CN104769316A - Shovel - Google Patents
Shovel Download PDFInfo
- Publication number
- CN104769316A CN104769316A CN201380057855.1A CN201380057855A CN104769316A CN 104769316 A CN104769316 A CN 104769316A CN 201380057855 A CN201380057855 A CN 201380057855A CN 104769316 A CN104769316 A CN 104769316A
- Authority
- CN
- China
- Prior art keywords
- rotary
- gear
- space
- lubricant oil
- box
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000000314 lubricant Substances 0.000 claims description 93
- 239000003638 chemical reducing agent Substances 0.000 claims description 91
- 238000007789 sealing Methods 0.000 claims description 15
- 230000015572 biosynthetic process Effects 0.000 claims description 10
- 238000005461 lubrication Methods 0.000 claims description 5
- 239000003921 oil Substances 0.000 description 110
- 235000015927 pasta Nutrition 0.000 description 13
- 230000000694 effects Effects 0.000 description 6
- 239000003990 capacitor Substances 0.000 description 5
- 239000004570 mortar (masonry) Substances 0.000 description 5
- 230000003068 static effect Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000033001 locomotion Effects 0.000 description 4
- 238000010276 construction Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000003756 stirring Methods 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000008929 regeneration Effects 0.000 description 1
- 238000011069 regeneration method Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/08—Superstructures; Supports for superstructures
- E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
- E02F9/12—Slewing or traversing gears
- E02F9/121—Turntables, i.e. structure rotatable about 360°
- E02F9/123—Drives or control devices specially adapted therefor
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/202—Mechanical transmission, e.g. clutches, gears
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/2058—Electric or electro-mechanical or mechanical control devices of vehicle sub-units
- E02F9/2095—Control of electric, electro-mechanical or mechanical equipment not otherwise provided for, e.g. ventilators, electro-driven fans
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
- F16H57/0445—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control for supply of different gearbox casings or sections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0482—Gearings with gears having orbital motion
- F16H57/0486—Gearings with gears having orbital motion with fixed gear ratio
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0415—Air cooling or ventilation; Heat exchangers; Thermal insulations
- F16H57/0416—Air cooling or ventilation
Abstract
A shovel according to an embodiment of the present invention is provided with the following: a revolving electric motor (21); a multistage revolving speed reduction mechanism (24) connected to the revolving electric motor (21); a space (SP1) accommodating a planetary gear mechanism that constitutes a first revolving speed reduction mechanism (24-1) which is the first stage of the multistage revolving speed reduction mechanism (24); and a space (SP2) accommodating a planetary gear mechanism that constitutes a second revolving speed reduction mechanism (24-2) which is the second stage of the multistage revolving speed reduction mechanism (24)
Description
Technical field
The present invention relates to the excavator possessing multi-stage rotary speed reducer.
Background technique
In the past, there will be a known the excavator possessing swirl gear, described swirl gear comprises rotary motor, the 1st rotary reducer be connected on the output shaft of rotary motor, the 2nd rotary reducer be connected on the output shaft of the 1st rotary reducer, be connected to the 3rd rotary reducer on the output shaft of the 2nd rotary reducer and be connected to the swing circle (for example, referring to patent documentation 1) on the output shaft of the 3rd rotary reducer.
In this excavator, if rotary motor rotates, the lubricant oil of then accommodating in the space of the planetary gears of formation the 1st rotary reducer forms the liquid level of mortar shape by centrifugal force, the pipeline through the top being connected to the 1st rotary reducer is discharged by baffle-box.In addition, if the rotation of rotary motor stops, be then discharged to lubricant oil in baffle-box by gravity through throttle orifice and be connected to the 1st rotary reducer bottom pipeline and return gradually in the space of the 1st rotary reducer.
Therefore, this excavator, when revolution action is carried out intermittently repeatedly, suppresses the rotary load of gear by maintaining less by the amount of the lubricant oil in space, the rotation of the gear when revolution action is risen to the time shorten of the rotating speed of hope.
Conventional art document
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 2008-232270 publication
Summary of the invention
The technical problem that invention will solve
But, excavator described in patent documentation 1, in order to make three spaces of accommodating three rotary reducers respectively be communicated with, the 1st rotary reducer and other rotary reducers can not use different lubricant oil, and the lubricant oil with the characteristics match of each rotary reducer can not be utilized.
Point in view of the above problems, can use various kinds of lubricating oil to moisten desirable to provide a kind of the excavator changing multi-stage rotary speed reducer.
For the means of technical solution problem
Excavator involved by embodiments of the invention possesses: rotary motor; The multi-stage rotary speed reducer be connected with described rotary motor; The 1st grade of the described multi-stage rotary speed reducer of collecting formation is the 1st confined space of the gear mechanism of the 1st rotary reducer; And collecting forms the 2nd confined space of the 2nd grade of the described multi-stage rotary speed reducer i.e. gear mechanism of the 2nd rotary decelerating mechanism.
The effect of invention
By technique scheme, provide a kind of various kinds of lubricating oil that can use to lubricate the excavator of multi-stage rotary speed reducer.
Accompanying drawing explanation
Fig. 1 is the side view of the excavator of the device for revolving and driving assembling one embodiment of the present invention.
Fig. 2 is the block diagram of the structure of the drive system representing the excavator shown in Fig. 1.
Fig. 3 is the block diagram of the structure of the device for revolving and driving representing one embodiment of the present invention.
Fig. 4 is the plan view of the device for revolving and driving of Fig. 3.
Fig. 5 is the V-V line sectional view of Fig. 4.
Fig. 6 be the state of device for revolving and driving when representing that the output shaft of rotary motor is static, the VI-VI line sectional view of Fig. 4.
Fig. 7 be the state of device for revolving and driving when representing that the output shaft of rotary motor rotates, the VI-VI line sectional view of Fig. 4.
Fig. 8 is the sectional view of the structure of the device for revolving and driving representing another embodiment of the present invention.
Fig. 9 is the sectional view of the structure of the device for revolving and driving representing another other mode of executions of the present invention.
Figure 10 is the sectional view of the structure of the device for revolving and driving representing another other mode of executions of the present invention.
Embodiment
First, the overall structure of excavator of device for revolving and driving and the structure of drive system that assemble one embodiment of the present invention are described.Fig. 1 is the side view of the excavator representing the device for revolving and driving assembling one embodiment of the present invention.In addition, excavator is an example of construction implement, and the device for revolving and driving of one embodiment of the present invention can be assembled into be had in the construction implement of pivotal for solid of rotation mechanism.
On the lower running body 1 of the excavator shown in Fig. 1, be equipped with upper rotation 3 via swirl gear 2.Upper rotation 3 is installed with swing arm 4.The front end of swing arm 4 is provided with dipper 5, the front end of dipper 5 is provided with scraper bowl 6.Swing arm 4, dipper 5 and scraper bowl 6 be passive arm cylinder 7, dipper cylinder 8 and scraper bowl cylinder 9 hydraulic driving respectively.Upper rotation 3 is provided with operator cabin 10, and is equipped with the power sources such as engine.
In addition, the excavator shown in Fig. 1 has the excavator of accumulation to the electric accumulator of the electric power of device for revolving and driving supply.But the present invention can be applicable to the arbitrary excavator adopting motoring, such as, also can be applicable to by the power driven excavator from external power supply supply electric power.
Fig. 2 is the block diagram of the structure of the drive system representing the excavator shown in Fig. 1.In fig. 2, represent mechanical dynamic system with doublet, represent high-pressure and hydraulic pipeline with heavy line, pilot line represented by dashed line, represent electric drive/control system by fine line.
Engine 11 as mechanical type drive portion and the motor generator set 12 as auxiliary drive section are connected with two input shafts of variable-speed motor 13 respectively.On the output shaft of variable-speed motor 13, be connected with main pump 14 and pioneer pump 15 as oil hydraulic pump.On main pump 14, be connected with control valve 17 via high-pressure and hydraulic pipeline 16.In addition, on pioneer pump 15, operation equipment 26 is connected with via pilot line 25.
Control valve 17 is control gear of the control of the hydraulic system of carrying out hybrid earth mover.Lower running body 1 with oil hydraulic motor 1A (right with) and 1B (left with), swing arm cylinder 7, dipper cylinder 8 and scraper bowl cylinder 9 be connected with control valve 17 via high-pressure and hydraulic pipeline.
On motor generator set 12, be connected to the accumulating system (electric accumulator) 120 of the capacitor comprised as electric storage means via inverter 18.On accumulating system 120, be connected to the rotary motor 21 as electronic operation important document via inverter 20.The output shaft 21b of rotary motor 21 is connected with resolver 22 and rotary reducer 24.The output shaft 24A of rotary reducer 24 is connected with mechanical brake 23.By rotary motor 21, resolver 22, mechanical brake 23 and rotary reducer 24, form device for revolving and driving 40 as load drive system.Here, rotary motor 21 is equivalent to the revolution electric motor for upper rotation 3 being turned round driving, and mechanical brake 23 is equivalent to braking device upper rotation 3 mechanically being applied to braking.
Operation equipment 26 comprises operating handle 26A, operating handle 26B, pedal 26C.Operating handle 26A, operating handle 26B and pedal 26C are connected with control valve 17 and pressure transducer 29 via hydraulic pipe line 27 and 28 respectively.Pressure transducer 29 is connected with the controller 30 of the drived control carrying out electric power system.
Controller 30 is the control gear as master control part of the drived control carrying out hybrid earth mover.Controller 30, by comprising CPU (Central Processing Unit) and the arithmetic processing apparatus of internal storage is formed, is perform the program of the drived control be kept in internal storage and the device that realizes by CPU.
The signal supplied from pressure transducer 29 is transformed to speed command by controller 30, carries out the drived control of rotary motor 21.The signal supplied from pressure transducer 29 is equivalent to represent the signal of operation amount swirl gear 2 being turned round and operates operation equipment 26.
Controller 30 controls (switching of electronic (assisting) operation or generator operation) and the type of voltage step-up/down converter of drived control accumulating system 120 by the operation carrying out motor generator set 12, carries out the charge and discharge control of capacitor.Controller 30 is based on the running state (power runs or regeneration runs) of the charged state of capacitor, the running state (electronic (assisting) is run or generator operation) of motor generator set 12 and rotary motor 21, carry out the boost action of the type of voltage step-up/down converter of accumulating system 120 and the switching controls of step-down action, carry out the charge and discharge control of capacitor thus.In addition, controller 30 amount (charging current or charging power) that also subtend capacitor charges as described later controls.
In the operation of the excavator of structure as described above, in order to upper rotation 3 is turned round driving, by the electric drive rotary motor 21 supplied via inverter 20.The rotating force of the output shaft 21b of rotary motor 21 is transmitted by via rotary reducer 24 and the mechanical brake 23 output shaft 40A to device for revolving and driving 40.
Fig. 3 is the block diagram of the structure of the device for revolving and driving 40 representing one embodiment of the present invention.As described above, device for revolving and driving 40 comprises electric motor as driving source and rotary motor 21.Rotary reducer 24 is connected in the output shaft side of rotary motor 21.
Specifically, rotary reducer 24 has 3 level structures of the 1st rotary reducer 24-1, the 2nd rotary reducer 24-2 and the 3rd rotary reducer 24-3.1st rotary reducer 24-1, the 2nd rotary reducer 24-2 and the 3rd rotary reducer 24-3 are made up of planetary speed reducer respectively.More particularly, the 1st rotary reducer 24-1 of the 1st grade is assembled on rotary motor 21.In addition, on the planetary wheel carrier 46 of output shaft becoming the 1st rotary reducer 24-1, the disk type braker as mechanical brake 23 is provided with.In addition, the 2nd rotary reducer 24-2 of the 2nd grade is assembled on the 1st rotary reducer 24-1 across mechanical brake 23, and the 3rd rotary reducer 24-3 of 3rd level is assembled on the 2nd rotary reducer 24-2.Further, the output shaft of the 3rd rotary reducer 24-3 is the output shaft 40A of device for revolving and driving 40.In addition, although do not illustrate, the output shaft 40A of device for revolving and driving 40 is connected with swirl gear 2, drives swirl gear 2 by the rotating force of output shaft 40A.
Then, be described with reference to the concrete structure of Fig. 4 ~ Fig. 7 to device for revolving and driving 40.In addition, Fig. 4 is the plan view of device for revolving and driving 40, and the dotted line in Fig. 4 represents the hidden line of the main composition assembly of the 1st rotary reducer 24-1.In addition, Fig. 5 is the V-V line sectional view of Fig. 4.
In addition, Fig. 5 is the sectional view of the part forming the 1st rotary reducer 24-1 in device for revolving and driving 40 and mechanical brake 23.In the present embodiment, the sun gear 42 forming the planetary speed reducer of the 1st rotary reducer 24-1 is fixed on the output shaft 21b of rotary motor 21.Sun gear 42 is fastened on 3 planetary pinions 44 respectively.Planetary pinion 44 can be rotated to support on via pin 44a on the planetary wheel carrier 46 of output shaft of formation the 1st rotary reducer 24-1 respectively.Further, each planetary pinion 44 engages with the internal gear 48 of the internal surface being formed in the 1st gear-box 50.
The 1st gear-box 50 being formed with internal gear 48 is fixed on the end plate 21a of rotary motor 21, and oneself can not rotate.On the other hand, the 2nd gear-box 52 that the planetary wheel carrier 46 forming output shaft is rotatably fixed on the 1st gear-box 50 via bearing 56 supports.
In addition, the 1st above-mentioned rotary reducer 24-1 have for by the lubricant oil of each gear of lubrication by the airtight structure of end plate 21a, the output shaft 21b of rotary motor 21, the 1st gear-box 50, the 2nd gear-box 52 and planetary wheel carrier 46.
In the 1st rotary reducer 24-1 of structure such above, if rotary motor 21 output shaft 21b rotate and sun gear 42 rotates, then planetary pinion 44 rotates (rotation).Planetary pinion 44 engages with the internal gear 48 on the internal surface being formed in the 1st gear-box 50, and by the rotating force of planetary pinion 44, the 1st gear-box 50 being formed with internal gear 48 will rotate.But the 1st gear-box 50 is because the end plate 21a being fixed on rotary motor 21 can not rotate.As a result, can oneself be rotated by the planetary wheel carrier 46 supported rotatably on one side by planetary gear bearing 44.By gearing such above, the rotation of the output shaft 21b of rotary motor 21 is decelerated, and is exported by from planetary wheel carrier 46.
Then, the structure of the disk type braker forming mechanical brake 23 is described.Disk type braker is formed in as between the 2nd gear-box 52 of fixing part and the planetary wheel carrier 46 as output shaft.Brake disc 60 extends outside the turning radius direction of planetary wheel carrier 46 from the periphery of planetary wheel carrier 46.Although brake disc 60 can not rotate relative to planetary wheel carrier 46, can axially moving at planetary wheel carrier 46.Specifically, brake disc 60 is connected with planetary wheel carrier 46 via the connecting structure that such as spline joint is such.
Keep plate 62 is configured with in the both sides up and down of brake disc 60.Although keep plate 62 can not rotate relative to the 2nd gear-box 52 as fixing part, can axially moving at planetary wheel carrier 46.Specifically, keep plate 62 is connected with the inner surface side of the 2nd gear-box 52 via the connecting structure that such as spline joint is such.On the keep plate 62 of upside, so that piston 64 can be configured with in the state of the axially movement of planetary wheel carrier 46.Piston 64 is pressed by spring 66 and is always pressed on the keep plate 62 of upside.Present embodiment uses helical spring as spring 66, but also can use the disc spring that can obtain the high multistage overlap exported with less displacement.
Keep plate 62 and brake disc 60 can axially moving at planetary wheel carrier 46.Therefore, if the keep plate of upside 62 is pressed by piston 64, then brake disc 60 is clamped by upper and lower keep plate 62 and presses.The surface of keep plate 62 and brake disc 60 is covered by the overlay film that friction factor is larger.Further, clamped by brake disc 60 and press by upper and lower keep plate 62, on brake disc 60, effect will stop the braking force of the rotation of brake disc 60.In addition, brake disc 60 connects with not revolvable mode opposing rows star wheel frame 46.Therefore, the braking force acted on brake disc 60 becomes the braking force applied to planetary wheel carrier 46.
Between piston 64 and the 2nd gear-box 52, be formed with the hydraulic space 68 that can supply working oil, be connected to brake release port 69 at hydraulic space 68.In addition, between piston 64 and the 2nd gear-box 52, be configured with the sealed members 91 such as O shape ring, carry out sealing in order to avoid the working oil in hydraulic space 68 spills.If supply hydraulic pressure via operation equipment 26, hydraulic pipe line 27a (with reference to Fig. 2) and brake release port 69 to hydraulic space 68 from pioneer pump 15, then piston 64 is pushed away by hydraulic pressure, disappears, brake and removed the power that keep plate 62 presses.
In the 1st rotary reducer 24-1 of structure such above, in the present embodiment, be formed with the recess of ring-type at the upper surface of the 1st gear-box 50, the bottom surface of the recess of ring-type is formed with multiple through hole.This through hole respective in insert above-mentioned spring 66.The lower end of each spring 66 is given prominence to from the through hole of the 1st gear-box 50, is connected on the bottom surface in the hole be formed on piston 64.Further, chimeric in the recess of the ring-type of the 1st gear-box 50 have spring push part 90.Spring push part 90 is tightened by multiple bolt 92 and is fixed on the 1st gear-box 50.
By recess internal fixtion from spring push part 90 to the ring-type of the 1st gear-box 50 before, the upper end of each spring 66 is given prominence to upward from the bottom surface of the recess of ring-type.Thus, by spring push part 90 to the recess internal fixtion of the ring-type of the 1st gear-box 50 time, each spring 66 is pressed by spring push part 90 and is compressed.If spring push part 90 be fixed in the recess of the ring-type of the 1st gear-box 50, then each spring 66 becomes and is clipped between spring push part 90 and piston 64 by the state compressed.The recuperability (spring force) of each spring 66 now becomes the power compressed to brake disc 60 by piston 64 (i.e. keep plate 62), becomes the braking force applied to planetary wheel carrier 46.
Under state in the recess that spring push part 90 is fixed on the ring-type of the 1st gear-box 50, spring push part 90 entirety is accommodated in the recess of ring-type.Therefore, spring push part 90 can not be given prominence to from the fitting surface of the 1st gear-box 50 abutted with the end plate 21a (also referred to as flange) of rotary motor 21.Thus, only the fitting surface of the 1st gear-box 50 is connected on the end plate 21a of rotary motor 21.But, the upper surface of spring push part 90 is configured with the sealed members 93 such as O shape ring, carries out sealing in order to avoid the lubricant oil that the planetary pinion 44 in the 1st gear-box 50 lubricates/cools is spilt.In addition, the lower surface of spring push part 90 is also configured with the sealed members 94 such as O shape ring, carries out sealing in order to avoid the lubricant oil in being filled in the part that accommodate spring 66 spills.Equally, between the 1st gear-box 50 and the 2nd gear-box 52, be also configured with the sealed members 95 such as O shape ring, carry out sealing in order to avoid the lubricant oil in being filled in the part containing spring 66 spills.
Then, with reference to Fig. 6 and Fig. 7, the transmission of the rotary driving force in device for revolving and driving 40 is described.In addition, Fig. 6 and Fig. 7 is the VI-VI line sectional view of Fig. 4, the state of the device for revolving and driving 40 when Fig. 6 represents that the output shaft 21b of rotary motor 21 is static, the state of the device for revolving and driving 40 when Fig. 7 represents that output shaft 21b rotates.
As shown in Figure 6, the 1st rotary reducer 24-1 is made up of the planetary gears comprising sun gear 42, planetary pinion 44, planetary wheel carrier 46 and internal gear 48.In addition, the 2nd rotary reducer 24-2 is made up of the planetary gears comprising sun gear 82, planetary pinion 84, planetary wheel carrier 86 and internal gear 88.Equally, the 3rd rotary reducer 24-3 is made up of the planetary gears comprising sun gear 102, planetary pinion 104, planetary wheel carrier 106 and internal gear 108.
In the 1st rotary reducer 24-1, sun gear 42 is fixed on the output shaft 21b of rotary motor 21, engages with planetary pinion 44.Between the internal gear 48 of planetary pinion 44 on the inwall being formed at the 1st gear-box 50 and sun gear 42, rotation is on one side while revolve round the sun.In the present embodiment, the 1st rotary reducer 24-1 has 3 planetary pinions 44.3 planetary pinions 44 respectively by one side rotation while revolution and make planetary wheel carrier 46 rotate.In addition, planetary wheel carrier 46 forms the output shaft of the 1st rotary reducer 24-1.
In the 2nd rotary reducer 24-2, sun gear 82 is fixed on the planetary wheel carrier 46 as the output shaft of the 1st rotary reducer 24-1, engages with planetary pinion 84.Between the internal gear 88 of planetary pinion 84 on the inwall being formed at the 3rd gear-box 54 and sun gear 82, rotation is on one side while revolve round the sun.In the present embodiment, the 2nd rotary reducer 24-2 has 3 planetary pinions 84.3 planetary pinions 84 are rotatably supported by planetary wheel carrier 86 via pin 84a respectively, by rotation while revolution, planetary wheel carrier 86 are rotated.In addition, planetary wheel carrier 86 forms the output shaft of the 2nd rotary reducer 24-2.
In the 3rd rotary reducer 24-3, sun gear 102 is fixed on the planetary wheel carrier 86 as the output shaft of the 2nd rotary reducer 24-2, engages with planetary pinion 104.Between the internal gear 108 of planetary pinion 104 on the inwall being formed at the 3rd gear-box 54 and sun gear 102, rotation is on one side while revolve round the sun.In the present embodiment, the 3rd rotary reducer 24-3 has 3 planetary pinions 104.3 planetary pinions 104 can be rotated to support on planetary wheel carrier 106 via pin 104a respectively, by rotation while revolution, planetary wheel carrier 106 are rotated.In addition, planetary wheel carrier 106 forms the output shaft 40A of rotary reducer 24.
By said structure, the rotational speed of the output shaft 21b of rotary motor 21 reduces and the torque of output shaft 40A is increased by device for revolving and driving 40.
Specifically, device for revolving and driving 40 as shown in Figure 7, corresponding to the rotation of the clockwise high speed-low torque of output shaft 21b, makes planetary pinion 44 rotation revolution clockwise on one side counterclockwise, planetary wheel carrier 46 is turned clockwise.Further, device for revolving and driving 40 corresponds to the clockwise rotation of planetary wheel carrier 46, makes planetary pinion 84 rotation revolution clockwise on one side counterclockwise, planetary wheel carrier 86 is turned clockwise.And then device for revolving and driving 40 corresponds to the clockwise rotation of planetary wheel carrier 86, make planetary pinion 104 rotation revolution clockwise on one side counterclockwise, planetary wheel carrier 106 i.e. output shaft 40A is rotated with low speed-high torque (HT) clockwise.When output shaft 21b is rotated counterclockwise, except the sense of rotation of each gear is contrary, other are all same.
Then, with reference to Fig. 6 and Fig. 7, the motion of the lubricant oil in device for revolving and driving 40 is described.
Device for revolving and driving 40 has and is output the airtight space S P1 of axle 21b, end plate 21a, the 1st gear-box 50, the 2nd gear-box 52 and planetary wheel carrier 46.In addition, output shaft 21b is installed with not shown oil sealing, planetary wheel carrier 46 is installed with oil sealing 57.Space S P1 holds sun gear 42, planetary pinion 44, planetary wheel carrier 46, brake disc 60, keep plate 62 and piston 64, is full of by the lubricant oil LB1 represented with thinner dot pattern.In addition, space S P1 is connected with baffle-box 70 via the circulation road 72 comprising the 1st circulation road 72a and the 2nd circulation road 72b.
In addition, device for revolving and driving 40 has by the airtight space S P2 of planetary wheel carrier 46, the 2nd gear-box 52, the 3rd gear-box 54 and planetary wheel carrier 106.In addition, planetary wheel carrier 106 is installed with not shown oil sealing.Space S P2 hold sun gear 82,102, planetary pinion 84,104 and planetary wheel carrier 86,106, be full of by the lubricant oil LB2 represented with thicker dot pattern.In addition, lubricant oil LB2 is isolated from lubricant oil LB1 by oil sealing 57.In addition, lubricant oil LB2 also can be the lubricant oil with lubricant oil LB1 identical type, also can be different types of lubricant oil.Such as, in device for revolving and driving 40, the high lubricant oil LB1 rotated also can be the different types of lubricant oil of lubricant oil LB2 with low rotation.
As shown in Figure 6, when output shaft 21b is static, the horizontal L1 of the pasta of the lubricant oil LB1 in baffle-box 70 is in the position higher than the bottom surface of end plate 21a.That is, space S P1 is in the state that lubricated oily LB1 is full of.In addition, the 2nd circulation road 72b is connected with baffle-box 70 in the position that the horizontal L1 than pasta is high.In addition also can be configured to, the link position of the 2nd circulation road 72b in baffle-box 70 is adjusted.
On the other hand, as shown in Figure 7, when output shaft 21b rotates, the centrifugal pump effect of the lubricant oil LB1 in space S P1 by being brought by the planetary wheel carrier 46 rotated and brake disc 60, the ostium through the bottom being formed in space S P1 is sent into by circulation road 72.Specifically, the lubricant oil LB1 in space S P1 is sent into by the 1st circulation road 72a between brake disc 60 and keep plate 62, and is discharged by baffle-box 70.In addition, the dotted arrow of Fig. 7 represents the flowing of lubricant oil LB1.
In addition, in planetary wheel carrier 46, oil circuit 74 is provided with, lubricant oil LB1 can be supplied inside the radial direction of brake disc 60.By oil circuit 74, device for revolving and driving 40 can form the flowing of the lubricant oil LB1 on the surface along brake disc 60, brake disc 60 can be cooled efficiently.In addition, in the present embodiment, between two keep plates 62, configure 1 brake disc 60, but also can adopt the structure using multiple brake disc 60.Specifically, also can adopt 4 keep plates 62 respective between configure the structure of 3 brake discs 60 respectively.In the case, device for revolving and driving 40 can promote the circulation of the lubricant oil LB1 be present in the space between two adjacent brake discs 60 by oil circuit 74.In addition, oil circuit 74 also can extend near the running shaft of planetary wheel carrier 46, is connected with a part of space S P1 for the below being in sun gear 42 through 1 or multiple opening.
In addition, space S P1 is discharged to baffle-box 70, so the air intake will be in baffle-box 70 through the 2nd circulation road 72b through the 1st circulation road 72a due to a part of lubricant oil LB1.As a result, the lubricant oil LB1 in space S P1 is formed the pasta L2 of mortar shape by the Stirring of the output shaft 21b of rotary motor 21.In addition, the 1st circulation road 72a and the 2nd circulation road 72b is in not by the unrestricted state of the flowing of the restriction lubricant oil such as throttle orifice.
Then, by the lubricant oil LB1 discharged from space S P1, the pasta of the lubricant oil LB1 in baffle-box 70 reaches the horizontal L3 more top than the 2nd circulation road 72b.In the case, the tap hole of the lubricant oil LB1 in baffle-box 70 through the 2nd circulation road 72b and the top that is formed in space S P1 flows into space S P1.In addition, tap hole is such as formed in top or the inside of internal gear 48.Flow into lubricant oil LB1 space S P1 after internal gear 48, planetary pinion 44, sun gear 42 and planetary wheel carrier 46 being lubricated from baffle-box 70, with formed mortar shape pasta L2 space S P1 in lubricant oil LB1 collaborate.
In addition, in baffle-box 70, be provided with the fan for the example as heat exchange mechanism 76 cooled by the lubricant oil LB1 in baffle-box 70.Therefore, the temperature that the temperature ratio flowing into the lubricant oil LB1 space S P1 from baffle-box 70 is discharged to the lubricant oil LB1 baffle-box 70 from space S P1 is low.As a result, the lubricant oil LB1 in internal gear 48, planetary pinion 44, sun gear 42, planetary wheel carrier 46 and space S P1 can cool by the lubricant oil LB1 flow into space S P1 from baffle-box 70.In addition, heat exchange mechanism 76 also can be formed in the mechanism beyond the fans such as radiating fin on the outer surface of baffle-box 70.In addition, baffle-box 70 can as heat exchange mechanism due to himself, so also additional heat exchange mechanism 76 can be omitted.In addition, baffle-box 70 also can arrange jagged stream in inside, after being reliably cooled, turns back to space S P1 through the 2nd circulation road 72b to make the lubricant oil LB1 flowed into from the 1st circulation road 72a in baffle-box 70.In addition, baffle-box 70 also can possess the refrigerator device that can adjust interior pressure.
Then, if the rotation of output shaft 21b stops, then the pasta of the lubricant oil LB1 formation level in space S P1 in the space S P1 of the pasta L2 of mortar shape is defined.Further, the centrifugal pump event resolves of the lubricant oil LB1 in baffle-box 70 owing to causing because of the rotation of planetary wheel carrier 46 and brake disc 60, so return to space S P1, until its pasta becomes lower than horizontal L3 through the 1st circulation road 72a and the 2nd circulation road 72b.In addition, the lubricant oil LB1 in baffle-box 70 its pasta become lower than horizontal L3 after, return to space S P1 through the 1st circulation road 72a, the L1 (with reference to Fig. 6) until its pasta is up to the standard.The L1 if the pasta of the lubricant oil LB1 in baffle-box 70 is up to the standard, then space S P1 becomes the state that lubricated oily LB1 is full of, and sun gear 42, planetary pinion 44, planetary wheel carrier 46 and internal gear 48 become the state be completely infused in lubricant oil LB1.
Like this, the lubricant oil LB1 in space S P1, when the output shaft 21b of rotary motor 21 rotates, discharges to baffle-box 70, the amount of the lubricant oil LB1 in space S P1 is reduced by device for revolving and driving 40.As a result, device for revolving and driving 40 makes the stirring resistance of lubricant oil LB1 reduce, and the rotary load of output shaft 21b, sun gear 42, planetary pinion 44, planetary wheel carrier 46 can be made to reduce.
In addition, the lubricant oil LB1 being in the bottom of space S P1, by the centrifugal pump effect caused because of the rotation of planetary wheel carrier 46 and brake disc 60, discharges to baffle-box 70 by device for revolving and driving 40.Further, the lubricant oil LB1 in baffle-box 70 sends back to the top of space S P1 by device for revolving and driving 40.As a result, device for revolving and driving 40 can not make the amount of the lubricant oil LB1 in space S P1 exceedingly reduce and sun gear 42, planetary pinion 44, planetary wheel carrier 46 and internal gear 48 reliably be lubricated.
In addition, the lubricant oil LB1 in baffle-box 70 is cooled by heat exchange mechanism 76 by device for revolving and driving 40.As a result, device for revolving and driving 40 can be sent back in space S P1 to space S P1 after being cooled in baffle-box 70 by the lubricant oil LB1 heated by rotation of each gear etc., can suppress that each gear and lubricant oil LB1's is overheated.
On the other hand, even if the lubricant oil LB2 in space S P2 is when the output shaft 21b of rotary motor 21 rotates, also can not circulate from lower to upper part in space S P2.This is because, because the rotational speed of each gear is lower than the rotational speed of the output shaft 21b of rotary motor 21, so lower for the desirability of the reduction of the rotary load of each gear, the cooling of lubricant oil LB2.But the present invention is not limited to this structure.Such as, as shown in Figure 8, device for revolving and driving 40 also can circulate to make the lubricant oil LB2 in space S P2 and lubricant oil LB2's is overheated in order to suppress, and possesses the baffle-box 70A and exchange heat mechanism 76A that are connected with space S P2.
Then, be described with reference to the structure example of Fig. 9 to the device for revolving and driving 40X of another embodiment of the present invention.In addition, the sectional view of state when Fig. 9 is the output shaft 21b rotation representing rotary motor 21, corresponding to Fig. 7.
Device for revolving and driving 40X possesses in the 72M this point of circulation road different from device for revolving and driving 40 replacing the combination of baffle-box 70, the 1st circulation road 72a and the 2nd circulation road 72b, but is common in other.Therefore, omit the explanation of common point and describe difference in detail.
Circulation road 72M is the oil circuit formed at the 1st gear-box 50 and the respective inside of the 2nd gear-box 52, though when the output shaft 21b of rotary motor 21 is static also lubricated oily LB1 be full of.That is, space S P1 and circulation road 72M is always in the state that lubricated oily LB1 is full of.
In addition, as shown in Figure 9, when output shaft 21b rotates, the centrifugal pump effect of the lubricant oil LB1 in space S P1 by being brought by the planetary wheel carrier 46 rotated and brake disc 60, the ostium via the bottom be formed in space S P1 is sent into by circulation road 72M.Specifically, the lubricant oil LB1 in space S P1 is sent into by circulation road 72M through brake disc 60 and keep plate 62.Be fed to the lubricant oil LB1 in the 72M of circulation road while cooled by heat exchange mechanism 76, promoted by the lubricant oil LB1 newly sent into and carried by vertical top.Then, move in the 72M of circulation road vertical above lubricant oil LB1 promoted by the lubricant oil LB1 newly sent into, by towards being formed in the tap hole on top of space S P1, namely close with running shaft direction carries.Now, the lubricant oil LB1 in space S P1 will be left from running shaft by centrifugal force.Therefore, to the lubricant oil LB1 of the direction movement close to running shaft while the lubricant oil LB1 that will leave from this running shaft pushes back to the direction close with running shaft in the 72M of circulation road, released in space S P1 by the tap hole from the top being formed in space S P1.In addition, the dotted arrow of Fig. 9 represents the flowing of the lubricant oil LB1 of movement in the 72M of circulation road.
Like this, space S P1 accepts lubricant oil LB1 with the amount being fed to the lubricant oil LB1 in the 72M of circulation road from circulation road 72M.Therefore, space S P1 is always in the state that lubricated oily LB1 is full of, and is stirred, but can not forms the pasta of mortar shape by the rotation of the output shaft 21b of rotary motor 21.
Then, if the rotation of output shaft 21b stops, then the lubricant oil LB1 in the 72M of circulation road stops it moving.In the case, the state that the lubricated oily LB1 of space S P1 is full of also does not change.
Like this, device for revolving and driving 40X makes the lubricant oil LB1 in space S P1 circulate upward from below when the output shaft 21b of rotary motor 21 rotates.Specifically, the centrifugal pump effect of device for revolving and driving 40X by being brought by the rotation of planetary wheel carrier 46 and brake disc 60, the circulation road 72M using the ostium of the bottom by being in space S P1 to be connected with the tap hole on the top being in space S P1 makes lubricant oil LB1 circulate.In addition, the lubricant oil LB1 in the 72M of circulation road is cooled by heat exchange mechanism 76 by device for revolving and driving 40X.As a result, device for revolving and driving 40X can be sent back to space S P1 after being cooled in the 72M of circulation road by the lubricant oil LB1 heated by the rotation etc. of each gear in space S P1, can suppress that each gear and lubricant oil LB1's is overheated.
On the other hand, even if the situation that the lubricant oil LB2 in space S P2 rotates at the output shaft 21b of rotary motor 21, also can not circulate from lower to upper part in space S P2.This is because, because the rotational speed of each gear is lower than the rotational speed of the output shaft 21b of rotary motor 21, so lower for the desirability of the reduction of the rotary load of each gear, the cooling of lubricant oil LB2.But the present invention is not limited to this structure.Such as, device for revolving and driving 40X also can in order to suppress, lubricant oil LB2's be overheated in order to make the lubricant oil LB2 in space S P2 circulate, in addition, and possesses the circulation road 72MB and heat exchange mechanism 76B that are connected with space S P2.
In addition, device for revolving and driving 40X is configured to, and though rotary motor 21 output shaft 21b rotate or static, always all space S P1 lubricant oil LB1 is full of.Therefore, no matter sun gear 42, planetary pinion 44, planetary wheel carrier 46 and internal gear 48 how, can both reliably lubricate by the inclination of the body of device for revolving and driving 40X excavator.
Above, the preferred embodiment of the present invention has been described in detail, but the present invention is not limited to above-mentioned mode of execution, can not departs from the scope of the present invention and to various distortion and the displacement in addition of above-mentioned mode of execution.
Such as, in the above-described embodiment, device for revolving and driving 40 possesses the 1 group of circulation road 72 (combination of the 1st circulation road 72a and the 2nd circulation road 72b) be connected with 1 baffle-box 70.But the present invention is not limited to this structure.Such as, device for revolving and driving 40 also can possess and 1 many groups that baffle-box is connected circulation road, also can possess the many groups circulation road be connected with multiple baffle-box.In addition, device for revolving and driving 40 also can not possess 1 the 2nd circulation road 72b corresponding with multiple 1st circulation road 72a, also can not possess the multiple 2nd circulation road 72bs corresponding with 1 the 1st circulation road 72a.
In addition, in the above-described embodiment, device for revolving and driving 40X possesses 1 circulation road 72M, but also can possess multiple circulation road 72M.
In addition, in the above-described embodiment, device for revolving and driving 40 possesses the baffle-box 70 and circulation road 72 that are connected with space S P1, but also can add or instead possess the baffle-box 70 and circulation road 72 that are connected with space S P2.Equally, device for revolving and driving 40X possesses the circulation road 72M be connected with space S P1, but also can add or instead possess the circulation road 72M be connected with space S P2.
In addition, in device for revolving and driving 40,40X, circulation road 72,72M are formed in the 1st gear-box 50 and the respective inside of the 2nd gear-box 52, but also can comprise the circle groove on the respective internal surface being formed in the 1st gear-box 50 and the 2nd gear-box 52.
In addition, in device for revolving and driving 40,40X, hold the space of spring 66, brake release port 69 and circulation road 72,72M and be biased in a circumferential direction respectively and formed.But the present invention is not limited to this structure.Such as, also can be hold in the space of spring 66, brake release port 69 and circulation road 72,72M at least both are formed in identical circumferential locations.
In addition, in device for revolving and driving 40,40X, the tap hole of circulation road 72,72M is all formed on the inwall of the 1st gear-box 50, enters from the top of side direction space S P1 to make lubricant oil LB1.But the present invention is not limited to this structure.Also can be such as that circulation road is formed in end plate 21a, the tap hole on this circulation road be formed on the bottom surface of end plate 21a, also can be that circle groove is formed on the bottom surface of end plate 21a, enter to make lubricant oil LB1 from the top of upper direction space S P1.In the case, device for revolving and driving 40,40X such as also can when the output shaft 21b of rotary motor 21 rotates to the sun gear 42 exposed from pasta L2 directly supply lubricant oil LB1.
In addition, in device for revolving and driving 40,40X, be configured to, by oil sealing 57, space S P1 be separated with space S P2, lubricant oil LB1 is not mixed with lubricant oil LB2.But the present invention is not limited to this structure.Such as also can by the oil lubrication of each gear identical type in each gear in space S P1 and space S P2.In addition, the space of the space that also space S P2 can be separated into the planetary gears holding formation the 2nd rotary reducer 24-2 and the planetary gears holding formation the 3rd rotary reducer 24-3.This is in order to the lubricant oil of the planetary gears by lubrication formation the 2nd rotary reducer 24-2 is isolated with the lubricant oil of the planetary gears of lubrication formation the 3rd rotary reducer 24-3, makes it possible to utilize respective lubricant oil.
In addition, in device for revolving and driving 40,40X, the planetary wheel carrier 46 of the 1st rotary reducer 24-1 is formed as the output shaft of the 1st rotary reducer 24-1 and the input shaft of the 2nd rotary reducer 24-2, and the sun gear 82 of the 2nd rotary reducer 24-2 is fixed.But the present invention is not limited to this structure.Such as, the output shaft of the 1st rotary reducer 24-1 also can be the structure removably linked with the input shaft of the 2nd rotary reducer 24-2.That is, the 1st rotary reducer 24-1 also can be configured to can dismantle from remaining part of rotary reducer 24.In the case, space S P2 is airtight by the input shaft of the not shown top board of the 2nd gear-box 52 as an alternative, the 2nd rotary reducer 24-2, the 3rd gear-box 54 and planetary wheel carrier 106.In addition, on the input shaft and planetary wheel carrier 106 of the 2nd rotary reducer 24-2, not shown oil sealing is installed.By this structure, device for revolving and driving 40,40X can, by remaining incorporating aspects of various 1st rotary reducers different for specification and rotary reducer 24, can make the characteristic adaptation such as reduction speed ratio in various purposes.
No. 2012-255736th, the Japanese patent application that the application on November 16th, No. 2012-249749 1 to propose based on the Japanese patent application proposed Japanese patent application on the November 13rd, No. 2012-244013 1 proposed on November 5th, 2012 Japanese patent application proposes on November 21st, No. 2012-252713 1 and the Japanese patent application 2013-027162 CLAIM OF PRIORITY proposed on February 14th, 2013, in this application by referring to and quote the full content of these Japanese patent applications.
Symbol description
1-lower running body, 1A, 1B-oil hydraulic motor, 2-swirl gear, 3-upper rotation, 4-swing arm, 5-dipper, 6-scraper bowl, 7-swing arm cylinder, 8-dipper cylinder, 9-scraper bowl cylinder, 10-operator cabin, 11-engine, 12-motor generator set, 13-speed changer, 14-main pump, 15-pioneer pump, 16-high-pressure and hydraulic pipeline, 17-control valve, 18, 20-inverter, 21-rotary motor, 21a-end plate, 21b-output shaft, 22-resolver, 23-mechanical brake, 24-rotary reducer, 24-1-the 1st rotary reducer, 24-2-the 2nd rotary reducer, 24-3-the 3rd rotary reducer, 25-pilot line, 26-operation equipment, 26A, 26B-operating handle, 26C pedal, 27, 27a, 28-hydraulic pipe line, 29-pressure transducer, 30-controller, 40, 40X-device for revolving and driving, 40A-output shaft, 42, 82, 102-sun gear, 44, 84, 104-planetary pinion, 44a, 84a, 104a-sells, and 46, 86, 106-planetary wheel carrier, 48, 88, 108-internal gear, 50-the 1st gear-box, 52-the 2nd gear-box, 54-the 3rd gear-box, 56-bearing, 57-oil sealing, 60-brake disc, 62-keep plate, 64-piston, 66-spring, 68-hydraulic space, 69-brake release port, 70, 70A-baffle-box, 72, 72A, 72M, 72MB-circulation road, 72a, 72Aa-the 1st circulation road, 72b, 72Ab-the 2nd circulation road, 74-oil circuit, 76, 76A, 76B-heat exchange mechanism, 90-spring push part, 91, 93, 94, 95-sealed member, 92-bolt, 120-accumulating system.
Claims (5)
1. an excavator, possesses:
Rotary motor;
The multi-stage rotary speed reducer be connected with described rotary motor;
The 1st grade of the described multi-stage rotary speed reducer of collecting formation is the 1st confined space of the gear mechanism of the 1st rotary decelerating mechanism; And
The 2nd grade of the described multi-stage rotary speed reducer of collecting formation is the 2nd confined space of the gear mechanism of the 2nd rotary decelerating mechanism.
2. excavator as claimed in claim 1,
Under the state of rest of described rotary motor, the lubricated oil of described 1st confined space fills up.
3. excavator as claimed in claim 1,
At least one of described 1st confined space and described 2nd confined space comprises the circulation road making lubrication oil circulation.
4. excavator as claimed in claim 1,
The lubricant oil of described 1st confined space isolates with the lubricant oil of described 2nd confined space by the oil sealing be arranged on the output shaft of described 1st rotary reducer.
5. excavator as claimed in claim 1,
The output shaft of described 1st rotary reducer is detachably connected on the input shaft of described 2nd rotary reducer,
Described 1st confined space by being arranged on the oil sealing sealing on the output shaft of described 1st rotary reducer,
Described 2nd confined space is airtight by the oil sealing be arranged on the input shaft of described 2nd rotary reducer.
Applications Claiming Priority (11)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-244013 | 2012-11-05 | ||
| JP2012244013 | 2012-11-05 | ||
| JP2012-249749 | 2012-11-13 | ||
| JP2012249749 | 2012-11-13 | ||
| JP2012-252713 | 2012-11-16 | ||
| JP2012252713 | 2012-11-16 | ||
| JP2012-255736 | 2012-11-21 | ||
| JP2012255736 | 2012-11-21 | ||
| JP2013-027161 | 2013-02-14 | ||
| JP2013027161A JP6158526B2 (en) | 2013-02-14 | 2013-02-14 | Excavator |
| PCT/JP2013/079449 WO2014069536A1 (en) | 2012-11-05 | 2013-10-30 | Shovel |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104769316A true CN104769316A (en) | 2015-07-08 |
| CN104769316B CN104769316B (en) | 2018-12-25 |
Family
ID=50627436
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380057855.1A Expired - Fee Related CN104769316B (en) | 2012-11-05 | 2013-10-30 | Excavator |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN104769316B (en) |
| WO (1) | WO2014069536A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6170321B2 (en) * | 2013-03-29 | 2017-07-26 | 住友重機械工業株式会社 | Excavator |
| EP3147538A1 (en) * | 2015-09-23 | 2017-03-29 | Inovacor Ab | Compound planet gear arrangement and drive train arrangement |
| DE202019101918U1 (en) * | 2019-03-08 | 2020-06-09 | Liebherr-Components Biberach Gmbh | Temperature control device for drive and / or gear units such as tunnel drill gear |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0571138A (en) * | 1991-11-15 | 1993-03-23 | Hitachi Constr Mach Co Ltd | Sealing structure of turning device for working machine |
| US20020049109A1 (en) * | 2000-10-20 | 2002-04-25 | Masanori Ohmi | Planetary gear speed reduction mechanism |
| JP2008232269A (en) * | 2007-03-20 | 2008-10-02 | Komatsu Ltd | Electric slewing device |
| JP2008232270A (en) * | 2007-03-20 | 2008-10-02 | Komatsu Ltd | Electric slewing device |
| CN101874166A (en) * | 2008-03-31 | 2010-10-27 | 爱信艾达株式会社 | Power transmission device |
| CN202418439U (en) * | 2012-02-20 | 2012-09-05 | 株洲齿轮有限责任公司 | Right-angle planetary speed reduction device |
| CN102762883A (en) * | 2010-03-03 | 2012-10-31 | 日信工业株式会社 | Electric brake device for vehicle |
-
2013
- 2013-10-30 WO PCT/JP2013/079449 patent/WO2014069536A1/en active Application Filing
- 2013-10-30 CN CN201380057855.1A patent/CN104769316B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0571138A (en) * | 1991-11-15 | 1993-03-23 | Hitachi Constr Mach Co Ltd | Sealing structure of turning device for working machine |
| US20020049109A1 (en) * | 2000-10-20 | 2002-04-25 | Masanori Ohmi | Planetary gear speed reduction mechanism |
| JP2008232269A (en) * | 2007-03-20 | 2008-10-02 | Komatsu Ltd | Electric slewing device |
| JP2008232270A (en) * | 2007-03-20 | 2008-10-02 | Komatsu Ltd | Electric slewing device |
| CN101874166A (en) * | 2008-03-31 | 2010-10-27 | 爱信艾达株式会社 | Power transmission device |
| CN102762883A (en) * | 2010-03-03 | 2012-10-31 | 日信工业株式会社 | Electric brake device for vehicle |
| CN202418439U (en) * | 2012-02-20 | 2012-09-05 | 株洲齿轮有限责任公司 | Right-angle planetary speed reduction device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104769316B (en) | 2018-12-25 |
| WO2014069536A1 (en) | 2014-05-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103975510B (en) | Electric motor | |
| CN101403435B (en) | Automatic transmission | |
| US7637101B2 (en) | Hydraulic power transmission device and work vehicle | |
| CN103080589B (en) | Wet type braking device | |
| JP5669878B2 (en) | Power transmission device for hybrid vehicle | |
| CN104769315A (en) | Shovel | |
| CN102221076B (en) | Multi-gear planet type hydraulic transmission driving mechanism | |
| JP2007524540A (en) | Hydraulic hybrid vehicle having integrated hydraulic drive module and four-wheel drive, and method of operating the same | |
| CN103987558A (en) | Vehicular electric drive apparatus | |
| CN103518080A (en) | Wheel loader | |
| CN103097759A (en) | Wet brake device | |
| JP2014156711A (en) | Shovel | |
| CN105431318A (en) | Hybrid system | |
| EP2568198A1 (en) | Differential axle assembly | |
| JP2012510598A (en) | Drive mechanism for vehicle | |
| CN104846866B (en) | Excavator and rotary reducer | |
| CN104769316A (en) | Shovel | |
| JP5976566B2 (en) | Excavator | |
| JP6158526B2 (en) | Excavator | |
| JP6289976B2 (en) | Slewing drive | |
| CN104769190B (en) | Swivel drive machine for construction machine | |
| CN103216588B (en) | Hybrid powertrain | |
| CN107269796A (en) | Power decomposition transmission device | |
| US20050284256A1 (en) | Drive system for mobile vehicles | |
| JP6462801B2 (en) | Excavator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| EXSB | Decision made by sipo to initiate substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20181225 |