CN106393629A - Transmission structure of drive for twin-screw extruder - Google Patents
Transmission structure of drive for twin-screw extruder Download PDFInfo
- Publication number
- CN106393629A CN106393629A CN201610175015.0A CN201610175015A CN106393629A CN 106393629 A CN106393629 A CN 106393629A CN 201610175015 A CN201610175015 A CN 201610175015A CN 106393629 A CN106393629 A CN 106393629A
- Authority
- CN
- China
- Prior art keywords
- gear
- shaft
- transmission component
- output shaft
- power distribution
- 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
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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
- F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
- B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
- B29C48/00—Extrusion moulding, i.e. expressing the moulding material through a die or nozzle which imparts the desired form; Apparatus therefor
- B29C48/25—Component parts, details or accessories; Auxiliary operations
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
- B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
- B29C48/00—Extrusion moulding, i.e. expressing the moulding material through a die or nozzle which imparts the desired form; Apparatus therefor
- B29C48/25—Component parts, details or accessories; Auxiliary operations
- B29C48/36—Means for plasticising or homogenising the moulding material or forcing it through the nozzle or die
- B29C48/395—Means for plasticising or homogenising the moulding material or forcing it through the nozzle or die using screws surrounded by a cooperating barrel, e.g. single screw extruders
-
- 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
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
Abstract
Provided is a transmission structure (10) of a drive for a twin-screw extruder, comprising a power distribution stage (11) and a power summing stage (12), the power distribution stage including intermeshing gearwheels (13, 14, 15), and the power summing stage also including intermeshing gearwheels (16, 17, 18). The gearwheels (13, 14, 15) of the power distribution stage (11) are single helical gearwheels and the gearwheels (16, 17, 18) of the power summing stage (12) are double helical gearwheels, or the gearwheels of the power distribution stage are double helical gearwheels and the gearwheels of the power summing stage are single helical gearwheels.
Description
Technical field
The present invention relates to a kind of transmission component of the driver for twin worm extruder (Doppelschneckenextruder) as described in the preamble according to claim 1.The present invention additionally relate to a kind of with such transmission component for twin worm extruder driver.
Background technology
By file DE 10 2,004 051
A kind of essential structure of the driving means for twin worm extruder known to 306 B4 and a kind of transmission component of such driving means, its output shaft collective effect with driving means.So by the prior art it is known that coefficient transmission component includes power distribution level and power accumulator stage (Leistungssummierungsstufe) with the output shaft of driving means.Power distribution level has the gear being engaged with each other, and power accumulator stage equally has the gear being engaged with each other.The gear of the gear of power distribution level and power accumulator stage is embodied as substance helical teeth meshed gears respectively.
If must be by the higher power of the transmission component transmission of the driving means of twin worm extruder and moment of torsion, then this can mate by the size of transmission component to realize according to prior art.However, no longer enable the raising of the growth of power waiting for transmission or moment of torsion by the structure type so far simply increasing transmission component.Accordingly, there exist the demand of the Novel transmission assembly to the driver for twin worm extruder, can be with respect to by the higher power of transmission component transmission known in the art or moment of torsion by means of it.
Content of the invention
Thus set out, present invention aim at provide a kind of new transmission component of the driver for twin worm extruder and a kind of with such transmission component for twin worm extruder driver.
This purpose is realized by a kind of transmission component according to claim 1.
According to the present invention, the gear of power distribution level is the engagement of substance helical teeth and the gear of power accumulator stage is dual helical teeth engagement, or the gear of power distribution level is dual helical teeth engagement and the gear of power accumulator stage is the engagement of substance helical teeth.Thus, bigger power and moment of torsion can be transmitted by transmission component.
It is advantageously improved scheme according to one, power distribution level has the first gear being positioned on the first output shaft, the second gear being positioned in the first branched shaft (Zweigwelle) and the 3rd gear being positioned in the second branched shaft, wherein, the gear of power distribution level is the engagement of substance helical teeth, and wherein, second gear and the 3rd gear are engaged in first gear respectively.Power accumulator stage has the 4th gear being positioned on the second output shaft, the 5th gear being positioned in the first branched shaft and the 6th gear being positioned in the second branched shaft, wherein, the gear of power accumulator stage is dual helical teeth engagement, and wherein, the 5th gear and the 6th gear are engaged in the 4th gear respectively.This design is particularly preferred for the larger power of transmission and moment of torsion.
Preferably, it is positioned at the dual helical teeth meshed gears on the second output shaft and in the first branched shaft and in the second branched shaft and is respectively provided with mesh section, it has with reverse inclination direction and different size of helical angle (Schraegungswinkel).The size of the helical angle stretching on contrary incline direction offsets with one another into so that existing in view of the dynamic balance of the power being caused by engagement at axle.Thus can compensate for the axial force being produced by engagement being applied on transmission component.
According to the present invention for twin worm extruder driver in claim 10 defining.
Brief description
The preferred improvement project of the present invention is drawn by dependent claims and ensuing explanation.To elaborate embodiments of the invention with reference to the accompanying drawings, and not limited to this.Wherein：
Fig. 1 shows the transmission component of the driver according to the present invention for twin worm extruder；And
Fig. 2 shows another transmission component according to the present invention for the driver of twin worm extruder.
List of numerals
10 transmission components
11 power distribution levels
12 power accumulator stages
13 gears
14 gears
The pitch circle of d14 gear 14
15 gears
16 gears
17 gears
The pitch circle of d17 gear 17
18 gears
The pitch circle of d18 gear 18
19 output shafts
20 branched shaft
21 branched shaft
22 output shafts
30 transmission components
31 power distribution levels
32 power accumulator stages
33 gears
34 gears
35 gears
36 gears
37 gears
38 gears
39 output shafts
40 branched shaft
41 branched shaft
42 output shafts.
Specific embodiment
The present invention relates to a kind of driver of the twin worm extruder of transmission component of the driver for twin worm extruder and a kind of such transmission component of inclusion.
For twin worm extruder driver construction for known to expert mentioned here and known to file DE 10 2,004 051 306 B4.
So, the driver for twin worm extruder includes at least one motor, and wherein, each motor acts at a drive shaft.Additionally, the driver of twin worm extruder includes multiple driven shafts, wherein, the worm shaft of twin worm extruder is attached at each driven shaft.One transmission component and be designed as the second transmission component of power distribution drive mechanism and be connected between the or each drive shaft and output shaft.
The present invention relates to a kind of construction of the such driver for twin worm extruder is the transmission component of power distribution drive mechanism.
Fig. 1 shows the preferred embodiment of the transmission component 10 being configured to power distribution drive mechanism of the driver of twin worm extruder, and wherein, transmission component 10 includes power distribution level 11 and power accumulator stage 12.Power distribution level 11 includes the gear 13,14 and 15 being engaged with each other.Power accumulator stage 12 equally has the gear 16,17 and 18 being engaged with each other.
In shown preferred embodiment, the gear 13 of power distribution level 11 is positioned on the first output shaft 19, first output shaft 19 is used for driving the first worm shaft of twin worm extruder, and wherein, the first worm shaft of twin worm extruder can be attached at this first output shaft 19.The gear 15 of the gear 14 of power distribution level 11 and power distribution level 11 is respectively positioned in branched shaft, that is, gear 14 in the first branched shaft 20 gear 15 in the second branched shaft 21.The gear 16 of power accumulator stage 12 is positioned on the second output shaft 22, and the second worm shaft of twin worm extruder can be attached at the second output shaft 22.The gear 17 and 18 being engaged in gear 16 of power accumulator stage 12 is positioned in branched shaft again, that is, the gear 17 of power accumulator stage 12 in the first branched shaft 20 gear 18 of power accumulator stage 12 in the second branched shaft 21.
In shown preferred embodiment, the gear 13,14 and 15 being engaged with each other of power distribution level 11 is the engagement of substance helical teeth and the gear 16,17 and 18 of power accumulator stage 12 is dual helical teeth engagement.So, can be learnt by Fig. 1, each in the gear 16,17 and 18 of power accumulator stage 12 is respectively provided with two mesh section 16a, 16b or 17a, 17b or 18a, 18b, wherein, mesh section 17a, 18a of gear 17,18 is engaged in the mesh section 16a of gear 16 and mesh section 17b, 18b of gear 17,18 are engaged in the mesh section 16b of gear 16.With regard to corresponding gear 16,17,18, mesh section 16b, 17b, 18b that mesh section 16a, 17a, the 18a being engaged with each other relative to each other engages has with reverse inclination direction and different size of helical angle.So, the mesh section 16a of gear 16, mesh section 18a, 18b of 16b, mesh section 17a, 17b of gear 17 and gear 18 are respectively equipped with reverse inclination direction and different size of helical angle.
Here, mesh section 16a, 16b or 17a of corresponding gear 16,17,18,17b or 18a, the size of the helical angle stretching on contrary incline direction of 18b offset with one another into and make to exist at axle 19,22,21,20 in view of the dynamic balance of (axial -) power being caused by engagement, that is, the dynamic balance in values below：
F15=(F18a–F18b)
F14=(F17a–F17b)
F13=(F15+F14)=(F16a+F16b)
Above-mentioned dynamic balance can particularly advantageously thus be realized, and that is, following relation is suitable for：
tan(β14)/d14=(tan(β17a)-tan(β17b))/d17
tan(β15)/d15=(tan(β18a)-tan(β18b))/d18
Wherein, β 14 is the helical angle of gear 14, wherein, β 17a is the helical angle of mesh section 17a of gear 17 and the helical angle reverse with this of mesh section 17b that β 17b is gear 17, wherein, β 15 is the helical angle of gear 15, wherein, β 18a is the helical angle of mesh section 18a of gear 18 and the helical angle reverse with this of mesh section 18b that β 18b is gear 18, wherein, d17 is two mesh section 17a of the gear 17 in branched shaft 20, the pitch diameter of 17b, and wherein, d18 is two mesh section 18a of the gear 18 in branched shaft 21, the pitch diameter of 18b.Correspondingly, d14 is the pitch diameter of gear 14 and pitch diameter that d15 is gear 15.
In the case of transmitting identical moment, due to mesh section 16a, 16b or 17a, 17b or 18a, 18b different helical angles, produce different axial forces.Can be ensured by above-mentioned condition or equation, the difference of the axial force at mesh section 17a, 17b or 18a, 18b of gear 17 or 18 corresponds to the value of the axial force at gear 14 or 15.
Lead to different power from the deviation of above-mentioned condition or the accurate satisfaction of equation, it can be balanced by the facewidth of mesh section 17a, 17b or 18a, the coupling of 18b.
In FIG in shown preferred embodiment, the transmission component 10 being configured to power distribution drive mechanism correspondingly has power distribution level 11 and power accumulator stage 12, wherein, the gear 13,14 and 15 of power distribution level 11 is the engagement of substance helical teeth and the gear 16,17 and 18 of power accumulator stage 12 is the engagement of dual helical teeth.Here, each in the gear 16,17 and 18 of power accumulator stage 12 has mesh section 16a, 16b or 17a with helixangleβ, 17b or 18a, 18b, helixangleβ has different incline directions and different sizes.
Different from this it is also possible that the gear of power distribution level is the engagement of dual helical teeth and the gear of power accumulator stage is the engagement of substance helical teeth.So, Fig. 2 shows an embodiment of the transmission component 30 being configured to power distribution drive mechanism, it includes power distribution level 31 and power accumulator stage 32 again, wherein, power distribution level 31 has the gear 33,34 and 35 being engaged with each other and power accumulator stage 32 has the gear 36,37 and 38 being engaged with each other.The gear 33 (it is dual helical teeth engagement and has two mesh section 33a and 33b) of power distribution level 31 is positioned on the first output shaft 39, and the first worm shaft of twin worm extruder can be attached at the first output shaft 39.The gear 34 and 35 (it is equally dual helical teeth engagement and has mesh section 34a, 34b or 35a, 35b) of power distribution level 31 is arranged in branched shaft 40,41, that is, the gear 34 carrying mesh section 34a, 34b carries the gear 35 of mesh section 35a, 35b in the second branched shaft 41 in the first branched shaft 40.In the variant of Fig. 2, the gear 36,37 of power accumulator stage 32 implements into the engagement of substance helical teeth with 38.
In the embodiment of fig. 2, mesh section 33a, 33b or 34a of corresponding gear 33,34 or 35,34b or 35a, 35b are in view of its helical angle distinguishes into makes to be respectively provided with reverse inclination direction and different size of helical angle with regard to each gear 33,34 or 35 corresponding mesh section 33a, 33b or 34a, 34b or 35a, 35b, wherein, the size of the helical angle stretching on contrary incline direction offsets with one another into so that existing in view of the dynamic balance of the power being caused by engagement at transmission component 30 in other words at axle 39,40,41,42 again.Condition illustrated by the embodiment of combination Fig. 1 related to this or equation are similarly applicable for the embodiment of Fig. 2.
Allow to transmit larger power according to the transmission component of the present invention and moment of torsion be used for driving the worm shaft of twin worm extruder, wherein, one of worm shaft of twin worm extruder can be attached to respectively each in the output shaft of corresponding transmission component 10 or 30 at.Additionally, the first output shaft 19 or 39 of corresponding transmission component 10 or 30 can be attached at least one motor in driving side, in the case of being especially connected in the middle of by planetary drive between transmission component 10 or 30 and the motor according to the present invention.The driving power being provided from motor correspondingly reach at the first output shaft 19,39 of transmission component 10,30 via unshowned planetary drive and from the first output shaft 19,39s via branched shaft 20,21 or 40,41 to corresponding second output shaft 22 of corresponding transmission component 10 or 30,42 directions.
Claims (10)
1. a kind of transmission component (10 of the driver for twin worm extruder;30), it has power distribution level (11;31) and power accumulator stage (12;32), wherein, described power distribution level (11;31) there is the gear (13,14,15 being engaged with each other;33,34,35), and wherein, described power accumulator stage (12;32) equally there is the gear (16,17,18 being engaged with each other;36,37,38), it is characterized in that, the gear (13 of described power distribution level (11), 14,15) it is that substance helical teeth engages and the gear (16 of described power accumulator stage (12), 17,18) it is dual helical teeth engagement, or the gear (33 of described power distribution level (31), 34,35) it is the engagement of dual helical teeth and the gear (36,37,38) of described power accumulator stage (32) is the engagement of substance helical teeth.
2. transmission component according to claim 1, it is characterized in that, described power distribution level (11) has the first gear (13) being positioned on the first output shaft (19), the second gear (14) being positioned in the first branched shaft (20) and the 3rd gear (15) being positioned in the second branched shaft (21), wherein, the gear of described power distribution level (11) is the engagement of substance helical teeth, and wherein, described second gear (14) and described 3rd gear (15) are engaged in described first gear (13) respectively.
3. transmission component according to claim 1 and 2, it is characterized in that, described power accumulator stage (12) has the 4th gear (16) being positioned on the second output shaft (22), it is positioned at the 5th gear (17) on described first branched shaft (20) and the 6th gear (18) being positioned on described second branched shaft (21), wherein, the gear of described power accumulator stage (12) is dual helical teeth engagement, and wherein, described 5th gear (17) and described 6th gear (18) are engaged in described 4th gear (16) respectively.
4. transmission component according to claim 3, it is characterized in that, it is positioned at described second output shaft (22) above and above and the dual helical teeth meshed gears (16,17,18) on described second branched shaft (21) is respectively provided with mesh section (16a in described first branched shaft (20), 16b, 17a, 17b, 18a, 18b), it has with reverse inclination direction and different size of helical angle.
5. transmission component according to claim 4 is it is characterised in that the size of the helical angle stretching on contrary incline direction offsets with one another into so that existing in view of the dynamic balance of the axial force being caused by engagement at axle.
6. transmission component according to claim 1, it is characterized in that, described power distribution level (31) has the first gear (33) being positioned on the first output shaft (39), the second gear (34) being positioned in the first branched shaft (40) and the 3rd gear (35) being positioned in the second branched shaft (41), wherein, the gear of described power distribution level (31) is dual helical teeth engagement, and wherein, described second gear (34) and described 3rd gear (35) are engaged in described first gear (33).
7. transmission component according to claim 6, it is characterized in that, described power accumulator stage (32) has the 4th gear (36) being positioned on the second output shaft (42), it is positioned at the 5th gear (37) on described first branched shaft (40) and the 6th gear (38) being positioned on described second branched shaft (41), wherein, the gear of described power accumulator stage (32) is the engagement of substance helical teeth, and wherein, described 5th gear (37) and described 6th gear (38) are engaged in described 4th gear (36) respectively.
8. the transmission component according to claim 6 or 7, it is characterized in that, it is positioned at described first output shaft (39) above and above and the dual helical teeth meshed gears (33,34,35) on described second branched shaft (41) is respectively provided with mesh section (33a in described first branched shaft (40), 33b, 34a, 34b, 35a, 35b), it has with reverse inclination direction and different size of helical angle.
9. transmission component according to claim 8 is it is characterised in that the size of the helical angle stretching on reverse inclination direction offsets with one another into so that existing in view of the dynamic balance of the axial force being caused by engagement at axle.
10. a kind of driver for twin worm extruder, it has：At least one input shaft, motor can be attached at described input shaft；First output shaft (19,39), the first worm shaft of described twin worm extruder can be attached at described first output shaft；With the second output shaft (22;42), the second worm shaft of described twin worm extruder can be attached at described second output shaft；And it is connected to described output shaft (19,39;22,42) transmission component (10 between;30) it is characterised in that described transmission component (10;30) constructed according to any one of claim 1 to 9.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102015004051.0A DE102015004051B4 (en) | 2015-03-27 | 2015-03-27 | Gear arrangement of a drive for a twin-screw extruder |
| DE102015004051.0 | 2015-03-27 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106393629A true CN106393629A (en) | 2017-02-15 |
| CN106393629B CN106393629B (en) | 2019-10-18 |
Family
ID=56889500
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610175015.0A Active CN106393629B (en) | 2015-03-27 | 2016-03-25 | The transmission component of driver for twin worm extruder |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6640626B2 (en) |
| CN (1) | CN106393629B (en) |
| DE (1) | DE102015004051B4 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109854722A (en) * | 2019-03-01 | 2019-06-07 | 郑州机械研究所有限公司 | A kind of twin-screw extrusion owner sliding tooth roller box |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101872432B1 (en) * | 2016-12-06 | 2018-06-28 | 김정완 | reducer for preventing wear of bearing due to thrust of helix gear |
| CN106969097B (en) * | 2017-04-27 | 2023-05-16 | 江阴齿轮箱制造有限公司 | Transmission device of homodromous conical double-screw extruder |
| CA3086234A1 (en) * | 2017-11-08 | 2019-05-16 | Genesis Advanced Technology Inc. | Gearbox |
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| GB170774A (en) * | 1920-11-12 | 1921-11-03 | Gen Electric | Improvements in and relating to toothed gearing |
| JPS5095662A (en) * | 1973-12-21 | 1975-07-30 | ||
| CN2189666Y (en) * | 1994-06-02 | 1995-02-15 | 李林 | Duplex gear wheel reducing device |
| US6029532A (en) * | 1997-01-31 | 2000-02-29 | Reliance Electric Industrial Company | Gearing commonality system for gear reducers |
| US6334368B1 (en) * | 2000-05-17 | 2002-01-01 | Harrier Technologies, Inc. | Multi-path gear sets with load sharing between paths |
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| CN101422714A (en) * | 2008-11-13 | 2009-05-06 | 大连橡胶塑料机械股份有限公司 | Main reducing gear output-axis key phase adjustment mechanism of large-scale twin-screw extrusion pelletizer |
| DE102008038069A1 (en) * | 2008-08-16 | 2010-02-25 | Schuler Pressen Gmbh & Co. Kg | Power-split transmission for e.g. press, has gear wheel with two helical teething, and helical-toothed gear wheels connected one below other in rotationally and axially fixed manner and together movable in axial direction |
| TW201226739A (en) * | 2010-12-29 | 2012-07-01 | Smart Mfg Technology Ltd | Gear set |
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| GB1093427A (en) | 1964-05-25 | 1967-12-06 | Vickers Ltd | Improvements in or relating to gear trains |
| DE6807991U (en) | 1968-11-21 | 1969-03-27 | Polysius Gmbh | DRIVE FOR LOW SPEED UNITS, IN PARTICULAR ROTATING DRUMS |
| DE102004051306B4 (en) | 2004-10-20 | 2009-10-01 | Renk Ag | Drive device for twin-screw extruder |
| DE102008013983B3 (en) | 2008-03-12 | 2009-08-13 | Jahnel-Kestermann Getriebewerke Gmbh & Co. Kg | Method for adjusting a tooth flank position of a toothed wheel, which is frictionally connected to a double helical pinion shaft |
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2015
- 2015-03-27 DE DE102015004051.0A patent/DE102015004051B4/en active Active
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- 2016-03-24 JP JP2016059523A patent/JP6640626B2/en active Active
- 2016-03-25 CN CN201610175015.0A patent/CN106393629B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB170774A (en) * | 1920-11-12 | 1921-11-03 | Gen Electric | Improvements in and relating to toothed gearing |
| JPS5095662A (en) * | 1973-12-21 | 1975-07-30 | ||
| CN2189666Y (en) * | 1994-06-02 | 1995-02-15 | 李林 | Duplex gear wheel reducing device |
| US6029532A (en) * | 1997-01-31 | 2000-02-29 | Reliance Electric Industrial Company | Gearing commonality system for gear reducers |
| US6334368B1 (en) * | 2000-05-17 | 2002-01-01 | Harrier Technologies, Inc. | Multi-path gear sets with load sharing between paths |
| CN201159267Y (en) * | 2008-02-20 | 2008-12-03 | 江苏省金象减速机有限公司 | Novel three-level center driving speed reducer |
| DE102008038069A1 (en) * | 2008-08-16 | 2010-02-25 | Schuler Pressen Gmbh & Co. Kg | Power-split transmission for e.g. press, has gear wheel with two helical teething, and helical-toothed gear wheels connected one below other in rotationally and axially fixed manner and together movable in axial direction |
| CN101422714A (en) * | 2008-11-13 | 2009-05-06 | 大连橡胶塑料机械股份有限公司 | Main reducing gear output-axis key phase adjustment mechanism of large-scale twin-screw extrusion pelletizer |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109854722A (en) * | 2019-03-01 | 2019-06-07 | 郑州机械研究所有限公司 | A kind of twin-screw extrusion owner sliding tooth roller box |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102015004051B4 (en) | 2022-09-08 |
| DE102015004051A1 (en) | 2016-09-29 |
| JP2016187960A (en) | 2016-11-04 |
| CN106393629B (en) | 2019-10-18 |
| JP6640626B2 (en) | 2020-02-05 |
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