CN110030360A - A kind of design method of gear wheel reversing mechanism and its gear pair - Google Patents
A kind of design method of gear wheel reversing mechanism and its gear pair Download PDFInfo
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H55/0806—Involute profile
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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
- 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
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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Abstract
本发明公开了一种齿轮换向机构和其齿轮副设计方法，包括：输入轴，其用于接收动力；第一传动轴、第二传动轴和输出轴，其与输入轴平行设置；第一主动非圆齿轮和第二主动非圆齿轮，其设置在输入轴上；第一从动非圆齿轮和第二从动非圆齿轮，其分别设于第二传动轴和第一传动轴上，且其配置为分别适于与第一主动非圆齿轮和第二主动非圆齿轮相啮合；以及第一圆柱齿轮、第二圆柱齿轮和第三圆柱齿轮，其分别设置在第一传动轴、第二传动轴和输出轴上，且第二圆柱齿轮、第三圆柱齿轮分别与第一圆柱齿轮相啮合；该齿轮换向机构能够以减少抽油过程中的漏油量，增加单位时间内的产量；该方法简单可靠，具有灵活可调的设计参数，提高了非圆齿轮副设计的灵活性。
The invention discloses a gear reversing mechanism and a method for designing a gear pair thereof, comprising: an input shaft, which is used for receiving power; a first transmission shaft, a second transmission shaft and an output shaft, which are arranged in parallel with the input shaft; The driving non-circular gear and the second driving non-circular gear are arranged on the input shaft; the first driven non-circular gear and the second driven non-circular gear are respectively arranged on the second transmission shaft and the first transmission shaft, And it is configured to be respectively suitable for meshing with the first driving non-circular gear and the second driving non-circular gear; and the first cylindrical gear, the second cylindrical gear and the third cylindrical gear, which are respectively arranged on the first transmission shaft, the on the second drive shaft and the output shaft, and the second spur gear and the third spur gear mesh with the first spur gear respectively; the gear reversing mechanism can reduce the oil leakage during the oil pumping process and increase the output per unit time. ; The method is simple and reliable, has flexible and adjustable design parameters, and improves the flexibility of non-circular gear pair design.
Description
技术领域technical field
本发明涉及抽油机设备领域，尤其涉及一种用于抽油机的齿轮换向机构和其齿轮副的设计方法。The invention relates to the field of pumping unit equipment, in particular to a design method of a gear reversing mechanism for an oil pumping unit and a gear pair thereof.
背景技术Background technique
由于传统游梁式抽油机运行能耗高，惯性大，振动冲击大，运行不稳定，安全隐患大，难以实现长冲程抽油；在此基础上人们又研究出了立式抽油机，采用电机变频换向，解决了上述大部分问题，但仍有故障率高，能耗大，电气维护难度大的不足；在此基础上人们又研究了效率高、换向可靠的非圆齿轮抽油机。受异相型游梁式抽油机的启发，可以通过单独改变上下冲程的平均速度来提高效率，但单层非圆齿轮要实现上下行程相等必须保证其对称性，由于输入轴的转速恒定，所以上下冲程的平均速度相同。但试验表明，使上冲程的平均速度略大于下冲程的平均速度可以减少抽油过程中的漏油量，增加其单位时间内的产量，而上述已论证单层非圆齿轮无法满足改进需求。Due to the high energy consumption of traditional beam pumping units, large inertia, large vibration and impact, unstable operation, and great safety hazards, it is difficult to achieve long-stroke oil pumping; on this basis, people have developed vertical pumping units, The use of motor frequency conversion commutation solves most of the above problems, but there are still problems such as high failure rate, high energy consumption, and difficult electrical maintenance; on this basis, people have studied non-circular gear pumping with high efficiency and reliable commutation. oil machine. Inspired by the out-of-phase beam pumping unit, the efficiency can be improved by changing the average speed of the upper and lower strokes separately, but the symmetry of the single-layer non-circular gear to achieve equal upper and lower strokes must be ensured. Since the speed of the input shaft is constant, So the average speed for the up and down strokes is the same. However, the test shows that making the average speed of the upper stroke slightly larger than the average speed of the lower stroke can reduce the oil leakage during the pumping process and increase the output per unit time, while the above-mentioned single-layer non-circular gear can not meet the improvement needs.
发明内容SUMMARY OF THE INVENTION
本发明旨在至少解决上述现有技术存在的问题之一，本发明的一个目的在于提出了一种齿轮换向机构，该齿轮换向机构能够改变上冲程与下冲程的平均速度，以减少抽油过程中的漏油量，增加单位时间内的产量，而且结构简单，安全可靠。The present invention aims to solve at least one of the above-mentioned problems in the prior art. One object of the present invention is to provide a gear reversing mechanism, which can change the average speed of the upper stroke and the lower stroke to reduce pumping The oil leakage in the oil process increases the output per unit time, and the structure is simple, safe and reliable.
本发明的另一个目的在于提出一种上述齿轮换向机构所具有的非圆齿轮副的设计方法。Another object of the present invention is to provide a design method for the non-circular gear pair of the above-mentioned gear reversing mechanism.
根据本发明第一方面的一种齿轮换向机构，包括：输入轴，其用于接收动力；第一传动轴、第二传动轴和输出轴，其与所述输入轴平行设置；第一主动非圆齿轮和第二主动非圆齿轮，其设置在输入轴上；第一从动非圆齿轮和第二从动非圆齿轮，其分别设于第二传动轴和第一传动轴上，且其配置为分别适于与第一主动非圆齿轮和第二主动非圆齿轮相啮合；以及第一圆柱齿轮、第二圆柱齿轮和第三圆柱齿轮，其分别设置在第一传动轴、第二传动轴和输出轴上，且第二圆柱齿轮、第三圆柱齿轮分别与所述第一圆柱齿轮相啮合，其中，所述输入轴转动一周过程中，依次进行上冲程阶段和下冲程阶段，当处于上冲程阶段，所述第二主动非圆齿轮与第二从动非圆齿轮相啮合；当处于下冲程阶段，所述第一主动非圆齿轮与第一从动非圆齿轮相啮合，且在此过程中所述第二从动非圆齿轮与所述第一从动非圆齿轮的所转过的角度相等。A gear reversing mechanism according to the first aspect of the present invention includes: an input shaft for receiving power; a first transmission shaft, a second transmission shaft and an output shaft, which are arranged in parallel with the input shaft; a first drive shaft The non-circular gear and the second driving non-circular gear are arranged on the input shaft; the first driven non-circular gear and the second driven non-circular gear are respectively arranged on the second transmission shaft and the first transmission shaft, and It is configured to be respectively suitable for meshing with the first driving non-circular gear and the second driving non-circular gear; and the first cylindrical gear, the second cylindrical gear and the third cylindrical gear, which are respectively arranged on the first transmission shaft, the second On the transmission shaft and the output shaft, and the second cylindrical gear and the third cylindrical gear are meshed with the first cylindrical gear respectively, wherein, in the process of one rotation of the input shaft, the upper stroke stage and the lower stroke stage are performed in sequence, when In the up-stroke stage, the second driving non-circular gear meshes with the second driven non-circular gear; when in the down-stroke stage, the first driving non-circular gear meshes with the first driven non-circular gear, and During this process, the rotation angles of the second driven non-circular gear and the first driven non-circular gear are equal.
在该技术方案中，第二主动非圆齿轮从逆时针旋转并开始与第二从动非圆齿轮的有齿部分啮合，同时与第二从动非圆齿轮同轴连接的第一圆柱齿轮开始做顺时针旋转，与第一圆柱齿轮啮合的第二圆柱齿轮以及与第二圆柱齿轮同轴设置的第一从动非圆齿轮做逆时针旋转，当第二主动非圆齿轮与第二从动非圆齿轮啮合并逆时针继续旋转至一定角度时，第一传动轴以及其上的第二从动非圆齿轮和第一圆柱齿轮顺时针旋转了一次，第二传动轴以及其上的第一从动非圆齿轮和第二圆柱齿轮逆时针旋转了一次，此时第二主动非圆齿轮与第二从动非圆齿轮刚好脱开，第一主动非圆齿轮与第一从动非圆齿轮刚好啮合，即完成了一个上冲程；第一主动非圆齿轮继续逆时针旋转并开始与从第一动非圆齿轮的有齿部分啮合，第一从动非圆齿轮与同轴连接的第二圆柱齿轮开始做顺时针旋转，与第二圆柱齿轮啮合的第一圆柱齿轮以及与第一圆柱齿轮同轴的第一从动非圆齿轮做逆时针旋转，当第一主动非圆齿轮与第一从动非圆齿轮啮合并逆时针继续旋转至一定角度时，第一传动轴以及其上的第一从动非圆齿轮和第二圆柱齿轮顺时针旋转了一次，第一传动轴以及其上的第二从动非圆齿轮和第一圆柱齿轮逆时针旋转了一次，此时第一主动非圆齿轮与第一从动非圆齿轮刚好脱开，第二主动非圆齿轮与第二从动非圆齿轮重新啮合，此时完成了一个下冲程，至此一个完整的抽油过程结束，然后进行下一个抽油循环。In this technical solution, the second driving non-circular gear rotates counterclockwise and starts to mesh with the toothed portion of the second driven non-circular gear, while the first cylindrical gear coaxially connected with the second driven non-circular gear starts from Rotate clockwise, the second cylindrical gear meshing with the first cylindrical gear and the first driven non-circular gear arranged coaxially with the second cylindrical gear rotate counterclockwise, when the second driving non-circular gear and the second driven When the non-circular gear meshes and continues to rotate counterclockwise to a certain angle, the first transmission shaft and the second driven non-circular gear and the first cylindrical gear on it rotate clockwise once, and the second transmission shaft and the first The driven non-circular gear and the second cylindrical gear rotate counterclockwise once, at this time, the second driving non-circular gear and the second driven non-circular gear are just disengaged, and the first driving non-circular gear and the first driven non-circular gear are Just meshing, that is, an upstroke is completed; the first driving non-circular gear continues to rotate counterclockwise and starts to mesh with the toothed part of the first driven non-circular gear, and the first driven non-circular gear is coaxially connected to the second non-circular gear. The cylindrical gear starts to rotate clockwise, the first cylindrical gear meshing with the second cylindrical gear and the first driven non-circular gear coaxial with the first cylindrical gear rotate counterclockwise. When the driven non-circular gear meshes and continues to rotate counterclockwise to a certain angle, the first transmission shaft and the first driven non-circular gear and the second cylindrical gear on it rotate clockwise once, and the first transmission shaft and the The second driven non-circular gear and the first cylindrical gear rotate counterclockwise once. At this time, the first driving non-circular gear and the first driven non-circular gear are just disengaged, and the second driving non-circular gear and the second driven non-circular gear are just disengaged. The circular gear is re-engaged, and a downstroke is completed at this time, and a complete pumping process is completed, and then the next pumping cycle is performed.
另外，根据本发明的齿轮换向机构，还可以具有如下技术特征：In addition, the gear reversing mechanism according to the present invention may also have the following technical features:
进一步地，所述第一主动非圆齿轮和第二主动非圆齿轮的节曲线均包括无齿区、匀速区和两个对称设置的变速区。Further, the pitch curves of the first driving non-circular gear and the second driving non-circular gear each include a toothless area, a uniform speed area and two symmetrically arranged speed change areas.
进一步地，所述第一主动非圆齿轮无齿区的角度大于所述第二主动非圆齿轮无齿区的角度。Further, the angle of the toothless area of the first driving non-circular gear is greater than the angle of the toothless area of the second driving non-circular gear.
优选地，所述第一主动非圆齿轮的无齿区为195°，所述变速区为60°以及所述匀速区为45°。Preferably, the toothless area of the first driving non-circular gear is 195°, the speed change area is 60° and the constant speed area is 45°.
优选地，所述第二主动非圆齿轮的无齿区为165°，所述变速区为60°以及所述匀速区为75°。Preferably, the toothless area of the second driving non-circular gear is 165°, the speed change area is 60° and the constant speed area is 75°.
优选地，所述第一主动非圆齿轮同与之相啮合的第一从动非圆齿轮在初始啮合时，所述第一主动非圆齿轮与第一从动非圆齿轮的中心连线与所述第一主动非圆齿轮的对称轴线的夹角为87.5°；所述第二主动非圆齿轮同与之相啮合的第二从动非圆齿轮在初始啮合时，所述第二主动非圆齿轮与第二从动非圆齿轮的中心连线与所述第二主动非圆齿轮的对称轴线的夹角为87.5°。Preferably, when the first driving non-circular gear and the first driven non-circular gear meshing with it are initially meshed, the center line connecting the first driving non-circular gear and the first driven non-circular gear and the first driven non-circular gear The included angle of the symmetry axis of the first driving non-circular gear is 87.5°; when the second driving non-circular gear is initially meshed with the second driven non-circular gear meshing with it, the second driving non-circular gear is initially meshed with the second driving non-circular gear. The included angle between the center line connecting the circular gear and the second driven non-circular gear and the symmetry axis of the second driving non-circular gear is 87.5°.
根据本发明第二方面的一种非圆齿轮副的设计方法，包括如下步骤：A method for designing a non-circular gear pair according to the second aspect of the present invention includes the following steps:
S10：根据非圆齿轮的节曲线变化规律以及结合主动非圆齿轮同与之相啮合的从动非圆齿轮在啮合过程中需要满足减速、匀速和加速的运动过程设计传动比i；S10: Design the transmission ratio i according to the change rule of the pitch curve of the non-circular gear and the driven non-circular gear that meshes with the driving non-circular gear and needs to satisfy the motion process of deceleration, uniform speed and acceleration during the meshing process;
S20：根据传动比i和主动非圆齿轮与从动非圆齿轮的中心距a计算主动非圆齿轮的半径r1，并在极坐标下形成主动非圆齿轮的节曲线，其中，S20: Calculate the radius r1 of the driving non-circular gear according to the transmission ratio i and the center distance a between the driving non-circular gear and the driven non-circular gear, and form the pitch curve of the driving non-circular gear in polar coordinates, wherein,
所述主动非圆齿轮的半径满足以下公式：The radius of the driving non-circular gear satisfies the following formula:
其中，a为主动非圆齿轮与从动非圆齿轮的中心距；Among them, a is the center distance between the driving non-circular gear and the driven non-circular gear;
S30：根据主动非圆齿轮与从动非圆齿轮的中心距a和主动非圆齿轮的半径r1得出所述从动非圆齿轮的半径r2,并在极坐标下形成所述从动非圆齿轮的节曲线。S30: Obtain the radius r 2 of the driven non-circular gear according to the center distance a between the driving non-circular gear and the driven non-circular gear and the radius r 1 of the driving non-circular gear, and form the driven non-circular gear in polar coordinates Pitch curves of non-circular gears.
优选地，减速区和匀速区之间以及匀速区与加速区之间还设置过渡区。Preferably, transition zones are also provided between the deceleration zone and the constant velocity zone and between the constant velocity zone and the acceleration zone.
优选地，所述主动非圆齿轮同与之相啮合的从动非圆齿轮的传动比i满足以下公式：Preferably, the transmission ratio i of the driving non-circular gear and the driven non-circular gear meshing with it satisfies the following formula:
其中，为主动非圆齿轮节曲线对应的角度，i为传动比，β为匀速区的角度，第一主动非圆齿轮取45°，第二主动非圆齿轮取75°，A为最大传动比，B为最小传动比，m为传动比过渡因子，取0.5；且 in, is the angle corresponding to the pitch curve of the driving non-circular gear, i is the transmission ratio, β is the angle of the uniform speed area, the first driving non-circular gear is 45°, the second driving non-circular gear is 75°, A is the maximum transmission ratio, B is the minimum transmission ratio, m is the transmission ratio transition factor, which is taken as 0.5; and
根据本发明的一种非圆齿轮副的设计方法，该方法简单可靠，具有灵活可调的设计参数，提高了非圆齿轮副设计的灵活性。According to a method for designing a non-circular gear pair of the present invention, the method is simple and reliable, has flexible and adjustable design parameters, and improves the flexibility of designing a non-circular gear pair.
附图说明Description of drawings
图1为齿轮换向机构的主视图；Figure 1 is a front view of the gear reversing mechanism;
图2为图1的立体图；Fig. 2 is the perspective view of Fig. 1;
图3为第一主动非圆齿轮的结构示意图；3 is a schematic structural diagram of a first driving non-circular gear;
图4为第二主动非圆齿轮的结构示意图；4 is a schematic structural diagram of a second driving non-circular gear;
图5为主动非圆齿轮节曲线的结构示意图；Fig. 5 is the structural schematic diagram of the active non-circular gear pitch curve;
图6为引入过渡区的主动非圆齿轮节曲线的结构示意图。FIG. 6 is a schematic structural diagram of the pitch curve of the driving non-circular gear introduced into the transition area.
图中:齿轮换向机构100；输入轴1；第一主动非圆齿轮11；第二主动非圆齿轮12；第一传动轴2；第二从动非圆齿轮21；第一圆柱齿轮22；第二传动轴3；第一从动非圆齿轮31；第二圆柱齿轮32；输出轴4；第三圆柱齿轮41；对称轴线O；无齿区A；减速区B；匀速区C；加速区D。In the figure: gear reversing mechanism 100; input shaft 1; first driving non-circular gear 11; second driving non-circular gear 12; first transmission shaft 2; second driven non-circular gear 21; first cylindrical gear 22; The second transmission shaft 3; the first driven non-circular gear 31; the second cylindrical gear 32; the output shaft 4; the third cylindrical gear 41; the symmetry axis O; D.
具体实施方式Detailed ways
下面结合附图对本发明作进一步说明。The present invention will be further described below in conjunction with the accompanying drawings.
参考附图提供以下描述，以助于对权利要求所限定的本发明的各种实施例的全面理解。其包含各种特定的细节以助于该理解，但这些细节应当被视为仅是示范性的。相应地，本领域普通技术人员将认识到，在不背离由随附的权利要求所限定的本发明的范围的情况下，可以对本文所描述的各种实施例做出变化和改进。此外，为了清楚和简洁起见，可能省略对熟知的功能和构造的描述。The following description, with reference to the accompanying drawings, is provided to assist in a comprehensive understanding of various embodiments of the invention as defined by the claims. It contains various specific details to assist in this understanding, but these should be regarded as exemplary only. Accordingly, those of ordinary skill in the art will recognize that changes and modifications of the various embodiments described herein can be made without departing from the scope of the invention, which is defined by the appended claims. Also, descriptions of well-known functions and constructions may be omitted for clarity and conciseness.
对本领域技术人员显而易见的是，提供对本发明的各种实施例的下列描述，仅是为了解释的目的，而不是为了限制由随附的权利要求所限定的本发明。It will be apparent to those skilled in the art that the following description of various embodiments of the present invention is provided for purposes of explanation only and not for the purpose of limiting the invention as defined by the appended claims.
根据本发明第一方面的一种齿轮换向机构100，如图1、图2所示，包括：输入轴1，其用于接收动力；第一传动轴2、第二传动轴3和输出轴4，其与所述输入轴1平行设置；第一主动非圆齿轮11和第二主动非圆齿轮12，其设置在输入轴1上；第一从动非圆齿轮31和第二从动非圆齿轮21，其分别设于第二传动轴3和第一传动轴2上，且其配置为分别适于与第一主动非圆齿轮11和第二主动非圆齿轮12相啮合；以及第一圆柱齿轮22、第二圆柱齿轮32和第三圆柱齿轮41，其分别设置在第一传动轴2、第二传动轴3和输出轴4上，且第二圆柱齿轮32、第三圆柱齿轮41分别与所述第一圆柱齿轮22相啮合，在本发明中第一圆柱齿轮22和第二圆柱齿轮32的模数和齿数相同，即连个齿轮结构一样；其中，所述输入轴1转动一周过程中，依次进行上冲程阶段和下冲程阶段，当处于上冲程阶段，所述第二主动非圆齿轮12与第二从动非圆齿轮21相啮合；当处于下冲程阶段，所述第一主动非圆齿轮11与第一从动非圆齿轮31相啮合，且在此过程中所述第二从动非圆齿轮21与所述第一从动非圆齿轮31的所转过的角度相等。A gear reversing mechanism 100 according to the first aspect of the present invention, as shown in FIGS. 1 and 2 , includes: an input shaft 1 for receiving power; a first transmission shaft 2 , a second transmission shaft 3 and an output shaft 4. It is arranged in parallel with the input shaft 1; the first driving non-circular gear 11 and the second driving non-circular gear 12 are arranged on the input shaft 1; the first driven non-circular gear 31 and the second driven non-circular gear 12; The circular gears 21 are respectively arranged on the second transmission shaft 3 and the first transmission shaft 2, and are configured to be respectively adapted to engage with the first driving non-circular gear 11 and the second driving non-circular gear 12; and the first The spur gear 22, the second spur gear 32 and the third spur gear 41 are respectively arranged on the first transmission shaft 2, the second transmission shaft 3 and the output shaft 4, and the second spur gear 32 and the third spur gear 41 are respectively Meshing with the first cylindrical gear 22, in the present invention, the module and the number of teeth of the first cylindrical gear 22 and the second cylindrical gear 32 are the same, that is, the structure of the two gears is the same; wherein, the input shaft 1 rotates for one cycle. In the process, the upper stroke stage and the lower stroke stage are performed in sequence. When in the upper stroke stage, the second driving non-circular gear 12 meshes with the second driven non-circular gear 21; when in the down stroke stage, the first driving The non-circular gear 11 meshes with the first driven non-circular gear 31 , and the second driven non-circular gear 21 and the first driven non-circular gear 31 rotate at the same angle during this process.
在该技术方案中，第二主动非圆齿轮12从逆时针旋转并开始与第二从动非圆齿轮21的有齿部分啮合，同时与第二从动非圆齿轮21同轴连接的第一圆柱齿轮22开始做顺时针旋转，与第一圆柱齿轮22啮合的第二圆柱齿轮32以及与第二圆柱齿轮32同轴设置的第一从动非圆齿轮31做逆时针旋转，当第二主动非圆齿轮12与第二从动非圆齿轮21啮合并逆时针继续旋转至一定角度时，第一传动轴2以及其上的第二从动非圆齿轮21和第一圆柱齿轮22顺时针旋转了一次，第二传动轴3以及其上的第一从动非圆齿轮31和第二圆柱齿轮32逆时针旋转了一次，此时第二主动非圆齿轮12与第二从动非圆齿轮21刚好脱开，第一主动非圆齿轮11与第一从动非圆齿轮31刚好啮合，即完成了一个上冲程；第一主动非圆齿轮11继续逆时针旋转并开始与从第一动非圆齿轮的有齿部分啮合，第一从动非圆齿轮31与同轴连接的第二圆柱齿轮32开始做顺时针旋转，与第二圆柱齿轮32啮合的第一圆柱齿轮22以及与第一圆柱齿轮22同轴的第一从动非圆齿轮31做逆时针旋转，当第一主动非圆齿轮11与第一从动非圆齿轮31啮合并逆时针继续旋转至一定角度时，第一传动轴2以及其上的第一从动非圆齿轮31和第二圆柱齿轮32顺时针旋转了一次，第一传动轴2以及其上的第二从动非圆齿轮21和第一圆柱齿轮22逆时针旋转了一次，此时第一主动非圆齿轮11与第一从动非圆齿轮31刚好脱开，第二主动非圆齿轮12与第二从动非圆齿轮21重新啮合，此时完成了一个下冲程，至此一个完整的抽油过程结束，然后进行下一个抽油循环。In this technical solution, the second driving non-circular gear 12 rotates counterclockwise and starts to mesh with the toothed portion of the second driven non-circular gear 21 , and at the same time the first driven non-circular gear 21 is coaxially connected The cylindrical gear 22 starts to rotate clockwise, the second cylindrical gear 32 meshing with the first cylindrical gear 22 and the first driven non-circular gear 31 coaxially arranged with the second cylindrical gear 32 rotate counterclockwise. When the non-circular gear 12 meshes with the second driven non-circular gear 21 and continues to rotate counterclockwise to a certain angle, the first transmission shaft 2 and the second driven non-circular gear 21 and the first cylindrical gear 22 thereon rotate clockwise. Once, the second transmission shaft 3 and the first driven non-circular gear 31 and the second cylindrical gear 32 thereon rotate counterclockwise once, at this time the second driving non-circular gear 12 and the second driven non-circular gear 21 Just disengaged, the first driving non-circular gear 11 is just meshed with the first driven non-circular gear 31, that is, an upward stroke is completed; The toothed part of the gear meshes, the first driven non-circular gear 31 and the coaxially connected second cylindrical gear 32 start to rotate clockwise, the first cylindrical gear 22 meshing with the second cylindrical gear 32 and the first cylindrical gear 22 The coaxial first driven non-circular gear 31 rotates counterclockwise, when the first driving non-circular gear 11 meshes with the first driven non-circular gear 31 and continues to rotate counterclockwise to a certain angle, the first transmission shaft 2 And the first driven non-circular gear 31 and the second cylindrical gear 32 thereon rotate clockwise once, and the first transmission shaft 2 and the second driven non-circular gear 21 and the first cylindrical gear 22 on it rotate counterclockwise. At this time, the first driving non-circular gear 11 is just disengaged from the first driven non-circular gear 31, and the second driving non-circular gear 12 and the second driven non-circular gear 21 are re-engaged. stroke, so far a complete pumping process is over, and then the next pumping cycle is performed.
进一步地，如图3、图4所示，所述第一主动非圆齿轮11和第二主动非圆齿轮12的节曲线均包括无齿区A、匀速区C和两个对称设置的变速区；具体地，第一主动非圆齿轮11、第二主动非圆齿轮12均依次包括无齿区A、减速区B、匀速区C和加速区D，减速区B和加速区D共同形成变速区，且沿着第一主动非圆齿轮11或者第二主动非圆齿轮12的对称轴线O分布设置。Further, as shown in FIG. 3 and FIG. 4 , the pitch curves of the first driving non-circular gear 11 and the second driving non-circular gear 12 include a toothless area A, a uniform speed area C and two symmetrically arranged speed change areas. Specifically, the first driving non-circular gear 11 and the second driving non-circular gear 12 all include a toothless zone A, a deceleration zone B, a uniform speed zone C and an acceleration zone D in turn, and the deceleration zone B and the acceleration zone D jointly form a speed change zone , and are distributed along the symmetry axis O of the first driving non-circular gear 11 or the second driving non-circular gear 12 .
进一步地，所述第一主动非圆齿轮11无齿区A的角度大于所述第二主动非圆齿轮12无齿区A的角度，也就是说，第一主动非圆齿轮11以及与之相啮合的第一从动非圆齿轮31所形成的齿轮副完成上冲程阶段；而第二主动非圆齿轮12以及与之相啮合的第二从动非圆齿轮21所形成的齿轮副完成下冲程阶段，为了使得上冲程的平均角速度大于下冲程的角速度，故而在设计主动非圆齿轮时，将第一主动非圆齿轮11的无齿区A的角度要大于第二主动非圆齿轮12无齿区A的角度。Further, the angle of the toothless area A of the first driving non-circular gear 11 is greater than the angle of the toothless area A of the second driving non-circular gear 12, that is to say, the first driving non-circular gear 11 and its relative The gear pair formed by the meshed first driven non-circular gear 31 completes the upstroke stage; while the gear pair formed by the second driving non-circular gear 12 and the meshed second driven non-circular gear 21 completes the downstroke In order to make the average angular velocity of the upper stroke greater than the angular velocity of the lower stroke, when designing the driving non-circular gear, the angle of the toothless area A of the first driving non-circular gear 11 is larger than that of the second driving non-circular gear 12 without teeth The angle of zone A.
优选地，所述第一主动非圆齿轮11的无齿区A为195°，所述变速区为60°以及所述匀速区C为45°。Preferably, the toothless area A of the first driving non-circular gear 11 is 195°, the speed change area is 60° and the constant speed area C is 45°.
优选地，所述第二主动非圆齿轮12的无齿区A为165°，所述变速区为60°以及所述匀速区C为75°。Preferably, the toothless area A of the second driving non-circular gear 12 is 165°, the speed change area is 60° and the constant speed area C is 75°.
优选地，所述第一主动非圆齿轮11同与之相啮合的第一从动非圆齿轮31在初始啮合时，所述第一主动非圆齿轮11与第一从动非圆齿轮31的中心连线与所述第一主动非圆齿轮11的对称轴线O的夹角为87.5°；所述第二主动非圆齿轮12同与之相啮合的第二从动非圆齿轮21在初始啮合时，所述第二主动非圆齿轮12与第二从动非圆齿轮21的中心连线与所述第二主动非圆齿轮12的对称轴线O的夹角为87.5°。Preferably, when the first driving non-circular gear 11 and the first driven non-circular gear 31 meshing with it are initially meshed, the first driving non-circular gear 11 and the first driven non-circular gear 31 The angle between the center line and the symmetry axis O of the first driving non-circular gear 11 is 87.5°; the second driving non-circular gear 12 meshes with the second driven non-circular gear 21 at the initial meshing , the angle between the center line connecting the second driving non-circular gear 12 and the second driven non-circular gear 21 and the symmetry axis O of the second driving non-circular gear 12 is 87.5°.
在本发明的一个具体实施例中，其工作过程如下：第二主动非圆齿轮12从逆时针旋转并开始与第二从动非圆齿轮21的有齿部分啮合，同时与第二从动非圆齿轮21同轴连接的第一圆柱齿轮22开始做顺时针旋转，与第一圆柱齿轮22啮合的第二圆柱齿轮32以及与第二圆柱齿轮32同轴设置的第一从动非圆齿轮31做逆时针旋转，当第二主动非圆齿轮12与第二从动非圆齿轮21啮合并逆时针继续旋转至165°时，第一传动轴2以及其上的第二从动非圆齿轮21和第一圆柱齿轮22顺时针旋转了一次，第二传动轴3以及其上的第一从动非圆齿轮31和第二圆柱齿轮32逆时针旋转了一次，此时第二主动非圆齿轮12与第二从动非圆齿轮21刚好脱开，第一主动非圆齿轮11与第一从动非圆齿轮31刚好啮合，即完成了一个上冲程；第一主动非圆齿轮11继续逆时针旋转并开始与从第一动非圆齿轮的有齿部分啮合，第一从动非圆齿轮31与同轴连接的第二圆柱齿轮32开始做顺时针旋转，与第二圆柱齿轮32啮合的第一圆柱齿轮22以及与第一圆柱齿轮22同轴的第一从动非圆齿轮31做逆时针旋转，当第一主动非圆齿轮11与第一从动非圆齿轮31啮合并逆时针继续旋转至195°时，第一传动轴2以及其上的第一从动非圆齿轮31和第二圆柱齿轮32顺时针旋转了一次，第一传动轴2以及其上的第二从动非圆齿轮21和第一圆柱齿轮22逆时针旋转了一次，此时第一主动非圆齿轮11与第一从动非圆齿轮31刚好脱开，第二主动非圆齿轮12与第二从动非圆齿轮21重新啮合，此时完成了一个下冲程，至此一个完整的抽油过程结束，然后进行下一个抽油循环。In a specific embodiment of the present invention, its working process is as follows: the second driving non-circular gear 12 rotates counterclockwise and starts to mesh with the toothed part of the second driven non-circular gear 21, and simultaneously with the second driven non-circular gear 21. The first cylindrical gear 22 coaxially connected to the circular gear 21 starts to rotate clockwise, the second cylindrical gear 32 meshing with the first cylindrical gear 22 and the first driven non-circular gear 31 coaxially arranged with the second cylindrical gear 32 Rotate counterclockwise, when the second driving non-circular gear 12 meshes with the second driven non-circular gear 21 and continues to rotate counterclockwise to 165°, the first transmission shaft 2 and the second driven non-circular gear 21 on it and the first cylindrical gear 22 rotates clockwise once, the second transmission shaft 3 and the first driven non-circular gear 31 and the second cylindrical gear 32 on it rotate counterclockwise once, at this time the second driving non-circular gear 12 Just disengaged from the second driven non-circular gear 21, the first driving non-circular gear 11 is just meshed with the first driven non-circular gear 31, that is, an up stroke is completed; the first driving non-circular gear 11 continues to rotate counterclockwise And start to mesh with the toothed part of the first driven non-circular gear, the first driven non-circular gear 31 and the coaxially connected second cylindrical gear 32 start to rotate clockwise, and the first driven non-circular gear 32 meshes with the second cylindrical gear 32. The cylindrical gear 22 and the first driven non-circular gear 31 coaxial with the first cylindrical gear 22 rotate counterclockwise. When the first driving non-circular gear 11 meshes with the first driven non-circular gear 31 and continues to rotate counterclockwise to At 195°, the first transmission shaft 2 and the first driven non-circular gear 31 and the second cylindrical gear 32 thereon rotate clockwise once, and the first transmission shaft 2 and the second driven non-circular gear 21 thereon It rotates counterclockwise once with the first cylindrical gear 22. At this time, the first driving non-circular gear 11 and the first driven non-circular gear 31 are just disengaged, and the second driving non-circular gear 12 and the second driven non-circular gear 21. Re-engagement, a downstroke is completed at this time, and a complete pumping process is completed, and then the next pumping cycle is performed.
根据本发明第二方面的一种非圆齿轮副的设计方法，包括如下步骤：A method for designing a non-circular gear pair according to the second aspect of the present invention includes the following steps:
S10：根据非圆齿轮的节曲线变化规律以及结合主动非圆齿轮同与之相啮合的从动非圆齿轮在啮合过程中需要满足减速、匀速和加速的运动过程设计传动比i；S10: Design the transmission ratio i according to the change rule of the pitch curve of the non-circular gear and the driven non-circular gear that meshes with the driving non-circular gear and needs to satisfy the motion process of deceleration, uniform speed and acceleration during the meshing process;
具体地，结合目前油田传动需求，将最大传动比A确定为2.81，将最小传动比B确定为1/3，其变化规律如图5所示；Specifically, according to the current oilfield transmission requirements, the maximum transmission ratio A is determined to be 2.81, and the minimum transmission ratio B is determined to be 1/3, and the change rule is shown in Figure 5;
优选地，所述主动非圆齿轮同与之相啮合的从动非圆齿轮的传动比i满足以下公式：Preferably, the transmission ratio i of the driving non-circular gear and the driven non-circular gear meshing with it satisfies the following formula:
其中，为主动非圆齿轮节曲线对应的角度，i为传动比，β为匀速区C的角度，第一主动非圆齿轮11取45°，第二主动非圆齿轮12取75°，A为最大传动比，B为最小传动比，结合目前油田的传动需求，最大传动比A确定为2.81，最小传动比B设置为1/3m为传动比过渡因子，取0.5；且 in, is the angle corresponding to the pitch curve of the driving non-circular gear, i is the transmission ratio, β is the angle of the constant speed zone C, the first driving non-circular gear 11 is 45°, the second driving non-circular gear 12 is 75°, and A is the maximum transmission ratio, B is the minimum transmission ratio, combined with the current transmission requirements of the oil field, the maximum transmission ratio A is determined to be 2.81, and the minimum transmission ratio B is set to 1/3m as the transmission ratio transition factor, which is taken as 0.5; and
S20：根据传动比i和主动非圆齿轮与从动非圆齿轮的中心距a计算主动非圆齿轮的半径r1，并在极坐标下形成主动非圆齿轮的节曲线，其中，S20: Calculate the radius r1 of the driving non-circular gear according to the transmission ratio i and the center distance a between the driving non-circular gear and the driven non-circular gear, and form the pitch curve of the driving non-circular gear in polar coordinates, wherein,
两非圆齿轮传动时，传动轴的中心距保持一定，其半径满足如下关系：When two non-circular gears are driven, the center distance of the transmission shaft is kept constant, and its radius satisfies the following relationship:
r1＝a-rg＝i×r2 (2-2)r 1 =ar g =i×r 2 (2-2)
因此：therefore:
其中：in:
a—主动非圆齿轮与从动非圆齿轮的中心距，a—the center distance between the driving non-circular gear and the driven non-circular gear,
r1—主动轮半径，r 1 — the radius of the driving wheel,
r2—从动轮半径，r 2 — the radius of the driven wheel,
i—瞬时传动比。i—Instantaneous transmission ratio.
S30：根据主动非圆齿轮与从动非圆齿轮的中心距a和主动非圆齿轮的半径r1得出所述从动非圆齿轮的半径r2,并在极坐标下形成所述从动非圆齿轮的节曲线；具体地，对于第一从动非圆齿轮31、第二从动非圆齿轮21，其节曲线可根据下式通过MATLAB编程计算生成S30: Obtain the radius r2 of the driven non-circular gear according to the center distance a between the driving non-circular gear and the driven non-circular gear and the radius r1 of the driving non-circular gear, and form the driven non-circular gear in polar coordinates The pitch curve of the gear; specifically, for the first driven non-circular gear 31 and the second driven non-circular gear 21, the pitch curve can be calculated and generated by MATLAB programming according to the following formula
具体地推导过程如下：对于从动非圆齿轮，根据两传动轴的半径关系，即：The specific derivation process is as follows: For the driven non-circular gear, according to the radius relationship of the two transmission shafts, that is:
根据从动非圆齿轮与非圆齿轮在啮合点的速度相等，即：v1＝v2 According to the speed of the driven non-circular gear and the non-circular gear at the meshing point are equal, namely: v 1 =v 2
式中：可以主从动轮的转角关系式：where: The rotation angle relationship of the main and driven wheels can be:
将式(2-1)带入(2-5)分段积分可得主动轮任意角度下对应的从动轮角度。以上进行了非圆齿轮结构形式的数学建模，在MATLAB中数值运算后，将计算结果导入CAD中生成了两对非圆齿轮结构图。Bringing equation (2-1) into (2-5) piecewise integration, the corresponding driven wheel angle at any angle of the driving wheel can be obtained. The mathematical modeling of the non-circular gear structure is carried out above. After numerical operation in MATLAB, the calculation results are imported into CAD to generate two pairs of non-circular gear structure diagrams.
在双层非圆齿轮的结构下，上下冲程的速度发生变化，但是行程仍然是一个定值，与之相对应的是第一对非圆齿轮在单周期内从动轮的啮合转角，即第一对非圆齿轮的从动轮啮合转角要与第二对非圆齿轮的啮合转角保持相等，即依据这一基本关系，进行如下的数学模型建立：Under the structure of double-layer non-circular gears, the speed of the upper and lower strokes changes, but the stroke is still a fixed value, which corresponds to the meshing angle of the driven wheels of the first pair of non-circular gears in a single cycle, that is, the first The meshing angle of the driven wheel of the non-circular gear should be equal to the meshing angle of the second pair of non-circular gears, that is, According to this basic relationship, the following mathematical model is established:
依据式(2-1)，根据抽油机工作要求，保持最大传动比A与第一对齿轮相等。两变速区转角为120度，因此确定匀速区C为75度。即β＝45°。式(2-1)中只有一个变量,即最小传动比B。将其带入式(2-5)，得到式(3-1)： According to formula (2-1), according to the working requirements of the pumping unit, keep the maximum transmission ratio A equal to the first pair of gears. The rotation angle of the two speed change areas is 120 degrees, so the constant speed area C is determined to be 75 degrees. That is, β=45°. There is only one variable in formula (2-1), namely the minimum transmission ratio B. Bringing it into equation (2-5), we get equation (3-1):
该求解过程涉及负高次幂的积分运算，一般的数值计算并无法求逆向求解出确定的B值。因此，同样依据第一对非圆齿轮的设计方法。首先给定最小传动比B的的范围，从最小值按固定的增量，据式(3-1)循环计算出对应的从动轮最大转角使之无限逼近 The solution process involves the integral operation of negative high power, and the general numerical calculation cannot solve the definite B value in reverse. Therefore, it is also based on the design method of the first pair of non-circular gears. First, the range of the minimum transmission ratio B is given, and the maximum rotation angle of the corresponding driven wheel is calculated cyclically according to the formula (3-1) according to the fixed increment from the minimum value. make it infinite
从而确定出第二对非圆齿轮的结构参数。Thereby, the structural parameters of the second pair of non-circular gears are determined.
以上进行了非圆齿轮结构形式的数学建模，在MATLAB中数值运算后，将计算结果导入CAD中生成了两对非圆齿轮结构图The mathematical modeling of the non-circular gear structure is carried out above. After numerical operation in MATLAB, the calculation results are imported into CAD to generate two pairs of non-circular gear structure diagrams.
优选地，如图6所示，减速区B和匀速区C之间以及匀速区C与加速区D之间还设置过渡区，即过渡抛物线，作为优选地，为了使非圆齿轮副在啮合过程中更加平稳，可以用圆弧进行过渡，具体函数如式(2-1)所示。Preferably, as shown in FIG. 6 , a transition area, that is, a transition parabola, is also set between the deceleration area B and the uniform speed area C and between the uniform speed area C and the acceleration area D. It is more stable in the transition, and the transition can be performed with an arc, and the specific function is shown in formula (2-1).
具体地，将主动非圆齿轮同与之相啮合的从动非圆齿轮的传动比i的公式依次代入主动非圆齿轮的半径r1公式可以求得主动非圆齿轮的半径r1关于主动非圆齿轮节曲线对应的角度的函数，然后利用MATLAB可以在极坐标上绘制主动非圆齿轮的节曲线；而由于从动非圆齿轮与主动非圆齿轮之间的中心距a不变，继而可以求得从动非圆齿轮的半径r2，由从动非圆齿轮的节曲线的角度从而得到从动非圆齿轮的半径r2关于从动非圆齿轮的节曲线的角度的函数，然后可以利用MATLAB可以在极坐标上绘制从动非圆齿轮的节曲线。Specifically, by substituting the formula of the transmission ratio i of the driving non-circular gear with the driven non-circular gear meshing with it into the formula of the radius r1 of the driving non-circular gear, the radius r1 of the driving non-circular gear can be obtained. The angle corresponding to the nodal curve , and then use MATLAB to draw the pitch curve of the driving non-circular gear on polar coordinates; and since the center distance a between the driven non-circular gear and the driving non-circular gear remains unchanged, then the driven non-circular gear can be obtained. The radius r2 is determined by the angle of the pitch curve of the driven non-circular gear Thereby, the angle of the radius r2 of the driven non-circular gear with respect to the pitch curve of the driven non-circular gear is obtained The function of , and then the pitch curve of the driven non-circular gear can be plotted in polar coordinates using MATLAB.
根据本发明的一种非圆齿轮副的设计方法，该方法简单可靠，具有灵活可调的设计参数，提高了非圆齿轮副设计的灵活性。According to a method for designing a non-circular gear pair of the present invention, the method is simple and reliable, has flexible and adjustable design parameters, and improves the flexibility of designing a non-circular gear pair.
以上所述仅是本发明的示范性实施方式，而非用于限制本发明的保护范围，本发明的保护范围由所附的权利要求确定。The above descriptions are only exemplary embodiments of the present invention, and are not intended to limit the protection scope of the present invention, which is determined by the appended claims.
本领域技术人员可以理解的是，上文中描述的本发明的多个实施例中的各个特征可以相应地省去、添加或者以任意方式组合。并且，本领域技术人员能够想到的简单变换方式以及对现有技术做出适应性和功能性的结构变换的方案，都属于本发明的保护范围。It will be understood by those skilled in the art that various features of the various embodiments of the present invention described above may be correspondingly omitted, added or combined in any manner. In addition, simple transformation methods that can be conceived by those skilled in the art and solutions for making adaptive and functional structural transformations to the prior art all belong to the protection scope of the present invention.
虽然已经参考各种实施例示出和描述了本发明，但本领域技术人员应当理解的是，可以在其中做出形式和细节上的各种改变，而不背离由随附的权利要求所限定的本发明的范围。Although the present invention has been shown and described with reference to various embodiments, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the meaning of the appended claims scope of the present invention.
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| Publication number | Priority date | Publication date | Assignee | Title |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010121739A (en) * | 2008-11-20 | 2010-06-03 | Institute Of National Colleges Of Technology Japan | Method, program, and device for generating profile shape of non-circular gear pair |
| CN103244620A (en) * | 2013-05-21 | 2013-08-14 | 江苏圣乐机械有限公司 | Mechanical reversing speed reducer and vertical type pumping unit |
| CN104121338A (en) * | 2014-03-14 | 2014-10-29 | 董剑 | Switching reciprocating incomplete non-circular gear speed changing box and transmitting mechanism thereof |
| CN105240464A (en) * | 2015-10-08 | 2016-01-13 | 杨靖康 | Reversing speed reducer |
| CN108412982A (en) * | 2018-05-11 | 2018-08-17 | 中国人民解放军陆军军事交通学院 | A kind of novel combination type non-circular gear infinitely variable speed transmission |
-
2019
- 2019-04-11 CN CN201910291114.9A patent/CN110030360B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010121739A (en) * | 2008-11-20 | 2010-06-03 | Institute Of National Colleges Of Technology Japan | Method, program, and device for generating profile shape of non-circular gear pair |
| CN103244620A (en) * | 2013-05-21 | 2013-08-14 | 江苏圣乐机械有限公司 | Mechanical reversing speed reducer and vertical type pumping unit |
| CN104121338A (en) * | 2014-03-14 | 2014-10-29 | 董剑 | Switching reciprocating incomplete non-circular gear speed changing box and transmitting mechanism thereof |
| CN105240464A (en) * | 2015-10-08 | 2016-01-13 | 杨靖康 | Reversing speed reducer |
| CN108412982A (en) * | 2018-05-11 | 2018-08-17 | 中国人民解放军陆军军事交通学院 | A kind of novel combination type non-circular gear infinitely variable speed transmission |
Non-Patent Citations (1)
| Title |
|---|
| 戴威骏: "非圆齿轮自动换向立式抽气机的设计与研究", 《中国优秀硕士学位论文全文数据库 工程科技Ⅰ辑》 * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111779326A (en) * | 2019-04-04 | 2020-10-16 | 宁波市普世达泳池用品有限公司 | Hydroenergy cleaner for overground swimming pool |
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