CN206338374U - A kind of two-stage planetary gear speed reducing mechanism - Google Patents
A kind of two-stage planetary gear speed reducing mechanism Download PDFInfo
- Publication number
- CN206338374U CN206338374U CN201621367491.4U CN201621367491U CN206338374U CN 206338374 U CN206338374 U CN 206338374U CN 201621367491 U CN201621367491 U CN 201621367491U CN 206338374 U CN206338374 U CN 206338374U
- Authority
- CN
- China
- Prior art keywords
- stage
- planetary
- gear
- primary
- ring gear
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 239000000969 carrier Substances 0.000 claims description 3
- 230000005540 biological transmission Effects 0.000 abstract description 8
- 238000002844 melting Methods 0.000 description 6
- 230000008018 melting Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 238000005452 bending Methods 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 239000004698 Polyethylene Substances 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 239000000155 melt Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- -1 polyethylene Polymers 0.000 description 1
- 229920000573 polyethylene Polymers 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Landscapes
- Retarders (AREA)
Abstract
本实用新型涉及齿轮传动装置技术领域,公开了一种两级行星减速机构,包括箱体和同轴的一级内齿圈和二级内齿圈,一级内齿圈啮合有三个一级行星轮,一级行星轮啮合一级太阳轮输入轴,二级内齿圈啮合有四个二级行星轮,二级行星轮啮合二级太阳轮;一级行星轮内装有一级滚子轴承,一级滚子轴承安装在一级行星轮轴上,一级行星轮轴固定在一级行星架上,一级行星架的输出端与二级太阳轮的输入端连接;二级行星轮内装有二级滚子轴承,二级滚子轴承安装在二级行星轮轴上,二级行星轮轴固定在二级行星架上。本实用新型将原两级行星减速机构中的单壁式行星架改为双壁整体式行星架,双壁整体式行星架刚性更好,不容易损坏,避免停机带来的经济损失。
The utility model relates to the technical field of gear transmission devices, and discloses a two-stage planetary reduction mechanism, which includes a box body and a coaxial first-stage internal ring gear and a second-stage internal ring gear. The first-stage internal ring gear meshes with three first-stage planets The primary planetary gear meshes with the input shaft of the primary sun gear, and the secondary internal ring gear meshes with four secondary planetary gears, and the secondary planetary gear meshes with the secondary sun gear; the primary planetary gear is equipped with a primary roller bearing, and a The first-stage roller bearing is installed on the first-stage planetary wheel shaft, and the first-stage planetary wheel shaft is fixed on the first-stage planetary carrier, and the output end of the first-stage planetary carrier is connected with the input end of the second-stage sun gear; Sub-bearings, the secondary roller bearings are installed on the secondary planetary shaft, and the secondary planetary shaft is fixed on the secondary planet carrier. The utility model changes the single-wall planetary frame in the original two-stage planetary reduction mechanism into a double-wall integral planetary frame. The double-wall integral planetary frame has better rigidity, is not easy to be damaged, and avoids economic losses caused by downtime.
Description
技术领域technical field
本实用新型涉及齿轮传动装置技术领域,更具体地是涉及一种优化结构的两级行星减速机构。The utility model relates to the technical field of gear transmission devices, in particular to a two-stage planetary reduction mechanism with an optimized structure.
背景技术Background technique
熔融泵齿轮箱是多数聚乙烯生产车间大型关键设备。The melt pump gearbox is a large key equipment in most polyethylene production workshops.
常用的熔融泵齿轮箱共有三级传动,第一级是行星齿轮传动,第二级也是行星齿轮传动,第三级是平行轴同步斜齿轮传动。The commonly used melting pump gearbox has three stages of transmission. The first stage is planetary gear transmission, the second stage is also planetary gear transmission, and the third stage is parallel shaft synchronous helical gear transmission.
如图1所示就是一种常用的熔融泵齿轮箱的两级行星减速机构,该齿轮箱由电机驱动,电机的额定功率为350kW,电机的输出转速为800r/min,齿轮箱输出端的负载是熔融泵,齿轮箱的减速比约为30。该两级行星减速机构包括箱体(11)和设在箱体(11)内且同轴的一级内齿圈(12)和二级内齿圈(22),一级内齿圈(12)啮合有三个相同的一级行星轮(13),三个一级行星轮(13)共同啮合一级太阳轮输入轴(14),一级太阳轮输入轴(14)通过两个深沟球轴承(15)与箱体(11)转动连接,二级内齿圈(22)啮合有四个相同的二级行星轮(23),四个二级行星轮(23)共同啮合二级太阳轮(24);每个一级行星轮(13)内装有一级滚子轴承(16),一级滚子轴承(16)安装在一级行星轮轴(18)上,三个一级行星轮轴(18)均固定在单壁式一级行星架(17)上,单壁式一级行星架(17)的输出端内花键与二级太阳轮(24)的输入端外花键连接;每个二级行星轮(23)内装有二级滚子轴承(26),二级滚子轴承(26)安装在二级行星轮轴(28)上,四个二级行星轮轴(28)均固定在单壁式二级行星架(27)上,单壁式二级行星架(27)的输出端作为行星减速机构的输出端,其中一级太阳轮输入轴(14)的分度圆直径为114mm,一级行星轮(13)的分度圆直径为264mm,一级内齿圈(12)的分度圆直径为642mm;二级太阳轮(24)的分度圆直径为240mm,二级行星轮(23)的分度圆直径为304mm,二级内齿圈(22)的分度圆直径为848mm;一级太阳轮输入轴(14)、一级行星轮(13)和一级内齿圈(12)的齿宽均为100mm,二级太阳轮(24)、二级行星轮(23)和二级内齿圈(22)的齿宽均为140mm。As shown in Figure 1, it is a two-stage planetary reduction mechanism of a commonly used melting pump gearbox. The gearbox is driven by a motor. The rated power of the motor is 350kW, and the output speed of the motor is 800r/min. The load at the output end of the gearbox is Melting pump, gear box reduction ratio is about 30. The two-stage planetary reduction mechanism includes a casing (11) and a first-stage inner ring gear (12) and a second-stage inner ring gear (22) that are arranged in the casing (11) and are coaxial ) are meshed with three identical primary planetary gears (13), and the three primary planetary gears (13) are jointly meshed with the primary sun gear input shaft (14), and the primary sun gear input shaft (14) passes through two deep groove balls The bearing (15) is rotationally connected with the case (11), the secondary ring gear (22) meshes with four identical secondary planetary gears (23), and the four secondary planetary gears (23) mesh with the secondary sun gear (24); each first-level planetary wheel (13) is equipped with a first-level roller bearing (16), and the first-level roller bearing (16) is installed on the first-level planetary wheel shaft (18), and the three first-level planetary wheel shafts (18) ) are fixed on the single-wall primary planetary carrier (17), and the inner spline of the output end of the single-wall primary planetary carrier (17) is connected with the external spline of the input end of the secondary sun gear (24); each The secondary planetary wheel (23) is equipped with secondary roller bearings (26), and the secondary roller bearings (26) are installed on the secondary planetary wheel shafts (28), and the four secondary planetary wheel shafts (28) are fixed on the single On the wall-type secondary planet carrier (27), the output end of the single-wall type secondary planet carrier (27) is used as the output end of the planetary reduction mechanism, and the index circle diameter of the primary sun gear input shaft (14) is 114mm, The index circle diameter of the primary planetary gear (13) is 264mm, the index circle diameter of the primary internal ring gear (12) is 642mm; the index circle diameter of the secondary sun gear (24) is 240mm, and the index circle diameter of the secondary planetary gear The indexing circle diameter of (23) is 304mm, the indexing circle diameter of the secondary internal gear (22) is 848mm; the primary sun gear input shaft (14), the primary planetary gear (13) and the primary internal gear The tooth width of (12) is 100mm, and the tooth width of secondary sun gear (24), secondary planetary gear (23) and secondary ring gear (22) is 140mm.
前述的两级行星减速机构是此熔融泵齿轮箱的核心变速机构,行星架是该两级行星减速机构中承受外力矩最大的零件,其中的一级行星架(17)和二级行星架(27)均采用单壁式行星架结构,但是单壁式行星架结构的刚性较差,导致该熔融泵齿轮箱运行一段时间后单壁式行星架损坏,不得不停机进行更换,停机就意味着生产车间停产,给企业带来一定的经济损失。The aforementioned two-stage planetary reduction mechanism is the core transmission mechanism of the melting pump gearbox, and the planetary carrier is the part that bears the largest external moment in the two-stage planetary reduction mechanism. The first-stage planetary carrier (17) and the second-stage planetary carrier ( 27) All adopt single-wall planetary frame structure, but the rigidity of the single-wall planetary frame structure is poor, resulting in damage to the single-wall planetary frame after the melting pump gearbox has been running for a period of time, and has to be shut down for replacement. Shutdown means The shutdown of the production workshop will bring certain economic losses to the enterprise.
前述的两级行星减速机构中一级太阳轮输入轴(14)通过两个深沟球轴承(15)与箱体(11)转动连接,深沟球轴承的额定动载荷较低,再有此处的深沟球轴承容易受到轴电流电腐蚀影响,导致在线运行仅十多天就需要更换一次轴承,轴承失效后齿轮运转精度会受到很大的影响。此外一级行星轮、二级行星轮的外啮合接触强度安全系数都达不到要求的最小允许安全系数,导致各齿轮的齿面发生点蚀或者磨损。In the above-mentioned two-stage planetary reduction mechanism, the first-stage sun gear input shaft (14) is rotationally connected with the box body (11) through two deep groove ball bearings (15), and the rated dynamic load of the deep groove ball bearings is relatively low. The deep groove ball bearings at the center are easily affected by the electric corrosion of the shaft current, which leads to the need to replace the bearings after only more than ten days of online operation. After the bearings fail, the running accuracy of the gears will be greatly affected. In addition, the contact strength safety factor of the external meshing of the primary planetary gear and the secondary planetary gear cannot reach the required minimum allowable safety factor, resulting in pitting or wear on the tooth surface of each gear.
实用新型内容Utility model content
本实用新型为克服上述现有技术中的不足,提供了一种优化结构的两级行星减速机构。The utility model provides a two-stage planetary reduction mechanism with an optimized structure in order to overcome the shortcomings of the above-mentioned prior art.
本实用新型通过以下技术方案来实现上述目的。The utility model realizes above-mentioned purpose through following technical scheme.
一种两级行星减速机构,包括箱体和设在箱体内且同轴的一级内齿圈和二级内齿圈,一级内齿圈啮合有三个相同的一级行星轮,三个一级行星轮共同啮合一级太阳轮输入轴,一级太阳轮输入轴通过轴承与箱体转动连接,二级内齿圈啮合有四个相同的二级行星轮,四个二级行星轮共同啮合二级太阳轮;每个一级行星轮内装有一级滚子轴承,一级滚子轴承安装在一级行星轮轴上,三个一级行星轮轴均固定在一级行星架上,一级行星架的输出端内花键与二级太阳轮的输入端外花键连接;每个二级行星轮内装有二级滚子轴承,二级滚子轴承安装在二级行星轮轴上,四个二级行星轮轴均固定在二级行星架上,二级行星架的输出端作为行星减速机构的输出端,其中一级太阳轮输入轴的分度圆直径为114mm,一级行星轮的分度圆直径为264mm,一级内齿圈的分度圆直径为642mm,二级太阳轮的分度圆直径为240mm,二级行星轮的分度圆直径为304mm,二级内齿圈的分度圆直径为848mm,前述的一级行星架和二级行星架均为双壁整体式行星架。A two-stage planetary reduction mechanism, including a box body and a coaxial first-stage inner ring gear and a second-stage inner ring gear arranged in the box body, the first-stage inner ring gear meshes with three identical first-stage planetary gears, and three one-stage The first-stage planetary gears mesh with the first-stage sun gear input shaft, the first-stage sun gear input shaft is rotationally connected with the box through bearings, the second-stage internal ring gear meshes with four identical second-stage planetary gears, and the four second-stage planetary gears mesh together Second-level sun gear; each first-level planetary wheel is equipped with a first-level roller bearing, and the first-level roller bearing is installed on the first-level planetary wheel shaft. The three first-level planetary wheel shafts are all fixed on the first-level planet carrier. The inner spline of the output end of the second-stage sun gear is connected with the outer spline of the input end of the second-stage sun gear; each second-stage planetary wheel is equipped with a second-stage roller bearing, and the second-stage roller bearing is installed on the shaft of the second-stage planetary wheel. The planetary gear shafts are all fixed on the secondary planet carrier, and the output end of the secondary planet carrier is used as the output end of the planetary reduction mechanism. The index circle diameter of the input shaft of the primary sun gear is 114mm, and the index circle diameter of the primary planet wheel The index circle diameter of the first-stage internal ring gear is 642mm, the index circle diameter of the second-stage sun gear is 240mm, the index circle diameter of the second-stage planetary gear is 304mm, and the index circle diameter of the second-stage inner ring gear It is 848mm, and the above-mentioned first-level planetary carrier and second-level planetary carrier are both double-wall integral planetary carriers.
本方案将原两级行星减速机构中的两个单壁式行星架改为两个双壁整体式行星架,双壁整体式行星架刚性更好,不容易损坏,避免停机带来的经济损失。This plan changes the two single-wall planetary frames in the original two-stage planetary reduction mechanism into two double-wall integral planetary frames. The double-wall integral planetary frames have better rigidity and are not easily damaged, avoiding economic losses caused by downtime .
作为进一步改进的结构形式,上述的一级太阳轮输入轴通过两个双列调心滚子轴承与箱体转动连接,双列调心滚子轴承的额定动载荷更大,不易损坏,可以延长设备的连续运行时间。As a further improved structure, the above-mentioned first-stage sun gear input shaft is rotationally connected with the box through two double-row spherical roller bearings. The double-row spherical roller bearings have a larger rated dynamic load, are not easily damaged, and can be The continuous operating time of the equipment.
作为进一步改进的结构形式,上述的一级太阳轮输入轴、一级行星轮和一级内齿圈的齿宽均为130mm,所述的二级太阳轮、二级行星轮和二级内齿圈的齿宽均为180mm。增加齿宽后,齿轮的齿面接触强度和齿根弯曲强度都相应提高并达到或者超过要求的最小允许安全系数,安全系数越大,除胜任正常运行以外,对较为恶劣的非正常运行状况耐受力也更高。As a further improved structure, the tooth widths of the above-mentioned primary sun gear input shaft, primary planetary gear and primary internal ring gear are all 130mm, and the secondary sun gear, secondary planetary gear and secondary internal gear The tooth width of the ring is 180mm. After increasing the tooth width, the contact strength of the tooth surface and the bending strength of the tooth root of the gear are correspondingly improved and reach or exceed the minimum allowable safety factor. The force is also higher.
本实用新型与现有技术相比主要具有如下有益效果:优化了两级行星减速机构的零部件结构,使各零部件不易损坏,延长设备的连续运行时间,避免停机带来的经济损失,提高了各齿轮的齿面接触强度和齿根弯曲强度,相应地提高了齿轮传动的安全系数,安全系数越大,除胜任正常运行以外,对较为恶劣的非正常运行状况耐受力也更高。Compared with the prior art, the utility model mainly has the following beneficial effects: the component structure of the two-stage planetary reduction mechanism is optimized, the components are not easy to be damaged, the continuous operation time of the equipment is prolonged, the economic loss caused by the shutdown is avoided, and the The contact strength of the tooth surface and the bending strength of the dedendum of each gear are improved, and the safety factor of the gear transmission is correspondingly improved. The larger the safety factor, the higher the tolerance to harsh abnormal operating conditions in addition to being competent for normal operation.
附图说明Description of drawings
图1为现有技术中熔融泵齿轮箱的两级行星减速机构的剖面结构示意图。Fig. 1 is a schematic cross-sectional structure diagram of a two-stage planetary reduction mechanism of a melting pump gearbox in the prior art.
图2为本实用新型实施例的两级行星减速机构的剖面结构示意图。Fig. 2 is a schematic cross-sectional structure diagram of a two-stage planetary reduction mechanism according to an embodiment of the present invention.
图3为本实用新型实施例中一级行星架的两个剖面结构示意图。Fig. 3 is a schematic diagram of two cross-sectional structures of the first-stage planet carrier in the embodiment of the utility model.
图4为本实用新型实施例中二级行星架的两个剖面结构示意图。Fig. 4 is a schematic diagram of two cross-sectional structures of the secondary planet carrier in the embodiment of the present invention.
具体实施方式detailed description
下面结合附图对本实用新型做进一步说明。附图仅用于示例性说明,不能理解为对本专利的限制。Below in conjunction with accompanying drawing, the utility model is further described. The accompanying drawings are for illustrative purposes only and should not be construed as limiting the patent.
为了更简洁的说明本实施例,附图或说明中某些本领域技术人员公知的、但与本创造的主要内容不相关的零部件会有所省略。另外为便于表述,附图中某些零部件会有省略、放大或缩小,但并不代表实际产品的尺寸或全部结构。In order to describe this embodiment more concisely, some components that are known to those skilled in the art but are not related to the main content of the invention will be omitted in the drawings or descriptions. In addition, for the convenience of expression, some parts in the drawings will be omitted, enlarged or reduced, but it does not represent the size or overall structure of the actual product.
实施例:Example:
如图2、图3和图4所示,一种两级行星减速机构,包括箱体(51)和设在箱体(51)内且同轴的一级内齿圈(52)和二级内齿圈(62),一级内齿圈(52)啮合有三个相同的一级行星轮(53),三个一级行星轮(53)共同啮合一级太阳轮输入轴(54),一级太阳轮输入轴(54)通过轴承与箱体(51)转动连接,二级内齿圈(62)啮合有四个相同的二级行星轮(63),四个二级行星轮(63)共同啮合二级太阳轮(64);每个一级行星轮(53)内装有一级滚子轴承(55),一级滚子轴承(55)安装在一级行星轮轴(56)上,三个一级行星轮轴(56)均固定在一级行星架(57)上,一级行星架(57)的输出端内花键与二级太阳轮(64)的输入端外花键连接;每个二级行星轮(63)内装有二级滚子轴承(65),二级滚子轴承(65)安装在二级行星轮轴(66)上,四个二级行星轮轴(66)均固定在二级行星架(67)上,二级行星架(67)的输出端作为行星减速机构的输出端,其中一级太阳轮输入轴(54)的分度圆直径为114mm,一级行星轮(53)的分度圆直径为264mm,一级内齿圈(52)的分度圆直径为642mm,二级太阳轮(64)的分度圆直径为240mm,二级行星轮(63)的分度圆直径为304mm,二级内齿圈(62)的分度圆直径为848mm,前述的一级行星架(57)和二级行星架(67)均为双壁整体式行星架。As shown in Fig. 2, Fig. 3 and Fig. 4, a two-stage planetary reduction mechanism includes a case (51) and a coaxial primary inner ring gear (52) and a secondary The inner ring gear (62), the first-stage inner ring gear (52) meshes with three identical first-stage planetary gears (53), and the three first-stage planetary gears (53) mesh together with the first-stage sun gear input shaft (54), one The first-stage sun gear input shaft (54) is rotationally connected to the case (51) through bearings, and the second-stage inner ring gear (62) meshes with four identical second-stage planetary gears (63), four second-stage planetary gears (63) Co-mesh secondary sun gears (64); each primary planetary wheel (53) is equipped with a primary roller bearing (55), and the primary roller bearing (55) is installed on the primary planetary wheel shaft (56), three The primary planetary gear shafts (56) are all fixed on the primary planet carrier (57), and the internal splines at the output end of the primary planet carrier (57) are connected with the external splines at the input end of the secondary sun gear (64); each The secondary planetary wheel (63) is equipped with secondary roller bearings (65), and the secondary roller bearings (65) are installed on the secondary planetary wheel shafts (66), and the four secondary planetary wheel shafts (66) are fixed on the secondary planetary wheel shafts (66). On the first-stage planetary carrier (67), the output end of the second-stage planetary carrier (67) is used as the output end of the planetary reduction mechanism, wherein the index circle diameter of the first-stage sun gear input shaft (54) is 114mm, and the first-stage planetary gear (53 ) index circle diameter is 264mm, the index circle diameter of the primary internal ring gear (52) is 642mm, the index circle diameter of the secondary sun gear (64) is 240mm, the index circle diameter of the secondary planetary gear (63) The diameter of the circle is 304mm, and the index circle diameter of the secondary internal ring gear (62) is 848mm. The aforementioned primary planetary carrier (57) and secondary planetary carrier (67) are double-wall integral planetary carriers.
本实施例的一级行星架(57)和二级行星架(67)均采用双壁整体式行星架结构,双壁整体式行星架刚性好,不容易损坏,避免停机带来的经济损失。Both the primary planetary carrier (57) and the secondary planetary carrier (67) of this embodiment adopt a double-walled integral planetary frame structure. The double-walled integral planetary frame has good rigidity, is not easy to be damaged, and avoids economic losses caused by downtime.
本实施例中一级太阳轮输入轴(54)通过两个双列调心滚子轴承(58)与箱体(51)转动连接,双列调心滚子轴承的额定动载荷更大,不易损坏,可以延长设备的连续运行时间。In this embodiment, the first-stage sun gear input shaft (54) is rotationally connected to the casing (51) through two double-row spherical roller bearings (58). damage, which can prolong the continuous operation time of the equipment.
本实施例中的一级太阳轮输入轴(54)、一级行星轮(53)和一级内齿圈(52)的齿宽均为130mm;本实施例中的二级太阳轮(64)、二级行星轮(63)和二级内齿圈(62)的齿宽均为180mm。增加齿宽后,各齿轮的齿面接触强度和齿根弯曲强度都相应提高并达到或者超过要求的最小允许安全系数,安全系数越大,除胜任正常运行以外,对较为恶劣的非正常运行状况耐受力也更高。The tooth width of the first-stage sun gear input shaft (54), the first-stage planetary gear (53) and the first-stage ring gear (52) in this embodiment are all 130mm; the second-stage sun gear (64) in this embodiment 1, the tooth width of the secondary planetary gear (63) and the secondary ring gear (62) are 180mm. After increasing the tooth width, the tooth surface contact strength and dedendum bending strength of each gear are correspondingly improved and reach or exceed the required minimum allowable safety factor. The larger the safety factor, the more severe the abnormal operation condition The tolerance is also higher.
以上仅为本实用新型的一个具体实施例,但本实用新型的设计构思并不局限于此,凡利用本实用新型构思对本实用新型做出的非实质性修改,均落入本实用新型的保护范围之内。The above is only a specific embodiment of the utility model, but the design concept of the utility model is not limited thereto, and all non-essential modifications made to the utility model by utilizing the utility model concept all fall under the protection of the utility model within range.
Claims (3)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201621367491.4U CN206338374U (en) | 2016-12-14 | 2016-12-14 | A kind of two-stage planetary gear speed reducing mechanism |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201621367491.4U CN206338374U (en) | 2016-12-14 | 2016-12-14 | A kind of two-stage planetary gear speed reducing mechanism |
Publications (1)
Publication Number | Publication Date |
---|---|
CN206338374U true CN206338374U (en) | 2017-07-18 |
Family
ID=59301797
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CN201621367491.4U Expired - Fee Related CN206338374U (en) | 2016-12-14 | 2016-12-14 | A kind of two-stage planetary gear speed reducing mechanism |
Country Status (1)
Country | Link |
---|---|
CN (1) | CN206338374U (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108468759A (en) * | 2018-05-31 | 2018-08-31 | 郑州机械研究所有限公司 | A kind of petroleum drilling machine winch shift-variable formula planetary gear reduction box |
CN111664177A (en) * | 2020-04-21 | 2020-09-15 | 重庆大学 | Integrated planetary reduction bearing for hub motor |
CN114352687A (en) * | 2022-01-25 | 2022-04-15 | 江苏省金象传动设备股份有限公司 | A BZMX semi-direct drive center drive mill planetary reducer |
-
2016
- 2016-12-14 CN CN201621367491.4U patent/CN206338374U/en not_active Expired - Fee Related
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108468759A (en) * | 2018-05-31 | 2018-08-31 | 郑州机械研究所有限公司 | A kind of petroleum drilling machine winch shift-variable formula planetary gear reduction box |
CN111664177A (en) * | 2020-04-21 | 2020-09-15 | 重庆大学 | Integrated planetary reduction bearing for hub motor |
CN114352687A (en) * | 2022-01-25 | 2022-04-15 | 江苏省金象传动设备股份有限公司 | A BZMX semi-direct drive center drive mill planetary reducer |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CN206338374U (en) | A kind of two-stage planetary gear speed reducing mechanism | |
CN202194785U (en) | Horizontal shaft wind turbine unit and gear box device thereof | |
CN202251737U (en) | Speed reducer in double-planet structure | |
CN104776202A (en) | Power flow division type acceleration gearbox for 6-8MW semi-direct driving wind generation set | |
CN203698660U (en) | Spiral bevel gear planetary gear train for helicopter main reducing gear | |
CN211314459U (en) | A speed-increasing gearbox for double-fed wind turbines | |
CN102230519B (en) | Face gear planetary gearbox | |
CN102312974B (en) | Double-output hydraulic power generation planetary speed increaser | |
CN102392879A (en) | Large velocity ratio marine gearbox | |
CN104343896B (en) | External-gearing type double-helical gear planetary transmission speed reducer | |
CN104061316A (en) | Low-speed shaft supporting structure for wind power gear box | |
CN202228626U (en) | Dual-output planet gear speeder for hydraulic power generation | |
CN202326925U (en) | Gearbox for high-speed-ratio ship | |
CN103343810B (en) | A kind of flexible planet gear drive of wind turbine gearbox | |
CN110617301A (en) | Three-stage transmission helical gear planetary gear type speed reducer | |
CN206338328U (en) | A kind of sliding bearing and improved compound epicyclic reduction gear | |
CN203892494U (en) | Screw drive planet reducer | |
CN209604485U (en) | A face gear planetary compound transmission reducer | |
CN203937219U (en) | The transmission device of twin-screw cold pressing expeller | |
CN204425109U (en) | A kind of combination harmonic reducing motor all-in-one | |
CN204852265U (en) | Two spiral bevel gear transmission cases of pair | |
CN210050261U (en) | A compact high-power fracturing planetary reducer | |
CN211693385U (en) | Multi-motor-driven parallel shaft gear resultant force reduction gearbox for petroleum drilling | |
CN203363007U (en) | Arc tooth hypoid gear speed reducer used for lift | |
CN210371845U (en) | Nine-planet gear speed reducer |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
GR01 | Patent grant | ||
GR01 | Patent grant | ||
CP03 | Change of name, title or address | ||
CP03 | Change of name, title or address |
Address after: 450001 science avenue of Zhengzhou high tech Industrial Development Zone, Zhengzhou, Henan Province, No. Patentee after: Zhengzhou Machinery Research Institute Co., Ltd. Address before: Fengyang high tech Industrial Development Zone, Henan province Zhengzhou city 450001 Street No. 10 Patentee before: Zhengzhou Research Institute of Mechanical Engineering |
|
CF01 | Termination of patent right due to non-payment of annual fee | ||
CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20170718 Termination date: 20201214 |