CN106286761B - Differential attachment formula three-axle table - Google Patents
Differential attachment formula three-axle table Download PDFInfo
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- CN106286761B CN106286761B CN201610891348.3A CN201610891348A CN106286761B CN 106286761 B CN106286761 B CN 106286761B CN 201610891348 A CN201610891348 A CN 201610891348A CN 106286761 B CN106286761 B CN 106286761B
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- 238000005096 rolling process Methods 0.000 claims abstract description 35
- 230000033001 locomotion Effects 0.000 claims abstract description 19
- 150000001875 compounds Chemical class 0.000 claims abstract description 7
- 125000006850 spacer group Chemical group 0.000 claims description 12
- 230000008878 coupling Effects 0.000 claims description 9
- 238000010168 coupling process Methods 0.000 claims description 9
- 238000005859 coupling reaction Methods 0.000 claims description 9
- 238000009434 installation Methods 0.000 claims description 5
- 241001416181 Axis axis Species 0.000 claims 4
- 230000001360 synchronised effect Effects 0.000 claims 1
- 230000007246 mechanism Effects 0.000 abstract description 20
- 239000003638 chemical reducing agent Substances 0.000 description 26
- 230000001681 protective effect Effects 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 101100327917 Caenorhabditis elegans chup-1 gene Proteins 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000004088 simulation Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
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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
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/12—Differential gearings without gears having orbital motion
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Abstract
本发明公开一种差动机构式三轴转台,包括机座、俯仰部件组、差动机构部件组,差动机构部件组与俯仰部件组配合形成俯仰轴、滚动轴、方位轴三个转动轴系,俯仰轴采用独立的驱动单元实现上台面的俯仰转动,滚动轴和方位轴的转动通过差动机构实现,该差动机构具有三个锥齿轮,其中有两个锥齿轮的轴线重合,第三个锥齿轮轴线垂直于前两个锥齿轮的公共轴线且与前两个锥齿轮分别啮合,共轴线的两个锥齿轮分别与对称布置的驱动马达传动连接实现两个锥齿轮的复合运动,从而带动第三个锥齿轮完成两个自由度运动,第三个锥齿轮和上台面连接,这样便实现工作台面的滚动和方位转动。本发明具有结构紧凑,滚动轴和方位轴尺寸小、质量轻的特点,适用于转台领域。
The invention discloses a differential mechanism type three-axis turntable, which includes a machine base, a pitching component group, and a differential mechanism component group, and the differential mechanism component group and the pitching component group cooperate to form three rotation axes of a pitch axis, a rolling axis and an azimuth axis system, the pitch axis adopts an independent drive unit to realize the pitch rotation of the upper table, and the rotation of the roll axis and the azimuth axis is realized by a differential mechanism. The differential mechanism has three bevel gears, and the axis of two bevel gears coincides. The axes of the three bevel gears are perpendicular to the common axis of the first two bevel gears and are respectively meshed with the first two bevel gears. The two coaxial bevel gears are respectively connected to the drive motors arranged symmetrically to realize the compound motion of the two bevel gears. Thus, the third bevel gear is driven to complete two degrees of freedom movement, and the third bevel gear is connected with the upper table, so that the rolling and azimuth rotation of the work table are realized. The invention has the characteristics of compact structure, small size and light weight of the rolling axis and the azimuth axis, and is suitable for the field of turntables.
Description
技术领域technical field
本发明涉及用于惯性导航和制导系统仿真试验的一种三轴转台,具体涉及一种具有自稳定和调节目标负载空间姿态的差动机构式三轴转台。The invention relates to a three-axis turntable used for simulation tests of inertial navigation and guidance systems, in particular to a differential mechanism type three-axis turntable with self-stabilization and adjustment of target load space attitude.
背景技术Background technique
目前,大多的三轴转台本体机械系统由三个框架和机座两大部分组成,主要为负载提供安装基准和实现滚动、俯仰、方位三轴系回转运动,所以它能够在地面上真实的模拟飞行器、导弹等的各种飞行姿态,对其元件和系统进行测试,避免了进行昂贵的实物试验,通过模拟可以对其过程进行预测和重复,为实物的研制奠定了坚实的基础。就其机械结构来看大多数采用实轴串联构型,每个轴系配上独立的驱动单元,从而实现目标负载的空间姿态调节。例如授权公告号为CN 103606737 B的中国专利公开了一种三轴转台,通过下方位转盘、上方位转盘、俯仰轴及各自的连接传动结构,可实现三轴方向的姿态变换。再比如专利号为201220751996.6的中国专利公开了一种电动三轴转台,其底座通过导电滑环与旋转架相连,旋转架上设有转台模块,可实现自由调整角度,定位精度高。但是,这类转台存在普遍的问题是结构不够紧凑,每个轴系都必须附加一套驱动单元,这势必会增大该轴系的空间尺寸和质量,阻碍转台性能的提升,尤其是所用的减速器尺寸较大时如蜗轮蜗杆减速器,这一问题就会更加突出。At present, most of the three-axis turntable body mechanical system consists of three frames and a machine base, which mainly provide the installation reference for the load and realize the three-axis rotary motion of rolling, pitching, and azimuth, so it can be simulated on the ground. Various flight attitudes of aircraft, missiles, etc. are tested for their components and systems, avoiding expensive physical tests, and the process can be predicted and repeated through simulation, laying a solid foundation for the development of physical objects. As far as its mechanical structure is concerned, most of them adopt a real shaft series configuration, and each shaft system is equipped with an independent drive unit, so as to realize the spatial attitude adjustment of the target load. For example, the Chinese patent with the authorized notification number CN 103606737 B discloses a three-axis turntable, through which the attitude transformation in the three-axis direction can be realized through the lower turntable, the upper turntable, the pitch axis and their respective connecting transmission structures. Another example is the Chinese patent No. 201220751996.6 which discloses an electric three-axis turntable, the base of which is connected to the rotating frame through a conductive slip ring, and the rotating frame is provided with a turntable module, which can freely adjust the angle and has high positioning accuracy. However, the general problem of this type of turntable is that the structure is not compact enough, and a drive unit must be added to each shaft system, which will inevitably increase the space size and quality of the shaft system, and hinder the improvement of the performance of the turntable, especially the used When the size of the reducer is large, such as a worm gear reducer, this problem will be more prominent.
发明内容Contents of the invention
为了克服现有转台的单个转轴单元质量尺寸大,结构不紧凑的不足,本发明旨在提供一种其转台滚动轴系和方位轴系的质量和尺寸相对较小,结构相对紧凑的差动机构式三轴转台。In order to overcome the shortcomings of large mass and size and uncompact structure of the single rotating shaft unit of the existing turntable, the present invention aims to provide a differential mechanism with a relatively small mass and size of the rolling shaft system and azimuth shaft system of the turntable, and a relatively compact structure Three-axis turntable.
本发明采用的技术方案是:一种差动机构式三轴转台,包括机座、俯仰部件组,所述机座为负载提供安装基准,其特征在于,还包括差动机构部件组,所述差动机构部件组与俯仰部件组配合形成用于实现目标负载的俯仰、滚动、方位转动的俯仰轴、滚动轴、方位轴三个转动轴系;初始状态时,所述的三个转动轴系的轴线相互垂直,俯仰轴轴线与滚动轴轴线位于水平面,方位轴轴线位于竖直面;工作过程中,俯仰轴轴线和滚动轴轴线始终垂直,方位轴轴线和滚动轴轴线始终垂直;所述俯仰轴采用独立的驱动单元实现上台面的俯仰转动;所述滚动轴和方位轴通过差动机构实现上台面的滚动和方位转动,所述差动机构包括差动锥齿轮一、二、三,所述差动齿轮一、三水平对置安装,所述差动锥齿轮二与差动锥齿轮一、三分别啮合,差动锥齿轮一、三的轴线在水平方向重合,差动锥齿轮二的轴线垂直于差动锥齿轮一、三的公共轴线,共轴线的差动锥齿轮一、三分别与对称布置的驱动马达传动连接实现差动锥齿轮一、三的复合运动,从而带动差动锥齿轮二完成两个自由度运动,所述差动锥齿轮二与上台面连接。The technical solution adopted in the present invention is: a differential mechanism type three-axis turntable, including a machine base and a pitching component group, the machine base provides an installation reference for the load, and is characterized in that it also includes a differential mechanism component group, the The differential mechanism component group cooperates with the pitch component group to form three rotation axis systems for pitching, rolling and azimuth rotation of the target load; in the initial state, the three rotation shaft systems The axes are perpendicular to each other, the axis of the pitch axis and the axis of the roll axis are located on the horizontal plane, and the axis of the azimuth axis is located on the vertical plane; during the working process, the axis of the pitch axis and the axis of the roll axis are always vertical, and the axis of the azimuth axis and the axis of the roll axis are always vertical; the pitch The shaft uses an independent drive unit to realize the pitch rotation of the upper table; the rolling axis and azimuth axis realize the rolling and azimuth rotation of the upper table through a differential mechanism, and the differential mechanism includes differential bevel gears 1, 2, and 3. The differential gears 1 and 3 are horizontally oppositely installed, the differential bevel gear 2 meshes with the differential bevel gears 1 and 3 respectively, the axes of the differential bevel gears 1 and 3 coincide in the horizontal direction, and the differential bevel gear 2 The axis is perpendicular to the common axis of the differential bevel gears 1 and 3, and the coaxial differential bevel gears 1 and 3 are respectively connected to the symmetrically arranged driving motors to realize the compound motion of the differential bevel gears 1 and 3, thereby driving the differential bevel gears The second gear completes the two-degree-of-freedom movement, and the second differential bevel gear is connected with the upper table.
作为优选,本发明所述差动机构的差动锥齿轮一、三用花键分别连接在差动驱动轴一、二上,其转动支撑和驱动由所述俯仰部件组提供,所述差动机构的差动锥齿轮二用花键与差动输出轴一端连接,所述差动输出轴通过差动套杯、差动角接触轴承、差动套杯端盖连接在差动主力板上,构成转动支撑的可动连接,差动输出轴另一端用花键与差动联轴件连接,所述上台面用螺栓固定在差动联轴件上,所述差动部件组左端通过差动转台轴承一、差动隔套一与俯仰机架连接,构成绕滚动轴的转动支撑的动连接,所述差动部件组右端通过差动转台轴承二、差动隔套二与俯仰机架连接,构成绕滚动轴的转动支撑的动连接,当差动锥齿轮一与差动锥齿轮三同速反向旋转时,上台面绕方位轴作方位转动;当差动锥齿轮一与差动锥齿轮三同速同向旋转时,上台面绕滚动轴作滚转运动,正常工作时,需要差动锥齿轮一、三作复合运动来实现滚动轴和方位轴的复合运动。As a preference, the differential bevel gears 1 and 3 of the differential mechanism in the present invention are respectively splined to the differential drive shafts 1 and 2, and their rotational support and drive are provided by the pitching component group. The differential bevel gear of the mechanism is splined to one end of the differential output shaft, and the differential output shaft is connected to the differential main force plate through the differential sleeve cup, the differential angular contact bearing, and the differential sleeve end cover. It constitutes a movable connection for rotating support. The other end of the differential output shaft is connected to the differential coupling with a spline. The upper table is fixed on the differential coupling with bolts. Turntable bearing 1 and differential spacer 1 are connected to the pitching frame to form a dynamic connection for rotating support around the rolling axis. The right end of the differential component group is connected to the pitching frame through differential turret bearing 2 and differential spacer 2. , constituting the dynamic connection of the rotating support around the rolling axis. When the differential bevel gear 1 and the differential bevel gear 3 rotate in reverse at the same speed, the upper table rotates azimuthally around the azimuth axis; when the differential bevel gear 1 and the differential bevel gear When the three gears rotate at the same speed and in the same direction, the upper table performs a rolling motion around the rolling axis. During normal operation, the differential bevel gears 1 and 3 are required to make compound motions to realize the compound motion of the rolling axis and the azimuth axis.
本发明的有益效果是:利用差动机构可以实现远距离传动,驱动马达采用对称布置,这样驱动马达安装在滚动轴和方位轴的末端,使滚动轴和方位轴的质量和尺寸都会大幅度减小,从而使转台结构紧凑,动态性能提升。The beneficial effects of the present invention are: the differential mechanism can be used to realize long-distance transmission, and the driving motors are arranged symmetrically, so that the driving motors are installed at the ends of the rolling shaft and the azimuth shaft, so that the quality and size of the rolling shaft and the azimuth shaft can be greatly reduced. Small, so that the structure of the turntable is compact and the dynamic performance is improved.
附图说明Description of drawings
图1为本发明整体效果图。Fig. 1 is the overall effect drawing of the present invention.
图2为本发明的主视图。Fig. 2 is a front view of the present invention.
图3为图2的A-A剖视图。Fig. 3 is a sectional view along line A-A of Fig. 2 .
图4为本发明的右视图。Fig. 4 is a right side view of the present invention.
图5为图4的B-B剖视图。Fig. 5 is a B-B sectional view of Fig. 4 .
图6为本发明的差动机构结构示意图。Fig. 6 is a structural schematic diagram of the differential mechanism of the present invention.
图中:1-俯仰防护罩一,2-吊环,3-上台面,4-俯仰机架,5-俯仰防护罩二,6-机座架,7-机座伺服电机,8-机座防护罩,9-机座蜗轮蜗杆减速器,10-机座深沟球轴承,11-机座减速器输出轴,12-机座小齿轮,13-机座偏心套,14-机座扇形齿轮,15-机座驱动轴端盖,16-机座驱动轴,17-机座驱动轴轴承,18-机座限位块,19-俯仰涨紧套一,20-俯仰限位块,21-俯仰涨紧套二,22-机座从动轴,23-机座从动轴轴承,24-机座从动轴端盖,25-配重块,26-机座装配孔端盖,27-俯仰小齿轮一,28-俯仰深沟球轴承,29-俯仰减速器输出轴一,30-俯仰大齿轮一,31-俯仰蜗轮蜗杆减速器一,32-俯仰偏心套一,33-俯仰伺服电机一,34-俯仰角接触轴承一,35-俯仰套杯一,36-俯仰套杯二,37-俯仰角接触轴承二,38-俯仰套杯二端盖,39-俯仰伺服电机二,40-俯仰偏心套二,41-俯仰蜗轮蜗杆减速器二,42-俯仰大齿轮二,43-俯仰减速器输出轴二,44-俯仰深沟球轴承二,45-俯仰小齿轮二,46-差动锥齿轮一,47-差动主力板,48-差动转台轴承一,49-差动隔套一,50-差动锥齿轮二,51-差动输出轴,52-差动套杯,53-差动角接触轴承,54-差动套杯端盖,55-差动转台轴承三,56-差动联轴件,57-差动辅助力板,58-差动转台轴承二,59-差动隔套二,60-差动驱动轴二,61-差动锥齿轮锁紧螺母,62-差动锥齿轮三,63-差动驱动轴一,64-差动封盖,I-俯仰轴,Ⅱ-滚动轴,Ⅲ-方位轴。In the figure: 1-pitch protective cover 1, 2-hanging ring, 3-upper table, 4-pitch frame, 5-pitch protective cover 2, 6-frame frame, 7-base servo motor, 8-base protection Cover, 9-base worm gear reducer, 10-base deep groove ball bearing, 11-base reducer output shaft, 12-base pinion, 13-base eccentric sleeve, 14-base sector gear, 15- End cover of machine base drive shaft, 16- Machine base drive shaft, 17- Machine base drive shaft bearing, 18- Machine base limit block, 19- Pitch tightening sleeve 1, 20- Pitch limit block, 21- Pitch Tightening sleeve 2, 22-driven shaft of machine base, 23-bearing of driven shaft of machine base, 24-end cover of driven shaft of machine base, 25-counterweight, 26-end cover of assembly hole of machine base, 27-pitch Pinion 1, 28-pitching deep groove ball bearing, 29-pitching reducer output shaft 1, 30-pitching large gear 1, 31-pitching worm gear reducer 1, 32-pitching eccentric sleeve 1, 33-pitching servo motor 1 , 34-pitching angular contact bearing 1, 35-pitching cup 1, 36-pitching cup 2, 37-pitching angular contact bearing 2, 38-pitching cup 2 end cover, 39-pitching servo motor 2, 40-pitching Eccentric sleeve 2, 41-pitch worm reducer 2, 42-pitch large gear 2, 43-output shaft 2 of pitch reducer, 44-pitch deep groove ball bearing 2, 45-pitch pinion 2, 46-differential cone Gear 1, 47-differential main force plate, 48-differential turntable bearing 1, 49-differential spacer 1, 50-differential bevel gear 2, 51-differential output shaft, 52-differential sleeve cup, 53- Differential angular contact bearing, 54-differential sleeve cup end cover, 55-differential turntable bearing three, 56-differential coupling shaft, 57-differential auxiliary force plate, 58-differential turntable bearing two, 59-differential Dynamic spacer 2, 60-differential drive shaft 2, 61-differential bevel gear lock nut, 62-differential bevel gear 3, 63-differential drive shaft 1, 64-differential cover, I-pitch shaft , Ⅱ-roll axis, Ⅲ-orientation axis.
具体实施方式Detailed ways
下面结合附图和实施例对本发明进行详细说明。The present invention will be described in detail below in conjunction with the accompanying drawings and embodiments.
本发明实施例的差动机构式三轴转台由三大部分组成,包括机座、俯仰部件组和差动部件组;由机座、俯仰部件组和差动部件组形成俯仰轴Ⅰ、滚动轴Ⅱ、方位轴Ⅲ三个转动轴系,参见图1;三个转动轴系用来实现目标负载的俯仰、滚动、方位转动,机座为负载提供一个安装基准。如图2、图3所示,俯仰机架4与机座之间一端通过俯仰涨紧套一19与机座驱动轴16固连,另一端通过俯仰涨紧套二21与机座从动轴22固连,构成绕俯仰轴Ⅰ转动支撑的动连接。另一方面,机座上的机座小齿轮12驱动固连在机座驱动轴16上的机座扇形齿轮14带动机座驱动轴16转动,从而实现俯仰机架4的±20度范围的俯仰运动。滚动和方位转动的实现方式,如图5、图6所示,这两个运动的实现用到了一个差动机构,该差动机构由差动锥齿轮一46、差动锥齿轮二50、差动锥齿轮三62构成,其中差动锥齿轮二50与上台面3固接并与差动锥齿轮一46和差动锥齿轮三62啮合,而差动锥齿轮一46、差动锥齿轮三62通过传动系统与两个驱动马达相连,形成差动机构。如图6所示,差动部件组左端通过差动转台轴承一48、差动隔套一49与俯仰机架4连接,构成绕滚动轴Ⅱ的转动支撑的动连接,同理差动部件组右端通过差动转台轴承二58、差动隔套二59与俯仰机架4连接,构成绕滚动轴Ⅱ的转动支撑的动连接。当差动锥齿轮一46与差动锥齿轮三62同速反向旋转时,上台面3绕方位轴Ⅲ作方位转动;当差动锥齿轮一46与差动锥齿轮三62同速同向旋转时上台面3绕滚动轴Ⅱ作滚转运动。正常工作时,滚动轴Ⅱ和方位轴Ⅲ的运动都是上述两种运动的组合。通过此差动机构,上台面3能实现±20度范围的滚动和±135度范围的方位转动。The differential mechanism type three-axis turntable of the embodiment of the present invention is composed of three major parts, including a machine base, a pitching component group and a differential component group; Ⅱ. Azimuth axis ⅢThree rotating shaft systems, see Figure 1; the three rotating shaft systems are used to realize the pitch, roll and azimuth rotation of the target load, and the machine base provides an installation reference for the load. As shown in Figure 2 and Figure 3, one end between the pitching frame 4 and the machine base is fixedly connected with the drive shaft 16 of the machine base through the first pitch tensioning sleeve 19, and the other end is connected with the driven shaft of the machine base through the second pitching tensioning sleeve 21. 22 are fixedly connected to form a dynamic connection around the pitch axis Ⅰ rotation support. On the other hand, the base pinion gear 12 on the base drives the base sector gear 14 fixedly connected to the base drive shaft 16 to drive the base drive shaft 16 to rotate, thereby realizing the pitch of the ±20 degree range of the pitch frame 4 sports. The implementation of rolling and azimuth rotation, as shown in Figure 5 and Figure 6, the realization of these two movements uses a differential mechanism, which is composed of differential bevel gear 1 46, differential bevel gear 2 50, differential bevel gear 2 Three differential bevel gears 62 are formed, in which the second differential bevel gear 50 is fixedly connected to the upper table 3 and meshes with the first differential bevel gear 46 and the third differential bevel gear 62, while the first differential bevel gear 46 and the third differential bevel gear 62 is connected with two driving motors through a transmission system to form a differential mechanism. As shown in Figure 6, the left end of the differential component group is connected to the pitch frame 4 through the differential turntable bearing 1 48 and the differential spacer 1 49 to form a dynamic connection of the rotation support around the rolling axis II. Similarly, the differential component group The right end is connected with the pitching frame 4 through the differential turntable bearing 2 58 and the differential spacer 2 59 to form a dynamic connection of the rotation support around the rolling axis II. When differential bevel gear 1 46 and differential bevel gear 3 62 rotate in opposite directions at the same speed, the upper table 3 rotates azimuthally around the azimuth axis III; when differential bevel gear 1 46 and differential bevel gear 3 62 rotate at the same speed When rotating, the upper table 3 makes a rolling motion around the rolling axis II. During normal operation, the movement of rolling axis II and azimuth axis III is a combination of the above two movements. Through this differential mechanism, the upper table 3 can realize rolling in the range of ±20 degrees and azimuth rotation in the range of ±135 degrees.
如图2、图3所示,机座伺服电机7与机座蜗轮蜗杆减速器9以串联的方式固连,机座小齿轮12装在机座蜗轮蜗杆减速器9输出端,机座蜗轮蜗杆减速器9用机座偏心套13固连在机座架6上,通过转动机座偏心套13的转角来调节机座小齿轮12和机座扇形齿轮14的中心距,从而消除圆柱齿轮啮合的齿侧间隙。机座驱动轴16用机座驱动轴轴承17和机座驱动轴端盖15连接在机座架6上,并与机座扇形齿轮14通过花键固连,与俯仰机架4通过俯仰涨紧套一19固连。机座从动轴22以机座从动轴轴承23和机座从动轴端盖24连接在机座架6上,并与俯仰机架4通过俯仰涨紧套二21固连。动力从机座伺服电机7输出,经过机座蜗轮蜗杆减速器9、机座减速器输出轴11、机座小齿轮12传递到机座扇形齿轮14,从而机座驱动轴16可以带动俯仰机架4实现俯仰运动。As shown in Fig. 2 and Fig. 3, the base servo motor 7 and the base worm gear reducer 9 are fixedly connected in series, the base pinion 12 is installed at the output end of the base worm gear reducer 9, and the base worm gear reducer 9 The reducer 9 is fixedly connected to the base frame 6 with the base eccentric sleeve 13, and the center distance between the base pinion gear 12 and the base sector gear 14 is adjusted by rotating the rotation angle of the base eccentric sleeve 13, thereby eliminating the meshing of cylindrical gears. Backlash. The base drive shaft 16 is connected to the base frame 6 with the base drive shaft bearing 17 and the base drive shaft end cover 15, and is fixedly connected with the base sector gear 14 through a spline, and is tightened with the pitch frame 4 by pitching. A set of 19 fixed connections. The machine base driven shaft 22 is connected on the machine base frame 6 with the machine base driven shaft bearing 23 and the machine base driven shaft end cover 24, and is fixedly connected with the pitch frame 4 through the pitch tensioner sleeve 2 21 . The power is output from the base servo motor 7, and is transmitted to the base sector gear 14 through the base worm gear reducer 9, the base reducer output shaft 11, and the base pinion 12, so that the base drive shaft 16 can drive the pitch frame 4 Realize pitching motion.
如图4、图5所示,俯仰部件组由俯仰防护罩一1,俯仰机架4,俯仰防护罩二5,俯仰涨紧套一19,俯仰限位块20,俯仰涨紧套二21,俯仰小齿轮一27,俯仰深沟球轴承28,俯仰减速器输出轴一29,俯仰大齿轮一30,俯仰蜗轮蜗杆减速器一31,俯仰偏心套一32,俯仰伺服电机一33,俯仰角接触轴承一34,俯仰套杯一35,俯仰套杯二36,俯仰角接触轴承二37,俯仰套杯二端盖38,俯仰伺服电机二39,俯仰偏心套二40,俯仰蜗轮蜗杆减速器二41,俯仰大齿轮二42,俯仰减速器输出轴二43,俯仰深沟球轴承二44,俯仰小齿轮二45组成。如图5右端所示,俯仰伺服电机二39与俯仰蜗轮蜗杆减速器二41以串联的方式固连,俯仰小齿轮二45装在俯仰蜗轮蜗杆减速器二41输出端,俯仰蜗轮蜗杆减速器二41用俯仰偏心套二40固连在俯仰机架4上,通过转动俯仰偏心套二40的转角来调节俯仰小齿轮二45与俯仰大齿轮二42的中心距,从而消除圆柱齿轮啮合的齿侧间隙。俯仰套杯二36,俯仰角接触轴承二37,俯仰套杯二端盖38与差动驱动轴二60构成转动支撑的动连接,俯仰大齿轮二42用花键固连在差动驱动轴二60上。动力从俯仰伺服电机二39输出,经过俯仰蜗轮蜗杆减速器二41、俯仰减速器输出轴二43通过俯仰小齿轮二45驱动俯仰大齿轮二42,从而驱动差动锥齿轮三62转动。同理,如图5左端所示,俯仰伺服电机一33与俯仰蜗轮蜗杆减速器一31以串联的方式固连,俯仰小齿轮一27装在俯仰蜗轮蜗杆减速器一31输出端,俯仰蜗轮蜗杆减速器一31用俯仰偏心套一32固连在俯仰机架4上,通过转动俯仰偏心套一32的转角来调节俯仰小齿轮一27与俯仰大齿轮一30的中心距,从而消除圆柱齿轮啮合的齿侧间隙。俯仰套杯一35,俯仰角接触轴承一34,与差动驱动轴一63构成转动支撑的动连接,俯仰大齿轮一30用花键固连在差动驱动轴一63上。动力从俯仰伺服电机一33输出,经过俯仰蜗轮蜗杆减速器一31、俯仰减速器输出轴一29通过俯仰小齿轮一27驱动仰大齿轮一30,从而驱动差动锥齿轮一46转动。As shown in Fig. 4 and Fig. 5, the pitch component group consists of a pitch protective cover 1, a pitch frame 4, a pitch protective cover 2 5, a pitch tightening sleeve 19, a pitch limit block 20, a pitch tightening sleeve 2 21, Pitching pinion gear 127, pitching deep groove ball bearing 28, pitching reducer output shaft 129, pitching gear 130, pitching worm gear reducer 131, pitching eccentric sleeve 132, pitching servo motor 133, pitching angle contact Bearing 1 34, pitch cup 1 35, pitch cup 2 36, pitch angular contact bearing 2 37, pitch cup 2 end cover 38, pitch servo motor 2 39, pitch eccentric sleeve 2 40, pitch worm reducer 2 41 , Pitch gear two 42, pitch reducer output shaft two 43, pitch deep groove ball bearing two 44, pitch pinion two 45 and form. As shown in the right end of Figure 5, the pitching servo motor 2 39 is connected in series with the pitching worm gear reducer 2 41, the pitching pinion 2 45 is installed at the output end of the pitching worm gear reducer 41, and the pitching worm gear reducer 2 41 Use the pitch eccentric sleeve 2 40 to be fixedly connected to the pitch frame 4, and adjust the center distance between the pitch pinion gear 2 45 and the pitch gear 2 42 by rotating the rotation angle of the pitch eccentric sleeve 2 40, so as to eliminate the meshing tooth side of the cylindrical gear gap. The pitching cup 2 36, the pitching angular contact bearing 2 37, the pitching cup 2 end cover 38 and the differential drive shaft 60 form a dynamic connection for the rotation support, and the pitching gear 2 42 is fixedly connected to the differential drive shaft 2 with splines. 60 on. The power is output from the pitch servo motor 2 39, through the pitch worm gear reducer 2 41, the pitch reducer output shaft 2 43 drives the pitch gear 2 42 through the pitch pinion 2 45, thereby driving the differential bevel gear 3 62 to rotate. Similarly, as shown in the left end of Fig. 5, the pitching servo motor one 33 is connected in series with the pitching worm gear reducer one 31, the pitching pinion one 27 is installed at the output end of the pitching worm gear reducer one 31, and the pitching worm gear Reducer 1 31 is fixedly connected to pitch frame 4 with pitch eccentric sleeve 1 32, and the center distance between pitch pinion 1 27 and pitch gear 1 30 is adjusted by turning the angle of pitch eccentric sleeve 1 32, thereby eliminating cylindrical gear meshing tooth backlash. Pitch cover cup one 35, pitch angular contact bearing one 34, and differential drive shaft one 63 form the dynamic connection of rotation support, and pitch gear one 30 is fixedly connected on the differential drive shaft one 63 with spline. The power is output from the pitch servo motor-33, through the pitch worm gear reducer-31, the output shaft of the pitch reducer-29 drives the pitch gear-30 through the pitch pinion-27, thereby driving the differential bevel gear-46 to rotate.
如图5、图6所示,所述的差动部件组由上台面3,差动锥齿轮一46,差动主力板47,差动转台轴承一48,差动隔套一49,差动锥齿轮二50,差动输出轴51,差动套杯52,差动角接触轴承53,差动套杯端盖54,差动转台轴承三55,差动联轴件56,差动辅助力板57,差动转台轴承二58,差动隔套二59,差动驱动轴二60,差动锥齿轮锁紧螺母61,差动锥齿轮三62,差动驱动轴一63,差动封盖64组成。差动锥齿轮一46、差动锥齿轮三62轴线重合水平布置,用花键分别连接在差动驱动轴一63、差动驱动轴二60上,并用差动锥齿轮锁紧螺母61锁紧,其转动支撑和驱动由俯仰轴Ⅰ部件组提供。差动锥齿轮二50轴线与差动锥齿轮一46和差动锥齿轮三62轴线垂直,并用花键和差动锥齿轮锁紧螺母61与差动输出轴51一端连接。差动输出轴51以差动套杯52、差动角接触轴承53、差动套杯端盖54连接在差动主力板47,构成转动支撑的可动连接。差动输出轴51另一端以花键和差动联轴件56连接,上台面3用螺栓固定在差动联轴件56上,从而差动锥齿轮二50的转动可以带动上台面3的运动。差动部件组绕滚动轴Ⅱ的转动支撑由左端的差动转台轴承一48和差动隔套一49,右端的差动转台轴承二58和差动隔套二59与俯仰机架4分别组成的可动连接提供。上台面绕方位轴Ⅲ的转动支撑由连接在差动联轴件56与差动主力板47之间的差动转台轴承三55提供。As shown in Fig. 5 and Fig. 6, the differential component group is composed of upper table 3, differential bevel gear 1 46, differential main force plate 47, differential turntable bearing 1 48, differential spacer 1 49, differential Bevel gear 2 50, differential output shaft 51, differential sleeve cup 52, differential angular contact bearing 53, differential sleeve end cover 54, differential turntable bearing 3 55, differential coupling 56, differential auxiliary force Plate 57, differential turntable bearing 2 58, differential spacer 2 59, differential drive shaft 2 60, differential bevel gear lock nut 61, differential bevel gear 3 62, differential drive shaft 1 63, differential seal The cover 64 is composed. Differential bevel gear 1 46 and differential bevel gear 3 62 are arranged horizontally on overlapping axes, respectively connected to differential drive shaft 1 63 and differential drive shaft 2 60 with splines, and locked with differential bevel gear lock nut 61 , its rotation support and drive are provided by the pitch axis I component group. The axis of differential bevel gear two 50 is perpendicular to the axes of differential bevel gear one 46 and differential bevel gear three 62, and is connected with one end of differential output shaft 51 with splines and differential bevel gear lock nut 61. The differential output shaft 51 is connected to the differential main force plate 47 by a differential sleeve cup 52 , a differential angular contact bearing 53 , and a differential sleeve end cover 54 , forming a movable connection for rotational support. The other end of the differential output shaft 51 is connected to the differential coupling 56 with a spline, and the upper table 3 is fixed on the differential coupling 56 with bolts, so that the rotation of the differential bevel gear 2 50 can drive the movement of the upper table 3 . The rotation support of the differential components around the rolling shaft II is composed of the differential turntable bearing 1 48 and the differential spacer 1 49 at the left end, the differential turntable bearing 2 58 and the differential spacer 59 at the right end, and the pitch frame 4 respectively The movable connection is provided. The rotation support of the upper table around the azimuth axis III is provided by the differential turntable bearing 3 55 connected between the differential coupling 56 and the differential main force plate 47 .
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