WO2018120629A1 - 螺栓及其制造方法 - Google Patents

螺栓及其制造方法 Download PDF

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Publication number
WO2018120629A1
WO2018120629A1 PCT/CN2017/086262 CN2017086262W WO2018120629A1 WO 2018120629 A1 WO2018120629 A1 WO 2018120629A1 CN 2017086262 W CN2017086262 W CN 2017086262W WO 2018120629 A1 WO2018120629 A1 WO 2018120629A1
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WO
WIPO (PCT)
Prior art keywords
thread
bolt
diameter
rod
standard
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Application number
PCT/CN2017/086262
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English (en)
French (fr)
Inventor
郑国龙
郭拥军
葛俊豪
石亦平
Original Assignee
北京金风科创风电设备有限公司
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.)
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Application filed by 北京金风科创风电设备有限公司 filed Critical 北京金风科创风电设备有限公司
Priority to KR1020187016849A priority Critical patent/KR102093051B1/ko
Priority to US15/777,049 priority patent/US11261900B2/en
Priority to EP17870631.3A priority patent/EP3388698B1/en
Priority to AU2017370319A priority patent/AU2017370319B2/en
Publication of WO2018120629A1 publication Critical patent/WO2018120629A1/zh

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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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B33/00—Features common to bolt and nut
    • F16B33/02—Shape of thread; Special thread-forms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21H—MAKING PARTICULAR METAL OBJECTS BY ROLLING, e.g. SCREWS, WHEELS, RINGS, BARRELS, BALLS
    • B21H3/00—Making helical bodies or bodies having parts of helical shape
    • B21H3/02—Making helical bodies or bodies having parts of helical shape external screw-threads ; Making dies for thread rolling
    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B35/00—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws
    • F16B35/04—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws with specially-shaped head or shaft in order to fix the bolt on or in an object
    • F16B35/041—Specially-shaped shafts
    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B35/00—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws
    • F16B35/04—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws with specially-shaped head or shaft in order to fix the bolt on or in an object
    • F16B35/041—Specially-shaped shafts
    • F16B35/044—Specially-shaped ends
    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B39/00—Locking of screws, bolts or nuts
    • F16B39/22—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening
    • F16B39/28—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening by special members on, or shape of, the nut or bolt
    • F16B39/30—Locking exclusively by special shape of the screw-thread

Definitions

  • the present invention relates to a bolt and a method of manufacturing the same, and in particular to a bolt and a method of manufacturing a bolt which can optimize the distribution of force on a thread and improve its shear resistance and extend its service life.
  • the fastener In the form of industrial equipment connection, the fastener is one of the basic components with a large amount of surface, and is an indispensable weight part and coupling part of various industries, and is widely used in various mechanical equipments.
  • One of the most important functions of fasteners is to transfer loads, but for various reasons, fastener failure and breakage often occur, causing serious accidents in large equipment, resulting in property and personnel losses.
  • the bolts used as the coupling members are prone to fatigue fracture under the action of varying dynamic loads, resulting in failure of the coupling.
  • FIG. 1A is an engagement diagram of a standard bolt and a standard nut according to the prior art
  • FIG. 1B is a force distribution diagram of each of the buckle threads when the standard bolt is engaged with a standard nut according to the prior art.
  • the threaded engagement form of the bolt rod 10 and the nut 20 of the bolt is as shown in FIG. 1A, and the bolt rod 10 is subjected to tensile deformation during operation, and compression deformation occurs at the thread. Therefore, the load distribution on each of the threads on the bolt rod is uneven, and the first several threads of the bolt rod 10 and the nut 20 are screwed together (for example, the first buckle T 1 and the second buckle T 2 shown in FIG. 1A ).
  • the stress on the root of the third buckle T 3 , the fourth buckle T 4 , etc. is much larger than the stress on the rear thread, as shown in FIG. 1B .
  • the pulling force of the first buckle T 1 of the thread is about 35% of the total pulling force
  • the pulling force of the second buckle T 2 is about 25% of the total pulling force
  • the pulling force of the third buckle T 3 is about 15% of the total tensile force
  • the first three buckles of the thread (T 1 , T 2 and T 3 ) are subjected to a tensile force of 75% of the total tensile force of the bolt, and starting from the sixth buckle T 6 of the thread
  • the tensile force is small and relatively uniform. More statistics show that about 65% of all broken bolts are fatigue fractures at the first and second threads T 1 and T 2 calculated from the nut support surface.
  • the present invention provides a bolt including a nut and a bolt rod, the bolt rod including a positioning rod, a flexible rod, and a threaded portion, the positioning rod being coupled to one end of the nut,
  • the flexible rods are respectively coupled to the positioning rod and the threaded portion.
  • the flexible rod is formed with a shearing table.
  • the threaded portion comprises a standard thread and a transition thread formed between the flexible rod and the standard thread, and the thread height of the transition thread is less than the thread height of the standard thread, wherein The thread height (H 0 ) of the standard thread (1241) remains constant.
  • the transition thread may be formed in a form in which the crest of the thread is partially removed.
  • the thread height of the transition thread may gradually increase toward the direction of the standard thread.
  • the thread of the transition thread may be in the shape of a diagonal line or a curve.
  • the thread line forms a cone angle with respect to an axis of the bolt, wherein the angle of the cone angle may range from 1° to 10°.
  • the angle of the taper angle may range from 3° to 5°.
  • the transition threads can include 4-5 buckle threads.
  • the flexible rod diameter may be smaller than the diameter of the positioning rod, and the diameter of the shearing table may be equal to the diameter of the positioning rod.
  • the diameter of the flexible rod may be 0.85 times the nominal diameter of the bolt.
  • the length of the positioning rod may be 20 mm along the axial direction of the bolt, and the length of the shearing table may be 8 mm to 10 mm.
  • the shearing station (123) is arranged such that when the bolt (1) is connected to two or more connected members (2), the shearing station (123) is located at the connected member (2) Combined with the joint surface.
  • the present invention provides a method of making a bolt according to the present invention, the method comprising: forming a positioning rod, a flexible rod, a shearing station on the flexible rod, and an embryonic diameter corresponding to the threaded portion, A nut is formed, and a standard thread and a transition thread are formed on the embryo diameter by a thread rolling process. wherein, in the thread rolling process, the standard thread and the transition thread are formed at one time with the thread bottom diameter of the thread portion as a reference line.
  • the embryonic diameter may include a cylindrical diameter of an embryonic diameter and a diameter of a revolving body of a variable diameter.
  • the bolt according to the present invention can optimize the force distribution of the thread (especially the force distribution of the first three threads), and can effectively cooperate with the thread of the nut, and the manufacturing process is simple and the cost is low.
  • 1A is a schematic view of a threaded engagement of a standard bolt in combination with a standard nut according to the prior art
  • 1B is a force distribution diagram of each buckle thread when a standard bolt is engaged with a standard nut according to the prior art
  • FIG. 2 is a schematic structural view of a bolt according to an embodiment of the present invention.
  • 3A is a schematic view of a state when fastening is performed using a bolt according to an embodiment of the present invention
  • Figure 3B is an enlarged view of a portion A in Figure 3A;
  • FIG. 4 is a cross-sectional view of a threaded portion in accordance with an embodiment of the present invention.
  • 5A is a schematic view showing engagement of a threaded portion with a standard nut in accordance with an embodiment of the present invention
  • 5B is a diagram showing the force distribution of each thread when the threaded portion is engaged with the standard nut according to an embodiment of the present invention
  • Figure 6A is a schematic view showing a bolt structure in the process of manufacturing a bolt according to the present invention.
  • Figure 6B is an enlarged view of a portion B in Figure 6A;
  • Fig. 6C is a schematic view showing a bolt manufactured according to the manufacturing method of the present invention.
  • FIG. 2 is a schematic structural view of a bolt 1 according to an embodiment of the present invention
  • FIG. 3A is a schematic view showing a state in which fastening is performed using a bolt according to an embodiment of the present invention
  • FIG. 3B is an enlarged view of a portion A in FIG. 3A
  • 4 is a cross-sectional view of a threaded portion according to an embodiment of the present invention
  • FIG. 5A is a schematic view showing engagement of a threaded portion with a standard nut according to an embodiment of the present invention
  • FIG. 5B is a view showing a thread according to an embodiment of the present invention.
  • the structure of the bolt 1 according to an embodiment of the present invention will be described in detail below with reference to Figs.
  • the bolt 1 includes a nut 11 and a bolt shaft 12.
  • the bolt rod 12 includes a positioning rod 121, a flexible rod 122, and a threaded portion 124.
  • the positioning rod 121 is connected to one end of the nut 11
  • the flexible rod 122 is respectively connected to the positioning rod 121 and the threaded portion 124 .
  • the flexible rod 122 is formed with a shearing station 123 that includes a transition thread 1242 and a standard thread 1241 that is disposed adjacent to the flexible rod 122.
  • the diameter d 1 of the positioning rod 121 is substantially equal to the diameter d of the bolt hole (the hole formed by the bolt for connection using the bolt 2), as shown in Fig. 3A.
  • the diameter d 1 of the positioning rod 121 is about 0.95 times the diameter d of the bolt hole, or the gap L 1 between the positioning rod 121 and the bolt hole is less than 0.5 mm (the bolt above M16), more preferably less than 0.25 mm. (M16 and below bolts), so that the positioning rod 121 can better position the entire bolt-nut joint structure.
  • the diameter d 2 of the flexible rod 122 is smaller than the diameter d 1 of the positioning rod 121 because the smaller the diameter of the bolt rod under the same stress, the smaller the stress on the entire bolt coupling structure and the fatigue strength. The better the performance. However, although the smaller the diameter d 2 of the flexible rod 122, the better the fatigue strength performance of the bolt 1, but if the diameter d 2 of the flexible rod 122 is smaller than the minimum diameter of the standard thread (about the bolt nominal diameter d 0 (not shown) When the height is 0.85 times), the rigidity of the flexible rod 122 is too low, which reduces the maximum tensile force that the entire bolt-and-nut joint structure can withstand, thereby reducing the fastening performance of the bolt 1.
  • the connected member 2 fastened by using the bolt 1 is subjected to the ultimate force caused by the force majeure, lateral slip occurs, resulting in the bolt rod 12 being subjected to strong shear at the joint surface of the joined member 2. Stress, if the bolt 1 cannot withstand the shear stress at this time, the bolt coupling structure is damaged, which may cause failure of the connected member 2. In order to avoid this, the diameter of the bolt rod 12 at the joint surface should be as large as possible, so that it improves the shear resistance.
  • the shearing table 123 may be formed on the bolt shaft 12 according to the embodiment of the present invention, and since the joint surface generally corresponds to the middle of the flexible rod 122 Position, therefore, a shear station 123 having a predetermined length is provided at a position of the flexible rod 122 corresponding to the joint surface (typically an intermediate position of the flexible rod 122), as shown in FIGS. 2 and 3.
  • the diameter d 3 of the shearing table 123 is substantially equal to the diameter d of the bolt hole.
  • the diameter d 3 of the shearing table 123 can be set to be about 0.95 times the diameter d of the bolt hole, or the gap L 2 between the shearing table 123 and the bolt hole is less than 0.5 mm (the bolt of M16 or more), More preferably less than 0.25 mm (M16 and below bolts).
  • the length of the shearing table 123 is set in the case where the bolt 1 is guaranteed to have good fatigue resistance (i.e., the performance of the flexible rod 122 is ensured). Between 8-10mm.
  • the bolt 1 according to the present invention can simultaneously improve the fatigue resistance, the shear resistance and the tensile resistance of the bolt 1 by providing the flexible rod 122 and the shearing table 123 formed on the flexible rod 122.
  • a rounded transition such as a radius of R25 may be adopted between the positioning rod 121 and the flexible rod 122, and the shearing table 123 and the flexible rod 122 may be taken.
  • Rounded corners such as R10, R20 or R40 perform a smooth transition.
  • the threaded portion 124 includes a standard thread 1241 and a transition thread 1242 (see FIG. 4 for details), and the transition thread 1242 may be formed in a form in which the crest of the thread is partially removed, as shown in the figure. 3B is shown.
  • the standard thread 1241 and the transition thread 1242 have the same thread bottom diameter ds (as shown in FIG.
  • each thread height H of the transition thread 1242 is smaller than the thread height H 0 of the standard thread 1241, as shown in the figure. 3B is shown.
  • the thread height H 0 of the standard thread 1241 remains constant, i.e., the height of each of the standard threads 1241 is the same.
  • the transition thread 1242 is preferably the first 4 to 5 buckles of the threaded portion 124 (ie, 4 to 5 closer to the nut 11)
  • the thread is tightened, and the angle of inclination of the thread height H toward the standard thread 1241 is gradually increased.
  • the thread S of the transition thread 1242 may have a shape such as a diagonal line or a curve with respect to the axis O of the bolt 1.
  • the thread S may have a shape of a quadratic logarithmic function curve, a parabola, a binomial curve, or the like.
  • the thread S refers to a virtual side S formed by connecting the crests of each of the threads on the section of the transition thread 1242 (i.e., the section shown in Fig. 4).
  • the thread S forms a taper angle 1243 with the axis O of the bolt 1.
  • the taper angle 1243 refers to a line formed by connecting the two end points of the thread S and the axis O.
  • the angle of the taper angle 1243 may increase as the tensile force of the bolt 1 increases, thereby better distributing the force of the bolt, and the taper angle 1243 may be designed to be in the range of 1 to 10 degrees as needed.
  • the angle of the taper angle 1243 is designed to be between 3 and 5 degrees.
  • the optimum angle of the taper angle 1243 is about 3°.
  • the length of the threaded portion 124 is preferably 2-3 times the nominal diameter of the bolt (ie, 2d 0 - 3d 0 ).
  • the transition thread 1242 is The contact area Fw is smaller than the contact area Fw 0 of the standard thread 1241 as shown in FIG. 3B.
  • the threaded portion 124 can reduce the tensile force of the transition thread 1242 when it is engaged with the standard nut 4, and when the threaded portion 124 is subjected to the tensile force, the thread is originally bent by the front The tensile force to be received is partially transferred to the subsequent stitches, so that the force applied to the entire thread portion 124 becomes uniform, as shown in Figs. 5A and 5B, while also minimizing the stress concentration factor. Therefore, the threaded portion 124 according to the present invention can effectively prevent the occurrence of the phenomenon of fatigue fracture caused by the excessive force of the first three buckles (especially the first buckle), thereby effectively improving the service life of the bolt.
  • the threaded portion 124 of the bolt according to the present invention can be effectively engaged not only with the thread of the nut but also with the thread in the blind hole of the base.
  • the combined structure with the connected member 2 is as shown in FIG. 3A, and between the nut 11 and the standard nut 4 and the connected member 2 A gasket 3 is provided to protect the surface of the connected member 2 from the nut damage while dispersing the pressure of the standard nut 4 against the connected member 2.
  • FIG. 6A is a schematic view showing a bolt structure in the process of manufacturing the bolt 1 according to the present invention
  • FIG. 6B is an enlarged view of a portion B in FIG. 6A
  • FIG. 6C is a view showing the bolt 1 manufactured according to the manufacturing method of the present invention.
  • schematic diagram. A bolt according to the present invention will be described in detail below with reference to FIGS. 6A-6C. The manufacturing method of 1.
  • the positioning rod 121 of the bolt rod 12, the flexible rod 122, the shearing table 123 are manufactured by a turning process according to the length and shape of each portion of the bolt rod 12, and a thread portion is manufactured.
  • the embryo diameter 5 of 124 is as shown in Fig. 6A.
  • a nut portion for forming the nut 11 may be manufactured by a turning process.
  • the embryo diameter 5 of the threaded portion 124 includes the embryo diameter 51 of the standard thread 1241 and the embryo diameter 52 of the transition thread 1242.
  • the shape of the embryo diameter 52 can be made according to the shape of the transition thread 1242 to be formed. Therefore, the embryo diameter 52 has a shape of a rotating body having a variable diameter. Among them, the shape of the embryo diameter 52 coincides with the shape of the thread S to be formed.
  • the nut portion is formed into a nut (such as a hex head) 11 by a forging process as shown in Fig. 6A. Since the positioning rod 121 is required to withstand a large bending moment resistance in the forging process, the length of the positioning rod 121 should be at least 20 mm, and preferably 20 mm in the present invention.
  • the heat-treated embryo diameter 5 is subjected to a thread rolling process using the thread rolling process with the thread bottom diameter ds of the thread portion 124 as a reference line, thereby forming the thread portion 124 according to the embodiment of the present invention, as shown in Fig. 6C.
  • the threaded portion 124 of the present invention can be completed at one time using only the take-up reel forming the standard thread 1241, and it is no longer necessary to perform any treatment on the threaded portion 124 after the completion of the rolling process, Therefore, the manufactured bolt 1 can maintain a smooth metal flow line, and therefore the manufacturing process according to the present invention is simple and low in cost.
  • the manufacturing method of the bolt according to the present invention solves the difficulty in the processing of the tapered thread as compared with the manufacturing process of the bolt of the prior art, and can ensure the smooth flow of the metal wire and the state of the surface compressive stress without Increase work processes and reduce production costs.
  • the bolt according to the present invention can make the force distribution between the buckles of the thread more uniform, and effectively prevent the fatigue fracture caused by the excessive force of the first three buckles (especially the first buckle) when the thread is engaged.
  • the occurrence of the bolt increases the reliability of the use of the bolt and reduces the processing difficulty and processing cost of the transition thread.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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Abstract

一种螺栓及其制造方法，该螺栓包括螺帽（11）和螺栓杆（12），螺栓杆（12）包括定位杆（121）、柔性杆（122）和螺纹部（124），定位杆（121）连接在螺帽（11）的一端，柔性杆（122）分别与定位杆（121）和螺纹部（124）相连接。其中，柔性杆（122）上形成有抗剪台（123）。螺纹部（124）包括标准螺纹（1241）和过渡螺纹（1242），过渡螺纹（1242）形成在柔性杆（122）与标准螺纹（1241）之间，且过渡螺纹（1242）的螺纹高度小于标准螺纹（1241）的螺纹高度，标准螺纹(1241)的螺纹高度(H0)保持恒定。该螺栓的螺纹受力分布均匀，并可与螺母的螺纹进行有效地配合，而且制造过程简单，成本较低。

Description

螺栓及其制造方法 技术领域
本发明涉及一种螺栓及其制造方法，具体地，涉及一种可以优化螺纹受力分布并能提高其抗剪能力、延长其使用寿命的螺栓及制造螺栓的方法。
背景技术
随着现代工业技术的快速发展，对于工业设备的要求也越来越高。越来越多的工业设备，被要求在诸如高速、及高压等环境比较苛刻的条件下使用。在这样的工作环境下，例如发动机的涡轮转子、叶片以及机车车辆的悬挂零部件等一些比较关键性的动力设备，经常会遇到疲劳失效问题。
在工业设备联接的形式中，紧固件是量大面广的基础性元件之一，是各产业必不可少的重量零件和联接件，广泛用于各种机械设备。紧固件最重要的作用之一是传递载荷，但由于各种原因，经常发生紧固件失效断裂情况，从而使得大型设备发生严重事故，带来财产和人员损失。尤其是作为联接件的螺栓，在变化的动载荷的作用下，极易发生疲劳断裂，导致联接失效。
图1A是根据现有技术的标准螺栓与标准螺母的啮合图，图1B是根据现有技术的标准螺栓与标准螺母啮合时各扣螺纹的受力分布图。
在使用根据现有技术的螺栓和螺母20连接其他设备时，螺栓的螺栓杆10与螺母20的螺纹啮合形式如图1A所示，工作时螺栓杆10发生拉伸变形，螺纹处发生压缩变形，从而导致螺栓杆上的螺纹各扣上的载荷分布不均匀，螺栓杆10与螺母20进行螺纹结合的前几扣螺纹(例如，图1A中所示的第一扣T1、第二扣T2、第三扣T3、第四扣T4等)的根部所承受的应力比后面螺纹所承受的应力要大很多，如图1B所示。具体地，螺纹的第一扣T1所承受的拉力约为总拉力的35％，第二扣T2所承受的拉力约为总拉力的25％，第三扣T3所承受的拉力约为总拉力的15％，即，螺纹的前三扣(T1、T2和T3)所承受的拉力为螺栓所承受的总拉力的75％，且从螺纹的第六扣T6开始，其所承受的拉力较小且较为均匀。更有统计表明，在所有断裂的螺栓中，约65％左右是在螺母支撑面算起的第一、二扣螺纹T1、T2处疲劳断裂。
在现有技术中，已经提出了多种方法来提高螺栓连接抗疲劳性能，例如，采用高强度材料制造的柔性螺栓方案、采用柔性螺栓和弹性设备组合成螺栓联接装置的方案或采用由螺帽和螺纹体组成的可控力矩螺栓方案等。然而，上述这些方法通常不能满足在所联接设备承受频繁波动载荷下所需的抗疲劳性能、抗拉强度以及疲劳寿命等。
发明内容
提供本发明内容以介绍发明构思的选择，以下在具体实施方式中以简化形式进一步描述该发明构思。本发明内容并不意在确定所要求保护的主题的关键特征或必要特征，也不意在用于帮助确定所要求保护的主题的范围。
在一个总的方面，本发明提供一种螺栓，所述螺栓包括螺帽和螺栓杆，所述螺栓杆包括定位杆、柔性杆和螺纹部，所述定位杆连接在所述螺帽的一端，所述柔性杆分别与所述定位杆和所述螺纹部相连接。其中，所述柔性杆上形成有抗剪台。其中，所述螺纹部包括标准螺纹和过渡螺纹，所述过渡螺纹形成在所述柔性杆与所述标准螺纹之间，且所述过渡螺纹的螺纹高度小于所述标准螺纹的螺纹高度，其中所述标准螺纹(1241)的螺纹高度(H0)保持恒定。
所述过渡螺纹可以以螺纹的牙顶被部分地去除的形式形成。
所述过渡螺纹的螺纹高度可朝向所述标准螺纹的方向逐渐增大。
所述过渡螺纹的螺牙线可呈斜直线或曲线形状。
所述螺牙线相对于所述螺栓的轴线形成锥形角，其中，所述锥形角的角度范围可为1°-10°。
所述锥形角的角度范围可为3°-5°。
所述过渡螺纹可包括4-5扣螺纹。
所述柔性杆直径可小于所述定位杆的直径，所述抗剪台的直径可等于所述定位杆的直径。
所述柔性杆的直径可为螺栓公称直径的0.85倍。
沿着所述螺栓的轴线方向，所述定位杆的长度可为20mm，所述抗剪台的长度可为8mm-10mm。
所述抗剪台(123)设置成，当所述螺栓(1)连接两个或更多个被连接件(2)时，所述抗剪台(123)位于所述被连接件(2)相结合的结合面处。
在另一个总的方面，本发明提供一种制造根据本发明的螺栓的方法，所述方法包括：形成定位杆、柔性杆、柔性杆上的抗剪台以及与螺纹部相对应的胚径，形成螺帽，采用滚丝工艺在所述胚径上形成标准螺纹和过渡螺纹，其中，在滚丝工艺中，标准螺纹和过渡螺纹均以螺纹部的螺牙底径为基准线一次形成。
所述胚径可包括圆柱形状的胚径和变直径的回转体形状的胚径。
根据本发明的螺栓可以优化螺纹的受力分布(尤其是前三扣螺纹受力分布)，并可与螺母的螺纹进行有效地配合，而且制造过程简单，成本较低。
附图说明
通过下面结合附图对实施例进行详细地描述，本发明的这些和/或其他方面将会变得明显并更易于理解，在附图中：
图1A是根据现有技术的标准螺栓与标准螺母结合时螺纹啮合的示意图；
图1B是根据现有技术的标准螺栓与标准螺母啮合时各扣螺纹的受力分布图；
图2是根据本发明的实施例的螺栓的结构示意图；
图3A是使用根据本发明的实施例的螺栓进行紧固时的状态的示意图；
图3B是图3A中的A部分的放大图；
图4是根据本发明的实施例的螺纹部的截面图；
图5A是示出根据本发明的实施例的螺纹部与标准螺母啮合的示意图；
图5B是示出根据本发明的实施例的螺纹部与标准螺母啮合时各扣螺纹的受力分布图；
图6A是示出制造根据本发明的螺栓过程中的螺栓结构的示意图；
图6B是图6A中的B部分的放大图；
图6C是示出根据本发明的制造方法所制造的螺栓的示意图。
在所有的附图和具体实施方式中，相同的标号指示相同的元件。附图可不按照比例绘制，为了清楚、说明及简洁起见，附图中的元件的相对尺寸、比例和描绘可被夸大。
具体实施方式
现在对本发明的实施例进行详细的描述。其中，相同的标号始终表示相 同部件。本发明中的各个示例仅是作为对本发明的说明，而非出于限制本发明的目的而提供。实际上，本领域的技术人员将理解的是，在不脱离本发明的范围或精神的情况下，可在本发明中做出各种修改和变化。例如，作为一个实施例的一部分而被显示或被描述的特征可供另一实施例使用，从而产生又一实施例。因而，只要其落入权利要求及其等价物的范围内，则本发明意图包含这种修改和变化。
图2是根据本发明的实施例的螺栓1的结构示意图，图3A是使用根据本发明的实施例的螺栓进行紧固时的状态的示意图，图3B是图3A中的A部分的放大图，图4是根据本发明的实施例的螺纹部的截面图，图5A是示出根据本发明的实施例的螺纹部与标准螺母啮合的示意图，图5B是示出根据本发明的实施例的螺纹部与标准螺母啮合时各扣螺纹的受力分布图。下面参照图1-图5B详细地描述根据本发明的实施例的螺栓1的结构。
如图2所示，根据本发明的实施例的螺栓1包括螺帽11和螺栓杆12。螺栓杆12包括定位杆121、柔性杆122和螺纹部124。其中，定位杆121连接在螺帽11的一端，柔性杆122分别与定位杆121和螺纹部124相连接。此外，柔性杆122上形成有抗剪台123，螺纹部124包括过渡螺纹1242和标准螺纹1241，过渡螺纹1242与柔性杆122相邻地布置。
下面详细介绍螺栓杆12的各部分的形状和结构。
定位杆121的直径d1与螺栓孔(被连接件2中用于使用螺栓进行连接所形成的孔)的直径d大致相等，如图3A所示。优选地，定位杆121的直径d1约为螺栓孔的直径d的0.95倍，或者，定位杆121与螺栓孔之间的间隙L1小于0.5mm(M16以上螺栓)，更优选地小于0.25mm(M16及以下螺栓)，以使定位杆121对整个螺栓-螺母结合结构起到较好的定位作用。
柔性杆122的直径d2小于定位杆121的直径d1，这是因为在承受同等应力的情况下，螺栓杆的直径越小，整个螺栓联接结构所承受的应力也越小，并且抗疲劳强度性能也越好。然而，虽然柔性杆122的直径d2越小，螺栓1的抗疲劳强度性能也越好，但如果柔性杆122的直径d2小于标准螺纹的最小直径(约为螺栓公称直径d0(未示出)的0.85倍)时，则柔性杆122的刚性过低，会减小整个螺栓-螺母结合结构所能承受的最大拉力值，从而降低螺栓1的紧固性能。因此，为了能够在降低载荷因子以使螺栓1整体受力更均匀的同时又不减小螺栓1的所能承受的最大拉力值，柔性杆122的直径d2可大 约是螺栓公称直径d0的0.85倍(即，d2＝0.85d0)。
此外，由于使用螺栓1进行紧固的被连接件2在受到不可抗力导致的极限受力时，会发生横向的滑移，从而导致螺栓杆12在被连接件2的结合面处受到较强的剪应力，如果螺栓1无法承受此时的剪应力，则会损坏螺栓联接结构，进而会导致被连接件2的失效。为了避免这种情况的发生，螺栓杆12的位于所述结合面处的直径应尽可能地大，从而其提高抗剪能力。因此，为了在保证抗疲劳强度性能的同时提高抗剪能力，可在根据本发明的实施例的螺栓杆12上形成抗剪台123，且由于通常所述结合面对应于柔性杆122的中间位置，因此，在柔性杆122的与所述结合面相对应的位置处(通常为柔性杆122的中间位置)设置具有预定长度的抗剪台123，如图2和图3所示。
由于抗剪台123的直径越大，螺栓的抗剪能力和抗拉能力越好，因此抗剪台123的直径d3与螺栓孔的直径d大致相等。具体地，抗剪台123的直径d3可被设置为约为螺栓孔的直径d的0.95倍，或者，抗剪台123与螺栓孔之间的间隙L2小于0.5mm(M16以上螺栓)，更优选地小于0.25mm(M16及以下螺栓)。由于螺杆抗剪能力＝螺杆抗剪面积*螺杆抗剪强度，因此在保证螺栓1具有较好的抗疲劳性能(即，保证柔性杆122的性能)的情况下，将抗剪台123的长度设置在8-10mm之间。这样，根据本发明的螺栓1通过设置柔性杆122以及形成在柔性杆122上的抗剪台123，能够同时提高螺栓1的抗疲劳性能、抗剪能力和抗拉能力。
此外，为了防止螺栓杆12在受外应力时出现应力集中的现象，定位杆121与柔性杆122之间可采取诸如R25的圆角进行圆滑过渡，抗剪台123与柔性杆122之间可采取诸如R10、R20或R40等的圆角进行圆滑过渡。
为了保证螺纹在啮合时所需的有效啮合长度，并使螺纹中的每一扣受力均匀，减少现有技术中存在的螺纹前几扣(特别是首扣)因受拉力过大而易疲劳断裂的现象的发生，根据本发明的实施例的螺纹部124包括标准螺纹1241和过渡螺纹1242(详见图4)，过渡螺纹1242可以以螺纹的牙顶被部分地去除的形式形成，如图3B所示。具体地，标准螺纹1241和过渡螺纹1242具有相同的螺牙底径ds(如图2中所示)，且过渡螺纹1242中的每一个螺纹高度H小于标准螺纹1241的螺纹高度H0，如图3B所示。标准螺纹1241的螺纹高度H0保持恒定，即，标准螺纹1241中的每一个螺纹的高度相同。
过渡螺纹1242优选为螺纹部124的前4～5扣(即，更靠近螺帽11的4～5 扣螺纹)，且螺纹高度H朝向标准螺纹1241的方向倾斜角度逐渐增大。在这种情况下，过渡螺纹1242的螺牙线S相对于螺栓1的轴线O可具有斜直线或曲线等的形状。例如，螺牙线S可具有二次对数函数曲线、抛物线、二项式曲线等形状。这里，螺牙线S指的是在过渡螺纹1242的截面(即，图4中所示出的截面)上连接其每个螺纹的牙顶形成的一条虚拟的边S。螺牙线S与螺栓1的轴线O形成锥形角1243，当螺牙线S为曲线时，锥形角1243指的是连接螺牙线S的两个端点所形成的直线与轴线O所形成的夹角。锥形角1243的角度可随着螺栓1所受拉力的增加而增大，从而更好地分布螺栓的受力，锥形角1243可根据需要设计为1°-10°的范围。优选地，锥形角1243的角度设计为3°-5°。例如，在螺栓的预紧力为75％的屈服轴力的情况下，锥形角1243的最优角度约为3°。
此外，螺纹部124的长度优选为螺栓公称直径的2-3倍(即，2d0-3d0)。在这种情况下，首先，根据本发明的螺纹部124与具有标准螺纹的螺母4啮合受力时，由于过渡螺纹1242的螺纹高度H比标准螺纹1241的螺纹高度低，因此，过渡螺纹1242的接触面积Fw小于标准螺纹1241的接触面积Fw0，如图3B所示。因此，根据本发明的实施例的螺纹部124在与标准螺母4啮合受力时可减小过渡螺纹1242所承受的拉力，且当螺纹部124在受到拉力时，原本由其前几扣螺纹所承受的拉力会被部分地转移到其后几扣螺纹上，从而使得螺纹部124整体的受力变得均匀，如图5A和图5B所示，同时也将应力集中的因素最小化。因此，根据本发明的螺纹部124可有效地防止螺纹因前三扣(特别是首扣)受力过大而引起的易疲劳断裂的现象的发生，从而有效地提高了螺栓的使用寿命。
此外，根据本发明的螺栓的螺纹部124不仅可与螺母的螺纹进行有效的配合，而且还可与基体盲孔内的螺纹进行有效的配合。
当根据本发明的实施例的螺栓1与标准螺母4作为紧固件使用时，与被连接件2的结合结构如图3A所示，螺帽11和标准螺母4与被连接件2之间可分别设有垫圈3，以保护被连接件2的表面不受螺母损伤，同时分散标准螺母4对被连接件2的压力。
图6A是示出制造根据本发明的螺栓1过程中的螺栓结构的示意图，图6B是图6A中的B部分的放大图，图6C是示出根据本发明的制造方法所制造的螺栓1的示意图。下面将参照图6A-图6C详细地描述根据本发明的螺栓 1的制造方法。
在制造根据本发明的螺栓1时，首先，根据螺栓杆12的各部分的长度和形状采用车削工艺制造出螺栓杆12的定位杆121、柔性杆122、抗剪台123，并制造出螺纹部124的胚径5，如图6A所示。此外，还可以采用车削工艺制造出用于形成螺帽11的螺帽部分。参照图6B，螺纹部124的胚径5包括标准螺纹1241的胚径51和过渡螺纹1242的胚径52。其中，可根据将要形成的过渡螺纹1242的形状来制造胚径52的形状。因此，胚径52呈变直径的回转体形状。其中，胚径52的形状与将要形成的螺牙线S的形状一致。
然后，采用锻造工艺将螺帽部分形成为螺帽(诸如六角头)11，如图6A所示。由于在锻造工艺中定位杆121需承受较大的抗弯矩能力，因此定位杆121的长度应至少为20mm，本发明优选为20mm。
接着，采用滚丝工艺以螺纹部124的螺牙底径ds为基准线对热处理后的胚径5进行滚丝处理，从而形成根据本发明的实施例的螺纹部124，如图6C所示。此外，由于在本发明中，仅使用形成标准螺纹1241的滚丝轮即可一次完成本发明中的螺纹部124，且不再需要对执行完滚丝工艺后的螺纹部124进行任何的处理，因此制造后的螺栓1可保持顺畅的金属流线，因此且根据本发明的制造工序简单、成本较低。
如上所述，与现有技术的螺栓的制造过程相比，根据本发明的螺栓的制造方法解决了锥形螺纹加工困难的难题，而且既能保证金属流线顺畅及表面压应力状态，又不增加作业工序，并能降低生产成本。
如上所述，根据本发明的螺栓能够使螺纹各扣之间受力分配更为均匀，有效防止了螺纹啮合时因前三扣(特别是首扣)受力过大而导致的疲劳断裂的现象的发生，增加了螺栓的使用可靠性，并且降低了过渡螺纹的加工难度和加工成本。
虽然已示出和描述了本发明的一些实施例，但本领域技术人员应该理解，在不脱离由权利要求及其等同物限定其范围的本发明的原理和精神的情况下，可以对这些实施例进行改变。

Claims (13)

  1. 一种螺栓，包括螺帽(11)和螺栓杆(12)，其特征在于，所述螺栓杆(12)包括定位杆(121)、柔性杆(122)和螺纹部(124)，所述定位杆(121)连接在所述螺帽(11)的一端，所述柔性杆(122)分别与所述定位杆(121)和所述螺纹部(124)相连接，
    其中，所述柔性杆(122)上形成有抗剪台(123)；
    其中，所述螺纹部(124)包括标准螺纹(1241)和过渡螺纹(1242)，所述过渡螺纹(1242)形成在所述柔性杆(122)与所述标准螺纹(1241)之间，且所述过渡螺纹(1242)的螺纹高度(H)小于所述标准螺纹(1241)的螺纹高度(H0)，其中所述标准螺纹(1241)的螺纹高度(H0)保持恒定。
  2. 根据权利要求1所述的螺栓，其特征在于，所述过渡螺纹(1242)以螺纹的牙顶被部分地去除的形式形成。
  3. 根据权利要求2所述的螺栓，其特征在于，所述过渡螺纹(1242)的螺纹高度(H)朝向所述标准螺纹(1241)的方向逐渐增大。
  4. 根据权利要求3所述的螺栓，其特征在于，所述过渡螺纹(1242)的螺牙线(S)呈斜直线或曲线形状。
  5. 根据权利要求4所述的螺栓，其特征在于，
    所述螺牙线(S)相对于所述螺栓(1)的轴线(O)形成锥形角(1243)，
    其中，所述锥形角(1243)的角度范围为1°-10°。
  6. 根据权利要求5所述的螺栓，其特征在于，所述锥形角(1243)的角度范围为3°-5°。
  7. 根据权利要求1-6中任一项所述的螺栓，其特征在于，所述过渡螺纹(1242)包括靠近所述螺帽(11)的4-5扣螺纹。
  8. 根据权利要求1-6中任一项所述的螺栓，其特征在于，
    所述柔性杆(122)直径(d2)小于所述定位杆(121)的直径(d1)；
    所述抗剪台(123)的直径(d3)等于所述定位杆(121)的直径(d1)。
  9. 根据权利要求8所述的螺栓，其特征在于，
    所述柔性杆(122)的直径(d2)为螺栓公称直径(d0)的0.85倍。
  10. 根据权利要求9所述的螺栓，其特征在于，沿着所述螺栓的轴线方向，所述定位杆(121)的长度为20mm，所述抗剪台(123)的长度为8mm-10mm。
  11. 根据权利要求1-6和9-10中任一项所述的螺栓，其特征在于，所述抗剪台(123)设置成，当所述螺栓(1)连接两个或更多个被连接件(2)时，所述抗剪台(123)位于所述被连接件(2)相结合的结合面处。
  12. 一种制造如权利要求1所述的螺栓的方法，所述方法包括：
    形成定位杆(121)、柔性杆(122)、柔性杆(122)上的抗剪台(123)以及与螺纹部(124)相对应的胚径(5)；
    形成螺帽(11)；
    采用滚丝工艺在所述胚径(5)上形成标准螺纹(1241)和过渡螺纹(1242)，其中，在滚丝工艺中，标准螺纹(1241)和过渡螺纹(1242)均以螺纹部(124)的螺牙底径(ds)为基准线一次形成。
  13. 根据权利要求12所述的方法，其特征在于，所述胚径(5)包括圆柱形状的胚径(51)和变直径的回转体形状的胚径(52)。
PCT/CN2017/086262 2016-12-26 2017-05-27 螺栓及其制造方法 WO2018120629A1 (zh)

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US11261900B2 (en) 2022-03-01
EP3388698A4 (en) 2019-10-23
KR102093051B1 (ko) 2020-04-23
EP3388698C0 (en) 2024-05-01
KR20180090821A (ko) 2018-08-13
EP3388698B1 (en) 2024-05-01
US20190353194A1 (en) 2019-11-21
AU2017370319A1 (en) 2018-07-19
CN106763072B (zh) 2019-06-11
CN106763072A (zh) 2017-05-31
EP3388698A1 (en) 2018-10-17
AU2017370319B2 (en) 2019-08-22

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