CN100580275C - Planetary gear - Google Patents
Planetary gear Download PDFInfo
- Publication number
- CN100580275C CN100580275C CN200480030916A CN200480030916A CN100580275C CN 100580275 C CN100580275 C CN 100580275C CN 200480030916 A CN200480030916 A CN 200480030916A CN 200480030916 A CN200480030916 A CN 200480030916A CN 100580275 C CN100580275 C CN 100580275C
- Authority
- CN
- China
- Prior art keywords
- sleeve
- sliding sleeve
- centering
- gear
- hub
- 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.)
- Expired - Lifetime
Links
- 230000005540 biological transmission Effects 0.000 claims description 16
- 238000009826 distribution Methods 0.000 description 4
- 238000000465 moulding Methods 0.000 description 4
- 238000005096 rolling process Methods 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000007731 hot pressing Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 238000007514 turning Methods 0.000 description 2
- 239000000969 carrier Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000003801 milling Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
Images
Classifications
-
- 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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
- F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
- F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q5/00—Driving or feeding mechanisms; Control arrangements therefor
- B23Q5/02—Driving main working members
- B23Q5/04—Driving main working members rotary shafts, e.g. working-spindles
- B23Q5/12—Mechanical drives with means for varying the speed ratio
- B23Q5/14—Mechanical drives with means for varying the speed ratio step-by-step
- B23Q5/142—Mechanical drives with means for varying the speed ratio step-by-step mechanically-operated
-
- 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
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
-
- 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
- General Details Of Gearings (AREA)
Abstract
The invention relates to a planetary gear, especially for machine tools, comprising a drive shaft which is connected to a sun wheel, a driven shaft which is connected to a planetary gear, and a hollow wheel which is connected to the housing in a first shift position, and to the sun wheel in a second shift position, also comprising a hub which surrounds the drive shaft in a concentric manner, and a sliding sleeve which also surrounds the hub in a concentric manner and is in contact with the hub when in a shift position. The sliding sleeve (5) has a centering diameter which is arranged in a concentric manner on the hub (6) on the end thereof oriented away from the hollow wheel (4). Said centering diameter overlaps with a centering band (8) which is embodied in a concentric manner on the axis of the hub when the sliding sleeve (5) comprising the hub (6) is in an engaged position.
Description
Technical field
The present invention relates to a kind of epicyclic gearbox, it is especially for lathe.
Background technique
This most epicyclic gearbox as single-stage or multi-stage planetary gear case formation mainly uses on lathe transmission device and turning, milling and machining center.Attachable epicyclic gearbox strengthens the power bandwidth of spindle drive motor, so that the flexibility that improves lathe by high moment of torsion or high rotating speed when the processing different materials.For example constitute two gear stages, method is that the transmission shaft that is connected with sun gear on the one hand can be connected with shell with ring gear on the other hand with ring gear.Planet carrier is connected with driven shaft.
Claimant's DE A19917673 discloses a kind of like this two-stage planetary gear, has transmission shaft and by rolling bearing supporting driven shaft in the enclosure.Transmission shaft with is connected with the sun gear of planetary pinion engagement, planetary pinion is bearing on the interior planet post of planet carrier, planet carrier is connected with driven shaft by the moulding connection.The engagement of planetary pinion and ring gear, ring gear by the rolling bearing rotatable support in the enclosure or in the planet carrier and moulding reasonably be connected with sleeve.Sleeve is by first parts antitorque be connected of the outer gear teeth with sliding sleeve.Rolling bearing is on the sliding sleeve.In addition, the exterior part in the shell can move axially on bolt of bearing cap and guide, and wherein, moves axially from exterior part and is delivered on the rolling bearing.
Sliding sleeve can take three link positions, exactly be neutral position, first link position, sliding sleeve is connected sun gear and second link position by connecting the gear teeth with shell on this position, and ring gear is connected with sun gear by the link that has the synchronous gear teeth and be connected with moulding on this position.Link is connected with transmission shaft is antitorque in this regard.
Moving of sliding sleeve carried out by means of connection set in this case, and its actuator is electromagnet or the linkage unit with motor, and its armature then is connected with sliding sleeve according to transmission.
On modern lathe, more and more higher to the requirement of rotating speed, vibration values and precision aspect.Epicyclic gearbox as a machine tool gear mechanism part is that surface to be processed thus is affected relatively along with rotating speed improves a kind of possible source that vibration increases in this regard.
The reason of this vibration also is the imbalance in the epicyclic gearbox.Need the gap as sliding sleeve, so that can move it.The decentraction running is also caused in the gap, produces uneven thus.For example, if the sliding sleeve of weight 1.6kg commonly used only moves 0.1mm outside neutral position, so consequent imbalance just reaches 160gmm, produces serious imbalance thus.(i=1: when 1) turning round, the desired accurate processing of workpiece surface also can only utilize the lathe of low vibration just can reach with high rotating speed at epicyclic gearbox.
Summary of the invention
The objective of the invention is to, a kind of epicyclic gearbox is provided, it does not produce or only produces small vibration with high rotating speed operative workpiece the time.
The epicyclic gearbox of described type sets out from the outset, and this purpose utilizes following feature to be achieved: it has: the transmission shaft that is connected with sun gear; The driven shaft that is connected with planet carrier, this driven shaft have can be at the ring gear that is connected and is connected with sun gear on second link position with shell on first link position; Concentric ring is around the sleeve of transmission shaft; With concentric ring around sleeve and on a link position with the sliding sleeve of sleeve interlocking, it is characterized in that, sliding sleeve has the centering diameter with the concentric setting of sleeve on its end away from ring gear, this centering diameter in the interlocking position of sliding sleeve and sleeve around the centering bundle that constitutes thereon with one heart with sleeve axis and above being close to.
The present invention is therefore from a kind of epicyclic gearbox, and particularly a kind of two-stage planetary gear that is used for lathe has: the transmission shaft that is connected with sun gear; The driven shaft that is connected with planet carrier, this driven shaft have can be at the ring gear that is connected and is connected with sun gear on second link position with shell on first link position; Concentric ring is around the sleeve of transmission shaft; With concentric ring around sleeve and on one of two link positions with the sliding sleeve of sleeve interlocking.
According to the present invention, sliding sleeve has the centering diameter with the concentric setting of sleeve on its end away from ring gear in this regard, it on the interlocking position of sliding sleeve and sleeve around centering bundle concentric with sleeve axis and that constitute in the above and above being close to.
The advantage that is close to this so-called " capture " sliding sleeve above the sleeve centering bundle on one of link position is, sliding sleeve has the gap that is significantly less than traditional epicyclic gearbox between sleeve and the sliding sleeve on this link position, this gap only is made up of the matching gap between centering diameter and the centering bundle.The function in past promptly produces the moulding connection and obtains fully keeping between sliding sleeve and the sleeve.
In another kind of formation of the present invention, the sliding sleeve bearing is located in the axial direction by the stop ring of hot pressing suit.Its advantage is not produce additional imbalance thus.
In further formation of the present invention, at sliding sleeve centering diameter near at first contacting under the situation and having gradient with the limit of the centering diameter of movement direction transverse distribution with the centering bundle of sleeve; Equally the centering diameter near the time at first contact and has gradient with the limit of the centering bundle of the movement direction transverse distribution of the diameter of feeling relieved with the centering diameter.
The attendant advantages of doing like this is, even also can contact without a doubt on the centering bundle to centering diameter under the situation of sleeve offset some small amount at sliding sleeve.
Description of drawings
The present invention is described in detail by accompanying drawing below, and this accompanying drawing illustrates an embodiment with advantage according to epicyclic gearbox of the present invention.
Embodiment
Unique accompanying drawing illustrates the part sectioned view of the epicyclic gearbox that constitutes according to the present invention, and this gear-box constitutes as two-stage planetary gear and uses on lathe.
Epicyclic gearbox has transmission shaft 1 that is connected with sun gear 2 and the driven shaft 3 that is connected with planet carrier 10, and wherein, one of planetary pinion adopts 11 marks.Driven shaft also has ring gear 4, and it is being connected with the shell 12 of epicyclic gearbox on first link position and can utilizing sleeve 6 to be connected with sun gear 2 on second link position.Sleeve 6 concentric rings are around transmission shaft 1.Sliding sleeve adopts 5 marks, and it produces transformation between two link positions.Sliding sleeve 5 in this regard movable axle to being bearing on the ring gear 4.
Be in unique accompanying drawing upper half part is and the sliding sleeve 5 of brake disc 14 interlockings that wherein, this link position is equivalent to the velocity ratio of two-stage planetary gear i＞1.
According to the present invention, sliding sleeve 5 has the centering diameter 7 with sleeve 6 concentric settings on its end away from ring gear 4, shown in Fig. 1 lower half portion, under the situation of i=1, it on the interlocking position of sliding sleeve 5 and sleeve 6 around centering bundle 8 concentric with the axis of sleeve 6 and that constitute in the above and above being close to.
What have advantage is, at centering diameter 7 near at first that contact under the situations and have gradient with the limit of the centering diameter of movement direction transverse distribution with centering bundle 8; With the mode that has advantage equally centering bundle 8 near the time at first that contact and have gradient with the limit of the centering bundle of movement direction transverse distribution with centering diameter 7, restraint thereby between centering diameter 7 and centering bundle 8, still can make the centering diameter contact centering without a doubt during minor shifts.
Around and be close on the centering bundle 8 after should centering bundle and the gap of existence of feeling relieved between the diameter 7 such as already mentioned, be significantly less than the gap that exists between the gear teeth of sliding sleeve and ring gear in traditional epicyclic gearbox.
The stop ring 9 that has sliding sleeve bearing 13 best hot pressing suits on the surface of centering diameter 7 in addition.The effect of the stop ring 9 of this axially locating is the imbalance that does not occur adding.
What also need emphasize is, does not need centering between sliding sleeve 5 and the sleeve 6 on the link position shown in accompanying drawing upper half part (i＞1) because on this link position sliding sleeve 5 static and with break or brake disc 14 interlockings.
Have on the coefficient end of sliding sleeve and sleeve and having the centering bundle on centering diameter and the sleeve and be not limited on the epicyclic gearbox of lathe, but for example also can be used for all that gear-box as sliding sleeve on the automotive transmission and sleeve or the interlocking of other links, wherein, also can improve tranquil running here by the idle running noise in the obvious reduction gear-box.
Reference numeral
1 power transmission shaft
2 sun gears
3 driven shafts
4 ring gears
5 sliding sleeves
6 sleeves
7 centering diameters
8 centering bundles
9 stop rings
10 planet carriers
11 planetary pinions
12 shells
13 sliding sleeve bearings
14 brake discs
Claims (2)
1. epicyclic gearbox is used for lathe, and it has: the transmission shaft that is connected with sun gear; The driven shaft that is connected with planet carrier, this driven shaft have can be at the ring gear that is connected and is connected with sun gear on second link position with shell on first link position; Concentric ring is around the sleeve of transmission shaft; With concentric ring around sleeve and on a link position with the sliding sleeve of sleeve interlocking, it is characterized in that, sliding sleeve (5) has the centering diameter (7) with the concentric setting of sleeve (6) on its end away from ring gear (4), this centering diameter in the interlocking position of sliding sleeve (5) and sleeve (6) around the centering bundle (8) that constitutes thereon with one heart with sleeve axis and above being close to.
2. by the described epicyclic gearbox of claim 1, wherein, centering diameter (7) has stop ring (9) away from the surface of sleeve (6).
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10348757.3 | 2003-10-21 | ||
| DE10348755.7 | 2003-10-21 | ||
| DE2003148755 DE10348755A1 (en) | 2003-10-21 | 2003-10-21 | Machine tool gear mechanism for transferring power and/or torque from a driven shaft of the gear mechanism to a spindle comprises an integrated rotary transmission leadthrough that serves as a supply device for coolants, oil or air |
| DE102004003684.5 | 2004-01-24 | ||
| DE102004003685.3 | 2004-01-24 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1871458A CN1871458A (en) | 2006-11-29 |
| CN100580275C true CN100580275C (en) | 2010-01-13 |
Family
ID=34608881
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200480030997XA Pending CN1871099A (en) | 2003-10-21 | 2004-09-29 | Machine tool gear mechanism |
| CN200480030916A Expired - Lifetime CN100580275C (en) | 2003-10-21 | 2004-09-29 | Planetary gear |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200480030997XA Pending CN1871099A (en) | 2003-10-21 | 2004-09-29 | Machine tool gear mechanism |
Country Status (3)
| Country | Link |
|---|---|
| CN (2) | CN1871099A (en) |
| DE (1) | DE10348755A1 (en) |
| TW (1) | TWI342933B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI629423B (en) * | 2015-01-08 | 2018-07-11 | 永合精機股份有限公司 | Zweigang-planetengetriebe, two speed |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE202005016177U1 (en) * | 2005-10-12 | 2005-12-22 | Dbt Gmbh | First chisel support adjustment arrangement for production plane has gear mechanism consisting of planetary gear that is interposed between input shaft and worm wheel |
| DE102016221297A1 (en) | 2016-10-28 | 2018-05-03 | Zf Friedrichshafen Ag | Switchable planetary gear |
| DE102016221310A1 (en) | 2016-10-28 | 2018-05-03 | Zf Friedrichshafen Ag | clamp coupling |
| AT520296B1 (en) * | 2017-11-10 | 2019-03-15 | Avl Commercial Driveline & Tractor Eng Gmbh | SWITCHING DEVICE FOR A GEARBOX |
| DE102018204200A1 (en) | 2018-03-20 | 2019-09-26 | Zf Friedrichshafen Ag | Planetary gear with a line for passing lubricant and / or coolant through the planetary gear |
-
2003
- 2003-10-21 DE DE2003148755 patent/DE10348755A1/en not_active Withdrawn
-
2004
- 2004-09-29 CN CNA200480030997XA patent/CN1871099A/en active Pending
- 2004-09-29 CN CN200480030916A patent/CN100580275C/en not_active Expired - Lifetime
- 2004-10-15 TW TW93131290A patent/TWI342933B/en active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI629423B (en) * | 2015-01-08 | 2018-07-11 | 永合精機股份有限公司 | Zweigang-planetengetriebe, two speed |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1871458A (en) | 2006-11-29 |
| CN1871099A (en) | 2006-11-29 |
| TWI342933B (en) | 2011-06-01 |
| DE10348755A1 (en) | 2005-06-23 |
| TW200514939A (en) | 2005-05-01 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term |
Granted publication date: 20100113 |