CN202864782U - Long load distance and big traction parallel axis double-speed winch - Google Patents
Long load distance and big traction parallel axis double-speed winch Download PDFInfo
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- CN202864782U CN202864782U CN201220521471.3U CN201220521471U CN202864782U CN 202864782 U CN202864782 U CN 202864782U CN 201220521471 U CN201220521471 U CN 201220521471U CN 202864782 U CN202864782 U CN 202864782U
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Abstract
The utility model relates to mining transport machinery, in particular relates to a long load distance and big traction parallel axis double-speed winch. The long load distance and big traction parallel axis double-speed winch comprises a operating platform, a hydraulic pressure station, a disc brake, a winch chassis and a planetary differential gear mechanism which is driven by a motor and arranged on the winch chassis, a speed reducer connected with the planetary differential gear mechanism, and roller components connected with the speed reducer. The speed reducer is in a parallel structure, and an output shaft and an input shaft are arranged on the same side of the speed reducer. The output shaft and a roller shaft of the roller components are arranged on the same axis, a center wheel of the planetary differential gear mechanism and the input shaft of the speed reducer are arranged on the same axis, and arrangement of two mutually parallel axes is formed. With the above arrangement, the size of the winch is more compact, and problems in operation are also easier to find by an operator.
Description
Technical field
The utility model relates to carrying machine in mine, especially a kind of long haul distance large traction parallel shafts haulage gear that adopts the planet speed change mechanism speed governing.
Background technology
In the prior art, known a kind of technology is to adopt the winch of the built-in planetary gear speed-reduction of reel, such as JD type car hauler and JYB type haulage gear, and the winch of this structure, haul distance is little, tractive force is little, and only has a kind of speed.Another known technology is the double-speed winch that a kind of drop-gear box that adopts direct motor drive to have two grades of speed changes consists of, such as JSDB type Dual-speed multi-purpose lift winch, the winch of this structure, although have two kinds of running velocitys, but these two kinds of speed are when switching, must be to carry out in the situation that when stopping, not have to load, in service can not speed change, and haul distance is also less.The damper brake that above winch adopts is conventional hand brake and variable device, and its deceleration and stopping performance is relatively poor, and all can not take into account simultaneously long haul distance, large traction and speed change demand.
Summary of the invention
The purpose of this utility model is exactly the problem that exists for solving prior art, for the defective of winch speed governing difficulty, and has designed a kind of long haul distance large traction parallel shafts double speed haulage gear.
The technical solution of the utility model is: a kind of long haul distance large traction parallel shafts double speed haulage gear comprises the drum assembly that is connected by motor-driven planet differential speed-changing mechanism, the latter linked retarder of planet differential speed-changing mechanism, retarder on operator's station, Hydraulic Station, plate disc brake, winch chassis and the winch chassis.Be fixed with gear I, gear II on the center gear of described planet differential speed-changing mechanism, gear I connects with quick pinion carrier by planetary wheel, gear II connects with pinion carrier at a slow speed by planetary wheel, and it is characterized in that: described quick pinion carrier is connected with the input shaft of retarder; The output shaft of described retarder is connected with the drum shaft of drum assembly; Described retarder is the parallel construction that output shaft and input shaft homonymy are arranged, the drum shaft of reducer output shaft and drum assembly is arranged on the same axis, the center gear of motor shaft, planet differential speed-changing mechanism and the input shaft of retarder form the arrangement form that two axial lines is parallel to each other on an axis.
Described drum assembly comprises drum shaft, cylinder, cylinder disc, coupling sleeve, brake disc, bearing and bearing seat; Described cylinder both sides are connected with cylinder disc and coupling sleeve, the input end of cylinder adopts coupler to connect by coupling sleeve and drum shaft with the output shaft of retarder, the other end of cylinder connects with brake disc and drum shaft by coupling sleeve, and cylinder, cylinder disc, coupling sleeve, brake disc all are supported on the drum shaft; Described drum shaft is supported on the winch chassis by bearing and the bearing seat at two ends.
Described drg is plate disc brake; Described cylinder-cylinder disc, cylinder-coupling sleeve, coupling sleeve-brake disc all adopt pin, screw or bolt to be connected.
Described cylinder or cylinder disc or brake disc are divided into two bodies vertically at least; Its division plane is not at grade when described cylinder, cylinder disc, brake disc assembling splicing; Described cylinder adopts expansion set to be connected with drum shaft, and cylinder-cylinder disc, cylinder-coupling sleeve, coupling sleeve-brake disc, coupling sleeve-drum shaft be mutually socket radially; Described brake disc, coupling sleeve, cylinder disc and cylinder consist of the axial separation radial support structure, and dismounting is convenient with transportation.
The output shaft of described motor adopts spline housing to connect with the center gear of planet differential speed-changing mechanism, the quick pinion carrier of planet differential speed-changing mechanism and the input shaft of retarder adopt splined, and the output shaft of retarder adopts spline to be connected with drum-shaped tooth type shaft coupling with drum assembly.
Described planet differential speed-changing mechanism housing and be furnished with respectively at a slow speed quick-acting brake on the pinion carrier and drg at a slow speed, and be connected with pressure-modulation valve with change-over valve on the operator's station by hydraulic oil pipe; Described change-over valve is connected hydraulic oil pipe and is connected with Hydraulic Station with pressure-modulation valve.
The Manual pressure control cock that arranges on the described operator's station is connected with plate disc brake by hydraulic oil pipe, realizes the service braking of plate disc brake.
Described operator's station panel is provided with the elongated slot that can stretch out and regulate for the regulating handle of Manual pressure control cock.
The beneficial effects of the utility model can draw by such scheme: the retarder that adopt (1) is the parallel construction that output shaft and input shaft homonymy are arranged, the drum shaft of reducer output shaft and drum assembly is arranged on the same axis, the center gear of motor shaft, planet differential speed-changing mechanism and the input shaft of retarder are on an axis, form the arrangement form that two axial lines is parallel to each other, this arrangement makes the winch size compacter, and the operator is the operating problem of easier discovery also; (2) supporting construction of cylinder and drum shaft is more reasonable, more is conducive to improve functional reliability; (3) adopt plate disc brake, brake disc and cylinder direct connection, the direct brake drum of drg is braked more reliable; (4) adopt the planet differential speed-changing mechanism, can in operational process, realize changing soon, at a slow speed and the speed adjustment of winch, more convenient to operate reliable, also can realize Long-distance Control; (5) plate disc brake is controlled the complexity that the service braking that can realize plate disc brake and Long-distance Control have been avoided again electric utility by the Manual pressure control cock on the operator's station; (6) entrance point of power adopts spline housing to connect, and the output point of power adopts spline directly to connect, and makes transmission compacter reliable; (7) the cylinder disc on the drum assembly and cylinder, brake disc radially are divided into two bodies, and cylinder disc and cylinder and drum shaft consist of the axial separation radial support structure, and dismounting is convenient with transportation.
This shows that the utility model compared with prior art has substantive distinguishing features and progress, the beneficial effect of its enforcement also is apparent.
Description of drawings:
Fig. 1 is transmission scheme drawing of the present utility model;
Fig. 2 is the drum assembly structural representation.
Wherein, 1 is motor, and 2 are pinion carrier at a slow speed, 3 are drg at a slow speed, wheel centered by 4, and 5 is the planet differential speed-changing mechanism, 6 is quick-acting brake, and 7 is planet differential speed-changing mechanism housing, and 8 is quick pinion carrier, 9 is reducer input shaft, and 10 is retarder, and 11 is reducer output shaft, 12 is drum assembly, and 13 is drum shaft, and 14 is cylinder, 15 is plate disc brake, 16 is operator's station, and 17 is pressure-modulation valve, and 18 is Hydraulic Station, 19 is change-over valve, 20 is spline housing, and 21 is drum-shaped tooth type shaft coupling, and 22 is the cylinder disc, 23 is brake disc, and 24 is coupling sleeve.
The specific embodiment:
In order to understand better the utility model, explain in detail embodiment of the present utility model below in conjunction with accompanying drawing.
The specific embodiment: as shown in Figure 1, a kind of long haul distance large traction parallel shafts double speed haulage gear, comprise the drum assembly 12 that the planet differential speed-changing mechanism 5, planet differential speed-changing mechanism 5 latter linked retarders 10, the retarder 10 that are driven by motor 1 connect, also include operator's station 16 and the Hydraulic Station 18 of brake-pressure is provided.Be fixed with gear I, gear II on the center gear 4 of described planet differential speed-changing mechanism 5, gear I connects with quick pinion carrier 8 by planetary wheel, and gear II connects with pinion carrier 2 at a slow speed by planetary wheel; The center gear 4 of described planet differential speed-changing mechanism 5 adopts spline housing to connect with the output shaft of motor 1; Described quick pinion carrier 8 adopts spline housing to connect with reducer input shaft 9; Described reducer output shaft 11 and drum assembly 12 adopts splines to be connected with drum-shaped tooth type shaft coupling to be connected.Described planet differential speed-changing mechanism housing 7 and be furnished with respectively at a slow speed quick-acting brake 6 on the pinion carrier 2 and drg 3 at a slow speed, and the change-over valve by on hydraulic oil pipe and the operator's station 16 19 is connected with pressure-modulation valve and is connected; Described change-over valve 19 is connected with pressure-modulation valve and is connected with Hydraulic Station 18 by hydraulic oil pipe.Described retarder 10 is the parallel construction that output shaft 11 and input shaft 9 homonymies are arranged, reducer output shaft 11 is arranged on the same axis with the drum shaft 13 of drum assembly 12, the center gear 4 of motor 1 output shaft, planet differential speed-changing mechanism 5 and reducer input shaft 9 form the arrangement form that two axial lines is parallel to each other on an axis.The Manual pressure control cock 17 that arranges on the described operator's station 16 is connected with plate disc brake 15 by hydraulic oil pipe, realizes the service braking of plate disc brake 15.
As shown in Figure 2, drum assembly 12 comprises drum shaft 13, cylinder 14, cylinder disc 22, coupling sleeve 24, brake disc 23, bearing and bearing seat.Described cylinder 14 both sides are connected with cylinder disc 22 and coupling sleeve 24, the input end of cylinder 14 adopts spline and drum-shaped tooth type shaft coupling 21 to connect by coupling sleeve 24 and drum shaft 13 with reducer output shaft 11, the other end of cylinder 14 connects with brake disc 23 and drum shaft 13 by coupling sleeve 24, and cylinder 14, cylinder disc 22, coupling sleeve 24, brake disc 23 all are supported on the drum shaft 13; Described drum shaft 13 is supported on the winch chassis by bearing and the bearing seat at two ends.Described cylinder 14 or cylinder disc 22 or brake disc 23 are divided into two bodies vertically at least; Its division plane is not at grade when described cylinder 14, cylinder disc 22, brake disc 23 assembling splicing; Described cylinder 14 adopts expansion set to be connected with drum shaft 13, and cylinder 14-cylinder disc 22, cylinder 14-coupling sleeve 24, coupling sleeve 24-brake disc 23, coupling sleeve 24-drum shaft 13 be mutually socket radially; Described brake disc 23, coupling sleeve 24, cylinder disc 22 and cylinder 14 consist of the axial separation radial support structure, and dismounting is convenient with transportation.
Above-mentioned explanation is not to be to restriction of the present utility model; the utility model also is not limited in above-mentioned giving an example; the variation that those skilled in the art make in essential scope of the present utility model, remodeling, interpolation or replacement also should belong to protection domain of the present utility model.
Claims (8)
1. one kind long haul distance large traction parallel shafts double speed haulage gear, comprise on operator's station, Hydraulic Station, plate disc brake, winch chassis and the winch chassis drum assembly that the output shaft by motor-driven planet differential speed-changing mechanism, the latter linked retarder of planet differential speed-changing mechanism, retarder connects, it is characterized in that: be fixed with gear I, gear II on the center gear of described planet differential speed-changing mechanism, gear I connects with quick pinion carrier by planetary wheel, and gear II connects with pinion carrier at a slow speed by planetary wheel; The center gear of described planet differential speed-changing mechanism connects with the output shaft of motor; Described quick pinion carrier is connected with the input shaft of retarder; The output shaft of described retarder is connected with the drum shaft of drum assembly; Described retarder is the parallel construction that output shaft and input shaft homonymy are arranged, the drum shaft of reducer output shaft and drum assembly is arranged on the same axis, the center gear of motor shaft, planet differential speed-changing mechanism and the input shaft of retarder form the arrangement form that two axial lines is parallel to each other on an axis.
2. long haul distance large traction parallel shafts double speed haulage gear as claimed in claim 1, it is characterized in that: described drum assembly comprises drum shaft, cylinder, cylinder disc, coupling sleeve, brake disc, bearing and bearing seat; Described cylinder both sides are connected with cylinder disc and coupling sleeve, the input end of cylinder adopts coupler to connect by coupling sleeve and drum shaft with the output shaft of retarder, the other end of cylinder connects with brake disc and drum shaft by coupling sleeve, and cylinder, cylinder disc, coupling sleeve, brake disc all are supported on the drum shaft; Described drum shaft is supported on the winch chassis by bearing and the bearing seat at two ends.
3. long haul distance large traction parallel shafts double speed haulage gear as claimed in claim 2, it is characterized in that: described drg is plate disc brake; Described cylinder-cylinder disc, cylinder-coupling sleeve, coupling sleeve-brake disc all adopt pin, screw or bolt to be connected.
4. long haul distance large traction parallel shafts double speed haulage gear as claimed in claim 2, it is characterized in that: described cylinder or cylinder disc or brake disc are divided into two bodies vertically at least; Its division plane is not at grade when described cylinder, cylinder disc, brake disc assembling splicing; Described cylinder-cylinder disc, cylinder-coupling sleeve, coupling sleeve-brake disc, coupling sleeve-drum shaft be mutually socket radially; Described brake disc, coupling sleeve, cylinder disc and cylinder consist of the axial separation radial support structure.
5. long haul distance large traction parallel shafts double speed haulage gear as claimed in claim 1, it is characterized in that: the output shaft of described motor adopts spline housing to connect with the center gear of planet differential speed-changing mechanism, the quick pinion carrier of planet differential speed-changing mechanism and the input shaft of retarder adopt splined, and the output shaft of retarder adopts spline and drum-shaped tooth type shaft coupling to connect with drum assembly.
6. long haul distance large traction parallel shafts double speed haulage gear as claimed in claim 1, it is characterized in that: described planet differential speed-changing mechanism housing and be furnished with respectively at a slow speed quick-acting brake on the pinion carrier and drg at a slow speed, and be connected with pressure-modulation valve with change-over valve on the operator's station by hydraulic oil pipe; Described change-over valve is connected hydraulic oil pipe and is connected with Hydraulic Station with pressure-modulation valve.
7. long haul distance large traction parallel shafts double speed haulage gear as claimed in claim 6, it is characterized in that: the Manual pressure control cock that arranges on the described operator's station is connected with plate disc brake by hydraulic oil pipe.
8. long haul distance large traction parallel shafts double speed haulage gear as claimed in claim 6, it is characterized in that: described operator's station panel is provided with the elongated slot that can stretch out and regulate for the regulating handle of Manual pressure control cock.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220521471.3U CN202864782U (en) | 2012-10-12 | 2012-10-12 | Long load distance and big traction parallel axis double-speed winch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220521471.3U CN202864782U (en) | 2012-10-12 | 2012-10-12 | Long load distance and big traction parallel axis double-speed winch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202864782U true CN202864782U (en) | 2013-04-10 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201220521471.3U Expired - Fee Related CN202864782U (en) | 2012-10-12 | 2012-10-12 | Long load distance and big traction parallel axis double-speed winch |
Country Status (1)
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| CN (1) | CN202864782U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107738998A (en) * | 2017-11-07 | 2018-02-27 | 山东百海逸机电有限公司 | A kind of stepless time adjustment double-speed chain traction winch |
| CN110329934A (en) * | 2019-07-25 | 2019-10-15 | 徐州苏煤矿山设备制造有限公司 | A kind of haulage gear with disk brake |
| CN113135518A (en) * | 2020-03-20 | 2021-07-20 | 福建省东山县辉永泰体育用品实业有限公司 | Large-torque rescue winch speed changing device |
-
2012
- 2012-10-12 CN CN201220521471.3U patent/CN202864782U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107738998A (en) * | 2017-11-07 | 2018-02-27 | 山东百海逸机电有限公司 | A kind of stepless time adjustment double-speed chain traction winch |
| CN110329934A (en) * | 2019-07-25 | 2019-10-15 | 徐州苏煤矿山设备制造有限公司 | A kind of haulage gear with disk brake |
| CN113135518A (en) * | 2020-03-20 | 2021-07-20 | 福建省东山县辉永泰体育用品实业有限公司 | Large-torque rescue winch speed changing device |
| CN113135519A (en) * | 2020-03-20 | 2021-07-20 | 福建省东山县辉永泰体育用品实业有限公司 | Rescue capstan winch speed change gear of convenient processing |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130410 Termination date: 20211012 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |