CN1052517C - Drive for friction spindle units - Google Patents
Drive for friction spindle units Download PDFInfo
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- CN1052517C CN1052517C CN96193048A CN96193048A CN1052517C CN 1052517 C CN1052517 C CN 1052517C CN 96193048 A CN96193048 A CN 96193048A CN 96193048 A CN96193048 A CN 96193048A CN 1052517 C CN1052517 C CN 1052517C
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- friction
- driving shaft
- mandrel
- spindle units
- friction mandrel
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- 230000005540 biological transmission Effects 0.000 claims abstract description 17
- 230000008878 coupling Effects 0.000 claims description 23
- 238000010168 coupling process Methods 0.000 claims description 23
- 238000005859 coupling reaction Methods 0.000 claims description 23
- 230000007246 mechanism Effects 0.000 claims description 10
- 239000002184 metal Substances 0.000 claims 1
- 230000002093 peripheral effect Effects 0.000 description 6
- 230000003139 buffering effect Effects 0.000 description 3
- 230000021615 conjugation Effects 0.000 description 3
- 230000001360 synchronised effect Effects 0.000 description 3
- 230000002349 favourable effect Effects 0.000 description 2
- 230000001143 conditioned effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
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Abstract
A friction spindle unit consists of a basic component (4) in which spindles (1) are fitted to rotate at the corners of an equilateral triangle. The spindles (1) have friction discs (3) mutually overlapping at the center of the equilateral triangle. In order to attain higher revolution speeds, it is proposed that there be a drive shaft (9) rotatable about the centre of the equilateral triangle and arranged axially parallel to the spindles (1), between which and each spindle (1) there are means for torque transmission.
Description
The present invention relates to friction spindle units, on basic component, rotatably mounted the friction mandrel in three summits of equilateral triangle is being fixed the dot location that overlaps each other in the equilateral triangle center on this friction mandrel.
The friction spindle units of this form, for example open in No. 7525192 specification of the Federal Republic of Germany's utility model.In the axially-extending portion of one friction mandrel in 3 friction mandrels, engaging the tangential direction belt that drives this friction mandrel.Each friction mandrel has the belt plectane, and this belt engages with all belt plectane.Like this, can guarantee of the rotation number rotation of 3 friction mandrels to equate.The running maximal rate of used flat belt is 25m/sec, so that reach the friction mandrel rotation number of common about 20000rpm.But for the desirable higher friction mandrel rotation number of user, the friction spindle units of this structure can not reach.
The objective of the invention is to improve the friction spindle units of above-mentioned form, provide can reach higher friction mandrel rotation number, particularly when adopting flat belt to drive, between flat belt and friction mandrel, can transmit the friction spindle units of above-mentioned higher axle rotation number.
In order to realize this purpose, friction spindle units of the present invention, being provided with can be center rotation and the driving shaft that is parallel to friction mandrel with the center of equilateral triangle, between this driving shaft and each friction mandrel, is provided with the output transmission mechanism.Driving shaft is as carrying out the drive disk assembly that speedup is transmitted from drive unit to driven device.Driving shaft itself for example can be driven by flat belt, can obtain high friction mandrel rotation number by suitably selecting the transmission ratio between driving shaft and each friction mandrel.Other advantage of the present invention is to improve the forms of distribution that drive output.In the prior art, the friction mandrel that is driven by flat belt passes through other 2 friction mandrels of belt drives again.Therefore, transmit the belt that is provided with for output and must bear 2/3 of whole driving outputs.And among the present invention, the output transmission that is provided with on each friction mandrel is only born 1/3 of whole driving outputs with mechanism.This is because these mechanisms are arranged on cause between driving shaft and each friction mandrel in the present invention.
The present invention program's 2 described friction spindle units is characterized in that, are located at the 1st spur gear and the 2nd spur gear engagement that is located on the driving shaft on each friction mandrel.This transmission mechanism can omit necessary belt in the prior art.
The present invention program's 3 described friction spindle units is characterized in that, each friction mandrel rotates by the side face of its dot location along driving shaft.With the driving shaft that flat belt drives, when reeling flat belt on driving shaft, diameter can be little; When engaging dot location, diameter can be done greatly, and at this moment the diameter of dot location can be selected for a short time.
The present invention program's 4 described friction spindle units is characterized in that driving shaft forms quill shaft, and friction mandrel stretches in this quill shaft.At this moment, available particularly advantageous form is regulated required transmission ratio.This is constructed similarly, and when driving shaft was being engaged by flat belt, diameter can be done for a short time.Quill shaft internal diameter ratio when friction mandrel stretches in the quill shaft is significantly big when engaging flat belt.As mentioned above, friction mandrel has spur gear or dot location, and quill shaft footpath portion within it has the 2nd spur gear as required.
The present invention program's 5 described friction spindle units is characterized in that driving shaft is configured between the friction mandrel.The advantage of this collocation form of driving shaft is, also with the present invention program's 4 structures similarly, also have no relations even the friction mandrel rotation number is not too high.In this variation of the present invention, also can construct similarly, spur gear and dot location are used for the output transmission with the present invention program 4.
The present invention program's 6 described friction spindle units is characterized in that the magnet-type coupling is located between each friction mandrel and the driving shaft.The magnet-type coupling of exporting transmission between 2 axles itself is known.Putting down in writing the use-case that makes of magnet-type coupler configuration and effect, for example open by the company of the same name catalogue " Magnetfabrik Bonn, PhysikalischeGrundlagenund Leistungsumfang " in Bonn.Driving shaft collocation form of the present invention can use the magnet-type coupling that can transmit less moment.The advantage of this magnet-type coupling be can be contactless ground, be noiselessness, export transmission to friction.Also can select favourable transmission ratio in this friction assembly of the present invention as described above.
This magnet-type coupling is characterized in that in the present invention program's 7 described structures, is disposing the 1st permanent magnet around driving shaft, is disposing the 2nd permanent magnet around each friction mandrel, and the 2nd permanent magnet is relative at radial direction with the 1st permanent magnet.In this case, permanent magnet is invested polarity at radial direction.In this case, when driving shaft is quill shaft, also can be configured between the friction mandrel.Annular gap between the 1st permanent magnet and the 2nd permanent magnet can be tried to achieve by calculating according to the characteristic value of permanent magnet and the relation of geometry.In of the present invention should the structure, it is favourable making 3 synchronized belts of friction mandrel or toothed timing belt.After the fracture of magnet-type coupling, because synchronization, half one of two couplings is that driving shaft and this friction mandrel are stopped earlier.This is disadvantageous for running.Take place for fear of this situation, moment is mechanically transmitted as described above, that is, once more before the rotation synchronously, moment is mechanically transmitted at this friction mandrel and driving shaft.Begin the moment of rotation synchronously once more at this friction mandrel and driving shaft, the magnet-type coupling is exported transmission again, and at this moment, the mechanism that mechanically transmits output rotates with no load condition.
The present invention program's 8 described friction spindle units is characterized in that, each the 2nd spur gear of each friction mandrel and the spur gear engagement that can be rotated to support on the equilateral triangle center.This collocation form is used to export that to transmit be the occasion that employing power splice or be frictionally engaged formula or magnet-type coupling formula are carried out.This collocation form can be guaranteed the rotation synchronously always of 3 friction mandrels.
When driving shaft is made the quill shaft structure, as as described in the present invention program 9, quill shaft becomes basin shape and is to use the deep draw manufactured, center at the bottom of the basin of quill shaft, be provided with the hollow shaft that stretch out vertically on the plane at the bottom of this basin, this hollow shaft can be rotated to support on the axle that is fixed in the basic component center.At this moment, at the peripheral part of hollow shaft, for example engaging and driving the flat belt that driving shaft is used.
The structure of another friction assembly of the present invention on basic component, is supporting rotating friction mandrel in three vertex position places of equilateral triangle as described in the present invention program 10, is fixing the dot location that overlaps each other at the equilateral triangle center on this friction mandrel; It is characterized in that each friction mandrel is by Motor Drive.This collocation form can save widely used flat belt in the prior art fully.For synchronization, can as above-mentioned each claim record, be bonded to each other in conjunction with mode or shape combination between 3 friction mandrels by frictional force.
Fig. 1 is the skiagraph of one embodiment of the invention friction spindle units.
Fig. 2 is the skiagraph of another embodiment of the present invention friction spindle units.
Fig. 3 is the cross-sectional view along III-III line among Fig. 2.
Fig. 4 is the skiagraph of another embodiment of the present invention friction spindle units.
Fig. 5 is the cross-sectional view along V-V line among Fig. 4.
Fig. 6 is the skiagraph of another embodiment of the present invention friction spindle units.
Fig. 7 is the skiagraph of another embodiment of the present invention friction spindle units.
Fig. 8 is the cross-sectional view along VIII-VIII line among Fig. 7.
Fig. 9 is the skiagraph of another embodiment of the present invention friction spindle units.
Figure 10 is the cross-sectional view along X-X line among Fig. 9.
Figure 11 is the skiagraph of another embodiment of the present invention friction spindle units.
Figure 12 is the skiagraph of another embodiment of the present invention friction spindle units.
Figure 13 is a plane of seeing friction spindle units shown in Figure 12 from the top.
Figure 14 is the skiagraph of another embodiment of the present invention friction spindle units.
Figure 15 is the cross-sectional view along XV-XV line among Figure 14.
Below, with reference to totally 9 embodiment in 15 accompanying drawings of description of drawings.
Fig. 1 represents the skiagraph of one embodiment of the invention friction spindle units.Disposing spacer 2 and dot location 3 on 3 friction mandrels 1 alternately, tensioning each other vertically.Friction mandrel 1 is configured in each vertex position place of equilateral triangle for example as shown in Figure 3 in parallel to each other.3 friction mandrels 1 can be rotated to support on axial 2 adjacent positions on the basic component 4 respectively.Upside deep trouth ball bearing 5 and downside deep trouth ball bearing 6 are used to support each friction mandrel 1.Upside deep trouth ball bearing 5 has buffering ring 7, and this buffering ring 7 is configured between the outside track 8 and basic component 4 of upside deep trouth ball bearing 5.The bottom of friction mandrel 1 is stretched in the basin shape driving shaft 9 of hollow circle tube, and this driving shaft 9 is to use the deep draw manufactured.10 have the hollow shaft 11 that stretches out to foreign side vertically from the basin baseplane at the bottom of the basin of driving shaft 9, and this hollow shaft 11 can be rotated to support on the axle 12 that is fixed in basic component 4 central authorities by axial 2 adjacent deep trouth ball bearings 13.Friction mandrel 1 respectively has 1 dot location 14 in its bottom, these dot locations 14 difference pushing tows the inner peripheral surface of hollow circle tube driving shaft 9.Engaging the flat belt 15 that drives driving shaft 9 on the outer peripheral face of hollow shaft 11.
Embodiment illustrated in fig. 2ly and embodiment illustrated in fig. 1 mainly contain following difference.That is, embodiment illustrated in fig. 2 in, each friction mandrel 1 also each pair is added with a band tooth plectane 16, surrounds the toothed timing belt 17 of 3 friction mandrels 1 and is with tooth plectane 16 to contact with each.Like this, can guarantee that 3 friction mandrels 1 rotate synchronously.In addition, with difference embodiment illustrated in fig. 1 be, hollow shaft 11 is inwardly to put in, and flat belt engages with the peripheral part of hollow circle tube driving shaft 9.Fig. 3 represents cross-sectional view embodiment illustrated in fig. 2, and from Fig. 3 as seen, 3 friction mandrels 1 are configured in three vertex positions of equilateral triangle respectively.
Embodiment illustrated in fig. 4ly and embodiment illustrated in fig. 2 mainly contain following difference.That is, embodiment illustrated in fig. 4 in, be not configured in the bottom of friction mandrel 1 dot location 14 does not resemble among Fig. 2 embodiment, but be configured between upside deep trouth ball bearing 5 and the downside deep trouth ball bearing 6.Cross-sectional view shown in Figure 5 clearly shows the collocation form of friction mandrel 1, also can see by the part of cross-sectional basic component 4 from Fig. 5.
Embodiment illustrated in fig. 6ly and embodiment illustrated in fig. 2 mainly contain following difference.That is, embodiment illustrated in fig. 6 in, driving shaft 9 is not rotatably mounted by the axle that is fixed on the basic component 4, but additional on the hollow shaft 11 pivot pin 18 that is fixed on the hollow shaft 11 is arranged.The Motor Drive that this pivot pin 18 for example can not shown by figure by the flat belt that figure does not show.
Embodiment illustrated in fig. 7ly and embodiment illustrated in fig. 4 mainly contain following two differences.Only show downside deep trouth ball bearing 6 among Fig. 7.The 1st difference is that the hollow shaft 11 of driving shaft 9 is not to put in towards axial inboard, but stretches out towards the axial outside that with embodiment illustrated in fig. 4 different flat belt 15 is bonded on the peripheral part of hollow shaft 11.The 2nd difference is or not to adopt dot location to export transmission, but be provided with magnet-type coupling 19.This magnet-type coupling 19 mainly is made of the permanent magnet 20 and the inboard permanent magnet 21 in the outside.The permanent magnet 20 in the outside is fixed on the driving shaft 9.In same plane, inboard permanent magnet 21 is adjacent to be configured on each friction mandrel at radial direction.The polarity of the permanent magnet 20,21 of the outside and inboard is towards radial direction.Form space 22 between two permanent magnets 20,21.Cross-sectional view shown in Figure 8 has roughly been represented the collocation form of permanent magnet 20,21.
Embodiment illustrated in fig. 9ly and embodiment illustrated in fig. 7 mainly contain two differences.First difference is, magnet-type coupling 19 is different with Fig. 7's, and it is arranged on the bottom of friction mandrel 1.Second difference is that it does not adopt the shape convolution coupling that with band tooth plectane 16 and toothed timing belt 17 3 friction mandrels 1 is linked mutually among Fig. 7, but is provided with rubber coupler 23.This rubber coupler 23 is fixed on the driving shaft 9, is provided with dot location 24 on each friction mandrel 1, and these dot locations 24 all pushing tow rubber coupler 23.In addition, the shape convolution coupling that adopts band tooth plectane and toothed timing belt that 3 friction mandrels 1 are linked mutually also can additionally be set.
Represented to have the collocation form of the permanent magnet 20,21 of radial direction polarity among Figure 10.
Embodiment illustrated in fig. 11ly and embodiment illustrated in fig. 2 mainly contain two differences.First difference is, driving shaft 9 is tubular structures, and this tubular drive shaft 9 is configured between 3 friction mandrels 1.Dot location 14 pushing tows of friction mandrel 1 peripheral part of tubular drive shaft 9.Second difference be, the variation of additional shape convolution coupling between 3 axles.In embodiment illustrated in fig. 11,3 friction mandrels 1 respectively have 1 spur gear 25, and these spur gears 25 can not be combined on the friction mandrel 1 respectively rotationally.Another spur gear 26 that is configured in equilateral triangle central authorities can be rotated to support on the axle 12 by sliding bearing 27.3 spur gears 25 all mesh with spur gear 26.
Embodiment illustrated in fig. 12ly and embodiment illustrated in fig. 6 mainly contain following difference.That is, driving shaft 9 forms the driven shaft of motor 28 simultaneously.Do not adopt embodiment illustrated in fig. 6 in such box-like output transmission of friction knot, but driving shaft 9 has and is bonded on 3 spur gears 29 between the friction mandrel 1, this spur gear 29 with fix on respectively under spur gear 30 engagements on the friction mandrel 1.In this friction spindle units, be that the output of shape convolution is transmitted, omitted the appended synchronization device among Fig. 6 embodiment.The plane of expression friction assembly shown in Figure 12 among Figure 13.
In embodiment illustrated in fig. 14, on basic component 31, supporting rotatable 3 friction mandrels 32 in three vertex position places of equilateral triangle.For friction mandrel 32 is bearing on the basic component 31, each friction mandrel is provided with upside deep trouth ball bearing 33 and axial adjacent downside deep trouth ball bearing 34, these deep trouth ball bearings 33,34 are bearing on the basic component 31.Between the outside track 35 and basic component 31 of upside deep trouth ball bearing 33, respectively be provided with a buffering ring 36 that is used for damping.
The bottom of friction mandrel 32 is respectively in conjunction with miniature motor 37.3 motor have a stator case 38, can know from Figure 15 and see, this stator case 38 has the stator hole (Staenderbohrung) 39 that each friction mandrel is used.Each stator hole 39 has magnet exciting coil and magnetic pole piece, and they are by the circular rings symbol ground expression of annotating label 40 among Figure 15.Rotor is being fixed in bottom at friction mandrel 32, and this rotor is formed by the permanent magnet that polarity is arranged on the rotor radius direction, and these rotors are by the circular rings symbol ground expression of annotating label 41 among Figure 14, Figure 15.Here Ji Zai structure is the typical construction that is used for the direct current machine.Electric connection part is not represented at this.
In order to make 3 friction mandrels 32 synchronous, on each friction mandrel 32, be provided with spur gear 42, toothed timing belt 43 is wound on 3 spur gears 42.
The following describes the action form of friction spindle units of the present invention.To embodiment illustrated in fig. 13, the structure of its driving mechanism is identical for Fig. 1.Driving shaft 9 is driven by flat belt 15 or motor 28, and the rotation of driving shaft 9 is passed to 3 friction mandrels 1 respectively.In order to export transmission, some different mechanisms have been proposed in the illustrated embodiment.Fig. 1 to Fig. 5 and embodiment illustrated in fig. 11 in, on each friction mandrel, fixing dot location 14, this dot location 14 rotates with the side face CONTACT WITH FRICTION of driving shaft 9.Fig. 2 to Fig. 5 and embodiment illustrated in fig. 11 in, friction mandrel 1 is by additional sychronisation synchronization.During Fig. 7 is extremely embodiment illustrated in fig. 10, be provided with magnet coupling 19, these magnet couplings 19 are configured between driving shaft 9 and each friction mandrel 1.Outside permanent magnet 20 is with driving shaft 9 rotations, and the magnetic force between outside permanent magnet 20 and the inboard permanent magnet 21 makes each friction mandrel 1 contactless ground interlock.Fig. 1, Fig. 7 are to driving shaft shown in Figure 10, and its diameter ratio is made particularly advantageous structure.In the zone that flat belt 15 engages, the diameter of driving shaft 9 is little, and in the zone of outside permanent magnet 20 or dot location 14,24, the diameter of driving shaft 9 is very big.Driving shaft 9 is made this structure, can obtain high circular velocity, this circular velocity is delivered to each friction mandrel 1.Also can not adopt magnet-type coupling 19, and in other embodiment, put down in writing, the joint portion of frictional engagement formula or shape convolution selectively is set between driving shaft 9 and friction mandrel 1.Distinguishing feature embodiment illustrated in fig. 9 is to be provided with drive unit more.On the one hand, be provided with magnet coupling 19 between driving shaft 9 and each friction mandrel 1, on the other hand, the dot location 24 that is fixed on each friction mandrel 1 rotates on rubber coupler 23.Output is delivered in usually only to be undertaken by magnet coupling 19.An occasion of being unable to undergo conjugation in magnet coupling 19 only, moment is transmitted by rubber coupler 23.23 of rubber coupler played conjugation before this friction mandrel 1 rotates synchronously with driving shaft 9 again.That is, at this moment this permanent magnet 20,21 is conditioned once more, so that magnet coupling 19 plays conjugation again.From this constantly, rubber coupler is zero load rotation.Feature embodiment illustrated in fig. 12 is as follows: promptly, during this was embodiment illustrated in fig. 12, the output transmission between driving shaft 9 and the friction mandrel 1 was to be undertaken by the spur gear 29,30 that is being engaged with each other.In this structure, omitted and made 3 friction mandrels, 1 synchronized other mechanism.
Figure 14, embodiment illustrated in fig. 15 in, each friction mandrel 32 is driven by intrinsic motor 37.Motor 37 can be made minor structure based on little output transmission, at this moment can side by side obtain high rotating speed by this motor 37.
Claims (10)
1. a friction spindle units on basic component (4), is supporting rotating friction mandrel (1) in three vertex position places of equilateral triangle, is fixing the dot location (3) that overlaps each other at the equilateral triangle center on this friction mandrel (1); It is characterized in that being provided with can be center rotation and the driving shaft (9) that is parallel to friction mandrel (1) with the center of equilateral triangle, between this driving shaft (9) and each friction mandrel (1), is provided with output transmission mechanism (14,19,29,30).
2. friction spindle units as claimed in claim 1 is characterized in that, each friction mandrel (1) is by being located at the 1st spur gear (30) and the 2nd spur gear (29) engagement that is located on the driving shaft (9) on this friction mandrel (1).
3. friction spindle units as claimed in claim 1 is characterized in that, each friction mandrel (1) rotates by the side face of its dot location (14) along driving shaft (9).
4. friction spindle units as claimed in claim 1 is characterized in that, driving shaft forms quill shaft (9), and friction mandrel (1) stretches in this quill shaft.
5. friction spindle units as claimed in claim 1 is characterized in that, driving shaft (9) is configured between the friction mandrel (1).
6. friction spindle units as claimed in claim 1 is characterized in that, magnet-type coupling (19) is located between each friction mandrel (1) and the driving shaft (9).
7. friction spindle units as claimed in claim 6, it is characterized in that, disposing the 1st permanent magnet (21) on every side at driving shaft (9), disposing the 2nd permanent magnet (20) on every side at each friction mandrel (1), the 2nd permanent magnet (20) is relative at radial direction with the 1st permanent magnet (21).
8. friction spindle units as claimed in claim 1 is characterized in that, each the 2nd spur gear (25) of each friction mandrel (1) and spur gear (26) engagement that can be rotated to support on the equilateral triangle center.
9. friction spindle units as claimed in claim 4, it is characterized in that, the basin shape quill shaft (9) that the sheet metal deep draw is formed, the center of (10) at the bottom of its basin, be provided with the hollow shaft (11) that stretch out vertically on the plane of (10) at the bottom of this basin, this hollow shaft (11) can be rotated to support on the axle (12), and this axle (12) is fixed on the center of basic component (4).
10. a friction spindle units on basic component (31), is supporting rotating friction mandrel (32) in three vertex position places of equilateral triangle, is fixing the dot location (3) that overlaps each other at the equilateral triangle center on this friction mandrel (32); It is characterized in that each friction mandrel (32) is driven by motor (37).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN96193048A CN1052517C (en) | 1995-06-01 | 1996-04-26 | Drive for friction spindle units |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19520120.5 | 1995-06-01 | ||
| DE19520120A DE19520120A1 (en) | 1995-06-01 | 1995-06-01 | Drive for friction spindle units |
| CN96193048A CN1052517C (en) | 1995-06-01 | 1996-04-26 | Drive for friction spindle units |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1180388A CN1180388A (en) | 1998-04-29 |
| CN1052517C true CN1052517C (en) | 2000-05-17 |
Family
ID=25744088
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN96193048A Expired - Lifetime CN1052517C (en) | 1995-06-01 | 1996-04-26 | Drive for friction spindle units |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1052517C (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009040864A1 (en) * | 2009-09-09 | 2011-03-10 | Schaeffler Technologies Gmbh & Co. Kg | Friction motor spindle |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1379960A (en) * | 1972-03-30 | 1975-01-08 | Scragg & Sons | False twisting apparatus |
| GB2212176A (en) * | 1987-12-23 | 1989-07-19 | Kugelfischer G Schaefer & Co | False-twisting texturing appliance |
| GB2254342A (en) * | 1991-03-30 | 1992-10-07 | Kugelfischer G Schaefer & Co | Friction false-twisting unit with a drive motor |
-
1996
- 1996-04-26 CN CN96193048A patent/CN1052517C/en not_active Expired - Lifetime
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1379960A (en) * | 1972-03-30 | 1975-01-08 | Scragg & Sons | False twisting apparatus |
| GB2212176A (en) * | 1987-12-23 | 1989-07-19 | Kugelfischer G Schaefer & Co | False-twisting texturing appliance |
| GB2254342A (en) * | 1991-03-30 | 1992-10-07 | Kugelfischer G Schaefer & Co | Friction false-twisting unit with a drive motor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1180388A (en) | 1998-04-29 |
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