CN115823226A

CN115823226A - Power branch forward and reverse drive load balancing mechanism and working method

Info

Publication number: CN115823226A
Application number: CN202211518545.2A
Authority: CN
Inventors: 赵天宇; 田昊; 刘强; 张超; 龙相瑞
Original assignee: 703th Research Institute of CSIC
Current assignee: 703th Research Institute of CSIC
Priority date: 2022-11-29
Filing date: 2022-11-29
Publication date: 2023-03-21

Abstract

A power branch forward and reverse drive load balancing mechanism and a working method thereof are provided, wherein the load balancing mechanism comprises a torsion shaft, a primary big gear, a secondary small gear and an interstage connection assembly; the first-stage big gear is sleeved on the torsion shaft, the second-stage small gear is sleeved on the torsion shaft, one side of the first-stage big gear is connected with one end of the torsion shaft through the interstage connecting assembly, one side of the second-stage small gear is connected with the other end of the torsion shaft in a flange mode, the load balancing mechanism transmits half of the input total power, and the first-stage big gear transmits the input total power to the second-stage small gear through the torsion shaft and the interstage connecting assembly. The invention can reduce the load born by the meshing gear, greatly reduce the volume and the weight of the gear box and further reduce the overall dimension and the weight of the main reducer.

Description

Power branch forward and backward drive load balancing mechanism and working method

Technical Field

The invention relates to the field of transmission testing, in particular to a power branch forward and reverse transmission load balancing mechanism and a working method.

Background

With the development of ships, high-power ships increasingly become the indispensable ship variety for future development, the reduction gear box is indispensable for reducing the size and improving the power density, the weak link of the reduction gear box for the high-power ships is the strength of gear teeth, and the strength of the gear teeth is one of important factors determining the final size and weight of the gear box. Although power split drives have a higher number of parts, a higher amount of machining and a more complex assembly than power non-split drives. In summary, it is necessary to reduce the size of the gear box and the corresponding parts while maintaining the load transmission.

Disclosure of Invention

The invention provides a power branch forward and reverse drive load balancing mechanism and a working method for overcoming the defects of the prior art.

A power branch forward and reverse drive load balancing mechanism comprises a torsion shaft, a primary big gear, a secondary small gear and an interstage connection assembly; the first-stage big gear is sleeved on the torsion shaft, the second-stage small gear is sleeved on the torsion shaft, one side of the first-stage big gear is connected with one end of the torsion shaft through the interstage connecting assembly, one side of the second-stage small gear is connected with the other end of the torsion shaft in a flange mode, the load balancing mechanism transmits half of the input total power, and the first-stage big gear transmits the input total power to the second-stage small gear through the torsion shaft and the interstage connecting assembly.

A power branch is just reversing the work method of the drive uniform load mechanism, after the host computer starts, the torque exerted on the axle of the first-class pinion gear increases gradually, in the course of loading, the first-class bull gear of a uniform load mechanism enters and engages with existing first-class pinion gear, and the second-class pinion gear enters the engaging state with the second-class bull gear, inner, outer tooth of the spline of the interstage linkage assembly at the same time, because of making and installing the error, the first-class gear pair, second-class gear pair and spline pair in another power branch mechanism do not enter the engaging state or one or two links do not enter the engaging state, namely there is a gap in the tooth side, with the increase of input torque, through the elastic deformation of the torsion shaft of the uniform load mechanism entering the engaging state first, dispel the tooth side gap of another uniform load mechanism, make all gears and splines of two uniform load mechanisms enter the engaging state; the power branch mechanism which is firstly in the meshing state transmits larger power, but because the torsional rigidity of the torsion shaft is smaller and the backlash is eliminated when the two power branch mechanisms are assembled, the difference of the power transmitted by the two load sharing mechanisms can be controlled within a smaller range.

Compared with the prior art, the invention has the beneficial effects that:

the load balancing mechanism transfers half of the original load of the power to be transferred by the primary gear pair and then transfers the power to the secondary pinion gear by the torsion shaft and the interstage connection assembly, so that the power of each branch gear set of the power branch can be uniformly distributed, the power transferred by the gears is reduced by half, the load born by the meshed gears is greatly reduced, the width and the outer diameter of the large and small gears can be reduced, the volume and the weight of the gear box are greatly reduced, the overall dimension and the weight of the main reducer are reduced, and the dimensions of the gear pairs and the reducer at all stages are reduced.

The technical scheme of the invention is further explained by combining the drawings and the embodiment:

drawings

FIG. 1 is a schematic view of a power-split forward and reverse drive load balancing mechanism according to the present invention;

FIG. 2 is a schematic view of the interstage coupling assembly A and a first bolt assembly C of FIG. 1;

fig. 3 is a schematic view of the second bolt assembly B of fig. 1.

Detailed Description

Embodiments of the present invention will be described in detail below with reference to the accompanying drawings. The following examples are only for illustrating the technical solutions of the present invention more clearly, and therefore are only examples, and the protection scope of the present invention is not limited thereby.

It is to be noted that, unless otherwise specified, technical or scientific terms used herein shall have the ordinary meaning as understood by those skilled in the art to which the invention pertains.

As shown in fig. 1, a power-split forward and reverse drive load balancing mechanism comprises a torsion shaft 12, a primary big gear 9, a secondary small gear 11 and an interstage connection assembly a;

the primary gearwheel 9 is sleeved on the torsion shaft 12, the secondary pinion 11 is sleeved on the torsion shaft 12, one side of the primary gearwheel 9 is connected with one end of the torsion shaft through an interstage connecting component A, one side of the secondary pinion 11 is connected with the other end of the torsion shaft in a flange manner, the load balancing mechanism transfers half of the input total power, and the primary gearwheel 9 is transferred to the secondary pinion 11 through the torsion shaft 12 and the interstage connecting component A.

In order to greatly reduce the load borne by the meshing gear and make the power distribution of the gear set uniform, as shown in fig. 2, the interstage coupling assembly a comprises a round nut 1, a round nut stop washer 2, an intermediate spline housing 3, a stop ring 4, an outer spline housing 5, an oil deflector ring 7 and a first bolt assembly C;

spline grooves distributed along the axial direction are processed on the outer side face of one end of the torsion shaft 12, the middle spline housing 3 is sleeved on the spline grooves at the end part of the torsion shaft 12, spline grooves distributed along the axial direction are processed on the outer side face of the middle spline housing 3, the outer spline housing 5 is sleeved on the spline grooves of the middle spline housing 3, one side of the one-level large gear 9 is processed with one-level end flange, the outer spline housing 5 is fixedly connected with the one-level end flange through a first bolt assembly C and is sealed through an oil retainer ring 7, and the side part of the middle spline housing 3 is axially positioned through a round nut 1 and a round nut locking washer 2 which are arranged at the end part of the torsion shaft 12. With the arrangement, the first-stage large gear 9 transmits power to the middle spline housing 3 through the outer spline housing 5 and further transmits the power to the torsion shaft 12, then the torsion shaft 12 transmits the power to the second-stage small gear 11, the sleeve gear is connected with the spline, the radial rigidity is extremely high, and a certain amount of play is allowed in the axial direction. The round nut 1, the round nut stop washer 2 and the first bolt assembly C all play corresponding fixing roles.

The slinger 7 is disposed on the inner side of the primary end flange and is secured by a first bolt assembly C. Specifically, the first bolt assembly C includes a first bolt 6 and a first nut 8, and the external spline housing 5, the primary end flange and the slinger 7 are fixed together by the first bolt 6 and the first nut 8, so that force transmission is realized.

Further, an inwards concave arc transition section is arranged between the spline groove at one end of the torsion shaft 12 and the shaft section of the torsion shaft 12, and a distance ring 10 is sleeved on the arc transition section. The use of the distance ring 10 for positioning the intermediate spline housing 3 ensures a reliable transfer.

In another possible embodiment, as shown in fig. 3, the other end of the torsion shaft 12 is formed with a torsion flange, and one side of the secondary pinion 11 is formed with a secondary end flange connected to the torsion flange by a second bolt assembly B. In particular, the second bolt assembly B comprises a first bolt 13 and a first nut 14, and the first-stage gearwheel 9 and the torsion shaft 12 are fixed together by the second bolt 13 and the second nut 14, so that force transmission is realized.

In particular, the error of the load balancing mechanism for transmitting half of the input total power is not more than 3%. The power of each side (each host) of the parallel operation transmission is transmitted to the second-stage large gear through the load balancing mechanism, so that the power distribution of each branch gear set in the double branches is uniform. The power of the main machine is input through a primary pinion shaft, each primary pinion is meshed with two primary large gears 9 to divide the power of the main machine into two parts, and the two primary large gears 9 transmit half of the power of the main machine respectively. Each primary gearwheel 9 is connected with a secondary pinion, and 2 secondary pinions 11 are simultaneously meshed with the existing secondary gearwheels to transmit the power of the two main machines to the secondary gearwheels and the output shaft. The power of each host is divided into two parts, and the two secondary small gears 11 transmit the power to the existing secondary large gear, and finally parallel operation is achieved.

In another specific embodiment, a working method of the power-branch forward and reverse drive load balancing mechanism is further provided, which specifically includes: after the host computer starts, the torque exerted on the first-level pinion shaft increases gradually, in the process of loading, the first-level big gear 9 of one load balancing mechanism in two load balancing mechanisms is meshed with the existing first-level pinion, and the second-level pinion 11, the second-level big gear and the inner and outer teeth of the spline of the interstage connection assembly also enter a meshed state at the same time;

the power branch mechanism which is firstly in the meshing state transmits larger power, but because the torsional rigidity of the torsion shaft is smaller and the backlash is eliminated when the two power branch mechanisms are assembled, the difference of the power transmitted by the two load sharing mechanisms can be controlled within a smaller range.

The torsional stiffness of the loadbalancing mechanism on both sides of the power branch should be equal and should be as low as possible. In operation, each side of the transmission parts is deformed due to stress, so that the ratio of the number of revolutions of the primary small gear and the secondary large gear is not completely equal to the total transmission ratio in the process from no torque transmission to torque transmission of each part. Taking a marine unit as an example, under all working conditions, the secondary pinion 11 rotates more than 1.9 degrees relative to the primary bull gear due to torsional deformation of the torsion shaft. The torsional deformation of the torsion shaft due to the torque transmission causes the circumferential displacement of the gear pair I to reach about 14 mm, which is equivalent to that the gear pair II does not rotate. If the torsional stiffness of the two sides is unequal, unequal transmission of torque at the two sides is caused. In addition, the torsional rigidity should be as low as possible, which guarantees the load-sharing performance of the power branch.

The present invention is not limited to the above embodiments, and those skilled in the art can make various changes and modifications without departing from the scope of the invention.

Claims

1. The utility model provides a power branch is just reversing drive and is carried mechanism equally which characterized in that: comprises a torsion shaft (12), a primary gearwheel (9), a secondary pinion (11) and an interstage coupling component (A);

the torsion shaft is characterized in that the first-stage large gear (9) is sleeved on the torsion shaft (12), the second-stage small gear (11) is sleeved on the torsion shaft (12), one side of the first-stage large gear (9) is connected with one end of the torsion shaft through the interstage connection component (A), one side of the second-stage small gear (11) is connected with the other end of the torsion shaft in a flange mode, half of the total input power is transmitted by the load balancing mechanism, and the first-stage large gear (9) is transmitted to the second-stage small gear (11) through the torsion shaft (12) and the interstage connection component (A).

2. The power-split forward and reverse drive load balancing mechanism of claim 1, wherein: the interstage coupling assembly (A) comprises a round nut (1), a round nut stop washer (2), a middle spline sleeve (3), a stop ring (4), an outer spline sleeve (5), an oil scraper ring (7) and a first bolt assembly (C);

the outer side face of one end of a torsion shaft (12) is provided with spline grooves distributed along the axial direction, an intermediate spline sleeve (3) is sleeved on the spline grooves at the end part of the torsion shaft (12), the outer side face of the intermediate spline sleeve (3) is provided with spline grooves distributed along the axial direction, an outer spline sleeve (5) is sleeved on the spline grooves of the intermediate spline sleeve (3), one side of a one-level large gear (9) is provided with a one-level end flange, the outer spline sleeve (5) is fixedly connected with the one-level end flange through a first bolt assembly (C) and is sealed through an oil retainer (7), and the side part of the intermediate spline sleeve (3) is axially positioned through a round nut (1) and a round nut locking washer (2) arranged at the end of the torsion shaft (12).

3. The power branch forward and reverse drive load balancing mechanism according to claim 2, wherein: the oil slinger (7) is arranged on the inner side surface of the primary end flange and is fixed through a first bolt assembly (C).

4. The load balancing mechanism of the power-split forward and reverse transmission device according to claim 1, wherein: the other end of the torsion shaft (12) is processed with a torsion flange, one side of the second-stage pinion (11) is processed with a second-stage end flange, and the second-stage end flange is connected with the torsion flange through a second bolt component (B).

5. The power-split forward and reverse drive load balancing mechanism of claim 1, wherein: the error of half of the total power transmitted by the load balancing mechanism is not more than 3%.

6. The power branch forward and reverse drive load balancing mechanism according to claim 2, wherein: an inwards concave arc transition section is arranged between the spline groove at one end of the torsion shaft (12) and the shaft section of the torsion shaft (12), and a distance ring (10) is sleeved on the arc transition section.

7. A method of operating the power branch forward and reverse drive load balancing mechanism of claim 1, wherein:

after the host computer starts, the torque applied on the shaft of the first-level pinion gear increases gradually, in the course of loading, the first-level bull gear (9) of a load-sharing mechanism enters and engages with existing first-level pinion gear, and the second-level pinion gear (11) enters the engaging state with the second-level bull gear, inner and outer teeth of the spline of the interstage linkage assembly at the same time, because of making and installation error, the first-level gear pair, second-level gear pair and spline pair in another power branch mechanism do not enter the engaging state or one or two links do not enter the engaging state, namely there are gaps in the tooth side, with the increase of input torque, through the elastic deformation of the torsion shaft of the load-sharing mechanism which enters the engaging state first, dispel the tooth side gap of another load-sharing mechanism, make all gears and splines of two load-sharing mechanisms enter the engaging state;

the power branch mechanism which is firstly in the meshing state transmits larger power, but the torsional rigidity of the torsion shaft is smaller, and the backlash is eliminated when the two power branch mechanisms are assembled, so that the difference of the power transmitted by the two load sharing mechanisms can be controlled within a smaller range.