CN111503226A

CN111503226A - Gear box and hard rock heading machine

Info

Publication number: CN111503226A
Application number: CN201910092369.2A
Authority: CN
Inventors: 米中生; 邬明均; 安博; 张田; 柳志强; 杜萍
Original assignee: Nanjing High Speed and Accurate Gear Group Co Ltd
Current assignee: Nanjing High Speed and Accurate Gear Group Co Ltd
Priority date: 2019-01-30
Filing date: 2019-01-30
Publication date: 2020-08-07

Abstract

The invention discloses a gear box and a hard rock tunneling machine, which belong to the technical field of transmission, and comprise a box body and a transmission mechanism arranged in the box body, wherein the transmission mechanism comprises a parallel gear mechanism, a bevel gear mechanism, a planetary gear mechanism and two output planetary gear trains which are sequentially connected to form four-stage transmission, so that the transmission ratio and the output torque are increased; the planetary gear mechanism comprises a first sun gear, a first planet gear and a first planet carrier, and the first sun gear drives the first planet carrier to rotate through the first planet gear; the output planetary gear train comprises a second sun gear, a second planet gear and a second inner gear ring, the second inner gear ring is sleeved on the periphery of the second sun gear and meshed with the second planet gear, and the second sun gear drives the second inner gear ring to rotate through the second planet gear; the two second sun gears are coaxially arranged and detachably connected, and one of the second sun gears is fixedly connected with the first planet carrier. The hard rock heading machine comprises the gear box.

Description

Gear box and hard rock heading machine

Technical Field

The invention relates to the technical field of transmission, in particular to a gear box and a hard rock heading machine.

Background

With the development of underground space, hard rock tunnel boring machines have been widely used in the engineering fields of subways, tunnels, municipal pipelines and the like as tunnel construction machines.

The conventional gear box for the cutting part of the heading machine mainly comprises a primary bevel gear mechanism 10, a secondary parallel gear mechanism 20 and two planetary gear output mechanisms 30 as shown in fig. 1 and 2. In order to ensure the installation space of the cutting head, sometimes an idler wheel 40 is required to be added between two gears of the secondary parallel gear mechanism 20, which undoubtedly increases the volume of a gear box for the cutting part of the heading machine, and the gear box has small transmission ratio and low power density and is mainly used for a low-power transverse-axis heading machine; in addition, the output torque is small, only coal seams with low hardness can be cut, the cutting hardness is about 90MPa, the excavation efficiency is low, rocks with high hardness cannot be excavated, and the application range is limited.

Disclosure of Invention

The invention aims to provide a gear box and a hard rock heading machine, and aims to solve the technical problems of large size, small transmission ratio, small power density and small output torque of the gear box in the prior art.

As the conception, the technical scheme adopted by the invention is as follows:

a gear box comprises a box body and a transmission mechanism arranged in the box body, wherein the transmission mechanism comprises a parallel gear mechanism, a bevel gear mechanism, a planetary gear mechanism and two output planetary gear trains which are connected in sequence; the planetary gear mechanism comprises a first sun gear, a first planet gear and a first planet carrier, and the first sun gear drives the first planet carrier to rotate through the first planet gear; the output planetary gear train comprises a second sun gear, a second planetary gear and a second inner gear ring, the second inner gear ring is sleeved on the periphery of the second sun gear and meshed with the second planetary gear, and the second sun gear drives the second inner gear ring to rotate through the second planetary gear; the two second sun gears are coaxially arranged and detachably connected, and one of the second sun gears is fixedly connected with the first planet carrier.

The bevel gear mechanism comprises a bevel gear shaft and a bevel gear meshed with the bevel gear shaft, the parallel gear mechanism is connected with the bevel gear shaft, and the first sun gear is fixedly connected with the bevel gear.

The parallel gear mechanism comprises an input shaft and a parallel gear pair, and the input shaft is in transmission connection with the bevel gear shaft through the parallel gear pair.

And the plane where the axes of the parallel gear pairs are positioned is vertical to the planes where the axes of the bevel gear shaft and the bevel gear are positioned.

The bevel gear comprises a bevel gear body, a first sun gear and a second sun gear, wherein a hollow first containing cavity is formed inside the bevel gear body, part of the first sun gear is located in the first containing cavity, a hollow second containing cavity is formed inside the first sun gear, and part of the two second sun gears are located in the second containing cavity.

The planetary gear mechanism further comprises a first inner gear ring, the first inner gear ring is sleeved on the periphery of the first sun gear and is fixedly connected with the box body, and the first planetary gear is meshed with the first sun gear and the first inner gear ring at the same time.

The output planetary gear train further comprises a second planetary carrier and a planetary shaft, the second planetary carrier is fixedly connected with the box body, the planetary shaft is fixedly connected with the second planetary carrier, and the second planetary gear is rotatably arranged on the planetary shaft.

The box body is provided with a containing groove, the first inner gear ring is located in the containing groove, and one of the second planet carriers is arranged at an opening of the containing groove and is abutted to the first inner gear ring.

The two second sun gears are connected with the spline sleeve through bolts, the bolts extend along the axial direction of the second sun gears, the spline sleeve is sleeved at the joint of the two second sun gears, and the second sun gears are provided with external splines matched with the spline sleeve.

A hard rock ripper comprising a gearbox as described above.

The invention has the beneficial effects that:

according to the gear box, four-stage transmission is formed through the parallel gear mechanism, the bevel gear mechanism, the planetary gear mechanism and the two output planetary gear trains which are sequentially connected, so that the transmission ratio and the output torque are increased, and the requirement of the heading machine for cutting hard rock is met; an output planetary gear train is adopted at the output end of the gear box, so that the load balancing performance and the bearing capacity are improved, and single-input double-output is realized by performing power splitting through two second sun gears; the two second sun gears are detachably connected, so that the installation and the disassembly are convenient, the two second sun gears are conveniently arranged in a box body with a smaller volume, the space is saved, the volume and the weight of the gear box are reduced, the structure is more compact, and the power density is increased.

Drawings

Fig. 1 is a sectional view in one direction of a gear box for a cutting part of a conventional heading machine;

fig. 2 is a sectional view of the gear box for the cutting part of the existing heading machine in another direction;

FIG. 3 is a cross-sectional view of one orientation of a gearbox provided by an embodiment of the present invention;

FIG. 4 is a cross-sectional view in another orientation of a gearbox provided by an embodiment of the present invention.

In fig. 1 and 2:

10. a primary bevel gear mechanism; 20. a secondary parallel gear mechanism; 30. a planetary gear output mechanism; 40. an idler pulley;

in fig. 3 and 4:

11. a main box body; 12. an auxiliary box body;

21. an input shaft; 22. a pair of parallel gears;

31. a bevel gear shaft; 32. a bevel gear;

41. a first sun gear; 42. a first planet gear; 43. a first carrier; 44. a first ring gear; 45. a bearing seat;

51. a second sun gear; 52. a second planet wheel; 53. a second ring gear; 54. a second planet carrier; 55. a planet shaft; 56. a bolt; 57. a spline housing;

61. an oil pump; 62. a first gear; 63. a second gear; 64. an oil seal pressing plate; 65. a rotary joint.

Detailed Description

In order to make the technical problems solved, the technical solutions adopted and the technical effects achieved by the present invention clearer, the technical solutions of the present invention are further described below by way of specific embodiments with reference to the accompanying drawings. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. It should be further noted that, for the convenience of description, only some but not all of the elements associated with the present invention are shown in the drawings.

Referring to fig. 3 and 4, the embodiment of the invention provides a gear box, which can meet the requirement of cutting hard rock due to a large transmission ratio and a large power density, and is mainly used for a hard rock heading machine, and of course, can also be used for other mechanical equipment, and is not limited herein.

The gear box includes the box and sets up the drive mechanism in the box, and the box includes main tank 11 and sets up in two of main tank 11's both sides and assist box 12, can dismantle through the bolt and be connected between assisting box 12 and the main tank 11. The main box body 11 is integrally cast, has higher strength and rigidity, conforms to the severe working condition of the excavator, and ensures the safety when cutting hard rocks.

The transmission mechanism comprises a parallel gear mechanism, a bevel gear mechanism, a planetary gear mechanism and two output planetary gear trains which are connected in sequence, wherein the parallel gear mechanism, the bevel gear mechanism and the planetary gear mechanism are all positioned in the main box body 11, and each output planetary gear train is positioned in one auxiliary box body 12. The parallel gear mechanism, the bevel gear mechanism, the planetary gear mechanism and the output planetary gear train are adopted to form four-stage transmission, so that the transmission ratio and the output torque are increased, and the requirement of the heading machine for cutting hard rock is met. All levels of transmission mechanisms are assembled on the box body in a partially assembled mode, and all the parts can be assembled and disassembled conveniently and integrally, so that the maintenance is more convenient.

The parallel gear mechanism comprises an input shaft 21 and a parallel gear pair 22, the bevel gear mechanism comprises a bevel gear shaft 31 and a bevel gear 32 meshed with the bevel gear shaft 31, the input shaft 21 and the bevel gear shaft 31 are in transmission connection through the parallel gear pair 22, the power of the input shaft 21 is transmitted to the bevel gear shaft 31 through the parallel gear pair 22 to perform primary speed reduction, and then transmitted to the bevel gear 32 through the bevel gear shaft 31 to perform secondary speed reduction. The parallel gear mechanism is used as a primary transmission mechanism, the bevel gear mechanism is used as a secondary transmission mechanism, an idler wheel in a traditional gear box is omitted, the occupied space of the parallel gear mechanism is reduced, and the size of the whole gear box is reduced.

The plane on which the axes of the parallel gear pair 22 lie is perpendicular to the plane on which the axes of the bevel gear shaft 31 and the bevel gear 32 lie. The plane in which the axes of the parallel gear pair 22 lie refers to the plane in which the axes of the two parallel gears lie. For example, the input shaft 21 and the bevel gear shaft 31 may be in a vertical plane, the axes of the bevel gear shaft 31 and the bevel gear 32 may be in a horizontal plane, and the arrangement of the parallel gear pair 22 does not occupy the space in the horizontal direction, thereby reducing the volume of the whole gearbox. Or, the axes of the bevel gear shaft 31 and the bevel gear 32 are in a horizontal plane, and the plane where the axes of the input shaft 21 and the bevel gear shaft 31 are located and the horizontal plane form an included angle, so that the arrangement direction of the parallel gear pair 22 has no influence on the arrangement direction of the bevel gear mechanism, the space is fully utilized, and the volume of the whole gear box is reduced.

Of course, the parallel gear mechanism may also include an input gear shaft and an input gear meshed with the input gear shaft, and the input gear is connected with the bevel gear shaft 31 through a key, and the structure is not limited herein.

The input shaft 21 is supported by bearings on a first bearing bush, which is mounted on the main housing 11 by bolts. The bevel gear shaft 31 is supported by bearings on a second bearing bush, which is mounted on the main case 11 by bolts.

The planetary gear mechanism comprises at least a first sun gear 41, a first planet gear 42 and a first planet carrier 43, and the first sun gear 41 drives the first planet carrier 43 to rotate through the first planet gear 42. First sun gear 41 is fixedly connected to bevel gear 32, first planetary gear 42 is meshed with first sun gear 41, and first carrier 43 is configured to support first planetary gear 42 and rotate with first planetary gear 42. Bevel gear 32 transmits power to first sun gear 41, first sun gear 41 rotates first planetary gear 42, and first carrier 43 rotates with first planetary gear 42 to transmit power. The first carrier 43 and the first planetary gear 42 are supported by bearings therebetween. Here, the number of first planetary gears 42 is not limited.

The bevel gear 32 has a hollow first accommodating chamber formed therein, and a part of the first sun gear 41 is located in the first accommodating chamber, so that the space is fully utilized. The first sun gear 41 is connected with the bevel gear 32 through bolts and positioning pins, so that the assembly and disassembly are convenient. The first sun gear 41 is supported on a bearing housing 45 by a bearing, and the bearing housing 45 is mounted on the main case 11 by a bolt.

Optionally, in order to ensure the structural stability, the planetary gear mechanism further includes a first ring gear 44, the first ring gear 44 is sleeved on the periphery of the first sun gear 41 and is fixedly connected with the main case 11, and the first planet gears 42 are simultaneously meshed with the first sun gear 41 and the first ring gear 44. During the rotation of first sun gear 41, first planetary gears 42 rotate around first sun gear 41, and first planetary gears 42 rotate around first ring gear 44, and first ring gear 44 plays a supporting role.

The main box 11 is provided with a receiving groove, the first inner gear ring 44 is located in the receiving groove, and one side of the first inner gear ring 44 abuts against the inner wall of the receiving groove. In order to avoid the internal transmission space of the first ring gear 44, the accommodating groove is an annular groove, and one side of the first ring gear 44 is axially limited. For convenience of positioning, the first inner gear ring 44 and the main box body 11 are positioned by a positioning pin.

The output planetary gear train at least comprises a second sun gear 51, a second planet gear 52 and a second annular gear 53, the second annular gear 53 is sleeved on the periphery of the second sun gear 51 and meshed with the second planet gear 52, and the second sun gear 51 drives the second annular gear 53 to rotate through the second planet gear 52. The output planetary gear train is adopted at the output end of the gear box, so that the load balancing performance and the bearing capacity are improved, and the power is divided through the two second sun gears 51, so that single input and double output are realized. Here, the number of the second planetary gears 52 is not limited.

Each output planetary gear train is provided with a second sun gear 51, wherein one second sun gear 51 is fixedly connected with the first planet carrier 43, the first planet carrier 43 transmits power to one second sun gear 51, the second sun gear 51 transmits power to the other second sun gear 51, and a planetary gear mechanism is adopted to drive the two output planetary gear trains for power splitting so as to realize single input and double output.

Two second sun gear 51 coaxial settings and can dismantle the connection, and the installation of being convenient for is dismantled, and is convenient for pack into the less box of volume, saves space, reduces the volume and the weight of gear box for the structure is compacter, and power density increases.

Optionally, in order to ensure the structural stability, the output planetary gear train further includes a second planet carrier 54 and a planet shaft 55, the second planet carrier 54 is fixedly connected with the main box 11, the planet shaft 55 is fixedly connected with the second planet carrier 54, and the second planet gear 52 is rotatably arranged on the planet shaft 55. A bearing is arranged between the second planet gear 52 and the planet shaft 55, and a bearing is arranged between the second ring gear 53 and the second planet carrier 54. When the second sun gear 51 rotates, the second planet gear 52 is driven to rotate around the planet shaft 55, and because the planet shaft 55 is fixedly arranged, the second planet gear 52 transmits power to the second inner gear ring 53, so that the second inner gear ring 53 rotates and is used for outputting power to the cutting head of the heading machine.

One of the second planet carriers 54 is disposed at the opening of the accommodating groove and abuts against the first ring gear 44, so as to limit the axial direction of the other side of the first ring gear 44, that is, the axial limit of the first ring gear 44 is realized through the matching of the main box body 11 and the second planet carriers 54. One of the two output planetary gear sets abuts the first ring gear 44 with the second carrier 54 that is close to the planetary gear mechanism, i.e., close to the first ring gear 44.

The first sun gear 41 forms a hollow second accommodating cavity inside, and both the two second sun gears 51 are partially located in the second accommodating cavity, so that the space is fully utilized. The second sun gear 51 is provided with a shaft shoulder, and the shaft shoulders of the two second sun gears 51 are arranged with a gap from the first sun gear 41 and used for axial limiting.

Alternatively, the two second sun gears 51 are connected by a bolt 56 and a spline housing 57, and the bolt 56 extends in the axial direction of the second sun gears 51, passes through the shaft inner hole of one second sun gear 51, and is connected with the other second sun gear 51. The spline housing 57 is located in the second accommodating cavity and sleeved at the connection position of the two second sun gears 51,

the second sun gear 51 is provided with an external spline which is matched with the spline housing 57, and the spline housing 57 axially limits the spline housing 57 through limitation of root circles of the external splines on the two second sun gears 51.

The first planet carrier 43 is sleeved on the periphery of one of the second sun gears 51 and connected with the second sun gear 51 through a key or a gear, and then the first planet carrier 43 transmits power to one of the second sun gears 51. Positioning rings are arranged on two axial sides of the first planet carrier 43 to axially limit the first planet carrier 43. Two positioning rings are mounted, one of which is clamped on the first planet carrier 43 and abuts against the pump group of the gearbox, by means of an annular groove provided on the second sun wheel 51.

The pump group in the gear box comprises an oil pump 61, a first gear 62 connected with the input end of the oil pump 61 and a second gear 63 meshed with the first gear 62, and the second gear 63 is fixedly connected with the first sun gear 41. The oil pump 61 is mounted on an oil pump support seat, the oil pump support seat is mounted on the main case 11 through a bolt, and the second gear 63 is sleeved on the first sun gear 41 and is connected with the first sun gear 41 through a key or a pin. The rotation of the first sun gear 41 is transmitted to the second gear 63. And is transmitted to the oil pump 61 through the first gear 62. A bearing and a bearing support are arranged between the main box 11 and the second gear 63, and a positioning ring is clamped on the first planet carrier 43 and is abutted against the bearing support.

Besides, the pump set in the gear box further comprises an oil seal pressing plate 64, the oil seal pressing plate 64 is connected with the second inner gear ring 53 through bolts, an oil seal for preventing oil leakage is installed between the auxiliary box body 12 and the oil seal pressing plate 64, and an oil hole for accelerating the oil liquid near the oil seal to flow fast is formed in the second inner gear ring 53. The second planet carrier 54 is connected with a rotary joint 65 through a bolt, and high-pressure water is transmitted to the inside of the rotary joint 65 through a hole in the second planet carrier 54 and then transmitted into a cutting head of the heading machine for cooling.

The oil pump 61 is adopted for lubrication, and the transmission mechanism is low in damage risk under the condition that lubricating oil is abundant. The oil pump 61 is driven by the first sun gear 41 through the transmission of the first gear 62 and the second gear 63, and has the advantages of simple structure, few parts, low oil leakage risk and safe and reliable lubrication mode.

All gears in the gear box can adopt gear hobbing and gear grinding simultaneously in combination with actual stress conditions for convenient processing, and the gear box has high processing efficiency and low processing cost.

When the gearbox is in use, power is input from the input shaft 21 of the parallel gear mechanism, is transmitted to the bevel gear shaft 31 through the parallel gear pair 22, is transmitted to the first sun gear 41 through the bevel gear 32, is transmitted to the first planet carrier 43 through the first planet gear 42, and is transmitted to the other second sun gear 51 through one second sun gear 51, so that power split is formed; the second sun gear 51 transmits power to the second planet gears 52, the second planet gears 52 transmit power to the second inner gear ring 53, and the second inner gear ring 53 outputs power, so that single-input double-output is realized.

Embodiments of the present invention also provide a hard rock heading machine including the above-mentioned gearbox, and other structures of the heading machine will not be described in detail herein and are considered to be prior art.

The foregoing embodiments are merely illustrative of the principles and features of this invention, which is not limited to the above-described embodiments, but rather is susceptible to various changes and modifications without departing from the spirit and scope of the invention, which changes and modifications are within the scope of the invention as claimed. The scope of the invention is defined by the appended claims and equivalents thereof.

Claims

1. A gear box comprises a box body and a transmission mechanism arranged in the box body, and is characterized in that the transmission mechanism comprises a parallel gear mechanism, a bevel gear mechanism, a planetary gear mechanism and two output planetary gear trains which are connected in sequence;

the planetary gear mechanism comprises a first sun gear (41), a first planet gear (42) and a first planet carrier (43), wherein the first sun gear (41) drives the first planet carrier (43) to rotate through the first planet gear (42);

the output planetary gear train comprises a second sun gear (51), a second planet gear (52) and a second inner gear ring (53), the second inner gear ring (53) is sleeved on the periphery of the second sun gear (51) and meshed with the second planet gear (52), and the second sun gear (51) drives the second inner gear ring (53) to rotate through the second planet gear (52);

the two second sun gears (51) are coaxially arranged and detachably connected, and one of the second sun gears (51) is fixedly connected with the first planet carrier (43).

2. Gearbox according to claim 1, characterised in that the bevel gear mechanism comprises a bevel gear shaft (31) and a bevel gear (32) meshing with the bevel gear shaft (31), that the parallel gear mechanism is connected with the bevel gear shaft (31), and that the first sun gear (41) is fixedly connected with the bevel gear (32).

3. A gearbox according to claim 2, in which the parallel gear mechanism comprises an input shaft (21) and a pair of parallel gears (22), the input shaft (21) being in driving connection with the bevel gear shaft (31) via the pair of parallel gears (22).

4. A gearbox according to claim 3 in which the plane of the axes of the parallel gear pair (22) is perpendicular to the plane of the axes of the bevel gear shaft (31) and the bevel gear (32).

5. Gearbox according to claim 2, characterised in that the bevel gear (32) has an interior forming a first hollow housing chamber, in which part of the first sun wheel (41) is located, and in that the first sun wheel (41) has an interior forming a second hollow housing chamber, in which both second sun wheels (51) are located.

6. The gearbox according to claim 1, characterized in that the planetary gear mechanism further comprises a first ring gear (44), the first ring gear (44) is sleeved on the periphery of the first sun gear (41) and is fixedly connected with the box body, and the first planet gears (42) are simultaneously meshed with the first sun gear (41) and the first ring gear (44).

7. A gearbox according to claim 6, characterised in that the output planetary gear set further comprises a second planet carrier (54) and a planet shaft (55), the second planet carrier (54) being fixedly connected to the casing, the planet shaft (55) being fixedly connected to the second planet carrier (54), the second planet wheels (52) being rotatably arranged on the planet shaft (55).

8. A gearbox according to claim 7 in which the casing is provided with a receptacle in which the first annulus gear (44) is located, and in which one of the second planet carriers (54) is located at the opening of the receptacle and in abutment with the first annulus gear (44).

9. A gearbox according to any one of the preceding claims 1-8, characterised in that the two second sun wheels (51) are connected by means of a bolt (56) and a spline housing (57), the bolt (56) extending in the axial direction of the second sun wheel (51), the spline housing (57) being fitted over the connection of the two second sun wheels (51), and that the second sun wheel (51) is provided with external splines which cooperate with the spline housing (57).

10. A hard rock ripper including a gearbox according to any one of claims 1 to 9.