EP3514270A1 - Drive device for a nipper mechanism of a comber - Google Patents

Abstract

The present invention relates to a drive device for a nipper unit (10) of a comber (4), with a driven forceps shaft (22) for the reciprocating movement of the nipper unit (10) and an upper nipper shaft (27) for opening and closing a nipper ( 11). According to the invention a pliers auxiliary shaft (100) is provided, on which at least one upper nipper cam (110a, 110b) and at least one nipper cam (102a, 102b) are arranged rotationally fixed, wherein for opening and closing the upper nipper (11), the upper nippers Cam plate (110) with an upper nipper cam roller (112) and independently of the reciprocating movement of the nipper unit (10), the nipper cam (102) with a nipper cam roller (104) cooperates.

Description

The present invention relates to a drive device for a nipper unit of a comber, with a driven forceps shaft for the reciprocation of a nipper unit and a top nipper shaft for opening and closing the upper nipper.

In a combing machine with a large number of combing points, each nipper unit, which has a lower nipper plate and an upper nipple rotatably mounted thereon, presents a tuft of a tuft to a round comb arranged beneath the nipper unit for combing out. During a Kämmspiels the nipper unit moves from a rearward open position to a front closed position, during this reciprocation of the nipper unit opens and closes the upper nipper, wherein in the closed state of the nipper unit, the lower nipper with the upper nipper forms a clamping point while a hanging tuft presents a combing segment of the circular comb. After combing with the circular comb, the nipper unit opens, in which the upper nipper lifts off from the lower nipper plate and the combed tuft is fed via a rotatably mounted in the nipper unit feed cylinder a downstream Abreisswalzenpaar for soldering the combed fiber slivers. The combed slivers formed at the individual combing points are then transferred on a conveyor table side by side to a subsequent drafting system in which they are stretched and then combined to form a common combing machine belt. The sliver produced at the drafting system is then placed on a funnel wheel in a pot.

For optimum combing of the tuft aggregate fed tuft the position of the nipper unit and the pivot position of the upper nipper is important, since in this way the hanging tuft defines the time of reaching the clamping action. With optimum adjustment of the upper nipper to the lower nipper plate thus the combing quality of the circular comb and the soldering can be positively influenced with the tear-off rollers.

From the EP 2 489 767 A1 is a drive device for a nipper unit of a comber known. The drive device has a tongs axis for a reciprocating movement of the nipper unit and an upper nipper shaft for opening and closing the upper nipper. On the upper tongs shaft rotatably seated an upper nipper rocker arm with two rotatably mounted upper nipper cam rollers, which cooperate with two on an upper nipper auxiliary shaft rotatably mounted upper nipper cams. The upper tongs shaft is disposed axially parallel to the upper tongs auxiliary shaft and thus allows the interaction of the upper nipper cam rollers with the upper nipper cams, wherein the upper nipper auxiliary shaft is connected to a separate upper nipper drive motor. The aim of this device is a gentle closing of the upper nipper against the lower forceps plate.

A further disadvantage of the known drive device for the upper nipper of the combing machine is that the upper nipper auxiliary shaft must be arranged with the upper nipper cams very close to the upper nipper shaft, so that the upper nipper cams can cooperate with the arranged on the upper nipper shaft upper nipper cam rollers , Accordingly, the upper nipper cams must be formed with such a large diameter of about 200 mm, so that a deflection angle for opening and closing the upper nipper is sufficient. Usually, a cam arrangement is designed such that a maximum deflection angle of +/- 15 ° is adjustable.

Object of the present invention is thus to provide a drive device for a nipper unit of a combing machine, which adjusts the position of the reciprocating motion of the nipper unit synchronously to open and close the upper nipper.

The object is achieved by a drive device having the features of independent patent claim 1.

Proposed is a drive device for a nipper unit of a comber, with a driven tong axis for the reciprocation of a Nipper unit and an upper nipper shaft for opening and closing the upper nipper.

According to the invention a pliers auxiliary shaft is provided, on which at least one upper nipper cam and at least one nipper cam rotatably disposed, wherein for opening and closing the upper nipper, the upper nipper cam with a caliper cam follower and regardless of the reciprocating motion of Zangenaggregates the pliers cam interacts with a pliers cam roller. In a known manner, the upper nipper shaft is provided with an eccentric to increase the deflection of the movement of the upper nipper. The forceps auxiliary shaft has the advantage that the forceps movement and the upper forceps movement are coupled to each other via a drive train, but the forceps cams and the upper nipper cams are designed so that independently different motion profiles are adjustable. In this way, the upper nipper can be opened when the lower nipper is in the rear position and the upper nipper can form a clamping point with the lower nipper, when the nipper unit is in the forward position, where a tuft sticks out of the nip of the nipper and combed out in a known manner by a circular comb.

Preferably, the upper nipper cam follower is connected via a four-joint to a top nipper shaft. The four-joint has the advantageous effect that the deflection angle of the upper nipper cam can be extended so that even with very small cams and a corresponding eccentric meaningful opening and closing of the upper nipper is possible.

Particularly preferably, the four-joint is formed by the upper nipper cam roller is held by a top caliper rocker arm and is connected via a coupling rod in conjunction with an upper nipper shaft clamp with the upper nipper shaft. This is a specific solution for the four-joint to take advantage of the advantages mentioned above.

Alternatively, the upper nipper rocker arm and the upper nipper shaft clamp are pivotally connected via a screw to the coupling rod. The screw connection a very quick assembly and disassembly of the four-joint. Thus, an element of the coupling rod can be replaced on the spot very quickly.

Preferably, the four-joint reinforced an outer angle for the opening and closing of the upper nipper in a ratio of 1: 2, preferably up to an outer angle of +/- 30 °. Accordingly, with the four-joint in a very simple and cost-effective manner, the extension of the deflection angle of the upper nipper at a certain distance to the upper nipper cam in conjunction with the upper nipper cam follower possible. As a result, comparatively small top calipers can be used since the four-joint enlargement is 1: 2, i. for a deflection angle up to +/- 30 °. Thus, the upper nipper cam in conjunction with the upper nipper cam follower may be spaced from the upper nipper shaft, and these elements need not be adjacent to one another as in the prior art.

In addition, the first upper nipper cam and a second upper nipper cam are preferably arranged on the nipper auxiliary shaft independently of the at least one nipper cam, so that the first nipper cam follower and a second upper nipper cam follower are each rotatably mounted on the top nipper rocker arm such that the first top caliper cam interacts with the first top caliper cam roller and the second top caliper cam cooperates with the second top caliper cam roller, whereby the second top caliper cam roller prevents the first top caliper cam roller from lifting off the first top caliper cam ,

Further preferably, the first pliers cam and a second pliers cam are rotatably disposed on the pliers auxiliary shaft regardless of the at least one upper nipper cam, wherein the first nipper cam follower and a second nipper cam follower rotatably on the nipper rocker arm such that the first caliper cam interacts with the first caliper cam roller and the second caliper cam interacts with the second caliper cam roller, whereby the second caliper cam roller prevents the first caliper cam roller from interfering with the first caliper cam follower. Cam lifts off.

In addition, on the pliers auxiliary shaft, a single upper-nosed cam disk is also non-rotatably arranged independently of the at least one nipper cam disk, which cooperates with a single upper nipper cam follower rotatably mounted on the upper nipper rocker arm, wherein a spring element is provided on the upper nipper rocker arm between a machine frame and the upper nipper rocker lever cooperates such that the single upper nipper cam follower does not lift off the single upper nipper cam.

Further preferably, a single pliers cam is rotatably arranged on the pliers auxiliary shaft independent of the at least one upper nipper cam, which cooperates with a rotatably mounted on the pliers rocker arm single pliers cam roller, wherein on the pliers rocker arm, a spring element is provided which cooperates between a machine frame and the pincer rocker arm such that the single pincer cam does not lift off the single pincer cam.

Furthermore, the invention relates to a combing machine with a drive device for a nipper unit in conjunction with an upper nipper.

Further advantages of the invention will be apparent from an embodiment described below and shown.

Fig. 1

einen Querschnitt durch eine Kämmmaschine;

Fig. 2

eine erfindungsgemässe Kombination von vier Getriebe-Modulen mit einem einzigen Antriebsmotor;

Fig. 3

eine weitere Ausführung einer Kombination von Getriebe-Modulen;

Fig. 4

eine erfindungsgemässe Antriebsvorrichtung;

Fig. 5

Bewegungsprofil der Zange und Bewegungsprofil der Oberzange;

Fig. 6

ein erfindungsgemässes Ausführungsbeispiel;

Fig. 7

ein weiteres erfindungsgemässes Ausführungsbeispiel.

Show it:

Fig. 1

a cross section through a comber;

Fig. 2

an inventive combination of four transmission modules with a single drive motor;

Fig. 3

another embodiment of a combination of transmission modules;

Fig. 4

an inventive drive device;

Fig. 5

Movement profile of the forceps and movement profile of the upper forceps;

Fig. 6

an inventive embodiment;

Fig. 7

another embodiment of the invention.

Fig. 1 schematically shows a cross section of a Kämmstelle 2 of a combing machine 4. In practice, eight such Kämmstellen 2 are arranged side by side. each Kämmstelle 2 consists of a nipper unit 10 (short: pliers called), which performs a reciprocating motion of the forceps 10 via front wings 12 and rear wings 14. The front wings 12 (only one shown) are rotatably mounted on a circular comb shaft 16 and a front tongs axis 18 of the forceps 10. The rear swing arm 14, which is rotatably mounted on a rear tong axis 20 of the forceps 10, is rotatably connected to a driven forceps shaft 22. A feed cylinder 24, which is rotatably mounted within the forceps 10, a cotton wool 26 is supplied. The cotton wool 26 is unwound from a cotton roll, not shown, which rests on winding rollers, also not shown for the rolling process.

In the in Fig. 1 shown position, the pliers 10 is opened, that is, a collet 11 is pivotally mounted relative to a lower jaw 13 via a upper jaw pin 25 and thus lifted from the lower jaw 13 and the forceps 10 is in a forward position, in which the out of the forceps 10 tuft 28 is attached to a fiber end 30 of an already formed nonwoven fabric 32 and soldered thereto. The fiber fleece 32 is held by a pair of Abreisswalzen 34, which perform a rotational movement indicated by the arrows for the soldering and tearing off and thus the nonwoven fabric 32, and the fiber end 30 moves in the transport direction T.

In a rear, not shown, end position of the forceps 10, this is closed, wherein the tuft 10 projecting from the tongs 10 is combed out by a combing segment 36, or by a combing set of a rotatably mounted circular comb 38. The combing segment 36 is in an upper position during the combing process. The combing segment 36 is usually provided with Garniturzähnen which engage during the combing process in the tuft 28.

The circular comb 38, which is rotatably supported by the circular comb shaft 16 in the machine frame, is located within a substantially closed suction duct 40, which opens into a channel 42. The channel 42 is, as shown schematically, in communication with a vacuum source 44, by means of which the separated material is fed to a collection point, not shown.

The separated material is short fibers, shell parts, and other contaminants, which are combed out of the tuft 28 by the combing segment 36 during the combing process. A portion of the combed material is transferred by the applied negative pressure via the vacuum source 44 and the resulting air flow directly to the channel 42. The rest of the part, in particular the combed fibers remains in the combing segment 36, or settles between the Garniturzähnen and is by the rotational movement of the circular comb 38 down in the in Fig. 1 transported position shown. In this case, the combing segment 36 passes into the area of action of a brush 48 likewise rotatably mounted in the suction duct 40 via a brush shaft 46, which brush is provided with distributed bristles 50 on its circumference.

In Fig. 2 is a combination 51 of a first gear 52 for generating a pilgrim movement for the Abreisswalzen 34 (see Fig. 1 ), a second gear 54 for non-uniform driving of the circular comb 38 (see Fig. 1 ), a third gear 56 for reciprocating the pliers 10 (see Fig. 1 ) and a fourth gear 58 for opening and closing the upper nipper 11 (see Fig. 1 ) intended. The four transmissions 52, 54, 56, 58 are provided in a module construction, wherein the combination 51 of the four transmission modules 52, 54, 56, 58 is enclosed by a housing 60.

The first transmission module 52 has a first drive train 62 with a first drive shaft 64, which transmits via a differential gear 66 a continuous rotational movement to a ring gear 74. The transmission module 52 also includes a second driveline 68 having a breakaway roll auxiliary shaft 70 on which a breakaway cam plate means 72 for generating a forward and backward movement 87 is disposed.

The differential gear 66 is formed as a planetary gear, wherein the first drive train 62 via the ring gear 74 in conjunction with Planentenrädern 76 drives a sun gear 78 to transmit the continuous rotational movement of the ring gear 74 to the tear-off rollers 34. Independently of this, the forward and backward movement 87 is formed by the tear-off roller cam device 72, wherein the tear-off roller cam device 72 two on the Abreisswalzen auxiliary shaft 70 rotatably arranged Abreisswalzen cams 80 which interact in interaction with two Abreisswalzen cam rollers 82. The two Abreisswalzen cam rollers 82 are connected via a Abreisswalzen rocker arm 84 with a planet carrier 86 of the differential gear 66, so that the forward and backward movement 87 of the Abreisswalzen cams 80 is superimposed on the planet carrier 86 with the continuous rotational movement of the ring gear 74 to to transmit a pilgrim movement on the tear-off rollers 34.

The first drive train 62 is drive-connected according to the present embodiment with a table calender 88 and with transport rollers 90, and is in this way a part of the first gear module 52. It is of course also possible Tischkalander 88 and transport rollers 90 via a separate Drive powertrain.

The second gear module 54 has a circular comb auxiliary shaft 92 which is connected via a non-circular gear stage 94 of two intermeshing non-circular gears 96a, 96b with the circular comb shaft 16, the non-circular gear stage 94 is a continuous rotational movement of the circular comb auxiliary shaft 92 in a non-uniform rotational movement the circular comb shaft 16 converts.

It should be noted at this point that the diameter of the circular comb shaft according to the prior art is 30 mm and 35 mm. By increasing the combing machine speed, the multiples of the natural frequency are superimposed with the combing machine speed, so that an undesired resonance of the round comb waves is excited. To prevent this it is proposed to minimize the natural frequency by stiffening the ridge corrugation. Therefore, it is ideally proposed to select a circular comb shaft diameter of 35 mm to 45 mm, preferably 40 mm.

The third gear module 56 is designed for the reciprocating movement of the forceps 10 with a forceps cam device 98, wherein in the embodiment according to Fig. 2 pliers cam 98 has two pliers cam 102 (only one shown) rotatably mounted on pliers auxiliary shaft 100 that interact with two pliers cam rollers 104 (only one shown). interact. The two pincer rollers 104 are connected to the driven pincer shaft 22 via a pincer rocker arm 106 (see FIG Fig. 1 ), so that the movement profile, in particular the reciprocating movement of the forceps cam 102 on the forceps 10 (see Fig. 1 ) is transmitted.

The fourth transmission module 58 is for the opening and closing of the upper nipper 11 (see Fig. 1 ) is formed with an upper nipper cam device 108, wherein in the embodiment according to Fig. 2 the upper nipper cam 108 has two upper nipper cams 110 rotatably mounted on the nipper auxiliary shaft 100 (only one shown) that interact with two upper nib followers 112 (only one shown). The two top caliper rollers 112 are rotatably mounted via a screw connection to a top caliper rocker arm 114, wherein the top caliper rocker arm 114 is connected via a coupling rod 116 in conjunction with an upper nipper shaft clamp 118 with the upper nipper shaft 27. The upper nipper rocker arm 114 and the upper nipper shaft clamp 118 are connected by screw 122 with the coupling rod 116, wherein the coupling rod 116 is formed of three elements 116 a, 116 b, 116 c and so the tongs auxiliary shaft 100 via a four-joint 124 with the Upper tongs shaft 27 connects.

In the embodiment according to Fig. 2 the combination 51 of transmission modules 52, 54, 56, 58 is driven by a common motor 128. On the Abreisswalzen auxiliary shaft 70 of the second drive train 68 rotatably sits a Abreisswalzen drive gear 130, on the circular comb auxiliary shaft 92 is rotatably seated a circular comb drive gear 132 and on the pliers auxiliary shaft 100 rotatably seated a pliers drive gear 134, wherein all drive gears 130th , 132, 134 are the same size and engaged with each other. By forming the drive gears 130, 132, 134 with the same dimension, the same speed is transmitted to all transmission modules via the common motor 128. This has an advantage, in particular, when a transmission module or a combination of at least two transmission modules are arranged between two groups of combing points, such as, for example, later in FIG Fig. 6 explained in more detail. An intermediate gear 136, which is engaged with the Abreisswalzen drive gear 130 is rotatably on an engine auxiliary shaft 138 and the motor auxiliary shaft 138 is guided through the housing 60 to the outside and there is non-rotatably a motor idler gear 140. The motor idler gear 140 is drivingly connected via a toothed belt 142 with a motor gear 144, wherein the motor gear 144th rotationally fixed on a motor shaft 146 of the common motor 128 is attached.

Alternatively, instead of the drive gears 130, 132, 134, a toothed belt drive may be used.

On a shaft (e.g., 70, 92, 100) with constant combing machine speed, at least one sensor in the form of a speed sensor (incremental with reference or absolute) is mounted outside the housing 60.

In the present embodiment, a control unit 131 is connected to a first sensor 133a, a second sensor 133b and a frequency converter 129, wherein the frequency converter 129 drives the common motor 128.

The first sensor 133a is a speed sensor and mounted outside of the housing 60 on the pliers auxiliary shaft 100 to determine the absolute machine position.

The second sensor 133b is preferably an induction sensor or tachometer and mounted outside of the housing 60 on the rear tongs shaft 22. The second sensor 133b is adapted to the distance of the lower nipper 13 in the front end position according to Fig. 1 to determine the Abwalwalzen 34, which is the so-called Ecartement in combing machines.

Fig. 3 11 shows an exemplary embodiment of a first combination 51a with the first transmission module 52 for the pilgrim movement of the tear-off rollers 34 and the second transmission module 54 for non-uniform movement of the circular comb shaft 16, wherein the transmission modules 52, 54 are enclosed by a first housing 60a are. A first frequency converter 129a in conjunction with a first drive motor 128a is connected to the first combination 51a in the same manner as in FIG Fig. 2 described drive-connected.

The third gear module 56 for the reciprocating motion of the driven forceps shaft 22 and the fourth transmission module 58 for the movement of the upper forceps shaft 27 are combined in a second combination 51b and enclosed by a second housing 60b. The pliers auxiliary shaft 100 is passed through the second housing 60b and externally connected directly to a second drive motor 128b. The forceps cam device 98 and the top caliper device 108 are disposed in the same manner on the forceps auxiliary shaft 100 as previously associated with FIG Fig. 2 described.

The first drive motor 128a and the second drive motor 128b are synchronized with each other via the control unit 131, the drive motors 128a, 128b being asynchronous motors drivingly connected to a corresponding frequency converter 129a, 129b.

In an alternative embodiment, the drive motors 128a, 128b are servomotors, each in communication with a servo amplifier 129a, 129b.

The circular comb auxiliary shaft 92 is guided by the housing 60a to the outside and a third sensor 133c in the form of a speed sensor is mounted outside the housing 60a on the circular comb auxiliary shaft 92. The third sensor 133c is drivingly connected to the control unit 131 and has the task of transmitting the rotational position of the circular comb auxiliary shaft 92 to the control unit 131, so that via the control unit 131 the second frequency converter 129b in conjunction with the second drive motor 128b, the position of the forceps 10 and the upper nipper 11 with respect to the rotational position of the Abreisswalzen 34 and the circular comb auxiliary shaft 92 can set optimally for the combing process and soldering.

According to Fig. 4 is purely schematically shown an inventive drive device 132 with the forceps cam device 98 (solid line) and the upper nipper cam device 108 (dashed line) shown. Two forceps cams 102a, 102b and two forceps cams 110a, 110b are non-rotatably mounted on the forceps auxiliary shaft 100.

The purely schematically illustrated pliers rocker arm 106 has two pliers cam rollers 104a, 104b, which are spaced apart at an angle α, the first pliers cam 102a with the first pliers cam 104a and the second pliers cam 102b with the second caliper cam 104b cooperates. The second pincer roller 104b prevents the first pincer roller 104a from being lifted off the first pincer cam 102a. The pliers cam rollers 104a, 104b have a diameter of 90 mm and the pliers cam plates 102a, 102b each have a disc width of 15 mm to 30 mm, preferably 20 mm. The bearing of the pliers cam 102 can be done either via rolling bearings or plain bearings. When using rolling bearings whose diameter is in the range of 90 mm to 120 mm. When using plain bearings whose diameter is preferably in the range of 60 mm to 90 mm. In particular in small spaces, the use of slide bearings is preferably accessed.

The purely schematically illustrated upper nipper rocker arm 114 has two upper nipper cam rollers 112a, 112b which are spaced apart at an angle β, the first Oberzangen- cam 110a with the first upper nipper cam follower 112a and the second Oberzangen- cam 110b with the second upper nipper cam follower 112b cooperates. The second upper nipper cam roller 112b prevents the first upper nipper cam roller 112a from being lifted off the first upper nipper cam 110a. The upper nipper cam rollers 112a, 112b have a diameter of 30 mm, and the upper nipper cams 110a, 110b each have a disk width of 10 mm to 20 mm, preferably 14 mm. The storage of the upper nipper cam 110 can be done either via roller bearings or plain bearings. When using rolling bearings, their diameters are in the range of 30 mm to 60 mm. When using plain bearings whose diameter is preferably in the range of 20 mm to 30 mm. In particular in small spaces, the use of slide bearings is preferably accessed.

Each cam 102, 110 has a specific outer circumference, on which the respective cam roller 104, 112 rests. By the mechanical connection of the respective cam roller 104, 112 with the corresponding drive shaft (forceps shaft 22 and Upper nipper shaft 27), a pincer movement profile 134 of the pincer cams 102 is transmitted to the driven pincer shaft 22 and an upper nipper movement profile 136 of the upper nipper cam 110 is transferred to the upper nipper shaft 27.

Advantageously, both cam devices 98, 108 are mechanically coupled to each other via the forceps auxiliary shaft 100, but are independently adjustable to tune the reciprocating motion of the forceps 10 and the opening and closing of the upper forceps 11. This situation is in Fig. 5 shown.

In Fig. 5 is on the abscissa (horizontal X-axis) a single revolution, ie from 0 ° to 360 °, the respective cam 102, 110 and on the ordinate axis (vertical Y-axis) a cam deflection angle of 0 ° to 35 ° for the Pliers cam 102 and the upper nipper cam 110 shown. The solid line is the forceps motion profile 134 and the dashed line is the upper forceps motion profile 136. At approximately 150 °, as in FIG Fig. 1 described the forceps 10 in the forward position and the upper nipper 11 is seated on the lower nipper 13 and is closed. At 0 ° and at 360 °, the forceps 10 is in the rearward position with a forceps deflection angle γ of about 31 °, and the upper forceps 11 is opened with a forceps deflection angle δ of about 27 °.

A significant advantage of the inventive drive device 132 as in Fig. 4 shown is the independent movement of the upper nipper opposite the lower nipper, which can be set via the upper nipper cam device 108 very different timing for the opening and closing of the upper nipper against the lower nipper. Accordingly, the top caliper movement may be phase shifted by adjusting the top calipers device for forceps movement, as also in FIG Fig. 5 for another upper forceps movement profile 136b. Here, the additional upper forceps movement profile 136b is generated in cooperation with an eccentric. In particular, the eccentric can further increase the deflection angle of the upper-nipper movement. Accordingly, via the upper nipper cam device 108 in conjunction with the four-joint and the eccentric an earlier opening of the upper nipper possible, whereby the tuft for the soldering process can optimally align in the direction of Abreisswalzen. By reducing the amplitude, a gentler closure of the upper nipper, whereby an advantageous noise reduction is given.

According to Fig. 6 The upper nipper cam 108 has two upper nipper cams 110a, 110b rotatably mounted on the pincer auxiliary shaft 100, which cooperate with two upper nip cam rollers 112a, 112b. The two upper nipper cam rollers 112a, 112b are rotatably mounted via a screw 122 on the upper nipper rocker arm 114 shown purely schematically, wherein the upper nipper rocker arm 114 is connected via the coupling rod 116 in conjunction with the upper nipper shaft clamp 118 with the upper nipper shaft 27. The upper nipper rocker arm 114 and the upper nipper shaft clamp 118 are connected by screw 122 with the coupling rod 116, wherein the coupling rod 116 is formed of three elements 116 a, 116 b, 116 c, and so the tongs auxiliary shaft 100 via the four-joint 124 with the Upper tongs shaft 27 connects. In Fig. 6 is clearly seen that the upper nipper deflection angle δ caused by the upper nipper cam device 108 is about 30 ° and the four-joint 124 is a new upper nipper deflection angle δ * of up to 60 ° adjustable.

According to Fig. 7 The upper nipper cam 108 has a single upper nipper cam 110 rotatably mounted on the nipper auxiliary shaft 100 that interacts with a single upper nib cam 112. The upper nipper rocker arm 114 is provided with a spring member 138 which cooperates between a machine frame 140 and the upper nipper rocker arm 114 so that the single upper nip cam follower 112 does not lift off the single upper nipper cam 110. The upper nipper cam follower 112 is rotatably mounted via a screw connection 122 to the upper nipper rocker arm 114 shown purely schematically, wherein the upper nipper rocker arm 114 is connected to the upper nipper shaft 27 via the connecting rod 116 in conjunction with the upper nipper shaft clamp 118. The upper nipper rocker arm 114 and the upper nipper shaft clamp 118 are connected by screw 122 with the coupling rod 116, wherein the coupling rod 116 is formed of three elements 116 a, 116 b, 116 c and so the pliers auxiliary shaft 100 connects via the four-joint 124 with the upper nipper shaft 27. In Fig. 7 is clearly seen that the upper nipper deflection angle δ caused by the upper nipper cam device 108 is about 30 ° and the four-joint 124 is a new upper nipper deflection angle δ * of up to 60 ° adjustable.

Legend

2

Kämmstelle

4

comber

10

Nipper unit (short tongs)

11

A nipper

12

front rocker

13

lower nipper

14

rear swingarm

16

Circular comb shaft

18

Front tongs axis

20

Rear pliers axis

22

Powered forceps shaft

24

feed cylinder

25

A nipper pins

26

wadding

27

A nipper shaft

28

tuft

30

fiber end

32

non-woven fabric

34

detaching roller

36

comb segment

38

circular comb

40

extraction well

42

channel

44

Vacuum source

46

brush shaft

48

brush

50

bristles

51

Combination of transmission modules

52

First transmission module

54

Second gear module

56

Third gear module

58

Fourth transmission module

60

casing

62

First drivetrain

64

First drive shaft

66

Differential gear (tarpaulin gearbox)

68

Second drive train

70

Detaching auxiliary shaft

72

Detaching-cam device

74

ring gear

76

planet

78

sun

80

Detaching-cam

82

Detaching type Cam

84

Detaching rocker arm

86

planet carrier

88

Tischkalander

90

transport rollers

92

Circular comb-auxiliary shaft

94

Circular comb differential gear

96

non-circular gear

98

Pliers cam device

100

Pliers auxiliary shaft

102

Pliers cam

104

Clamp follower

106

Pliers rocker

108

Upper tong cam device

110

Upper Clamp cam

112

Upper Clamp follower

114

Upper Clamp rocker

116

Coupling rod (three elements)

118

A nipper shaft bracket

122

screw

124

Four joint

128

Common engine, drive motor

129

frequency converter

132

driving device

133

Sensor (speed sensor)

134

Pliers motion profile

136

Upper Clamp motion profile

138

spring element

140

machine frame

α

Angle pliers cam rollers

β

Angle top calipers

γ

Upper Clamp deflection

δ

Pliers deflection

Claims (10)

Drive device for a nipper unit (10) of a combing machine (4), with a driven tongs shaft (22) for the reciprocating movement of the nipper unit (10) and an upper nipper shaft (27) for opening and closing an upper nipper (11), characterized in that a pliers auxiliary shaft (100) is provided, on which at least one upper nipper cam (110a, 110b) and at least one nipper cam (102a, 102b) are arranged rotationally fixed, wherein for opening and closing the upper nipper (11) Upper nipper cam (110) with an upper nipper cam roller (112) and independently of the reciprocating movement of the nipper unit (4), the nipper cam (102) with a nipper cam roller (104) cooperates. Drive device according to claim 1, characterized in that the upper nipper cam roller (112) via a four-joint (124) with the upper nipper shaft (27) is connected. Drive device according to claim 2, characterized in that the four-joint (124) is formed by the Oberkangen-cam roller (112) by a Oberzangen-rocker arm (114) is held and via a coupling rod (116) in conjunction with a Oberzangenwellen -Klammer (118) is connected to the upper nipper shaft (27). Drive device according to claim 3, characterized in that the upper nipper rocker arm (114) and the upper nipper shaft clamp (118) via a screw connection (122) are pivotally connected to the coupling rod (116). Drive device according to one of claims 2 to 4, characterized in that the four-joint (124) has an outer angle for opening and closing the upper nipper (11) in a ratio of 1: 2, preferably up to an outer angle of +/- 30 ° reinforced. Drive device according to one of claims 1 to 5, characterized in that on the pliers auxiliary shaft (100) independently of the at least one pliers cam (102) in addition, the first upper nipper cam (110a) and a second upper nipper cam (110b) are arranged rotationally fixed, wherein at the upper nipper rocker arm (114) the first upper nipper cam roller (112a) and a second upper nipper cam roller (112b) are respectively rotatably supported so that the first top nipper cam (110a) cooperates with the first top nill cam follower (112a) and the second top nipper cam (110b) interacts with the second top nip cam follower (112b), thereby providing the second top nip cam follower (112b) prevents the first upper nipper cam follower (112a) from lifting off the upper nipper cam disc (110a). Drive device according to one of claims 1 to 5, characterized in that on the tongs auxiliary shaft (100), in addition to the at least one upper nipper cam (110), the first nipper cam (102a) and a second nipper cam (102b) are rotatably mounted, wherein the forceps rocker arm (106), the first pincer roller (104a) and a second pincer roller (104b) are each rotatably mounted, so that the first pincer cam (102a) with the first pincer roller (104a) and the second tong cam (102b) cooperate with the second caliper cam roller (104b), whereby the second caliper cam roller (104b) prevents the first caliper cam roller (104a) from moving away from the first caliper cam (102a) takes off. Drive device according to one of claims 1 to 5, characterized in that on the pliers auxiliary shaft (100), in addition to the at least one pliers cam (102) also a single upper nipper cam (110) is rotatably disposed with one of the upper nippers Rocker arm (114) rotatably mounted single upper nipper cam roller (112) cooperates, wherein on the upper nipper rocker arm (114) is provided a spring element (138) which cooperates between a machine frame (140) and the upper nipper rocker arm (114), such that the single top caliper cam roller (112) does not lift off the single top caliper cam (110). Drive device according to one of claims 1 to 5, characterized in that on the forceps auxiliary shaft (100) independent of the at least one upper nipper cam (110) also a single nipper cam (102) is rotatably disposed with a on the pliers rocker arm (106) rotatably mounted single pliers cam roller (104) cooperates, wherein on the pliers rocker arm (106) a spring element (138) is provided, which between a machine frame (140) and the pliers rocker arm (106) cooperates so that the single pincer roller (104) does not lift off the single pincer cam (102). Combing machine with a drive device according to one of claims 1 to 9.

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