WO2022226781A1 - 曲轴与曲轴齿轮的连接结构、装配方法、发动机及车辆 - Google Patents

曲轴与曲轴齿轮的连接结构、装配方法、发动机及车辆 Download PDF

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Publication number
WO2022226781A1
WO2022226781A1 PCT/CN2021/090262 CN2021090262W WO2022226781A1 WO 2022226781 A1 WO2022226781 A1 WO 2022226781A1 CN 2021090262 W CN2021090262 W CN 2021090262W WO 2022226781 A1 WO2022226781 A1 WO 2022226781A1
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WIPO (PCT)
Prior art keywords
crankshaft
keyway
key
information
gear
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PCT/CN2021/090262
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English (en)
French (fr)
Inventor
蒋金良
洪敏�
王瑞平
肖逸阁
Original Assignee
浙江吉利控股集团有限公司
义乌吉利动力总成有限公司
宁波吉利罗佑发动机零部件有限公司
浙江吉利动力总成有限公司
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Application filed by 浙江吉利控股集团有限公司, 义乌吉利动力总成有限公司, 宁波吉利罗佑发动机零部件有限公司, 浙江吉利动力总成有限公司 filed Critical 浙江吉利控股集团有限公司
Priority to PCT/CN2021/090262 priority Critical patent/WO2022226781A1/zh
Publication of WO2022226781A1 publication Critical patent/WO2022226781A1/zh

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B11/00—Work holders not covered by any preceding group in the subclass, e.g. magnetic work holders, vacuum work holders
    • B25B11/02—Assembly jigs
    • 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
    • F16B3/00—Key-type connections; Keys
    • 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
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • 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
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/10—Crankshafts assembled of several parts, e.g. by welding by crimping
    • F16C3/12—Crankshafts assembled of several parts, e.g. by welding by crimping releasably connected
    • 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels

Definitions

  • the invention relates to the technical field of vehicle spare parts, in particular to a connection structure, an assembling method, an engine and a vehicle of a crankshaft and a crankshaft gear.
  • crankshaft of the engine usually has the function of driving the balance shaft system, because directly processing the crankshaft sprocket or crankshaft gear for driving the balance shaft system on the crankshaft will greatly increase the difficulty of crankshaft processing and increase the cost, so the crankshaft sprocket or crankshaft is usually processed separately.
  • the present invention solves the technical problems of complicated process, high cost and low assembling efficiency in the assembling method of the crankshaft gear and the crankshaft in the prior art.
  • the present invention discloses a connection structure of a crankshaft and a crankshaft gear, comprising: a crankshaft and a crankshaft gear;
  • crankshaft gear is sleeved on the crankshaft
  • the inner circumferential surface of the crankshaft gear is provided with a first preset number of keyways; the keyway is a right-angle keyway; the inner circumferential surface is matched with the crankshaft;
  • the outer circumferential surface of the crankshaft is provided with a first preset number of keys corresponding to the first preset number of keyways; the outer circumferential surface is matched with the crankshaft gear; the keys include The two sides of the shaft are parallel to the axis; the two sides are provided with a helix angle, and the key is in an interference fit with the side of the keyway.
  • a second preset number of teeth are provided on the inner circumferential surface of the crankshaft gear and the crankshaft, and the keyway is provided between two adjacent teeth; the second preset number is equal to the first preset number;
  • Both the keyway and the key are involute tooth shapes.
  • the angle of the helix angle is determined according to the target axial force information that the gear needs to bear and the effective matching length of the key and the keyway.
  • the key is prepared and formed by a tooth rolling process or a tooth hobbing process.
  • a second aspect of the present invention provides a method for assembling a crankshaft and a crankshaft gear, comprising the following steps:
  • a keyway is processed on the inner circumferential surface of the crankshaft gear; the keyway is a right-angle keyway;
  • a key corresponding to the keyway is formed on the outer circumferential surface of the crankshaft; the key includes two side surfaces parallel to the axis of the crankshaft; the two The sides are provided with a helix angle;
  • crankshaft gear is assembled to the crankshaft along the axis of the crankshaft until a preset amount of side interference fit between the key and the keyway is reached.
  • the size information of the key and the size information of the keyway are determined according to the target axial force information and the effective fitting length.
  • determining the size information of the key and the size information of the keyway according to the target axial force information and the effective fitting length including:
  • the size information of the key and the size information of the keyway are determined.
  • the dimension information of the key includes the thickness of the key and the angle of the helix angle; the dimension information of the keyway includes the width of the keyway.
  • a third aspect of the present invention provides an engine, which includes a connection structure between the crankshaft and the crankshaft gear.
  • a fourth aspect of the present invention provides a vehicle, characterized in that it includes the engine structure.
  • the keyway on the crankshaft gear is a right-angle keyway
  • the side surface of the key on the crankshaft is provided with a helix angle, so that the key and the side surface of the keyway are interference fit.
  • the lateral interference caused by the helix angle on the crankshaft can make the crankshaft gear axially constrained on the crankshaft journal, and at the same time make the crankshaft gear and the crankshaft journal concentric, improving the assembly accuracy; the crankshaft gear is axially constrained
  • the force can be adjusted by setting the helix angle on the side of the key structure.
  • crankshaft gears that generally cannot withstand axial force or can only withstand small axial forces, the assembly difficulty is greatly reduced, and the key and keyway matching method does not need to make or purchase special hot pressing
  • the crankshaft gear can be directly assembled by conventional simple tooling, which simplifies the assembly process, improves the assembly efficiency and reduces the assembly cost.
  • FIG. 1 is a schematic diagram of a connection structure of a crankshaft and a crankshaft gear according to an embodiment of the present invention.
  • FIG. 2 is a schematic diagram of the cooperation between a key and a keyway according to an embodiment of the present invention.
  • FIG. 3 is a flow chart of a method for assembling a crankshaft and a crankshaft gear according to an embodiment of the present invention.
  • references herein to "one embodiment” or “an embodiment” refers to a particular feature, structure, or characteristic that may be included in at least one implementation of the present invention.
  • the orientations or positional relationships indicated by the terms “upper”, “lower”, “top”, “bottom”, etc. are based on the orientations or positional relationships shown in the drawings, only It is to facilitate the description of the present invention and to simplify the description, rather than indicating or implying that the device or element referred to must have a particular orientation, be constructed and operate in a particular orientation, and therefore should not be construed as limiting the invention.
  • first and second are only used for descriptive purposes, and should not be construed as indicating or implying relative importance or implying the number of indicated technical features. Thus, a feature defined as “first” or “second” may expressly or implicitly include one or more of that feature. Also, the terms “first,” “second,” etc. are used to distinguish between similar objects, and are not necessarily used to describe a particular order or precedence. It is to be understood that the data so used may be interchanged under appropriate circumstances such that the embodiments of the invention described herein can be practiced in sequences other than those illustrated or described herein.
  • FIG. 1 is a connection structure of a crankshaft and a crankshaft gear according to an embodiment of the present invention.
  • the connection structure may include: a crankshaft 1 and a crankshaft gear 2;
  • crankshaft gear 2 is sleeved on the crankshaft 1;
  • the inner circumferential surface of the crankshaft gear 2 is provided with a first preset number of keyways 3; the keyway 3 is a right-angled keyway 3; the inner circumferential surface is matched with the crankshaft 1;
  • the outer circumferential surface of the crankshaft 1 is provided with a first preset number of keys 4 corresponding to the first preset number of key grooves 3; the outer circumferential surface is matched with the crankshaft gear 2; the keys 4 include two parallel to the axis of the crankshaft 1. Side; both sides are provided with a helix angle 5, and the key 4 is in an interference fit with the side of the keyway 3. The side clearance caused by the helix angle 5 is reduced until the interference is shown in Figure 2.
  • the side of the key 4 structure has a helix angle 5.
  • the side clearance gradually decreases with the increase of the fitting length, and finally reaches the preset key 4 and the side of the key groove 3. Winning amount.
  • the keyway 3 on the crankshaft gear 2 is set as a right-angle keyway 3, and the side surface of the key 4 on the crankshaft 1 is provided with a helix angle 5, so that the key 4 and the side surface of the keyway 3 pass through each other. Win cooperation.
  • the lateral interference caused by the helix angle 5 on the crankshaft 1 can make the crankshaft gear 2 axially restrain the crankshaft 1 journal, and the existence of the helix angle 5 can make the crankshaft gear 2 and the crankshaft 1 journal.
  • crankshaft gear 2 Concentricity improves assembly accuracy; the axial restraint force of crankshaft gear 2 can be adjusted by setting the helix angle 5 on the side of the key 4 structure.
  • crankshaft gears 2 that generally cannot withstand axial force or can only withstand small axial forces, assembly is difficult Greatly reduced, the key 4 and the keyway 3 do not need to make or purchase special hot-pressing and cold-pressing tooling and equipment, and conventional simple tooling can be used to directly assemble the crankshaft gear 2, which simplifies the assembly process, improves assembly efficiency, and reduces assembly costs.
  • the inner circumferential surface of the crankshaft gear 2 and the crankshaft 1 is provided with a second preset number of teeth, and the keyway 3 is provided between two adjacent teeth; that is, in the second preset number of teeth A keyway 3 is formed between any two adjacent teeth.
  • the number of teeth and keyways 3 can be determined according to actual needs, for example, for the assembly of crankshafts 1 of different diameters, crankshaft gears 2 containing different numbers of keyways 3 or different numbers of teeth can be selected.
  • the keyway 3 and the key 4 may both be involute tooth shapes.
  • the transmission torque of the crankshaft gear 2 can be effectively improved; While continuously adapting to the side of the key 4, the centerline of the crankshaft gear 2 is also constantly approaching the centerline of the journal of the crankshaft 1 during the assembly process to achieve the centering function.
  • the angle of the helix angle 5 can be determined according to the target axial force information that the gear needs to bear and the effective matching length of the key 4 and the keyway 3 .
  • the key 4 may be prepared and formed through a tooth rolling process or a tooth hobbing process.
  • FIG. 3 is a flowchart of an assembling method for a crankshaft and a crankshaft gear according to an embodiment of the present invention; the assembling method may include the following steps:
  • S301 obtain the size and quantity information of the preset keyway 3 on the inner circumferential surface of the crankshaft gear 2 and the size and quantity information of the preset key 4 on the outer circumferential surface of the crankshaft 1;
  • the size and quantity information of the preset keyways 3 on the inner circumferential surface of the crankshaft gear 2 and the size and quantity information of the preset keys 4 on the outer circumferential surface of the crankshaft 1 are obtained; including:
  • the target transmission torque information can be the torque value to be transmitted; determine the quantity information of keys 4 and the quantity information of keyways 3 according to the target transmission torque information;
  • M F ⁇ L
  • M is the required transmission torque value
  • L is the lever arm value, where the lever arm value is 1/2 of the pitch circle diameter of the tooth
  • F is the required bearing capacity of the key 4 and the keyway 3 force
  • Determining the quantity information of the keys 4 and the quantity information of the keyways 3 according to the target transmission torque information may include the following steps:
  • S405 Obtain the allowable compressive stress F2 of the key 4 and the keyway 3; in the embodiment of the present invention, the material of the key 4 and the keyway 3 can be selected from the same material; the key 4 and the keyway 3 can also be of different materials.
  • the keyway 3 is made of different materials, and the smaller of the allowable compressive stress of the key 4 and the allowable compressive stress of the keyway 3 is used as the allowable compressive stress F2 of the above-mentioned key 4 and the keyway 3;
  • F1 is less than or equal to F2, use the estimated lever arm value L as the determined lever arm value; determine the pitch circle diameter of the tooth portion according to the determined lever arm value; obtain the quantity information of the preset keyway 3 according to the pitch circle diameter of the tooth portion and the number of preset keys 4 information. If F1 is greater than F2, return to step S401, re-acquire the estimated force arm value L1, and execute the above steps S401-S405; until the acquired F1 is less than or equal to F2.
  • the details may include:
  • the minimum effective interference between the key 4 and the keyway 3 is determined according to the target axial force information and the effective fitting information;
  • the effective fitting information may include fitting length, fitting area and fitting friction coefficient;
  • Information and effective fit information to determine the minimum effective interference between key 4 and keyway 3; may include:
  • the minimum effective interference between key 4 and keyway 3 can be obtained;
  • the minimum effective interference between key 4 and keyway 3 can be the minimum diameter change of keyway 3 and key 4. the sum of the smallest diameter changes;
  • the minimum diameter change of the keyway 3 and the minimum diameter change of the key 4, and the preset accuracy of the key 4 and the keyway 3, determine the size information of the key 4 and the size information of the keyway 3;
  • the size information of the key 4 includes the thickness of the key 4 and the angle of the helix angle 5; the size information of the keyway 3 includes the width of the keyway 3
  • the thickness of the key 4 may include the maximum and minimum thicknesses of the solid key 4; wherein, the maximum and minimum thicknesses of the solid key 4 may be obtained by considering the machining error of the key 4 thickness, the side shape error and the shape error along the axis direction Maximum and minimum ideal solid state thickness.
  • the width of the keyway 3 may include the maximum and minimum widths of the solid keyway 3; wherein, the maximum and minimum widths of the solid keyway 3 may be the maximum and minimum ideal solids obtained by considering the machining error of the width of the keyway 3, the lateral shape error and the shape error along the centerline direction. The width of the keyway 3 in the state.
  • S302 Process the keyway 3 on the inner circumferential surface of the crankshaft gear 2 according to the size and quantity information of the preset keyway 3; the keyway 3 is a right-angled keyway 3; The size and quantity information of the preset keyway 3 can directly form the structure of the keyway 3;
  • a key 4 corresponding to the keyway 3 is formed on the outer circumferential surface of the crankshaft 1; the key 4 includes two sides parallel to the axis of the crankshaft 1; both sides are provided with There is a helix angle 5; the key 4 can be prepared by the gear rolling process or the gear hobbing process
  • the helix angle 5 on the side of the key 4 structure causes the assembly gap between the key 4 and the keyway 3 to decrease continuously until the side of the key 4 and the keyway 3 interfere, and the end face of the crankshaft gear 2 is in contact with the crankshaft. 1 shoulder when the assembly is complete.
  • the two sides of the key 4 structure have a helix angle 5 at an angle of ⁇ .
  • the keyway 3 gradually matches the key 4, and the side clearance Gradually decrease as the fit length increases until the preset fit interference is reached.
  • the involute side surface of the keyway 3 is constantly adapted to the side surface of the key 4 due to the helix of the key 4 structure, and the centerline of the crankshaft gear 2 is also constantly approaching the centerline of the crankshaft 1 journal during the assembly process to achieve the centering function.
  • a third aspect of the present invention provides an engine, which may include the above-mentioned connection structure of the crankshaft 1 and the crankshaft gear 2 .
  • a fourth aspect of the present invention provides a vehicle including the above engine structure.

Abstract

一种曲轴（1）与曲轴齿轮（2）的连接结构、装配方法、发动机及车辆，连接结构包括：曲轴（1）和曲轴齿轮（2）；曲轴齿轮（2）套设于曲轴（1）上；曲轴齿轮（2）的内圆周面上设置有第一预设数量的键槽（3）；键槽（3）为直角形键槽（3）；内圆周面与曲轴（1）配合；曲轴（1）的外圆周面上设有与第一预设数量的键槽（3）对应的第一预设数量的键（4）；外圆周面与曲轴齿轮（2）配合；键（4）包括与曲轴（1）的轴线平行的两个侧面；两个侧面上均设置有螺旋角（5），键（4）与键槽（3）侧面过盈配合。

Description

曲轴与曲轴齿轮的连接结构、装配方法、发动机及车辆 技术领域
本发明涉及车辆零配件技术领域，特别涉及一种曲轴与曲轴齿轮的连接结构、装配方法、发动机及车辆。
背景技术
发动机曲轴前端通常有驱动平衡轴系统功能，因直接在曲轴上加工用于驱动平衡轴系统的曲轴链轮或曲轴齿轮会造成曲轴加工难度大幅增加以及成本上涨，因此通常会单独加工曲轴链轮或曲轴齿轮并组装到曲轴上使用。
传统组装方式包括热压装及冷压装，目的是将曲轴链轮或曲轴齿轮完全紧固在曲轴上。无论是热压装还是冷压装，需要投入专用的压装工装，例如热压装需要制作感应线圈、加热机构及冷却机构等，工艺复杂，装配效率较低。冷压装通常需要专用压力装置，成本较高；且冷压装容易引起的曲轴弯曲变形，从而使传动精度受影响。
发明内容
本发明要解决是现有技术中曲轴齿轮与曲轴的组装方式工艺复杂、成本较高且装配效率较低的技术问题。
为解决上述技术问题，本发明公开了一种曲轴与曲轴齿轮的连接结构，包括：曲轴和曲轴齿轮；
所述曲轴齿轮套设于所述曲轴上；
所述曲轴齿轮的内圆周面上设置有第一预设数量的键槽；所述键槽为直角形键槽；所述内圆周面与所述曲轴配合；
所述曲轴的外圆周面上设有与所述第一预设数量的键槽对应的第一预设数量的键；所述外圆周面与所述曲轴齿轮配合；所述键包括与所述曲轴的轴线平行的两个侧面；所述两个侧面上均设置有螺旋角，所述键与所述 键槽侧面过盈配合。
进一步地，所述曲轴齿轮与所述曲轴配合的内圆周面上设有第二预设数量的齿，所述键槽设于相邻的两个所述齿之间；所述第二预设数量与所述第一预设数量相等；
所述键槽与所述键均为渐开线齿形。
进一步地，所述螺旋角的角度根据所述齿轮所需承受的目标轴向力信息以及所述键与所述键槽的有效配合长度确定。
进一步地，所述键通过搓齿工艺或滚齿工艺制备形成。
本发明第二方面提供一种曲轴与曲轴齿轮的装配方法，包括以下步骤：
获取曲轴齿轮的内圆周面上的预设键槽的尺寸与数量信息和曲轴的外圆周面上的预设键的尺寸与数量信息；
根据所述预设键槽的尺寸与数量信息在所述曲轴齿轮的内圆周面上加工形成键槽；所述键槽为直角形键槽；
根据所述预设键的尺寸与数量信息在所述曲轴的外圆周面上加工形成与所述键槽对应的键；所述键包括与所述曲轴的轴线平行的两个侧面；所述两个侧面上均设置有螺旋角；
沿所述曲轴的轴线将所述曲轴齿轮装配至所述曲轴上直至达到预设的所述键与所述键槽的侧面过盈配合量。
进一步地，所述获取曲轴齿轮的内圆周面上的预设键槽的尺寸与数量信息和曲轴的外圆周面上的预设键的尺寸与数量信息；包括：
获取目标传动力矩信息；
根据所述目标传动力矩信息确定所述键的数量信息和所述键槽的数量信息；
获取齿轮所承受的目标轴向力信息以及所述键与所述键槽的有效配合长度；
根据所述目标轴向力信息和所述有效配合长度确定所述键的尺寸信息和所述键槽的尺寸信息。
进一步地，所述根据所述目标轴向力信息和所述有效配合长度确定所述键的尺寸信息和所述键槽的尺寸信息；包括：
根据所述目标轴向力信息和所述有效配合长度确定所述键与所述键槽的最小有效过盈量；
根据所述键与所述键槽的最小有效过盈量，确定所述键的尺寸信息和所述键槽的尺寸信息。
进一步地，所述键的尺寸信息包括所述键的厚度和所述螺旋角的角度；所述键槽的尺寸信息包括所述键槽的宽度。
本发明第三方面提供一种发动机，包括所述曲轴与曲轴齿轮的连接结构。
本发明第四方面提供一种车辆，其特征在于，包括所述发动机结构。
采用上述技术方案，本发明具有如下有益效果：
本发明公开的曲轴与曲轴齿轮的连接结构中，曲轴齿轮上的键槽设为直角形键槽，所述曲轴上的键侧面设置有螺旋角，使得所述键与所述键槽侧面过盈配合。在轴向装配过程中由曲轴上螺旋角引起的侧向过盈能够使曲轴齿轮轴向约束在曲轴轴颈上，同时能使曲轴齿轮与曲轴轴颈同心，提高装配精度；曲轴齿轮轴向约束力可以通过设置键结构侧面螺旋角大小进行调整，对于普遍不能承受轴向力或只能承受微小轴向力作用的曲轴齿轮，装配难度大幅降低，键与键槽配合方法无需制作或购买专用热压装及冷压装工装及设备，可采用常规的简易工装直接装配曲轴齿轮，简化装配工艺，提高装配效率，降低装配成本。
附图说明
为了更清楚地说明本发明实施例中的技术方案，下面将对实施例描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本发明的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1为本发明实施例一种曲轴与曲轴齿轮的连接结构示意图。
图2为本发明实施例一种键与键槽的配合示意图。
图3为本发明实施例一种曲轴与曲轴齿轮的装配方法流程图。
以下对附图作补充说明：
1-曲轴；2-曲轴齿轮；3-键槽；4-键；5-螺旋角。
具体实施方式
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述。显然，所描述的实施例仅仅是本发明一部分实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有作出创造性劳动的前提下所获得的所有其他实施例，都属于本发明保护的范围。
此处所称的“一个实施例”或“实施例”是指可包含于本发明至少一个实现方式中的特定特征、结构或特性。在本发明实施例的描述中，需要理解的是，术语“上”、“下”、“顶”、“底”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含的包括一个或者更多个该特征。而且，术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本发明的实施例能够以除了在这里图示或描述的那些以外的顺序实施。
请参见图1，图1为本发明实施例一种曲轴与曲轴齿轮的连接结构，该连接结构可以包括：曲轴1和曲轴齿轮2；
曲轴齿轮2套设于曲轴1上；
曲轴齿轮2的内圆周面上设置有第一预设数量的键槽3；键槽3为直角形键槽3；内圆周面与曲轴1配合；
曲轴1的外圆周面上设有与第一预设数量的键槽3对应的第一预设数量的键4；外圆周面与曲轴齿轮2配合；键4包括与曲轴1的轴线平行的两个侧面；两个侧面上均设置有螺旋角5，键4与键槽3侧面过盈配合。由螺旋角5引起的侧面间隙减小直至过盈示意图见图2。
如图2所示，键4结构侧面带有螺旋角5，键槽3在装入键4结构过程中，侧面间隙随配合长度增加逐渐减小，最终达到预设的键4与键槽3的侧面过盈配合量。
本发明公开的曲轴1与曲轴齿轮2的连接结构中，曲轴齿轮2上的键槽3设为直角形键槽3，曲轴1上的键4侧面设置有螺旋角5，使得键4与键槽3侧面过盈配合。在轴向装配过程中由曲轴1上螺旋角5引起的侧向过盈能够使曲轴齿轮2轴向约束在曲轴1轴颈上，同时螺旋角5的存在能使曲轴齿轮2与曲轴1轴颈同心，提高装配精度；曲轴齿轮2轴向约束力可以通过设置键4结构侧面螺旋角5大小进行调整，对于普遍不能承受轴向力或只能承受微小轴向力作用的曲轴齿轮2，装配难度大幅降低，键4与键槽3配合方法无需制作或购买专用热压装及冷压装工装及设备，可采用常规的简易工装直接装配曲轴齿轮2，简化装配工艺，提高装配效率，降低装配成本。
本发明实施例中，曲轴齿轮2与曲轴1配合的内圆周面上设有第二预设数量的齿，键槽3设于相邻的两个齿之间；即第二预设数量的齿中任意两个相邻的齿之间均形成一个键槽3，例如，若齿的数量为3个，则形成的键槽的数量也为3个，若齿的数量为20个，则形成的键槽3的数量也为20个；即本发明实施例中齿的数量(第二预设数量)与上述键4和键槽3的数量(第一预设数量)相等；本发明实施例中，曲轴齿轮2上齿和键槽3的数量可以根据实际需求确定，例如用于不同直径的曲轴1的装配，则可以选用包含不同数量的键槽3或不同数量的齿的曲轴齿轮2。
本发明实施例中，键槽3与键4可以均为渐开线齿形。利用本发明渐开线齿形的键槽3与键4的配合方法，能有效提高曲轴齿轮2的传动力矩；另外，在装配过程中，键槽3的渐开线形侧面因键4结构的螺旋角5而不断适应键4的侧面，曲轴齿轮2的中心线也在装配过程中不断靠近曲轴1的轴颈中心线，实现定心功能。
本发明实施例中，螺旋角5的角度可以根据齿轮所需承受的目标轴向力信息以及键4与键槽3的有效配合长度确定。
本发明实施例中，键4可以通过搓齿工艺或滚齿工艺制备形成。
本发明第二方面提供一种曲轴与曲轴齿轮的装配方法，图3为本发明实施例一种曲轴与曲轴齿轮的装配方法流程图；该装配方法可以包括以下步骤：
S301:获取曲轴齿轮2的内圆周面上的预设键槽3的尺寸与数量信息和曲轴1的外圆周面上的预设键4的尺寸与数量信息；
其中，获取曲轴齿轮2的内圆周面上的预设键槽3的尺寸与数量信息和曲轴1的外圆周面上的预设键4的尺寸与数量信息；包括：
获取目标传动力矩信息；其中，目标传动力矩信息可以为所需传递的力矩值；根据目标传动力矩信息确定键4的数量信息和键槽3的数量信息；
根据公式M＝F×L，公式中M为所需传递力矩值，L为力臂值，其中，力臂值为齿部节圆直径的1/2；F为键4和键槽3所需承受的力；
根据目标传动力矩信息确定键4的数量信息和键槽3的数量信息可以包括以下步骤：
S401:获取预估力臂值L；
S402:根据预估力臂值L和所需传递力矩值，获取键4和键槽3所需承受的力F；
S403：根据键4的初步定义数量信息和键槽3的初步定义数量信息以及轴向键4与键槽3侧面过盈配合长度，获取F所作用的面积S；
S404：获取F对应的压应力F1,其中，F1可以根据公式F1＝F/S计算获取；
S405：获取键4和键槽3的许用压应力F2；本发明实施例中，键4和键槽3的材料可以选择同种材料；键4和键槽3也可为不同种材料，当键4和键槽3为不同种材料，以键4的许用压应力和键槽3的许用压应力中较小的作为上述键4和键槽3的许用压应力F2；
S406：若F1小于等于F2，则将预估力臂值L作为确定的力臂值；根据确定的力臂值确定齿部节圆直径；根据齿部节圆直径获取预设键槽3的数量信息和预设键4的数量信息。若F1大于F2，则返回步骤S401，重新获取预估力臂值L1，并执行上述步骤S401-S405；直至获取的F1小于等于F2。
获取齿轮所承受的目标轴向力信息以及键4与键槽3的有效配合长度；
根据目标轴向力信息和有效配合长度确定键4的尺寸信息和键槽3的尺寸信息；具体可以包括：
其中根据目标轴向力信息和有效配合信息确定键4与键槽3的最小有效过盈量；有效配合信息可以包括配合长度、配合面积和配合摩擦系数；本发明实施例中，根据目标轴向力信息和有效配合信息确定键4与键槽3的最小有效过盈量；可以包括：
获取目标轴向力信息和键4与键槽3的有效配合信息；获取键4与键槽3配合的最小所需压应力；
根据最小所需压应力和键槽3节圆直径获取传递扭矩所需的键槽3最小直径变化量；
根据最小所需压应力和键4节圆直径获取传递载荷所需的键4最小直径变化量；
根据键槽3最小直径变化量和键4最小直径变化量获取键4与键槽3的最小有效过盈量；其中键4与键槽3的最小有效过盈量可以为键槽3最小直径变化量和键4最小直径变化量的和；
键槽3最小直径变化量和键4最小直径变化量以及预设的键4与键槽3精度，确定键4的尺寸信息和键槽3的尺寸信息；
本发明实施例中，键4的尺寸信息包括键4的厚度和螺旋角5的角度；键槽3的尺寸信息包括键槽3的宽度
本发明实施例中，键4的厚度可以包括最大与最小实体键4厚度；其中，最大与最小实体键4厚度可以为考虑键4厚度加工误差及侧面形状误差及沿轴线方向的形状误差得到的最大与最小理想实体状态下厚度。键槽3的宽度可以包括最大与最小实体键槽3宽度；其中，最大与最小实体键槽3宽度可以为考虑键槽3宽度加工误差及侧面形状误差及沿中心线方向的形状误差得到的最大与最小理想实体状态下键槽3宽度。
S302:根据预设键槽3的尺寸与数量信息在曲轴齿轮2的内圆周面上加工形成键槽3；键槽3为直角形键槽3；本发明实施例中，当键槽3为粉末冶金材料，可根据预设键槽3的尺寸与数量信息直接成型键槽3结构；
S303:根据预设键4的尺寸与数量信息在曲轴1的外圆周面上加工形成 与键槽3对应的键4；键4包括与曲轴1的轴线平行的两个侧面；两个侧面上均设置有螺旋角5；键4可以通过搓齿工艺或滚齿工艺制备形成
S304:沿曲轴1的轴线将曲轴齿轮2装配至曲轴1上直至达到预设的键4与键槽3的侧面过盈配合量。
曲轴齿轮2沿轴线方向装入曲轴1过程中，由键4结构侧面螺旋角5引起键4与键槽3侧面装配间隙不断减小直至键4与键槽3侧面过盈，曲轴齿轮2轮毂端面接触曲轴1轴肩时，装配完成。螺旋角5引起的侧面间隙减小量计算公式如下：ΔC＝L0×sinβ；其中，ΔC：侧面间隙减小量；L0：键4与键槽3有效配合长度；β：键4侧面螺旋角5的角度。如图2所示，键4结构的两个侧面带有螺旋角5的角度为β，沿曲轴1的轴线将曲轴齿轮2装配至曲轴1上过程中，键槽3逐渐与键4配合，侧面间隙随配合长度增加逐渐减小，直至达到预设的配合过盈量。在装配过程中，键槽3渐开线形侧面因键4结构的螺旋线而不断适应键4侧面，曲轴齿轮2中心线也在装配过程中不断靠近曲轴1轴颈中心线，实现定心功能。
本发明第三方面提供一种发动机，可以包括上述曲轴1与曲轴齿轮2的连接结构。
本发明第四方面提供一种车辆，包括上述发动机结构。
以上仅为本发明的较佳实施例，并不用以限制本发明，凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (10)

  1. 一种曲轴(1)与曲轴齿轮(2)的连接结构，其特征在于，包括：曲轴(1)和曲轴齿轮(2)；
    所述曲轴齿轮(2)套设于所述曲轴(1)上；
    所述曲轴齿轮(2)的内圆周面上设置有第一预设数量的键槽(3)；所述键槽(3)为直角形键槽；所述内圆周面与所述曲轴(1)配合；
    所述曲轴(1)的外圆周面上设有与所述第一预设数量的键槽(3)对应的第一预设数量的键(4)；所述外圆周面与所述曲轴齿轮(2)配合；所述键(4)包括与所述曲轴(1)的轴线平行的两个侧面；所述两个侧面上均设置有螺旋角(5)，所述键(4)与所述键槽(3)侧面过盈配合。
  2. 根据权利要求1所述的曲轴(1)与曲轴齿轮(2)的连接结构，其特征在于，所述曲轴齿轮(2)与所述曲轴(1)配合的内圆周面上设有第二预设数量的齿，所述键槽(3)设于相邻的两个所述齿之间；所述第二预设数量与所述第一预设数量相等；
    所述键槽(3)与所述键(4)均为渐开线齿形。
  3. 根据权利要求1所述的曲轴(1)与曲轴齿轮(2)的连接结构，其特征在于，所述螺旋角(5)的角度根据所述齿轮所需承受的目标轴向力信息以及所述键(4)与所述键槽(3)的有效配合长度确定。
  4. 根据权利要求1所述的曲轴(1)与曲轴齿轮(2)的连接结构，其特征在于，所述键(4)通过搓齿工艺或滚齿工艺制备形成。
  5. 一种曲轴与曲轴齿轮的装配方法，其特征在于，包括以下步骤：
    获取曲轴齿轮的内圆周面上的预设键槽的尺寸与数量信息和曲轴的外圆周面上的预设键的尺寸与数量信息；
    根据所述预设键槽的尺寸与数量信息在所述曲轴齿轮的内圆周面上加 工形成键槽；所述键槽为直角形键槽；
    根据所述预设键的尺寸与数量信息在所述曲轴的外圆周面上加工形成与所述键槽对应的键；所述键包括与所述曲轴的轴线平行的两个侧面；所述两个侧面上均设置有螺旋角；
    沿所述曲轴的轴线将所述曲轴齿轮装配至所述曲轴上直至达到预设的所述键与所述键槽的侧面过盈配合量。
  6. 根据权利要求5所述的曲轴与曲轴齿轮的装配方法，其特征在于，
    所述获取曲轴齿轮的内圆周面上的预设键槽的尺寸与数量信息和曲轴的外圆周面上的预设键的尺寸与数量信息；包括：
    获取目标传动力矩信息；
    根据所述目标传动力矩信息确定所述键的数量信息和所述键槽的数量信息；
    获取齿轮所承受的目标轴向力信息以及所述键与所述键槽的有效配合长度；
    根据所述目标轴向力信息和所述有效配合长度确定所述键的尺寸信息和所述键槽的尺寸信息。
  7. 根据权利要求6所述的曲轴与曲轴齿轮的装配方法，其特征在于，所述根据所述目标轴向力信息和所述有效配合长度确定所述键的尺寸信息和所述键槽的尺寸信息；包括：
    根据所述目标轴向力信息和所述有效配合长度确定所述键与所述键槽的最小有效过盈量；
    根据所述键与所述键槽的最小有效过盈量，确定所述键的尺寸信息和所述键槽的尺寸信息。
  8. 根据权利要求6所述的曲轴与曲轴齿轮的装配方法，其特征在于，
    所述键的尺寸信息包括所述键的厚度和所述螺旋角的角度；所述键槽的尺寸信息包括所述键槽的宽度。
  9. 一种发动机，其特征在于，包括权利要求1-4任一项所述曲轴与曲轴齿轮的连接结构。
  10. 一种车辆，其特征在于，包括权利要求9所述发动机结构。
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10260044A1 (de) * 2002-12-19 2004-07-08 Volkswagen Ag Torsionsschwingungsdämpfer
CN1987130A (zh) * 2006-12-08 2007-06-27 奇瑞汽车有限公司 传递重载荷的联接装置
CN104006142A (zh) * 2014-05-13 2014-08-27 浙江吉利控股集团有限公司 一种曲轴与减震皮带轮总成连接结构
CN111120500A (zh) * 2020-01-10 2020-05-08 安徽华菱汽车有限公司 发动机曲轴、发动机及车辆
CN211778902U (zh) * 2020-03-23 2020-10-27 浙江振华精锻齿轮股份有限公司 一种圆柱齿轮

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10260044A1 (de) * 2002-12-19 2004-07-08 Volkswagen Ag Torsionsschwingungsdämpfer
CN1987130A (zh) * 2006-12-08 2007-06-27 奇瑞汽车有限公司 传递重载荷的联接装置
CN104006142A (zh) * 2014-05-13 2014-08-27 浙江吉利控股集团有限公司 一种曲轴与减震皮带轮总成连接结构
CN111120500A (zh) * 2020-01-10 2020-05-08 安徽华菱汽车有限公司 发动机曲轴、发动机及车辆
CN211778902U (zh) * 2020-03-23 2020-10-27 浙江振华精锻齿轮股份有限公司 一种圆柱齿轮

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