CN104947731B - Device for revolving and driving - Google Patents
Device for revolving and driving Download PDFInfo
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- CN104947731B CN104947731B CN201510114387.8A CN201510114387A CN104947731B CN 104947731 B CN104947731 B CN 104947731B CN 201510114387 A CN201510114387 A CN 201510114387A CN 104947731 B CN104947731 B CN 104947731B
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- output shaft
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- 206010055001 Hypodontia Diseases 0.000 claims abstract description 9
- 206010002583 anodontia Diseases 0.000 claims abstract description 9
- 230000005213 hypodontia Effects 0.000 claims abstract description 9
- 201000006680 tooth agenesis Diseases 0.000 claims abstract description 9
- 239000003638 chemical reducing agent Substances 0.000 claims description 47
- 239000010687 lubricating oil Substances 0.000 claims description 46
- 238000001816 cooling Methods 0.000 claims description 2
- 239000000314 lubricant Substances 0.000 abstract description 3
- 230000007246 mechanism Effects 0.000 description 7
- 238000003780 insertion Methods 0.000 description 5
- 230000037431 insertion Effects 0.000 description 5
- 239000003990 capacitor Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 239000003921 oil Substances 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 241000145637 Lepturus Species 0.000 description 1
- 241001494479 Pecora Species 0.000 description 1
- 241000220324 Pyrus Species 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000005461 lubrication Methods 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
- 235000021017 pears Nutrition 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000003252 repetitive effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Landscapes
- Braking Arrangements (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- General Details Of Gearings (AREA)
- Component Parts Of Construction Machinery (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The present invention provides a kind of device for revolving and driving that can efficiently cool down brake apparatus.Driving source, driving rotary body are included in device for revolving and driving；Retarder can be rotatably disposed in the shell filled with lubricant, and connect with above-mentioned driving source；And brake apparatus, there is brake plate, which has the spline tooth engaged with the output shaft side spline on the output shaft for being formed in above-mentioned retarder, be formed with hypodontia in any one of output shaft side spline or above-mentioned spline tooth.
Description
Technical field
This application claims the priority based on Japanese patent application filed on March 31st, 2014 the 2014-074520th.
All the contents of the application are applied in this specification by reference.
The present invention relates to the device for revolving and driving with rotary reducer.
Background technique
Excavator is provided with the device for revolving and driving of revolution driving upper rotation.The device for revolving and driving is subtracted by revolution
Fast device (hereinafter referred merely to as " retarder ") slows down to the power from power source (hydraulic motor, electric motor etc.), and leads to
The output torque crossed after increasing turns round upper rotation.Also, brake apparatus (patent document is sometimes provided in retarder
1)。
Patent document 1: Japanese Unexamined Patent Publication 2008-232270 bulletin
The brake apparatus of retarder includes multiple brake discs and the alternately stacked structure of multiple brake plates.By brake disc with
Brake plate contacts to be braked.Frictional heat is generated when braking, but can be cooled down by being filled in the lubricating oil inside retarder.
But when brake disc and the increase of the quantity of brake plate, it is difficult to flow in the brake disc of inside and brake plate sometimes
Enter lubricating oil, it is difficult to cooling inside.
The content of invention
The illustrative first purpose of some way of the invention is to provide a kind of time that can efficiently cool down brake apparatus
Rotary driving device.
Some way according to the present invention, excavator include
Driving source, driving rotary body；
Retarder can be rotatably disposed in the shell filled with lubricant, and connect with above-mentioned driving source；And
Brake apparatus, have brake plate, the brake plate have be formed in above-mentioned retarder output shaft on output shaft
The spline tooth of side spline engaging,
Hypodontia is formed on either one or two of output shaft side spline or above-mentioned spline tooth.
The effect of invention:
Some way according to the present invention can efficiently cool down brake apparatus.
Detailed description of the invention
Fig. 1 is the side view of the excavator of one embodiment of the present invention.
Fig. 2 is the block diagram for indicating the structure of drive system of one embodiment of the present invention.
Fig. 3 is the block diagram for indicating the structure of device for revolving and driving of a mode of the invention.
Fig. 4 is the sectional view of rotary reducer.
Fig. 5 is the cross-sectional view enlargedly indicated near mechanical brake.
Fig. 6 is the top view for enlargedly indicating brake disc.
Fig. 7 is the perspective view enlargedly indicated near mechanical brake.
Fig. 8 is the perspective view for illustrating morphotropism.
Symbol description
1 lower running body
1A, 1B hydraulic motor
2 swing mechanisms
3 upper rotations
11 engines
12 motor generators
13 speed changers
14 main pumps
15 pioneer pumps
16 high-pressure and hydraulic pipelines
17 control valves
18,20 inverter
21 rotary motors
21a end plate
21b output shaft
22 decomposers
23 mechanical brakes
24 rotary reducers
The 1st rotary reducer of 24-1
The 2nd rotary reducer of 24-2
25 pilot lines
26 operating devices
27a, 28 fluid pressure lines
30 controllers
40 device for revolving and driving
40A output shaft
42,82 sun gear
44,84 planetary gear
44a, 84a pin
46 planetary wheel carriers
48 internal gears
50 the 1st gear-boxes
52 the 2nd gear-boxes
54 the 3rd gear-boxes
56 bearings
57 oil sealings
60 brake discs
61,61A toothless portion)
60a spline tooth
62 brake plates
64 pistons
66 springs
67 brake release plates
68 hydraulic spaces
70,72 spline
74 top lubricating oil introducing ports
76 lower part lubricating oil introducing ports
120 accumulating systems
Specific embodiment
Hereinafter, being illustrated with reference to attached drawing to embodiment illustrated of the invention is not limited.
In addition, assigning identical or corresponding reference notation for identical or corresponding component or part in the record of attached drawing
Number, and the repetitive description thereof will be omitted.Also, in the figure as long as no specifying, purpose is just not representing between component or part
Comparison.Therefore, specific size can be determined referring to non-limiting implementation below by those skilled in the art.
Also, in embodiments described below, only illustrates and do not limit invention, the whole described in embodiment
Feature or combinations thereof be not limited to essential content of the invention.
Fig. 1 shows the excavators 100 of one embodiment of the present invention.
Excavator 100 is on the top of lower running body 1 via swing mechanism 2 equipped with upper rotation 3.Upper rotation
Engine chamber 3a, swing arm 4, dipper 5, scraper bowl 6 and driver's cabin 10 etc. are provided on 3.
Swing arm 4 is equipped with dipper 5 in front end, and dipper 5 is equipped with scraper bowl 6 in front end.Swing arm 4, dipper 5 and scraper bowl 6 divide
Not by 9 hydraulic-driven of swing arm cylinder 7, dipper cylinder 8 and scraper bowl cylinder.
Driver's cabin 10 is equipped with the operating device 26 (referring to Fig. 2) etc. operated by driver.In addition, being carried on engine chamber 3a
There are the power sources such as engine.
In addition, the storage for the electric power that there is excavator 100 involved in present embodiment accumulation to supply to device for revolving and driving
Electric installation usually enumerates hybrid earth mover.But as long as the excavator of the invention using aftermentioned mechanical brake,
It can be adapted for for example driving turn-around machine from the driven type excavator of external power supply supply charging power or by hydraulic motor
The hydraulic excavator of structure 2.
Fig. 2 is the block diagram for indicating the structure of drive system of excavator 100.In Fig. 2, indicate mechanical dynamic respectively with doublet
Force system indicates high-pressure and hydraulic pipeline with heavy line, is represented by dotted lines pilot line, indicates to be driven by electricity control system with fine line
System.
The drive system of excavator 100 have engine 11, motor generator 12, main pump 14, pioneer pump 15, control valve 17,
Operating device 26, controller 30, device for revolving and driving 40 and accumulating system etc..
Engine 11 and motor generator 12 are attached at respectively on two input shafts of speed changer 13.The output of speed changer 13
Axis is connect with main pump 14 and pioneer pump 15.Main pump 14 and pioneer pump 15 are hydraulic pumps.
Control valve 17 is connected with via high-pressure and hydraulic pipeline 16 on main pump 14.Also, via pilot line on pioneer pump 15
25 are connected with operating device 26.
Control valve 17 carries out the control of the hydraulic system of hybrid earth mover 100.Therefore, via high pressure liquid on control valve 17
Pressure pipe road is connected with hydraulic motor 1A, 1B, swing arm cylinder 7, dipper cylinder 8 and scraper bowl cylinder 9 of lower running body etc..
Motor generator 12 is connect via inverter 18 with accumulating system 120.Accumulating system 120 has as electric storage means
Capacitor (electrical storage device).Also, accumulating system 120 is connect with device for revolving and driving 40.
Device for revolving and driving 40 has rotary motor 21, decomposer 22, mechanical brake 23 and rotary reducer
24 etc..Accumulating system 120 is connect via inverter 20 with rotary motor 21.Also, the output shaft of rotary motor 21
21b is connect with decomposer 22 and rotary reducer 24.
The output shaft 24A of rotary reducer 24 is connect with mechanical brake 23.Rotary reducer 24 is provided with for supplying
The lower part lubricating oil introducing port 76 of lubricating oil and top lubricating oil introducing port 74 for removal of lubricant.
Rotary motor 21 is worked as the revolution for revolution driving upper rotation 3 with electric motor.Also,
Mechanical brake 23 works as the brake apparatus for applying mechanical braking to upper rotation 3.
Operating device 26 has operating stick 26A, operating stick 26B, pedal 26C.Operating stick 26A, operating stick 26B and pedal
26C is connect with control valve 17 and pressure sensor 29 respectively via fluid pressure line 27 and 28.Also, pressure sensor 29 with
The controller 30 for carrying out the drive control of electric system connects.
Controller 30 is the control device as main control unit for carrying out the drive control of hybrid earth mover.Controller 30
By including that CPU (Central Processing Unit) and the arithmetic processing apparatus of internal storage are constituted.The controller 30
The drive control being stored in internal storage is executed by CPU, and scheduled drive control is executed with program.
Specifically, the signal supplied from pressure sensor 29 is converted speed command by controller 30, and it is based on the letter
Number carry out rotary motor 21 drive control.At this point, the signal supplied from pressure sensor 29, which becomes to represent, to be made back
Rotation mechanism 2 turns round and is operated by driver the signal of the operating quantity of operating device 26.
And controller 30 carries out the operation control of motor generator 12.Here the operation control of motor generator 12 refers to
Carry out the control of electronic (auxiliary) operation or the switching of generator operation.
And then controller 30 is configured the charge and discharge control of the capacitor on accumulating system 120.Specifically, control
The operating status of charged state of the device 30 based on capacitor, the operating status of motor generator 12 and rotary motor 21 into
The switching control of the boost action of the type of voltage step-up/down converter of row accumulating system 120 and decompression movement.
In present embodiment, the operating status as motor generator 12 has electronic (auxiliary) operating status, power generation fortune
Both operating statuses of row state.Also, as the operating status of rotary motor 21 there is power to run and regenerate operation
Both operating statuses.In addition, controller 30 also carries out the control of the amount (charging current or charging power) to charge to capacitor.
Excavator 100 with above-mentioned drive system is in revolution driving upper rotation 3, by via 20 institute of inverter
The electric power of supply drives rotary motor 21.The rotary force of the output shaft 21b of rotary motor 21 slows down via revolution
Device 24 passes to the output shaft 40A of device for revolving and driving 40.
Fig. 3 is the block diagram of device for revolving and driving 40 mounted on the excavator 100 of one embodiment of the present invention.Revolution
Driving device 40 has rotary motor 21, decomposer 22, mechanical brake 23, rotary reducer 24 and output shaft 40A
Deng.
Rotary motor 21 is electric motor.Rotary reducer 24 is connect with the output shaft side of rotary motor 21.
The rotary reducer 24 includes the 1st rotary reducer 24-1 and the 2nd rotary reducer 24-2.1st rotary reducer 24-1
And the 2nd rotary reducer 24-2 be made of respectively planetary reduction gear.
1st grade of the 1st rotary reducer 24-1 is assembled on rotary motor 21.Also, subtract becoming the 1st revolution
Mechanical brake 23 is provided on the planetary wheel carrier 46 of the output shaft of fast device 24-1.2nd grade of the 2nd rotary reducer 24-2 across
Mechanical brake 23 is assembled on the 1st rotary reducer 24-1.Also, the output shaft of the 2nd grade of the 2nd rotary reducer 24-2 is
The output shaft 40A of device for revolving and driving 40.
In addition, though it is not shown, but the output shaft 40A of device for revolving and driving 40 is connect with swing mechanism 2, passes through output shaft
The rotation power drive swing mechanism 2 of 40A.
Then, it is illustrated referring to specific structure of the Fig. 4 and Fig. 5 to device for revolving and driving 40.
In addition, Fig. 4 is the sectional view of device for revolving and driving 40, Fig. 5 is enlargedly to indicate mechanical in device for revolving and driving 40
Sectional view near brake 23.
As shown in figure 4, the 1st rotary reducer 24-1 by with sun gear 42, planetary gear 44, planetary wheel carrier 46 and
The planetary gear mechanism of internal gear 48 etc. is constituted.1st rotary reducer 24-1 is incorporated in the 1st gear-box 50 and the 2nd tooth
The inside of roller box 52.
Sun gear 42 is fixed in the output shaft 21b of rotary motor 21.Three planet teeth in the present embodiment
Wheel 44 is fastened on respectively on the sun gear 42.
Each planetary gear 44 can be rotatably pivotally supported on the pin 44a erected on planetary wheel carrier 46.Each planet tooth
Wheel 44 engages with the internal gear 48 for the inner face for being formed in the 1st gear-box 50.
The 1st gear-box 50 for being formed with internal gear 48 is fixed on the end plate 21a of rotary motor 21.In as a result,
Gear 48 (the 1st gear-box 50) not can be carried out rotation.
And the lower part of planetary wheel carrier 46 is the output shaft of the 1st rotary reducer 24-1.Planetary wheel carrier as the output shaft
46 are rotatably pivotally supported on the 2nd gear-box 52 fixed on the 1st gear-box 50 via bearing 56.
The 1st above-mentioned rotary reducer 24-1 is lubricated by lubricating oil LB.Specifically, the 1st rotary reducer 24-1 has
Have through the end plate 21a of rotary motor 21, output shaft 21b, the 1st gear-box 50, the 2nd gear-box 52 and planetary wheel carrier 46
Closed confined space is filled with lubricating oil LB in the confined space (as shown in the pears surface of Fig. 5 and Fig. 6).
In the 1st rotary reducer 24-1 of above structure, the output shaft 21b of rotary motor 21 rotates and fixed star tooth
When 42 rotation of wheel, planetary gear 44 rotates (rotation).The internal gear 48 of planetary gear 44 and the inner face for being formed in the 1st gear-box 50
Engaging.Therefore, the 1st gear-box 50 for being formed with internal gear 48 is intended to rotate by the rotary force of planetary gear 44.
However, on end plate 21a of the 1st gear-box 50 due to being fixed on rotary motor 21 as described above therefore not
It can rotation.And planetary wheel carrier 46 is configured to rotate relative to the 2nd gear-box 52.
As a result, the rotary force of planetary gear 44 works as the power for rotating planetary wheel carrier 46, planetary wheel carrier 46 as a result,
Rotation.The rotation of the output shaft 21b of rotary motor 21 is slowed down by the 1st rotary reducer 24-1 as a result, and from planetary gear
Frame 46 exports.
Then, the 2nd rotary reducer 24-2 is illustrated.The sun gear 82 of 2nd rotary reducer 24-2 is fixed on
On the planetary wheel carrier 46 of output shaft as the 1st rotary reducer 24-1.The sun gear 82 engages with multiple planetary gears 84.
In turn, planetary gear 84 engages with the internal gear for the inner wall for being formed in the 3rd gear-box 54.Planetary gear 84 is in fixed star tooth as a result,
It revolves while rotation between wheel 82 and internal gear.
In the present embodiment, there are three planetary gears 84 for the 2nd rotary reducer 24-2 tool.Each planetary gear 84 passes through
It can be rotatably supported on planetary wheel carrier by pin 84a, and rotate planetary wheel carrier by revolving while rotation.
The planetary wheel carrier constitutes the output shaft of the 2nd rotary reducer 24-2.In the present embodiment, the 2nd rotary reducer
24-2 is the retarder of final level.Therefore, the planetary wheel carrier for becoming the output shaft of the 2nd rotary reducer 24-2 is rotary reducer
24 output shaft 40A.
By above structure, device for revolving and driving 40 reduces the revolving speed of the output shaft 21b of rotary motor 21 and increases
The torque of output shaft 40A.
In addition, in the present embodiment, being set as being made up of the 1st rotary reducer 24-1 and the 2nd rotary reducer 24-2
The deceleration device structure of the two-level configuration of rotary reducer 24, but the series of the retarder of rotary reducer 24 is not limited to
This, and can be based on rotary motor 21 output and swing mechanism 2 needed for torque etc. suitably set.
Then, mechanical brake 23 is illustrated.
Mechanical brake 23 is hyperphoric brake (the デ ィ ス プ レ ー サ ブ レ ー with brake disc 60 and brake plate 62
キ).The mechanical brake 23 be arranged on the 2nd gear-box 52 as fixed part and the planetary wheel carrier 46 as output shaft it
Between.
Brake disc 60 has disc-shape as shown in Figure 6, and the insertion hole 65 being inserted into for planetary wheel carrier 46 is formed in center.
Also, spline tooth 60a is formed in the inner circumferential in the insertion hole 65.
Spline 70 (output shaft side spline) is formed on the peripheral part (part for being equipped with brake disc 60) of planetary wheel carrier 46.
The spline 70 is formed as (direction indicated in figure with the arrow Z1, Z2) extension along the vertical direction on the periphery of planetary wheel carrier 46.
In addition, in the following description, 21 side of rotary motor is known as upside (arrow relative to planetary wheel carrier 46 sometimes
Z1 direction side), and the side opposite with 21 side of rotary motor is known as the downside (direction arrow Z2 by opposite planetary wheel carrier 46
Side).
The spline tooth 60a being formed in brake disc 60, which is configured to engage with the spline 70 being formed on planetary wheel carrier 46, (to be nibbled
It closes).As a result, in the state that brake disc 60 is installed in planetary wheel carrier 46, brake disc 60 and planetary wheel carrier 46 connect as spline
The structure connect.
In this way, brake disc 60 becomes from planetary wheel carrier 46 in the state that brake disc 60 is connect with 46 spline of planetary wheel carrier
The state extended on the outside of towards radius of gyration direction.Also, although brake disc 60 will not be rotated relative to planetary wheel carrier 46, at
For the state that can be moved on the axial direction of planetary wheel carrier 46 (direction of arrow Z1, Z2 in Fig. 4 and Fig. 5).
Brake plate 62 is provided in the two sides up and down of brake disc 60.Brake plate 62 also has disc-shape, although it is not shown,
But the insertion hole that embedding state insertion is swum for planetary wheel carrier 46 is formed in center.Also, the shape on the periphery of brake plate 62
At there is spline tooth.
Spline 72 is formed on the cricoid inner wall part (part for being equipped with brake plate 62) of 2nd gear-box 52.The spline
72 with (direction indicated in Fig. 4 and Fig. 5 with arrow Z1, Z2) extends along the vertical direction on the inner wall of the 2nd gear-box 52
Mode is formed.
The spline tooth formed on brake plate 62 structure in a manner of engaging with the spline 72 being formed on the 2nd gear-box 52
At.Therefore, in the state that brake plate 62 is installed in the 2nd gear-box 52, brake plate 62 and the 2nd gear-box 52 connect as spline
The structure connect.
In this way, brake plate 62 becomes from the 2nd gear-box in the state that brake plate 62 is connect with 52 spline of the 2nd gear-box
52 states extended towards direction of the rotating radius inside.Also, brake plate 62 cannot be rotated relative to the 2nd gear-box 52, but at
For the state that can be moved on the axial direction of planetary wheel carrier 46 (direction of arrow Z1, Z2).
Also, the top of brake plate 62 in upside, piston 64 is on the axial direction of planetary wheel carrier 46 (direction arrow Z1, Z2)
The state configuration that can be moved.Piston 64 is pressed and be always pressed against on the brake plate 62 of upside by spring 66.In addition, this reality
It applies in mode as spring 66 using coil spring, it can be to obtain the multistage weight of high output compared with thin tail sheep but be also able to use
Disc stack spring.
As described above, any one in brake disc 60 and brake plate 62 can be moved up in the axial direction of planetary wheel carrier 46
It is dynamic.Therefore, when brake plate 62 is pressed by piston 64, brake disc 60 clips pressing by upper and lower brake plate 62.
Overlay film 63 covering big by coefficient of friction of the surface of brake disc 60 (referring to Fig. 6).Also, brake disc 60 is braked plate
62 clip and are pressed, and mechanical brake 23 generates the brake force that brake disc 60 to be prevented rotates as a result,.
As described above, brake disc 60 becomes the opposite not revolvable structure of planetary wheel carrier 46.Brake disc 60 is acted on as a result,
On brake force become make planetary wheel carrier 46 rotation stop brake force (brake force).
The hydraulic space 68 that can supply working oil is formed between piston 64 and the 2nd gear-box 52.Also, hydraulic
Brake release plate 67 is connected on space 68.In turn, the seal members such as O-ring are configured between piston 64 and the 2nd gear-box 52
91 are sealed, to prevent the working oil in hydraulic space 68 from leaking out.
Brake release plate 67 is connect with operating device 26.Also, from pioneer pump 15 via operating device 26, fluid pressure line
27a (Fig. 2 reference.) and brake release plate 67 when supplying hydraulic to hydraulic space 68, piston 64 is pushed away under the action of hydraulic
It rises, becomes the power of urges brake plate 62 as a result, mechanical brake 23 becomes the state of brake release.
In addition, the mechanical brake 23 of above structure is controlled as, braking is released when upper rotation 3 is turned round, upper
State when portion's revolving body 3 stops as braking operation.
As shown in Figure 4 and 5, mechanical brake 23 is arranged on from lower part lubricating oil introducing port 76 to top lubricating oil
The lubricating oil LB of introducing port 74 the midway through route.Also, as Fig. 5 is indicated with expanding, mechanical brake 23
Brake disc 60 extends from planetary wheel carrier 46 towards gear-box 50,52, and brake plate 62 is from the 2nd gear-box 52 towards planetary wheel carrier 46
Extend.
Therefore, the brake disc 60 and brake plate 62 for constituting mechanical brake 23 become to be extended in the flow path of lubricating oil LB
Structure.Therefore, in the structure that only brake disc and brake plate extend in the flow path of lubricating oil LB, brake disc 60 and braking
Plate 62 is possible to hinder the flowing of lubricating oil LB.
In mechanical brake 23 involved in present embodiment, especially brake disc 60 is prolonged in the flow path of lubricating oil LB
It stretches, therefore, very big influence can be carried out on the fluxion strap of lubricating oil LB.
Therefore, in the present embodiment, as shown in fig. 6, to be formed by the inner circumferential in the insertion hole 65 of brake disc 60
The structure of toothless portion) 61 is formed on spline tooth 60a.The toothless portion) 61 can be readily formed for example, by laser processing etc..
In the present embodiment, the example that 4 toothless portion)s 61 are formed with 90 ° of intervals is shown.Also, in present embodiment
In, the structure of two teeth of shortcoming spline tooth 60a is set as in each toothless portion) 61.
In this way, when forming toothless portion) 61 in brake disc 60, as shown in Figure 5 and 7, spline 70 and brake disc 60 it
Between form gap.In this way, the forming position of toothless portion) 61 is as lubrication by forming gap between spline 70 and brake disc 60
The lubricating oil flow path of oily LB flowing works the flowing of lubricating oil LB (in Fig. 5, Fig. 7, Fig. 8 indicated by an arrow).
The lubricating oil LB of the lower space 77 is flowed by being formed in acting as in brake disc 60 as lubricating oil flow path
Toothless portion) 61 is flowed between multiple brake discs 60, cooled brake disc 60 and brake plate 62.Even if brake disc as a result,
60 and brake plate 62 with multistage is constituted when, not only on the outside of brake disc 60, be clipped between brake disc 60 and brake plate 62
It is sufficiently cooled.
In this way, in the present embodiment, lubricating oil LB flows through the forming position of the toothless portion) 61 as lubricating oil flow path, by
This, can swimmingly flow through the setting position of the mechanical brake 23 for the 1st rotary reducer 24-1.
That is, flowing through the forming position of toothless portion) 61 by lubricating oil LB, lubricating oil LB also flows into each brake disc 60 of stacking
Between the spatial portion that is formed between the spatial portion and brake disc 60 and brake plate 62 that are formed.
Since brake disc 60 and brake plate 62 overlap, the equipping position of mechanical brake 23 is lubricating oil LB
Flowing be easy obstruction position.Also, the equipping position of mechanical brake 23 is in braking due to brake disc 60 and system
Movable plate 62 slides and generates the position of heat.Therefore, if assuming not forming flow path 61, the temperature of mechanical brake 23 rises.
But it can make to lubricate in the equipping position of mechanical brake 23 by the way that flow path 61 is arranged in the present embodiment
Oily LB is flowed between brake disc 60 and brake plate 62 and leaves part.Therefore, even if to generate the machine of big calorimetric in braking
Tool brake 23 also can efficiently be cooled down by lubricating oil LB.
Also, in the hypodontia that the flow for the lubricating oil LB that toothless portion) 61 flows can be formed in brake disc 60 by change
The configuration number in portion 61 changes the hypodontia number of each toothless portion) 61 to adjust.
Specifically, by the number for the toothless portion) 61 that more configuration is formed in brake disc 60 and by more setting
The hypodontia number for setting each toothless portion) 61, can reduce the flow resistance of toothless portion) 61, thus make the flow of lubricating oil LB more.
In addition it is contemplated that when making the configuration number of toothless portion) 61 mostly and keeping the hypodontia number of each toothless portion) 61 more, row
Engaging strength reduction between star wheel frame 46 and brake disc 60.The configuration number of toothless portion) 61 and setting for hypodontia number as a result,
Surely it is also required to consider planetary wheel carrier 46 and the engaging intensity of brake disc 60 etc. to determine.
However, in the above-described embodiment, to be provided as the toothless portion) that lubricating oil flow path works in brake disc 60
61 structure.But the position that toothless portion) 61 is arranged is not limited to brake disc 60, can also engage with spline tooth 60a
The toothless portion) that lubricating oil flow path works is provided as on spline 70 (being set to planetary wheel carrier 46).
Fig. 8 shows the variations of above embodiment.In variation, set on the spline 70 for being set to planetary wheel carrier 46
It is equipped with toothless portion) 61A.By the way that the structure is arranged, lubricating oil LB is flowed between multiple brake discs 60 also by toothless portion) 61, and
Cooled brake disc 60 and brake plate 62.Even if brake disc 60 and brake plate 62 are constituted as a result, with multistage, not only on the outside of system
Moving plate 60, be sandwiched between brake disc 60 and brake plate 62 can also be sufficiently cooled.
Furthermore it is possible to be configured to, be provided as that lubricating oil flow path works on spline tooth 60a and 70 both sides of spline is lacked
Teeth portion.
Also, it in the above-described embodiment, shows and is set in the brake disc 60 that the spline 70 with planetary wheel carrier 46 engages
The example of toothless portion) 61 is set.But it can also be on the brake plate 62 engaged with the spline 72 being formed on the 2nd gear-box 52
It is provided as the toothless portion) that lubricating oil flow path works, and then lubricating oil flow path can also be provided as on spline 72 and worked
Toothless portion).
As described above, spline tooth 60a and spline 70 clamped position and spline 72 and the flower that is formed on brake plate 62
On at least one party of clamped position between key, according to the size of excavator 100 and the supply amount of required lubricating oil LB,
The toothless portion) 61 (lubricating oil flow path) to be circulated by the way that lubricating oil LB is suitably arranged, can reliably cool down mechanical brake 23,
And the part that can be lubricated the needs for constituting the 1st rotary reducer 24-1 is reliably lubricated.
More than, the preferred embodiment of the present invention is described in detail, but the present invention is not limited to above-mentioned implementation
Mode can be subject to various modifications and displacement without departing from the scope of the present invention to above embodiment.
Claims (2)
1. a kind of device for revolving and driving, which is characterized in that
It includes
Driving source, driving rotary body；And
Rotary reducer,
The rotary reducer includes
Shell is filled with lubricating oil；
Retarder can rotatably be disposed in the shell, and connect with above-mentioned driving source；And
Mechanical brake is disposed in above-mentioned shell, and has brake plate, which has and be formed in above-mentioned retarder
The spline tooth of output shaft side spline engaging on output shaft,
Above-mentioned brake plate be provided in above-mentioned shell lubricating oil introducing port set by the top of above-mentioned rotary reducer and
On the path of lubricating oil between lubricating oil introducing port set by the lower part of above-mentioned rotary reducer,
It is formed between above-mentioned output shaft side spline and the brake disc of above-mentioned mechanical brake by the hypodontia of above-mentioned spline tooth
Gap, above-mentioned gap is as the lubricating oil introducing port set by the top of above-mentioned rotary reducer and above-mentioned rotary reducer
The flow path of the lubricating oil flowed between lubricating oil introducing port set by lower part works,
Above-mentioned lubricating oil is flowed between multiple above-mentioned brake discs by above-mentioned gap, and cooling above-mentioned brake disc.
2. device for revolving and driving as described in claim 1, which is characterized in that
With 90 ° of intervals, above-mentioned hypodontia is set.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014074520A JP6289976B2 (en) | 2014-03-31 | 2014-03-31 | Slewing drive |
| JP2014-074520 | 2014-03-31 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104947731A CN104947731A (en) | 2015-09-30 |
| CN104947731B true CN104947731B (en) | 2019-07-30 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510114387.8A Expired - Fee Related CN104947731B (en) | 2014-03-31 | 2015-03-16 | Device for revolving and driving |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6289976B2 (en) |
| CN (1) | CN104947731B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109328015B (en) * | 2016-07-19 | 2021-06-01 | 有限会社西兴业八头 | Accessory attached to front end of boom of work vehicle, work vehicle provided with same, and accessory brake |
| JP6274342B1 (en) * | 2017-04-20 | 2018-02-07 | トヨタ自動車株式会社 | transmission |
| JP6384585B1 (en) * | 2017-12-13 | 2018-09-05 | トヨタ自動車株式会社 | transmission |
| CN110637128B (en) * | 2018-04-25 | 2021-05-18 | 株式会社小松制作所 | Operation device of motor-driven road grader |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2086317U (en) * | 1991-03-09 | 1991-10-09 | 宁波液压马达厂 | Hydraulic gearing with machinery brake characteristic |
| CN1300344A (en) * | 1999-05-07 | 2001-06-20 | 日立建机株式会社 | Hydraulic motor with brake device |
| EP1752586A2 (en) * | 2001-06-11 | 2007-02-14 | Brueninghaus Hydromatik Gmbh | Transmission system for hydraulically propulsed vehicle with a slewing upper body and with a hydrostatic piston engine with position feedback |
| CN102510921A (en) * | 2010-02-22 | 2012-06-20 | 日立建机株式会社 | Swing device for construction machinery |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0740693Y2 (en) * | 1986-04-25 | 1995-09-20 | 日立建機株式会社 | Hydraulic motor with brake device |
| JPH0551943A (en) * | 1991-08-23 | 1993-03-02 | Iseki & Co Ltd | Excavating service vehicle |
| JP3776365B2 (en) * | 2002-02-20 | 2006-05-17 | 本田技研工業株式会社 | Lubrication structure of hydraulic clutch |
| CN202251561U (en) * | 2011-08-29 | 2012-05-30 | 桂林禾田建筑机械有限公司 | Built-in brake device of revolving driver of hydraulic-electro hybrid power excavator |
| JP5969806B2 (en) * | 2012-04-26 | 2016-08-17 | コベルコ建機株式会社 | Construction machine drive |
-
2014
- 2014-03-31 JP JP2014074520A patent/JP6289976B2/en active Active
-
2015
- 2015-03-16 CN CN201510114387.8A patent/CN104947731B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2086317U (en) * | 1991-03-09 | 1991-10-09 | 宁波液压马达厂 | Hydraulic gearing with machinery brake characteristic |
| CN1300344A (en) * | 1999-05-07 | 2001-06-20 | 日立建机株式会社 | Hydraulic motor with brake device |
| EP1752586A2 (en) * | 2001-06-11 | 2007-02-14 | Brueninghaus Hydromatik Gmbh | Transmission system for hydraulically propulsed vehicle with a slewing upper body and with a hydrostatic piston engine with position feedback |
| CN102510921A (en) * | 2010-02-22 | 2012-06-20 | 日立建机株式会社 | Swing device for construction machinery |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2015197144A (en) | 2015-11-09 |
| CN104947731A (en) | 2015-09-30 |
| JP6289976B2 (en) | 2018-03-07 |
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