리까지 파여진 분리 홈을 형성한다. 상기 분리 홈은 그 단면은 원호의 형상이고, 깊이는 상기 슬라이드 베어링의 마찰면의 두께를 통과하여 상기 슬라이드 베어링의 마찰면의 모재까지 파여진 형상이다.The present invention provides a slide bearing in which an oil groove is formed on a friction surface of the slide bearing. The slide bearing has a friction surface on which a friction surface of the slide bearing is widened at regular intervals in the longitudinal direction to both edges of the friction surface of the slide bearing, Thereby forming a separation groove. The separating groove has a shape of a circular arc in cross section and has a depth passing through the thickness of the friction surface of the slide bearing and being pierced to the base material of the friction surface of the slide bearing.
또한, 상기 분리 홈은 상기 슬라이드 베어링의 길이 방향에 대해 직각 방향 또는 상기 슬라이드 베어링의 길이 방향의 직각 방향에 대해 일정 각도로 경사지게 형성할 수 있다.The separation groove may be inclined at an angle with respect to a direction perpendicular to the longitudinal direction of the slide bearing or a direction perpendicular to the longitudinal direction of the slide bearing.
또한, 상기 분리 홈을 사이에 두고 상기 분리 홈의 양측에 형성된 오일 그루브 간의 거리는 상기 오일 그루브의 상기 마찰면에 대한 가로방향의 길이의 0.8 내지 1.2 배 범위 내로 한다.The distance between the oil grooves formed on both sides of the separation groove with the separation groove therebetween is set within a range of 0.8 to 1.2 times the length of the oil groove in the transverse direction with respect to the friction surface.
또한, 상기 오일 그루브의 상기 마찰면에 대한 가로방향의 길이는 상기 마찰면 중에서 실질적으로 마찰이 일어나는 상대부재의 가이드웨이 폭 보다 좁다.In addition, the length of the oil groove in the transverse direction with respect to the friction surface is narrower than the width of the guide path of the counterpart in which friction occurs substantially in the friction surface.
상기한 본 발명은, 공작기계 슬라이드 베어링의 마찰면에 일정한 간격으로 분리 홈을 형성함으로써, 고하중 상태에서 이송 동작을 반복하는 슬라이드 베어링의 면압을 슬라이드 베어링의 마찰면 전체에 골고루 분산시키므로 슬라이드 베어링의 마찰 저항을 줄인다. According to the present invention, since the separating grooves are formed at regular intervals on the friction surfaces of the machine tool slide bearings, the surface pressure of the slide bearings repeating the conveying operation in a high-load state is uniformly distributed over the entire friction surface of the slide bearings. Reduce friction resistance.
또한 슬라이드 베어링의 마찰면과 상대부재의 마모로 인해 발생된 금속분말 등의 이물질을 효과적으로 배출하여 마찰면과 상대부재의 마모 촉진을 최소화 한다.In addition, the friction surface of the slide bearing and the foreign material such as metal powder generated due to wear of the mating member are effectively discharged to minimize the abrasion of the friction surface and the mating member.
나아가 슬라이드 베어링 마찰면의 면압과 마찰저항을 줄이므로 이송모터의 부하를 줄일 수 있고, 또한 이송부재의 이송오차도 줄일 수 있다. Further, since the surface pressure and the frictional resistance of the slide bearing friction surface are reduced, the load of the conveying motor can be reduced and the conveying error of the conveying member can be reduced.
이와 같이 윤활 특성이 향상됨으로 인해 슬라이드 베어링과 이 슬라이드 베어링의 상대부재의 내마모 성능을 향상 시킨다.As described above, since the lubrication characteristics are improved, the abrasion resistance of the slide bearing and the relative member of the slide bearing is improved.
도 1은 종래 기술 일 예로서, 다양한 형상의 오일 그루브 패턴을 나타내는 슬라이드 베어링의 마찰면 형상 도면이다.BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a friction surface view of a slide bearing showing oil groove patterns of various shapes as a prior art example; Fig.
도 2는 종래 기술 일 예로서, 슬라이드 베어링의 면압 분포 상태도이다.2 is a state-of-the-art pressure distribution diagram of a slide bearing as an example of the prior art.
도 3은 본 발명의 실시예로서, 분리 홈이 슬라이드 베어링의 마찰면에 일정한 간격으로 형성된 것을 나타내는 오일 그루브 형상 사시도이다.Fig. 3 is an oil groove-like perspective view showing that the separation grooves are formed at regular intervals on the friction surfaces of the slide bearings according to the embodiment of the present invention.
도 4는 도 3의 A-A선 단면도로서 본 발명의 분리 홈의 단면도이다.4 is a cross-sectional view taken along the line A-A in Fig. 3, showing the separation groove of the present invention.
도 5은 본 발명의 다른 실시예로서, 분리 홈이 슬라이드 베어링의 마찰면에 경사지게 형성된 것을 나타내는 오일 그루브 형상 사시도이다.5 is an oil groove-shaped perspective view showing another embodiment of the present invention in which the separation groove is formed obliquely on the friction surface of the slide bearing.
도 6는 본 발명의 실시예로서, 슬라이드 베어링의 면압 분포 상태도이다.6 is a state pressure distribution diagram of a slide bearing as an embodiment of the present invention.
도 7은 본 발명의 실시예로서, 종래 기술과 비교한 이송 모터의 부하율 그래프이다.Fig. 7 is a load factor graph of a feed motor compared with the prior art, as an embodiment of the present invention.
도 8은 본 발명의 일 실시예로서, 종래 기술과 비교한 마모율 그래프이다.FIG. 8 is a graph of wear rate compared to the prior art, according to an embodiment of the present invention.
이하에서, 첨부한 도 3 내지 도 8을 참조하여 본 발명의 바람직한 실시예에 대해 설명한다.Hereinafter, a preferred embodiment of the present invention will be described with reference to FIGS. 3 to 8 attached hereto.
우선 도 3 내지 도 5를 참조하여 본 발명의 실시예에 따른 구성을 살펴본다.3 to 5, a configuration according to an embodiment of the present invention will be described.
본 실시예에 따른 슬라이드 베어링(10)은, 슬라이드 베어링(10)의 바탕이 되는 모재(50)와, 상기 모재(50) 위에 비교적 얇은 두께로 내마성과 윤활성이 뛰어난 마찰면(40)으로 구성되고, 상기 마찰면(40)의 표면에는 오일을 내포할 수 있는 그루브(20)가 형성된다. 이 오일 그루브(20)는 상기 슬라이드 베어링(10)의 마찰면(40)에 일정한 패턴과 일정한 깊이의 홈으로 형성된다. The slide bearing 10 according to the present embodiment is constituted by a base material 50 serving as a base of the slide bearing 10 and a friction surface 40 having a relatively thin thickness and excellent abrasion resistance and lubricity on the base material 50 On the surface of the friction surface (40), a groove (20) capable of containing oil is formed. The oil groove 20 is formed on the friction surface 40 of the slide bearing 10 with a predetermined pattern and a predetermined depth.
또한 상기 슬라이드 베어링(10)의 마찰면(40)에는 일정한 간격 마다 상기 슬라이드 베어링(10)의 폭 방향으로 상기 슬라이드 베어링(10)의 마찰면(40)의 양쪽 가장자리까지 파여진 복수개의 분리 홈(30)을 형성한다. 이 분리 홈(30)은 도 6과 같이 이송부재인 상대부재(60)(예를 들면 컬럼 상에서 상하로 슬라이드 이동하는 스핀들 헤드나, 공작기계의 베드 상에서 수평 방향으로 슬라이드 이동하는 테이블)로부터 슬라이드 베어링(10)의 마찰면(40)에 가해지는 면압을 분산시키는 효과가 있다. The friction surface 40 of the slide bearing 10 is provided with a plurality of separating grooves (not shown) extending to both edges of the friction surface 40 of the slide bearing 10 in the width direction of the slide bearing 10 at regular intervals 30). 6, the separation groove 30 extends from a counter member 60 (for example, a spindle head that slides up and down on the column or a table that horizontally slides on a bed of the machine tool) There is an effect of dispersing the surface pressure applied to the friction surface 40 of the rotor 10.
또한 이 분리 홈(30)은 슬라이드 베어링(10)의 마찰면(40) 상에서 슬라이드 이동하는 상대부재(60)와 마찰이 일어날 때, 발생되는 금속 마모 분말을 배출시켜 내마모 특성을 향상시키기도 한다. 보다 구체적인 윤활 특성에 대해서는 하기 실시예를 통해 보다 자세히 설명한다. The separation groove 30 also discharges the generated metal abrasion powder when friction occurs with the mating member 60 slidably moving on the friction surface 40 of the slide bearing 10 to improve the abrasion resistance. More specific lubrication characteristics will be described in more detail through the following examples.
한편, 상기 분리 홈(30)의 깊이는 도 4와 같이 상기 슬라이드 베어링(10)의 마찰면(40)의 두께보다 깊게 상기 슬라이드 베어링(10)의 모재(50)까지 침범하여 파여진 형상이다. 이는 분리 홈(30)을 슬라이드 베어링(10)의 마찰면(40)에 만 형성되게 할 경우, 마찰면(40)의 두께가 얇아서 충분한 깊이를 확보하지 못하기 때문이다. 즉 분리 홈(30)의 적절한 깊이를 확보하기 위해서 이다. 4, the depth of the separating groove 30 is greater than the thickness of the friction surface 40 of the slide bearing 10 so as to penetrate into the base material 50 of the slide bearing 10 to form a recessed shape. This is because, when the separating groove 30 is formed only on the friction surface 40 of the slide bearing 10, the friction surface 40 is thin and the sufficient depth can not be ensured. That is, to ensure an adequate depth of the separation groove 30.
또한, 도 4와 같이 상기 분리 홈(30)의 단면은 원호 형상이다. 또한, 상기 분리 홈(30)은 상기 슬라이드 베어링(10)의 길이 방향에 대해 직각 방향으로 형성하기도 하고, 도 5와 같이 상기 슬라이드 베어링(10)의 길이 방향의 직각 방향에 대해 일정 각도(θ)로 경사지게 상기 슬라이드 베어링(10)의 가장자리까지 연통된 홈 형태로 구성할 수 있다. In addition, as shown in Fig. 4, the cross section of the separation groove 30 has an arc shape. 5, the separation groove 30 may be formed in a direction perpendicular to the longitudinal direction of the slide bearing 10, and may be formed at a predetermined angle? With respect to the direction perpendicular to the longitudinal direction of the slide bearing 10, The slide bearing 10 may be formed in the shape of a groove communicating with the edge of the slide bearing 10.
이러한 형상은 슬라이드 베어링(10)이 상대부재(60)와 마찰이 일어날 때, 발생되는 금속 마모 분말의 배출을 돕고, 윤활 특성을 향상시키는 작용을 한다.This shape serves to help the discharge of the metal wear powder generated when the slide bearing 10 is in friction with the mating member 60 and to improve the lubrication property.
한편, 상기 분리 홈(30)의 단면은 원호 형상이 아닌 채널 형상으로도 할 수 있다.Meanwhile, the cross-section of the separation groove 30 may be a channel shape instead of an arc shape.
이하 실시예에 따른 본 발명의 보다 구체적인 구성과 그 작용과 그 효과를 살펴본다.Hereinafter, the present invention will be described in more detail.
[실시예 1][Example 1]
아래 표 1과 같이 오일 그루브(20) 패턴이 지그재그 형상(Zigzag type)인 종래의 슬라이드 베어링과 본 발명의 슬라이드 베어링(10) 상에서 이송되는 이송부재에 대하여 각각 1톤의 하중을 가한 상태에서 각각 1㎛, 2㎛, 3㎛의 이송지령을 10회에 거쳐 실험해 보았다.As shown in Table 1 below, a load of 1 ton was applied to a conventional slide bearing having a zigzag pattern of an oil groove 20 pattern and a transporting member transported on the slide bearing 10 of the present invention, ㎛, 2 ㎛, and 3 ㎛.
구분division 이송지령 거리Feed command distance 이송지령 횟수Number of feed commands 기존 슬라이드베어링의총 이송거리Total travel distance of conventional slide bearings 기존 슬라이드베어링의이송거리 오차Feeding distance error of existing slide bearing 본 발명 슬라이드 베어링의총 이송거리The total distance traveled by the inventive slide bearing 본 발명 슬라이드 베어링의이송거리 오차The feeding distance error of the inventive slide bearing
실험1 Experiment 1 1㎛1 탆 10회10 times 8.69㎛8.69 탆 1.31㎛1.31 탆 9.28㎛9.28 탆 0.72㎛0.72 탆
실험2 Experiment 2 2㎛2 탆 10회10 times 19.05㎛19.05 탆 0.95㎛0.95 탆 19.38㎛19.38 탆 0.62㎛0.62 탆
실험3 Experiment 3 3㎛3 탆 10회10 times 29.38㎛29.38 탆 0.62㎛0.62 탆 29.81㎛29.81 탆 0.19㎛0.19 탆
실험4 Experiment 4 5㎛5 탆 10회10 times 49.85㎛49.85 탆 0.15㎛0.15 탆 49.87㎛49.87 탆 0.13㎛0.13 탆
그 결과, 표 1에서 나타난 바와 같이, 본 발명의 슬라이드 베어링(10)의 이송거리 오차는 종래의 슬라이드 베어링 보다 현저하게 줄어드는 것을 볼 수 있다. 특히 이송지령 거리가 짧을수록 이송거리 오차의 개선 정도는 뛰어난 것으로 나타났다.As a result, as shown in Table 1, it can be seen that the feed distance error of the slide bearing 10 of the present invention is remarkably reduced as compared with the conventional slide bearing. Especially, the shorter the feed command distance, the better the improvement of the feed distance error.
[실시예 2][Example 2]
한편, 아래 표 2와 같이 오일 그루브(20) 패턴이 지그재그 형상(Zigzag type)인 종래의 슬라이드 베어링과 본 발명의 슬라이드 베어링(10)에 각각 1톤과 2.5톤의 하중을 가한 상태에서 0에서 4000mm/min의 이송 속도로 상기 슬라이드 베어링(10)의 마찰면(40) 상의 상대 부재를 이송시켰을 경우, 본 발명의 슬라이드 베어링(10)은 이송 모터의 부하율은 표 2와 도 7에서 보는 바와 같이 1톤에서는 6.3%, 2.5톤에서 10.2%의 이송모터 부하 저감 효과가 있는 것으로 나타났다.Meanwhile, as shown in Table 2 below, a conventional slide bearing having a zigzag pattern of the oil groove 20 and the slide bearing 10 of the present invention were subjected to a load of 1 ton and 2.5 ton, respectively, the relative load on the friction surface 40 of the slide bearing 10 is transferred to the slide bearing 10 of the present invention by a feed rate of 1 / min as shown in Table 2 and FIG. 7 Ton by 6.3%, and 2.5 tons by 10.2%, respectively.
구분division 하중weight 이송속도Feeding speed 기존 슬라이드베어링의 이송모터 부하율Feeding motor load factor of conventional slide bearings 본 발명 슬라이드 베어링의 이송모터 부하율The feed motor load ratio of the slide bearing of the present invention 부하저감율Load reduction rate
실험1Experiment 1 1톤1 ton 0~ 4000mm/min0 to 4000 mm / min 34.0%34.0% 27.7%27.7% 6.3%6.3%
실험2 Experiment 2 2.5톤2.5 tons 0~ 4000mm/min0 to 4000 mm / min 38.2%38.2% 28.0㎛28.0 탆 10.2%10.2%
[실시예 3][Example 3]
한편, 아래 표 3과 같이 오일 그루브(20) 패턴이 지그재그 형상(Zigzag type)인 종래의 슬라이드 베어링과 본 발명의 슬라이드 베어링(10)에 대해 각각 면압 10g㎏/㎠, 이송 속도 10m/min로, 실험시간 100시간, 200시간, 300시간, 500시간동안 내마모 실험을 한 결과, 표 3과 도 7에서 보는 바와 같이 내마모 성능이 기존 지그재그 형상(Zigzag type)의 슬라이드 베어링에 비해 개선된 것으로 나타났다.On the other hand, with respect to the conventional slide bearing of which the oil groove 20 pattern is a zigzag type and the slide bearing 10 of the present invention, as shown in the following Table 3, a surface pressure of 10 g / cm 2 and a feed rate of 10 m / As a result of wear resistance test for 100 hours, 200 hours, 300 hours and 500 hours of experiment time, the abrasion resistance performance was improved as compared with the conventional slide bearings of Zigzag type as shown in Table 3 and FIG. 7 .
구분division 실험시간Experimental time 기존 슬라이드베어링의 마모 두께Wear thickness of conventional slide bearings 본 발명 슬라이드 베어링의 마모 두께Wear Thickness of Slide Bearings of the Invention 마모 두께 차이Wear Thickness Difference
실험1Experiment 1 100시간100 hours 1.75㎛1.75 탆 0.98㎛0.98 탆 0.77㎛0.77 탆
실험2 Experiment 2 200시간200 hours 2.80㎛2.80 탆 1.62㎛1.62 탆 1.18㎛1.18 탆
실험3 Experiment 3 300시간300 hours 3.75㎛3.75 탆 2.26㎛2.26 탆 1.49㎛1.49 탆
실험4 Experiment 4 500시간500 hours 6.58㎛6.58 탆 4.25㎛4.25 탆 2.33㎛2.33 탆
[실시예 4][Example 4]
한편, 본 발명에서 가장 바람직한 슬라이드 베어링(10)의 분리 홈(30) 위치와 오일 그루브(20) 위치를 찾기 위해, 아래 표 4와 같이 오일 그루브(20)의 가로방향 길이(a)과 슬라이드 베어링(10)의 분리 홈(30)을 사이에 둔 양 측 오일 그루브(20) 간의 거리(b)의 비율(b/a)을 달리하여 슬라이드 베어링(10)을 가속 마모실험을 해보았다. 본 실험에서 상기 오일 그루브(20) 간의 거리(b)는 슬라이드 베어링(10)의 분리 홈(30)의 양측 오일 그루브(20)를 기준으로 하였으며, 오일 그루브(20)의 가로방향 길이(a)는 슬라이드 베어링(10) 마찰면(40) 중에서 슬라드 마찰이 일어나는 상대부재(60)의 가이드웨이 폭(c)의 0.72배로 하였다.In order to find the position of the separation grooves 30 and the position of the oil grooves 20 of the slide bearing 10 most preferable in the present invention, the length a of the oil grooves 20 in the transverse direction (a) (B / a) of the distance b between the oil grooves 20 on both sides of the oil groove 10 between the oil groove 20 and the oil groove 20 of the oil groove 10 is varied. The distance b between the oil grooves 20 is based on the oil grooves 20 on both sides of the separation groove 30 of the slide bearing 10. The length a of the oil grooves 20 in the transverse direction a, Is set to 0.72 times the guide way width c of the mating member 60 in which slid friction occurs in the friction surface 40 of the slide bearing 10.
구분division 오일 그루브 간의 거리(b)과 오일 그루브 가로방향 길이(a)의 비율(b/a)(B / a) of the distance (b) between the oil grooves and the length (a) in the transverse direction of the oil groove, 베어링 마찰면 평균 마모깊이Bearing friction surface average wear depth
실험1Experiment 1 0.50.5 5.38㎛5.38 탆
실험2 Experiment 2 0.60.6 4.46㎛4.46 탆
실험3 Experiment 3 0.70.7 3.54㎛3.54 탆
실험4 Experiment 4 0.80.8 2.62㎛2.62 탆
실험5Experiment 5 0.90.9 1.70㎛1.70 탆
실험6 Experiment 6 1.01.0 0.78㎛0.78 탆
실험7 Experiment 7 1.11.1 1.65㎛1.65 탆
실험8Experiment 8 1.21.2 2.52㎛2.52 탆
실험9Experiment 9 1.31.3 3.38㎛3.38 탆
실험10 Experiment 10 1.41.4 4.25㎛4.25 탆
실험11Experiment 11 1.51.5 5.12㎛5.12 탆
본 실험의 결과, 본 발명의 슬라이드 베어링(10)의 내마모성이 우수한 가장 바람직한 오일 그루브(20) 간의 거리(b)는 오일 그루브(20) 가로방향 길이(a)에 대해 0.8 내지 1.2 배 범위 내인 것으로 나타났다.As a result of the experiment, the distance b between the most preferable oil grooves 20 having excellent abrasion resistance of the slide bearing 10 of the present invention is in the range of 0.8 to 1.2 times the transverse length a of the oil groove 20 appear.
상술한 바와 같이 본 실시예들에 따르면, 본 발명은 슬라이드 베어링(10)의 마찰면(40)에 일정한 간격으로 분리 홈(30)을 형성함으로써, 슬라이드 베어링(10)의 면압을 슬라이드 베어링(10)의 마찰면(40) 전체에 골고루 분산시켜 슬라이드 베어링(10)의 마찰 저항을 줄일 수 있다. 또한 슬라이드 베어링(10)의 마찰면(40)과 상대부재(60)와의 마찰저항이 줄어들고, 또한 이로 인해 발생된 금속 마모분을 효과적으로 배출할 수 있으므로 인해 마찰면(40)과 상대부재(60)의 마모를 최소화 할 수 있다.As described above, according to the present invention, the separation grooves 30 are formed at regular intervals on the friction surface 40 of the slide bearing 10, so that the surface pressure of the slide bearings 10 can be controlled by the slide bearings 10 The frictional resistance of the slide bearing 10 can be reduced. The frictional resistance between the friction surface 40 of the slide bearing 10 and the mating member 60 is reduced and the metal wear generated by the friction bearing surface 40 and the mating member 60 can be effectively discharged. The abrasion of the substrate can be minimized.
결국 이러한 윤활 특성이 향상됨으로 인해 상대부재(60)의 이송모터 부하를 줄일 수 있고, 나아가 상대부재(60)의 이송 오차를 최소화 할 수 있다.As a result, since the lubrication characteristics are improved, the load on the conveying motor of the counterpart member 60 can be reduced, and further, the conveyance error of the counterpart member 60 can be minimized.

Claims (7)

  1. 마찰면에 오일 그루브가 형성된 슬라이드 베어링에 있어서, 상기 슬라이드 베어링의 마찰면에 길이 방향으로 일정한 간격 마다 상기 슬라이드 베어링의 폭 방향으로 상기 슬라이드 베어링의 마찰면의 양쪽 가장자리까지 파여진 분리 홈을 형성한 것을 특징으로 하는 공작 기계용 슬라이드 베어링.The present invention relates to a slide bearing in which an oil groove is formed on a friction surface, wherein separation grooves are formed in the friction surface of the slide bearing at both ends of the friction surface of the slide bearing in the width direction of the slide bearing at regular intervals in the longitudinal direction Features a slide bearing for machine tools.
  2. 제 1 항에 있어서, 상기 분리 홈의 깊이는 상기 슬라이드 베어링의 마찰면의 두께보다 깊고 상기 슬라이드 베어링의 마찰면의 모재까지 파여진 형상인 것을 특징으로 하는 공작 기계용 슬라이드 베어링.The slide bearing for a machine tool according to claim 1, wherein a depth of the separating groove is larger than a thickness of the friction surface of the slide bearing and a shape of the base material of the friction surface of the slide bearing.
  3. 제 2 항에 있어서, 상기 분리 홈은 그 단면이 원호의 형상인 것을 특징으로 하는 공작 기계용 슬라이드 베어링.The slide bearing for a machine tool according to claim 2, wherein the separating groove has a circular arc shape in section.
  4. 제 1 항에 있어서, 상기 분리 홈은 상기 슬라이드 베어링의 길이 방향에 대해 직각 방향으로 형성된 것을 특징으로 하는 공작 기계용 슬라이드 베어링 구조.The slide bearing structure for a machine tool according to claim 1, wherein the separation groove is formed in a direction perpendicular to the longitudinal direction of the slide bearing.
    기계용 슬라이드 베어링.Slide bearings for machines.
  5. 제 1 항에 있어서, 상기 분리 홈은 상기 슬라이드 베어링의 길이 방향의 직각 방향에 대해 일정 각도로 경사지게 형성된 것을 특징으로 하는 공작 기계용 슬라이드 베어링.The slide bearing for a machine tool according to claim 1, wherein the separation groove is inclined at an angle with respect to a direction perpendicular to the longitudinal direction of the slide bearing.
  6. 제 1 항에 있어서, 상기 분리 홈을 사이에 두고 상기 분리 홈의 양측에 형성된 오일 그루브 간의 거리는 상기 오일 그루브의 상기 마찰면에 대한 가로방향의 길이의 0.8 내지 1.2 배 범위인 것을 특징으로 하는 공작기계용 슬라이드 베어링.The machine tool according to claim 1, wherein the distance between the oil grooves formed on both sides of the separation groove with the separation groove therebetween is in the range of 0.8 to 1.2 times the length of the oil groove in the transverse direction with respect to the friction surface. Slide bearings for.
  7. 제 1 항에 있어서, 상기 오일 그루브의 상기 마찰면에 대한 가로방향의 길이는 상기 마찰면 중에서 실질적으로 마찰이 일어나는 상대부재의 가이드웨이 폭 보다 좁은 것을 특징으로 하는 공작 기계용 슬라이드 베어링.The slide bearing for a machine tool according to claim 1, wherein a length of the oil groove in the transverse direction with respect to the friction surface is narrower than a guideway width of a mating member in which friction occurs substantially in the friction surface.
PCT/KR2018/012695 2017-11-20 2018-10-25 Slide bearing for machine tool WO2019098557A1 (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20070109270A (en) * 2006-05-10 2007-11-15 동성금속(주) A half bearing
KR20120063546A (en) * 2009-10-30 2012-06-15 다이호 고교 가부시키가이샤 Slide bearing
KR20150067532A (en) * 2013-12-10 2015-06-18 두산인프라코어 주식회사 Machine tool
JP2016161016A (en) * 2015-02-27 2016-09-05 大豊工業株式会社 Manufacturing method of slide bearing, and slide bearing
KR101747965B1 (en) * 2009-12-22 2017-06-15 두산인프라코어 주식회사 Sliding bearing and sliding bearing assembly

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20070109270A (en) * 2006-05-10 2007-11-15 동성금속(주) A half bearing
KR20120063546A (en) * 2009-10-30 2012-06-15 다이호 고교 가부시키가이샤 Slide bearing
KR101747965B1 (en) * 2009-12-22 2017-06-15 두산인프라코어 주식회사 Sliding bearing and sliding bearing assembly
KR20150067532A (en) * 2013-12-10 2015-06-18 두산인프라코어 주식회사 Machine tool
JP2016161016A (en) * 2015-02-27 2016-09-05 大豊工業株式会社 Manufacturing method of slide bearing, and slide bearing

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