CN1438375B - Thread adjusting device - Google Patents

Abstract

The inventive thread adjusting device (22) includes: a rotary thread wheel (102), contacted with the thread and fed along with the thread; force-produced devices (106, 110) for producing rotary resistance for the rotation of the rotary thread wheel (102) or the like; a rotary-resistence-produced device, and having a contact members (134, 140) contacted with the thread wheel (102) or the like, forproducing the rotary resistance by the rotation of thread wheel (102) or the like caused by the force which is produced in the state of the rolling between the thread wheel (102) or the like and the contact members (134, 140). The rolling produced between the thread wheel (102) or the like and the contact members (134, 140) can reduce the rotary resistance of the thread wheel (102) or the like inthe structure.

Description

line adjustment device

technical field

The invention relates to a wire adjusting device which adjusts the tension degree or usage amount of the wire by a rotating wire wheel according to the feeding of the wire.

Background technique

Conventionally, for example, Japanese Patent Application Laid-Open No. 63-63489 discloses a wire adjusting device having a wire wheel that rotates according to feeding of the wire. The wire adjusting device is provided with a wire wheel or a contact member in contact with a rotating shaft (hereinafter referred to as wire wheel, etc.) The rotational resistance caused by the friction force between them. The above-mentioned contact member is driven to move by various driving sources such as a solenoid, a pulse motor, and a piezoelectric element. The forces generated by these drive sources are used to press the contact member against the wire pulley and the like while maintaining the magnitude at the time of generation.

In addition, in a device such as a sewing machine having the above-mentioned thread adjusting device, in order to adapt the tension degree or usage amount of the thread to the operating state of the device, it is necessary to cause a force of rotational resistance (generated by the driving source) to the rotation of the thread wheel or the like. force) to control. For example, in a sewing machine, when the needle reaches a predetermined height position, a voltage is supplied to the piezoelectric element to push the contact member toward the rotating shaft. In addition, the wire adjusting device is configured to increase or decrease the amount of rotation of the wire pulley or the like by controlling the force pressing the contact member, that is, by switching whether rotation resistance is generated by the rotation of the wire pulley or the like.

In the wire adjusting device of the above-mentioned conventional structure, the force of the magnitude at the time of occurrence is used as usual in the action of pressing the contact member against the wire pulley or the like. At this time, if the rotational resistance due to the force generated by the driving source is large, the thread may break, so the power source needs to generate a small force to generate an appropriate magnitude of rotational resistance. However, fine control of small forces from a power source is generally more difficult than fine control of large forces from a power source. However, in the conventional structure, the magnitude of the force generated by the power source is reduced as much as possible, and the force generated by the power source is used for the action of pushing the contact member against the wire pulley or the like.

In general, precise control of small forces generated by a power source is difficult. For this reason, for example, in a sewing machine, once the force generated by the power source is smaller than the desired value, the rotational resistance caused by the force is also smaller than the appropriate value, and the amount of rotation of the thread wheel, etc. will be greater than the appropriate amount of rotation. As a result, , There will be problems with loose or entangled threads at the seam. Conversely, if the force generated by the power source is greater than the desired value, the rotational resistance caused by this force will also be greater than the appropriate value, and the amount of rotation of the wire pulley will be less than the appropriate amount. As a result, even if the thread is not broken, It is also possible to arch the cloth.

That is, once the force generated by the driving source exceeds the appropriate size range, the size of the error directly affects the size of the rotation resistance of the rotation of the wire wheel, so it may exceed the allowable range of tension or usage of the wire. Therefore, there is a problem that the tension or usage amount of the thread cannot be properly adjusted according to the operating conditions of devices such as the sewing machine.

Contents of the invention

An object of the present invention is to provide a wire adjusting device capable of properly adjusting the tension or usage amount of the wire by rotation of the wire wheel or the like in a state of rolling or sliding which reduces the rotation resistance of the wire wheel or the like.

The wire adjusting device of the present invention includes: a wire pulley that contacts the wire and rotates with the feed of the wire; a force generator that generates rotational resistance to the rotation of the wire pulley or a rotating portion that integrally rotates with the wire pulley; and a rotation resistance generator. The rotation resistance generating device has a contact member in contact with the above-mentioned wire wheel or the above-mentioned rotating part, and is configured to generate a force relative to the above-mentioned force generating device under the state of rolling between the above-mentioned wire wheel or the above-mentioned rotating part and the above-mentioned contact member. The rotation of the above-mentioned wire wheel or the above-mentioned rotating part caused by the force produces rotation resistance.

In the wire adjusting device having the above configuration, the magnitude of the rotational resistance generated between the wire wheel or the rotating portion and the contact member is smaller than that of a structure in which no rolling occurs between the wire wheel or the rotating portion and the contact member. . The wire wheel or the rotating portion rotates relative to the contact member while the reduced rotational resistance is generated between the wire wheel or the rotating portion and the contact member. Therefore, the magnitude of the force generated by the force generating device can be increased, and precise control of the force becomes easy. Therefore, the degree of tension and usage of the thread can be adjusted reasonably.

In the above configuration, the rotation resistance generating device has a contact member that is a rotating body that rotates in contact with the wire pulley or the rotating part, and it is preferable that the force generated by the force generating device is configured to cause the rotation resistance while the rotating body is rotating, The rotational resistance to the rotation of the wire pulley or the rotating part caused by the force generated by the force generating device is reduced.

In addition, it is preferable that the rotation resistance generating device has a cylindrical bearing in which a plurality of radial cylindrical rotating bodies are arranged on a surface intersecting the direction of the rotation axis of the wire pulley or the rotating portion.

It is preferable that the above-mentioned force generating device has a piezoelectric element that generates a force of rotational resistance against the rotation of the above-mentioned wire wheel or the above-mentioned rotating part. Alternatively, the rotation of the rotating portion generates rotational resistance, and when the power supply to the piezoelectric element is cut off, the preload spring generates rotational resistance against the rotation of the wire pulley or the rotating portion.

However, instead of the above-mentioned structure, it may be configured such that when a voltage is supplied to the piezoelectric element by the force generating device, the piezoelectric element generates rotational resistance relative to the rotation of the wire wheel or the rotating part, and the power supply to the piezoelectric element is cut off. , the preload spring generates rotation resistance relative to the rotation of the wire pulley or the rotating part.

In addition, in the other wire adjusting device of the present invention, the above-mentioned force generated by the above-mentioned force generating device may be caused by the force generating device in a state where the wire pulley or the above-mentioned rotating part and the above-mentioned contact member are sliding. The rotation of the wire wheel or the above-mentioned rotating part generates rotational resistance. In the case of this structure, it is preferable that the rotation resistance generator is provided with a sliding bearing having a contact member with a low coefficient of friction in surface contact with a surface intersecting the direction of the rotation axis of the wire pulley or the rotation portion.

In addition, it is preferable that the above-mentioned force generating device has a piezoelectric element and a preload spring that generate a force of rotational resistance against the rotation of the above-mentioned wire pulley or the above-mentioned rotating part, and is configured so that when a voltage is supplied to the above-mentioned piezoelectric element, the above-mentioned piezoelectric element And the preload spring generates rotational resistance against the rotation of the wire wheel or the rotating unit, and when the power supply to the piezoelectric element is cut off, the preload spring generates rotational resistance against the rotation of the wire wheel or the rotating unit.

However, instead of the above-mentioned structure, it may be configured such that when a voltage is supplied to the piezoelectric element by the force generating device, the piezoelectric element generates rotational resistance relative to the rotation of the wire wheel or the rotating part, and the power supply to the piezoelectric element is cut off. , the preload spring generates rotation resistance relative to the rotation of the wire pulley or the rotating part.

In addition, the rotation resistance generating device of the other thread adjusting device of the present invention preferably has two contact members that contact the two side surfaces of the above-mentioned wire wheel or the above-mentioned rotating part, and is configured so that there are two contact members between the above-mentioned wire wheel or the above-mentioned rotating part and the two sides. While rolling occurs between one of the two contact members, the above-mentioned wire wheel or the above-mentioned rotating part and the other of the above-mentioned two contact members slide and produce the above-mentioned force generated by the above-mentioned force generating device. Rotational resistance against rotation of the reel or the aforementioned rotating part.

Brief description of the drawings

Fig. 1 is an overall appearance view of the sewing machine of the present invention.

Fig. 2 is a cross-sectional view on a vertical plane in the front-back direction of the thread adjusting device according to the first embodiment of the present invention.

FIG. 3 is a diagram showing a shaft that is a rotating portion that rotates integrally with the wire pulley.

Fig. 4 is a view showing the axial thrust bearing in the part A-A of Fig. 2 above.

Fig. 5 is an electrical block diagram of the sewing machine of the present invention.

Fig. 6 is a graph showing the characteristics of the piezoelectric element of the present invention.

Fig. 7 is a cross-sectional view on a vertical plane in the front-rear direction of the thread adjusting device according to the second embodiment of the present invention.

Fig. 8 is a cross-sectional view on a vertical plane in the front-back direction of the thread adjusting device according to the third embodiment of the present invention.

Fig. 9 is a cross-sectional view of a thread adjusting device according to a fourth embodiment of the present invention on a vertical plane in the front-back direction.

Fig. 10 is a cross-sectional view on a vertical plane in the front-back direction of a thread adjusting device according to a fifth embodiment of the present invention.

Fig. 11 is a cross-sectional view on a vertical plane in the front-back direction of a thread adjusting device according to a sixth embodiment of the present invention.

Detailed ways

The first embodiment of the present invention will be described below with reference to the accompanying drawings 1 to 6 .

As shown in Figures 1 to 4, the sewing machine 10 includes: other needles 12 required for sewing, a needle bar 14, a main shaft 16, a balance 18, a needle position detector 20, a thread adjusting device 22, an auxiliary thread adjusting device 24, and a sewing machine Electric motor 26, coil 30 that winds upper line 28. In this sewing machine 10, a thread regulating device 22 is detachably mounted in a mounting hole formed in a front sewing machine frame 10a of the sewing machine 10. As shown in FIG. The adjuster 22 has an elongated shape in the front-rear direction, and is attached so as to protrude from the sewing machine 10 in the front-rear direction. However, as long as the radius and shape of the base of the thread regulating device match the above-mentioned mounting hole, the thread regulating device may have different functions and structures, and the sewing machine 10 is configured so that the thread regulating device can be replaced and reinstalled.

Moreover, as shown in FIG. 5 , the sewing machine 10 has a CPU 32 as the overall control device of the sewing machine 10, a ROM 34 storing various programs, a RAM 36 used in the execution of the programs, a sewing machine motor 26, and a drive circuit 38 for the thread adjusting device 22. , 40.

As shown in FIG. 2 , the thread adjusting device 22 includes: a substantially hollow cylindrical body 100 protruding in the front and rear directions; a thread wheel 102 that rotates corresponding to the upper thread 28 conveyed for sewing functions such as the needle 12 and the balance 18; The hard metal or resin shaft 104 that becomes the rotation shaft of the wire wheel 102; the piezoelectric element 106 that generates rotational resistance against the rotation of the wire wheel 102 and the shaft 104; the lead 108 that supplies power to the piezoelectric element 106; Regardless of whether the element 106 is powered or not, the preload spring 110 and the like can generate preload.

The main body 100 is made of hard metal or resin. The front cover 112 and the rear cover 114 are detachably mounted on the front end and the rear end of the main body by screws 116 and 118 respectively. The wire pulley 102 disposed on the front of the main body 100 is fixed to the front end of a shaft 104 that is elongated in the front-rear direction and is rotatably disposed in the inner space of the main body 100 . As shown in Figure 3, the shaft 104 is composed of the front end 104a of the installation wire wheel 102, the radial bearing part 104b with a larger radius than the front end 104a, the front axial guide bearing part 104c with a larger radius, and the radial bearing part 104c with a larger radius. The disc-shaped axial thrust bearing 104d and the rear axial thrust bearing guide 104e having the same radius as the front axial guide bearing 104c are configured. These parts are all concentric circles. The shaft 104 is placed on the front side of the inner space of the body 100 so that its front end 104a protrudes forward.

The radial bearing portion 104b of the shaft 104 is rotatably supported by two radial bearings 120, 122 separated in the front-rear direction. The reel 102 rotates integrally with the shaft 104. A spacer 124 is interposed between the two radial bearings 120, 122. The front and rear directions are separately arranged and fixed on the inner surface of the main body 100. The radial bearings 120, 122 respectively have a plurality of spherical rotating bodies, and their rotation friction is extremely small, and the rotation of the wire pulley 102 and the shaft 104 is hardly restrained. .The radial bearings 120, 122 are installed on the inner side of the main body 100 so as not to move in the front-rear direction.

The front axial thrust bearing outer ring 126 is fixed on the inner surface of the rear body 100 of the rear radial bearing 122 so as to be non-rotatable and unable to move forward and backward. The front axial thrust bearing outer ring 126 is made of hard metal or resin. A circular penetration portion is formed in the center of the front axial thrust bearing outer ring 126 . A gap is provided between the inner surface of the penetration portion of the forward axial thrust bearing outer ring 126 , the radial bearing portion 104b and the forward axial thrust bearing guide portion 104c. That is, the front axial thrust bearing outer ring 126 is disposed so as not to cause friction with the shaft 104 .

In the internal space of the wooden body 100 further rearward of the above-mentioned front axial thrust bearing outer ring 126, the rear surface of the front axial thrust bearing outer ring 126 and the front surface of the axial thrust bearing inner ring 104d are disposed. There is an axial thrust bearing 130 at the front. The front axial thrust bearing 130 is composed of a substantially disk-shaped holder 132 and, for example, 20 cylindrical rotating bodies 134 . The cylindrical rotating body 134 is made of hard metal or resin. The front axial thrust bearing 130 has the same structure as the rear axial thrust bearing 136 shown in FIG. 4 .

The center of the retainer 132 of the front axial thrust bearing 130 is formed with a circular penetration portion, and 20 rectangular penetration portions are formed radially and equally divided in the circumferential direction around the cage 132 . These cylindrical rotors 134 are rotatably fitted into the rectangular penetration portions. The cylindrical rotating body 34 has a radius that protrudes slightly in the front-back direction from the holder 132 . Therefore, all twenty cylindrical rotating bodies 134 of the front axial thrust bearing 130 are in contact with the rear surface of the front axial thrust bearing outer ring 126 and the front surface of the axial thrust bearing inner ring 104d. In addition, the front axial direction guide bearing part 104c is inserted into the circular penetration part of the holder 132. As shown in FIG. The retainer 132 of the forward axial thrust bearing 130 is guided slidably and rotatably relative to the shaft 104 .

The friction between the inner surface of the circular penetration portion of the retainer 132 and the outer surface of the forward axial guide bearing portion 104c is small but present. Accordingly, the holder 132 rotates in the same direction as the shaft 104 at a rotational speed that is less than the rotational speed of the shaft 104 .

Further, the rear axial thrust bearing 136 is arranged in the inner space of the main body 100 further rearward of the axial thrust bearing inner ring 104d, and is brought into contact with the rear surface of the axial thrust bearing inner ring 104d. The rear axial thrust bearing guide 104e is inserted into the circular penetration portion of the retainer 138 of the rear axial thrust bearing 136 . The above-mentioned holder 138 is guided to be slidable and rotatable relative to the shaft 104 . However, friction between the inner side of the circular penetration portion of the retainer 138 and the outer side of the rear axial thrust bearing guide 104e is small but present. Accordingly, retainer 138 rotates in the same direction as shaft 104 at a rotational speed that is less than the rotational speed of shaft 104 .

Gaps are provided between the outer side of the axial thrust bearing inner ring 104d and the inner side of the body 100 and between the outer sides of the two retainers 132 , 138 and the inner side of the body 100 . That is, friction is generated between the outer surfaces of the axial thrust bearing inner ring 104d and the outer surfaces of the retainers 132 and 138 and the inner surface of the main body 100 .

In addition, a rear axial thrust bearing outer ring 142 is arranged so as to be non-rotatable in the inner space of the main body 100 further rearward of the rear axial thrust bearing 136 . The rear axial thrust bearing outer ring 142 is made of hard metal or resin. Furthermore, all 20 cylindrical rotating bodies 140 of the rear axial thrust bearing 136 are in contact with both the rear surface of the axial thrust bearing inner ring 104d and the front surface of the rear axial thrust bearing outer ring 142 . Here, the front surface of the rear axial thrust bearing outer ring 142 is opposed to the rear surface of the rear axial thrust bearing guide 104e with a gap therebetween. No friction occurs between the front surface of the rear axial thrust bearing outer ring 142 and the rear surface of the rear axial thrust bearing guide 104e. There is a gap between the outer surface of the rear axial thrust bearing outer ring 142 and the inner surface of the main body 100 . That is, it is configured so that no friction occurs between the outer surface of the rear axial thrust bearing outer ring 142 and the inner surface of the main body 100 .

The compression spring, that is, the preload spring 110 is compressed and arranged in the inner space of the body 100 further behind the rear axial thrust bearing outer ring 142. The front end of the preload spring 110 is in contact with the rear axial thrust bearing outer ring 142 The rear end of the preload spring 110 is in contact with the front of the spring adjustment ring 144. The spring adjustment ring 144 is fixed on the inner side of the body 100 by the spring adjustment screw 146 so that it cannot rotate and move in the front and rear direction. Therefore, the preload spring 110 The compression spring 110 has been applying force to the rear axial thrust bearing outer ring 142 by the elastic force to move it forward. Under the forward force of the pre-compression spring 110, as shown in Figure 2, each structure contacts That is to say, even if the piezoelectric element 106 has no voltage supply at all, the rear axial thrust bearing outer ring 142 is pushed forward, and the axial thrust bearing inner ring 104d, the front axial thrust bearing 130, The rolling resistance caused by friction (that is, the rotational resistance caused by the pre-compressed spring 110) is generated between the outer rings 126 of the axial thrust bearing in the front.

And, as shown in FIG. 2 , in the central space of the circle of the preload spring 110, the hard steel ball 150, the head bush 152 of hard metal or resin, and the piezoelectric element 106 are arranged in order from the front to be aligned with the piezoelectric element 106. The preload spring 110 is separated. The head bushing 152 is fixed to the front end of the piezoelectric element 106 . The piezoelectric adjustment shaft 106 a at the rear end of the piezoelectric element 106 is fixed on the rear cover 114 by a piezoelectric adjustment screw 156 so as to be non-rotatable and immovable. The piezoelectric portion 106b in front of the piezoelectric adjustment shaft 106a is displaced (extended) in the front-rear direction according to the magnitude of the voltage when a voltage is supplied.

The steel balls 150 are fitted into a pair of mortar-shaped recesses formed in the center of the rear surface of the rear axial thrust bearing outer ring 142 and the center of the front surface of the head bushing 152 . The wire adjustment device 22 of this structure can eliminate the variation in the part shape and size of the piezoelectric element 106 . In this case, even if the piezoelectric element 106 is installed at a slight inclination, the piezoelectric element 106 can evenly press the rear of the axial thrust bearing outer ring 142 through the head bush 152 and the steel ball 150 . However, the position of the piezoelectric element 106 in the front-rear direction can also be adjusted by the piezoelectric adjustment screw 156 abutting on the tapered portion 106c formed at the rear end portion of the piezoelectric adjustment shaft 106a.

In the case of the above structure, the wire adjusting device 22 is configured such that the force generated by the voltage supplied to the piezoelectric element 106 passes through the head bush 152, the steel ball 150, the rear axial thrust bearing outer ring 142, and the rear axial thrust bearing. Bearing 136 , shaft 104 , front axial thrust bearing 130 act on stationary front axial thrust bearing outer ring 126 . Thus, a portion of the shaft 104 is clamped, and the clamped portion is subjected to a force in the direction of compression.

The resultant force (forward force) of the urging force of the preload spring 110 and the force generated by the piezoelectric element 106 is a force that generates rotational resistance to prevent rotation of the wire pulley 102 and the shaft 104 . This force creates rotational resistance on the front and rear faces of the axial thrust bearing inner ring 104d.

The resultant of this forward force acts on the member further forward than the preload spring 110 or piezoelectric element 106 . That is, the forward resultant force acts through the two front and rear axial thrust bearings 130 and 136 . In this case, since the cylindrical rotating bodies 134 and 140 rotate with the rotation of the wire pulley 102 and the shaft 104, the rotational resistance against the rotation of the wire pulley 102 and the shaft 104 can be reduced.

In the above structure, the main body 100, the axial thrust bearing inner ring 104d, the rotating bodies 134, 140, the two axial thrust bearing outer rings 126, 142 at the front and the rear, and the steel ball 150 are made of hard materials, so the pressure The force generated by the electrical element 106 acts on these structures without causing large indentations like a blanket.

In this embodiment, the piezoelectric element 106 and the preload spring 110 correspond to a force generating device. The rotors 134 and 140 correspond to contact members, and these form a rotational resistance generator together with the two axial thrust bearing outer rings 126 and 142 at the front and rear.

With the above structure, when the voltage supplied to the piezoelectric element 106 is increased from a low standby voltage (0V) to a high suppression voltage (100V), the force generated by the piezoelectric element 106 is strengthened, and the rolling of the cylindrical rotating bodies 134, 40 The resistance is also increased. In this way, the rotation resistance that inhibits the rotation of the wire wheel 102 and the shaft 104 also increases, making the wire wheel 102 difficult to rotate. On the contrary, when the voltage supplied to the piezoelectric element 106 is reduced from a high suppression voltage to a low standby voltage , the force generated by the piezoelectric element 106 is reduced. In this way, the rolling resistance of the cylindrical rotating bodies 134, 40 is also reduced, and the rotation resistance for restraining the rotation of the wire wheel 102 and the shaft 104 is also reduced, so that the wire wheel 102 smoothly Rotation. The voltage supplied to the piezoelectric element 106 is switched and controlled by the CPU 32 according to the detection signal of the needle position detector 20 and the sewing situation. As shown in Figure 6, the characteristics of the piezoelectric element 106 are determined by the voltage and the voltage supplied to the piezoelectric element 106. The relationship between the resulting rotational resistance is expressed.

Also, the standby voltage value is not limited to 0V, and an appropriate low voltage value is sufficient. In addition, the suppression voltage is not limited to 100V, and a voltage value higher than the standby voltage can be appropriately selected for voltage switching.

In a structure that does not have two axial thrust bearings 130, 136 and a smooth sliding surface to be described later as in the conventional structure, but directly uses the force generated by the piezoelectric element to generate rotation resistance, the CPU 32 controls the supply pressure of this embodiment. The voltage of the electrical element 106 is higher than the voltage supplied to the piezoelectric element to generate a large force. Therefore, compared with the conventional structure, the above-mentioned embodiment can easily control the rotation resistance of the wire pulley 102 and the shaft 104 precisely.

Incidentally, in the case of the conventional structure, since the static friction between the wire wheel and the like and the contact member is much larger than the dynamic friction, the rotation resistance of the wire wheel etc. is relatively large at the beginning of rotation, and rapidly decreases once it rotates. Due to this characteristic, it is also difficult to precisely control the rotation resistance of the wire wheel and the like in the case of the conventional structure. However, in the wire adjusting device of the above embodiment, the static friction and dynamic friction of the axial thrust bearings 130 and 136 are basically unchanged, and the rotational resistance of the wire wheel and the like can be precisely controlled.

Moreover, in the wire adjusting device of the above-mentioned embodiment, the rotational resistance caused by the force generated by the piezoelectric element 106 etc. (force generating means) is reduced due to the rolling of the rotating bodies 134, 140, and the degree of reduction can be achieved greatly. Therefore, even if a large force is generated by the piezoelectric element 106 or the like, the degree of tension and the usage amount of the wire can be appropriately adjusted compared to the case where the rotational resistance is not reduced.

Furthermore, in the wire adjusting device of the above-mentioned embodiment, since the plurality of cylindrical rotating bodies 134, 140 radially arranged on the surface intersecting the direction of the rotation axis of the wire wheel 102 etc. contacts with the wire wheel 102 and the like, and The tension of the wire can be appropriately adjusted even if a larger force is generated by the piezoelectric element 106, etc. than in the case where the extension direction of the cylindrical rotating bodies 134 and 140 is connected, compared with the case where the rotational resistance is not reduced. extent and usage.

In the thread adjusting device of the above-mentioned embodiment, when the piezoelectric element 106 is supplied with power, the rotation resistance is generated by the rotation of the piezoelectric element 106 and the preload spring 110 relative to the wire wheel 102, etc., and when the piezoelectric element 106 is not supplied with power, the preload spring The rotation of the spring 110 relative to the reel 102 and the like generates rotational resistance. Therefore, even if the power supply to the piezoelectric element 106 is cut off, unexpected rotation of the wire wheel 102 or the like due to no rotational resistance can be reduced. Therefore, the problem of unexpected rotation of the wire wheel 102 and the like can be prevented.

In the above embodiment, as shown in FIG. 2 , the two axial thrust bearings 130 and 136 at the front and the rear are arranged on the front and rear sides of the axial thrust bearing inner ring 104d so as to be in contact with each other. For desired rotation resistance, one of the axial thrust bearings 130 or 136 can also be eliminated. However, instead of one of them, the two axial thrust bearings 130 and 136 at the front and the rear are arranged to be in contact with the front and rear sides of the axial thrust bearing inner ring 104d, which can further reduce the rotational resistance, so It can be configured to generate a large force on the piezoelectric element 106 as a power source.

In addition, in the above-mentioned embodiment, as shown in FIG. 2, all the cylindrical rotating bodies 134, 140 are always in contact with the axial thrust bearing inner ring 104d and the two axial thrust bearing outer rings 126, 142 at the front, rear and rear. , but as long as the desired rotation resistance can be reduced, a part of the cylindrical rotating bodies 134, 140 may be in contact with it. Moreover, all the cylindrical rotating bodies 134, 140 protrude from the holders 132, 138 to the front and rear sides , but as long as the desired rotation resistance can be reduced, it is also possible to use a cylindrical rotating body that only protrudes from the front side of the holder 132, 138, and a cylindrical rotating body that only protrudes from the rear side of the holder 132, 138. Axial thrust bearing with two types of rotating bodies. In this structure, only the rotating body protruding forward of the rotating bodies of the front axial thrust bearing contacts with the back of the front axial thrust bearing outer ring 126, and the front Of the rotating bodies of the axial thrust bearing, only the rotating body protruding rearward is in contact with the front of the axial thrust bearing inner ring 104d, and among the rotating bodies of the rear axial thrust bearing, only the rotating body protruding forward is in contact with the shaft. The back of the thrust bearing inner ring 104d is in contact with the rear of the axial thrust bearing rotors, and only the rotor protruding rearward is in contact with the front of the rear axial thrust bearing outer ring 142.

In the above embodiment, as shown in FIG. 4, axial thrust bearings with cylindrical rotating bodies 134, 140 are used, but as long as the desired rotational resistance can be reduced, spherical or truncated conical rotating bodies can also be used. Body axial thrust bearing. Moreover, in the above-mentioned embodiment, the axial thrust bearing having only the cylindrical rotating body is used for the wire adjustment device 22, but it is also possible to use a bearing having a plurality of different rotating bodies such as a cylindrical rotating body and a spherical rotating body. Axial thrust bearings. Moreover, in the above-mentioned embodiment, as shown in FIG. 4, the axial thrust bearings 130, 136 in which the cylindrical rotating bodies 134, 140 are arranged at equal intervals (radially arranged angular intervals) are used, but as long as the required The desired rotation resistance may be unevenly spaced, and the cylindrical rotating bodies 134 and 140 may be arranged in an uneven radial pattern according to the reduction of rotation resistance.

In the above-mentioned embodiment, as shown in FIG. 4, the cylindrical rotating bodies 134, 140 are arranged at positions equidistant from the circle centers of the holders 132, 124, respectively. However, as long as the desired rotational resistance can be reduced, any It can be arranged radially unevenly from the center of the circle. Moreover, the materials of the cylindrical rotating bodies 134, 140 are all equal, but as long as the desired rotational resistance can be reduced, some of the rotating bodies may have different sizes, shapes, materials, and hardnesses, or all of the rotating bodies may have different Different size, shape, material, hardness. And, in the illustrated embodiment, in the vertical plane perpendicular to the direction of the rotation axis of the wire wheel 102 and the shaft 104, the rotating bodies 134, 140 constitute the rotating wire adjusting device 22, but the wire adjusting device 22 can also be configured so that The surface where the direction of the rotation axis of the wire pulley 102 and the shaft 104 intersects is inclined from the vertical surface, and the rotors 134 and 140 are rotated on the inclined surface. In this case, it is preferable to protrude or recess these members in the shape of a truncated cone so that the rotating bodies 134, 140 are located behind the axial thrust bearing outer ring 126 in front, in front of the axial thrust bearing inner ring 104d, and in front of the axial thrust bearing inner ring 104d. The rear, rear axial thrust bearing outer ring 142 rotates in the inclined plane of the front.

Next, the second to sixth embodiments obtained by partially deforming the first embodiment of the present invention will be described. The thread adjusting devices 100 and the like of the second to sixth embodiments also use the sewing machine 10 in the same manner as the thread adjusting device 22 of the first embodiment. Use the same names and symbols for parts of the same structure.

As shown in FIG. 7, the thread adjustment device 200 of the second embodiment is provided with an adjustment knob 202 which is not included in the thread adjustment device 22 of the first embodiment. The adjusting knob 202 is fixed on the front end of the connecting shaft 204 , and the adjusting knob 202 and the connecting shaft 204 rotate integrally. The middle portion of the connecting shaft 204 is slidably rotatable and axially slidably inserted into the hollow portion of the shaft 206 whose central portion is hollow. The rear end of the connecting shaft 204 is fixed to the rear axial thrust bearing outer ring 208 , and the connecting shaft 204 and the rear axial thrust bearing outer ring 208 rotate integrally.

The outer surface of the rear axial thrust bearing outer ring 208 forms a plurality of recesses for determining the rotation stop position of the adjustment knob 202, and the steel balls 210 for position fixing in the wire adjustment device 200 are located in the recesses. The steel ball 210 is always pushed downward by the weak compression spring 212 . An adjusting nut 214 is installed on the rear end of the axial thrust bearing outer ring 208 at the rear, so that it can move along the front-rear direction while rotating integrally. The adjustment nut 214 is engaged with the rear pin 215 of the rear axial thrust bearing outer ring 208 , and the adjustment nut 214 rotates together with the rear axial thrust bearing outer ring 208 and the adjustment knob 202 . The outer surface of the adjusting nut 214 forms a male thread portion, and the male thread portion is screwed with the female thread on the inner surface of the body 100 . At this time, by rotating the adjusting knob 202, the adjusting nut 214 can move in the front-rear direction. The wire adjusting device 200 increases or decreases the length of the preload spring 110 between the rear axial thrust bearing outer ring 208 and the adjusting nut 214 by moving the adjusting nut 214 in the front-rear direction, so as to adjust the preload The force of the spring 110.

The shaft 206 is the same as the above-mentioned first embodiment. The front end and the like are formed in a concentric cylindrical shape, rotatably supported by two radial bearings 120, 122, and integrally rotated with the knob 102. The thread adjusting device 200 is configured so that the shaft 206 rotates, the adjustment knob 202 and the connecting shaft 204 do not rotate either.

In the second embodiment, the two axial thrust bearings 130, 136 provided in the wire adjusting device 22 of the first embodiment described above are not provided. In the second embodiment, the front face of the axial thrust bearing inner ring 206a of the shaft 206 is in contact with the rear face of the axial thrust bearing outer ring 216 at the front, while the rear face of the axial thrust bearing inner ring 206a is in contact with the rear axial thrust bearing ring 216. The front faces of the thrust bearing outer ring 208 are in contact. Similar to the first embodiment, the axial thrust bearing outer ring 208 at the rear of the wire adjustment device 200 is pushed by the piezoelectric element 106 through the steel ball 150 . In this structure, due to the displacement (elongation) of the piezoelectric element 106, the sliding friction between the front surface of the axial thrust bearing inner ring 206a and the rear surface of the forward axial thrust bearing outer ring 216 The rotation resistance caused by the rotational resistance and the sliding friction caused by the contact surface between the back of the axial thrust bearing inner ring 206a and the front surface of the rear axial thrust bearing outer ring 208 has an effect on the rotation of the wire pulley 102 and the shaft 206 To suppress.

Coefficients of friction of the front of axial thrust bearing inner ring 206a, the rear of axial thrust bearing outer ring 216 of the front, the rear of axial thrust bearing inner ring 206a, the front of rear axial thrust bearing outer ring 208 The coefficient of friction may be sufficient as long as it is a coefficient of friction that can appropriately reduce the rotational resistance due to the sliding generated at the contact surface between them. For example, the coefficient of friction of each surface may be set to about 0.1. Furthermore, DLC (diamond like carbon: diamond-like carbon) treatment is used as a surface treatment for reducing rotational resistance by sliding, and the coefficient of friction is as low as about 0.1 to 0.01. In the case of a structure in which the rolling resistance is reduced by rolling as in the first embodiment, the coefficient of friction between the rolling bodies 132 and 140 and the rolling surfaces in contact with them may be set to, for example, about 0.01 to 0.002.

In the wire adjustment device 200 of the second embodiment, the friction generated by the contact surface between the front surface of the axial thrust bearing inner ring 206a and the rear surface of the forward axial thrust bearing outer ring 216, the axial thrust bearing inner Rotational resistance is created by friction at the contact surfaces between the rear face of ring 206a and the rear face of axial thrust bearing outer ring 208 . That is, in the second embodiment, the reduction of the rotational resistance against the rotation of the wire pulley 102 and the shaft 206 is achieved not by rolling but by sliding (sliding bearing).

In the second embodiment, the piezoelectric element 106 and the preload spring 110 correspond to force generating means. The two axial thrust bearing outer rings 216 and 208 at the front and rear correspond to contact members and constitute rotation resistance generating means.

In the thread adjusting device 300 of the third embodiment, as shown in FIG. The front end of the shaft 302 forms an axial thrust bearing inner ring 302a. Same as the first embodiment, two axial thrust bearings 130, 136 are arranged in the front and back of the axial thrust bearing inner ring 302a, so that the cylindrical rotating body 134 of the two axial thrust bearings 130, 136 , 140 are respectively in contact with the front and back of the axial thrust bearing inner ring 302a. The outer ring part 304a of the front axial thrust bearing outer ring 304 , the preload spring 110 , the piezoelectric element 106 , the head bush 152 , and the steel ball 150 are provided further forward of the front axial thrust bearing 130 . The wire adjusting device 300 is configured such that the piezoelectric element 106 and the preload spring 110 press the axial thrust bearing outer ring 304 whose rear end is fixed to the front inside the retaining ring 305, and push the front cover 112 forward at the same time. Press the two axial thrust bearings 130, 136 from the rear through the rear end of the main body 310 and the axial thrust bearing outer ring 306 fixed to the rear of the inner surface of the main body 310.

That is, in the wire adjustment devices 22 and 200 of the above-mentioned first and second embodiments, the piezoelectric element 106 is used to adjust the components (first and second) that are not located between the wire wheel 102 and the axial thrust bearing inner ring 302a. In the embodiment, the movable rear axial thrust bearing outer ring 142, 208) is pushed. Unlike the first and second embodiments, in the thread adjustment device 300 of the third embodiment, it is by pressing the body 310, and through the components between the wire wheel 102 and the axial thrust bearing inner ring 302a (the axial thrust bearing outer rings 142, 208 fixed in the front in the first and second embodiments), two The axial thrust bearings 130, 136 and the axial thrust bearing inner ring 302a between them are in contact under the force of the piezoelectric element 106 and the preload spring 110. In this way, only one radial bearing 331 supporting the shaft 302 is required. , the structure of the line adjusting device 300 is simplified.

The shaft 302 is sandwiched between the outer ring portion 304 a of the front axial thrust bearing outer ring 304 and the rear axial thrust bearing outer ring 306 via the two axial thrust bearings 130 and 136 . In this structure, the force generated by the piezoelectric element 106 and the preload spring 110 produces axial thrust bearings 130 , 136 and the rolling rotation resistance of the cylindrical rotating bodies 134 , 140 suppresses the rotation of the wire pulley 102 and the shaft 302 . That is, the third embodiment is also the same as the first embodiment, and uses rolling to reduce the rotational resistance against the rotation of the wire pulley 102 and the shaft.

The wire adjusting device 300 is configured so that the two axial thrust bearing outer rings 304 and 306 at the front and rear do not rotate even if the wire pulley 102 and the shaft 302 rotate. FIG. 8 is a cross-sectional view of the wire adjustment device 300 seen from the side opposite to FIG. 2 and FIG. 7 . The lead wire 108 for supplying power to the piezoelectric element 106 communicates with a hollow portion formed in the center of the front axial thrust bearing outer ring 304 . The thread take-up spring 312 is arranged around the rear portion of the axial thrust bearing outer ring 304 in front of the inner space of the holding ring 305 .

In the third embodiment, the piezoelectric element 106 and the preload spring 110 correspond to force generating means. The rotating bodies 134, 140 correspond to contact members, and these together with the front and rear axial thrust bearing outer rings 304, 306 constitute a rotation resistance generator.

In the thread adjusting device 400 of the fourth embodiment, as shown in FIG. 9 , it is basically the same as the thread adjusting device 300 of the third embodiment, and the wire wheel 102 is arranged at the center of the thread adjusting device 400 . However, in the fourth embodiment, unlike the thread adjustment device 300 of the third embodiment, the front of the axial thrust bearing inner ring 402a of the shaft 402 and the outer ring portion 404a of the axial thrust bearing outer ring 404 in front In addition, the rear of the axial thrust bearing inner ring 402a is in contact with the front of the axial thrust bearing outer ring 406 at the rear. The friction coefficients of these contact surfaces are the same as those shown in the second embodiment above.

Rotational resistance caused by the friction between the front surface of the axial thrust bearing inner ring 402a and the rear surface of the outer ring portion 404a of the axial thrust bearing outer ring 404 in front and the axial thrust bearing inner ring 402a Rotational resistance of the wire pulley 102 and the shaft 402 is restrained by the rotational resistance caused by the friction generated by the contact surface between the rear surface of the axial thrust bearing outer ring 406 and the front surface of the rear axial thrust bearing outer ring 406 . In the fourth embodiment, similar to the second embodiment, the rotational resistance to the rotation of the wire pulley 102 and the shaft is reduced by positive sliding. FIG. 9 is a cross-sectional view of the wire adjustment device 400 seen from the side opposite to FIG. 2 and FIG. 7 .

In the fourth embodiment described above, the piezoelectric element 106 and the preload spring 110 correspond to the force generating means. The front and rear axial thrust bearing outer rings 404 and 406 correspond to contact members and constitute rotation resistance generating means.

In the thread adjusting device 500 of the fifth embodiment, as shown in FIG. 10, a cam mechanism 520 is used instead of the thread adjusting device 22, etc. The piezoelectric element 106 used. The cam 522 of the cam mechanism 520 is fixed on a cam shaft 524 which is perpendicular to the axial directions of the wire pulley 102 and the shaft 502 and rotates integrally with the upper shaft 16 (see FIG. 1 ). The cam 522 generates a displacement amount in a direction perpendicular to the axial direction of the wire pulley 102 and the shaft 502 . The plunger 528 contacts the cam 522 through a cam follower. In this structure, the axial thrust bearing outer ring 530 at the rear moves the axial thrust bearing 136 at the rear to Push forward. Accordingly, the axial thrust bearing inner ring 502 a and the front axial thrust bearing 130 are pushed forward toward the front axial thrust bearing 532 which does not move in the front-rear direction.

In this way, through the displacement of the cam 522, the rolling rotation resistance of the cylindrical rotating bodies 134, 140 of the two axial thrust bearings 130, 136 increases or decreases. This fifth embodiment is the same as the first and third embodiments. , is to reduce the rotation resistance relative to the rotation of the wire wheel 102 and the shaft 502 by rolling. In the fifth embodiment, the cam mechanism 520 is equivalent to the force generating device. The rotating bodies 134, 140 are equivalent to the contact members, and these are connected to the front and rear The outer rings 530 and 532 of the axial thrust bearing together constitute the rotation resistance generating device.

In the above-mentioned first to fifth embodiments, the steel ball 150 is installed movably relative to the axial thrust bearing outer ring 142 and the head bushing 152 at the rear, but as long as the parts of the piezoelectric element 106 can eliminate the discrete error, it can also be Fixed installation. The steel ball 150 may also be replaced by a member having a hemispherical front end and fixed on the rear axial thrust bearing outer ring 142 . Furthermore, as long as the discrete error of the components of the piezoelectric element 106 can be eliminated, the tip of the head bush 152 may be formed integrally with the hemispherical shape.

Moreover, in the above-mentioned first to fifth embodiments, the contact member (axial thrust bearing 130, etc.) is brought into contact with the shaft 104 etc. which rotates integrally with the wire pulley 102, and the friction between the wire pulley 102 and the shaft is reduced by rolling or sliding. 104 rotation resistance for equal rotation. However, in the wire adjusting device 600 of the sixth embodiment shown in FIG. 11 , as long as the rotation resistance can be reduced as desired, the contact member (axial thrust bearing 601 ) can be brought into contact with the wire pulley 102 . The rear end of the shaft 602 is rotatably supported by the main body 603 via a radial bearing 604 . The wire pulley 102 is integrally rotatable and fixed to the front end of the shaft 602 so that it cannot move in the axial direction. In the inner space of the body 603 where the middle part of the shaft 602 is located, there are two piezoelectric elements 106 , a preload spring 110 , and an axial thrust bearing outer ring 605 . The axial thrust bearing outer ring 605 is mounted on the main body 603 so as to be movable in the front-rear direction and not rotatable, and is slightly moved in the front-rear direction by the displacement of the piezoelectric element 106 . In this structure, the force generated by the piezoelectric element 106 and the preload spring 110 acts on the axial thrust bearing outer ring 605, the axial thrust bearing 601, the wire pulley 102, and the cylindrical rotating body of the axial thrust bearing 605. 610 rotates behind the wire pulley 102 and in front of the axial thrust bearing outer ring 605 . The rotating body 610 is the same as the above-mentioned rotating bodies 134 and 140 and is embedded in the holder 611 .

Therefore, the sixth embodiment is the same as the first, third, and fifth embodiments in that the rotational resistance to the rotation of the wire pulley 102 and the shaft 602 is reduced by rolling. In the sixth embodiment, the piezoelectric element 106 and the preload spring 110 correspond to force generating means. The rotating body 610 corresponds to a contact member, and these together with the axial thrust bearing outer ring 605 constitute a rotation resistance generator.

In each of the above-mentioned embodiments, it is configured that either one of the wire wheel 102 or a member that rotates integrally with it or the non-rotating axial thrust bearing outer ring 142 is pressurized by the power source (piezoelectric element 106), and as long as it rotates The resistance can be reduced as desired, and both of the reel 102 or its integrally rotating members (shaft 104, etc.) and the axial thrust bearing outer ring 142, etc., can be pressurized by the power source (piezoelectric element 106).

In each of the above-mentioned embodiments, axial thrust bearings or sliding surfaces with the above-mentioned coefficient of friction are provided to reduce rotational resistance, but other structures are also possible. For example, the wire adjusting device may also be configured such that the contact surface between the wire pulley 102 or the rotating member and the member (shaft 104 etc.) in contact with it passes through lubricating oil, powdery powdery substance, and the wire pulley 102 or The rotation resistance of the rotating member is reduced. In addition, instead of the axial thrust bearing 130 and the like, a disc made of an oil-impregnated material (oil-impregnated metal, oil-impregnated ceramics) may be used as the wire adjustment device.

Moreover, in the above-mentioned embodiments, the power source (piezoelectric element 106, etc.) is set according to the displacement of the rotation axis direction of the wire wheel 102, but as long as the rotation resistance can be reduced as desired, it can also be adjusted according to the direction of the rotation axis of the wire wheel 102. The displacement in the vertical radial direction sets the power source.

In addition, in each of the above-mentioned embodiments, the wire adjusting device can also be configured so that the biasing force of the preload spring 110 always acts on the rotation resistance, but when the power supply to the piezoelectric element 106 is cut off or significantly lowered due to a power failure or failure, the preload spring can The applied force of 110 acts on the rotation resistance. This structure generates rotation resistance solely by the piezoelectric element 106, so the piezoelectric element 106 can generate a greater force, and it is easier to precisely control the occurrence of the force. In this structure, the pressure When the power supply of the electric element 106 is cut off or drops significantly due to a power accident or failure, the biasing force of the preload spring 110 generates rotation resistance, and prevents unexpected rotation caused by no rotation resistance such as the wire pulley 102.

In each of the above-mentioned embodiments, at least one of the piezoelectric element 106 or the preload spring 110, which is the power source for generating rotational resistance, is provided in the thread adjusting device, but all the power sources can also be provided on the sewing machine 10 side. In addition, the piezoelectric element 106 and the preload spring 110 are provided in the thread adjustment devices 22 and the like of the first to fourth and sixth embodiments using the piezoelectric element 106, but the thread adjustment device 500 of the fifth embodiment , the piezoelectric element 106 may also be provided not in the thread adjusting device but in the sewing machine 10 . Furthermore, parts including at least one of the piezoelectric element 106 and the preload spring 110 and parts that cause rolling and sliding to reduce rotational resistance may be manufactured as different units, and combined as necessary. As this unit structure, it is also possible to manufacture in advance a unit with a piezoelectric element 106 and a preload spring 110 that can generate different forces and a unit that can reduce rotation resistance to different degrees and slide, and according to the sewing machine 10 Use to combine these units rationally. Even if the parts including at least one of the piezoelectric element 106 and the preload spring 110 and the parts that roll and slide to reduce the rotational resistance are formed as separate units, it does not deviate from the scope of the present invention.

In the above-described embodiments, rolling or sliding that reduces rotational resistance is produced. However, in the conventional wire adjusting device, even if the power source generates the same force, the dynamic friction resistance of the friction surface of the wire wheel etc. changes with the rotation of the wire wheel etc. different. However, in the above-mentioned embodiments, the influence of the dynamic friction force is very small, and it is almost not affected by the rotation of the wire wheel 102 and the like.

Moreover, in each of the above-mentioned embodiments, the present invention is applied to the thread regulating device 22 of the upper thread 28 of the sewing machine 10, etc., but it can also be applied to an auxiliary thread that generates a load smaller than that of the thread regulating device 22 of the upper thread 28 for the same purpose. Thread regulating device or thread regulating device for lower thread. The type of the sewing machine 10 may be for industrial use, household use, straight line sewing, embroidery, or the like.

It can also be applied to other devices for the same purpose of thread, such as creels, spinning machines, weaving machines, winding machines for electric motors, spools for fishing rods, wire discharge processing machines, various wire winding machines, etc. A device that looks like something.

With the wire adjusting device 22 and the like of each of the above-described embodiments, the piezoelectric element 106 and the like can generate a large amount of rotation resistance as compared with a structure in which the rotational resistance caused by the force generated by the piezoelectric element 106 or the cam mechanism 520 as the force generating means is not reduced. big force. Therefore, the piezoelectric element 106 etc. can be easily controlled, and the rotational resistance caused by the force generated by the piezoelectric element 106 etc. is excellent in stability and repeatability, and the tension degree and usage amount of the wire can be reasonably adjusted. That is, compared with the power source of the conventional wire adjusting device, the power source of the wire adjusting device 22 etc. according to the embodiment of the present invention is configured to generate a large force, reduce the rotational resistance caused by the large force generated by it, and be used for Rotational resistance against rotation of the wire pulley 102 and the like is generated.

In conventional wire adjustment devices, it is very difficult to precisely control the magnitude of the force generated by the driving source, and the generated force is directly used to push the contact member against the wire wheel or the like with the magnitude of the generated force. Therefore, the force of this power source is unstable, and its magnitude changes at any time, and the amount of rotation of the thread wheel, etc. exceeds an appropriate value, or on the contrary, the amount of rotation of the thread wheel, etc. is less than an appropriate value, resulting in loosening of the seam or cloth arching. wait.

In order to solve the above-mentioned problems, the wire adjusting device 22 etc. of the embodiments of the present invention reduce the rotational resistance caused by the generated force by rolling or sliding, even if the magnitude of the force generated by the power The influence of rotation resistance is very small, so the tension and usage of the thread can be adjusted reasonably.

In the structure described in the gazette of the conventional technique of the present invention, the contact portion is extremely precise so as to generate a predetermined rotational resistance. But by using the above-mentioned rolling or sliding, such extremely high part precision is no longer required.

In the above-mentioned embodiments, when reducing the rotational resistance, it is configured to use rolling (the first, third, fifth, and sixth embodiments using axial thrust bearings) or sliding (the second and fourth embodiments) ), but both rolling and sliding can also be used at the same time. Specifically, one of the axial thrust bearings 130, 136 can be left, and the other can be changed to a sliding bearing structure. In this structure, it can also be obtained with The effects of the above-mentioned various embodiments are basically the same.

Claims (5)

1. line adjusting device comprises: body, with the line contact and with the line wheel of the conveying rotation of line and relative described line wheel or produce the power generating means of rotational resistance with the rotation of the rotating part of this line wheel one rotation;

It is characterized in that having the first axial thrust bearing outer shroud, the second axial thrust bearing outer shroud and described power generating means in the inside of described body,

Described rotating part is configured between described first axial thrust bearing outer shroud and the described second axial thrust bearing outer shroud,

The power that the described first axial thrust bearing outer shroud applies based on described power generating means and to described rotating part side shifting,

The described second axial thrust bearing outer shroud is fixed on the described body, and

Also comprise the rotational resistance generating unit, described rotational resistance generating unit has the described first axial thrust bearing outer shroud, the described second axial thrust bearing outer shroud and described power generating means,

Described rotational resistance generating unit produces rotational resistance by the described first axial thrust bearing outer shroud and the described second axial thrust bearing outer shroud, and this rotational resistance is that described power generating means makes the outer described rotating part side shifting of hoop of described first axial thrust bearing and produces friction with respect to the rotation of described rotating part and cause.

2. line adjusting device according to claim 1, it is characterized in that, described rotational resistance generating unit also has contact member between the described first axial thrust bearing outer shroud or described second axial thrust bearing outer shroud and described rotating part, this contact member is the rotor that contacts and rotate with described rotating part.

3. line adjusting device according to claim 2 is characterized in that, described contact member is the barrel bearing that disposes a plurality of rotors cylindraceous in the face that the rotation direction with described rotating part intersects radially.

4. line adjusting device according to claim 2 is characterized in that, described contact member is the barrel bearing that disposes a plurality of cone shape rotors in the face that the rotation direction with described rotating part intersects radially.

5. according to each described line adjusting device in the claim 1～4, it is characterized in that described power generating means has piezoelectric element and the set-up spring that produces the power of rotational resistance with respect to the rotation of described line wheel or described rotating part; Described power generating means constitutes: when described piezoelectric element provides voltage, the rotation of described relatively line wheel of described piezoelectric element and set-up spring or described rotating part produces rotational resistance; When the power supply of piezoelectric element is cut off, the rotation of described relatively line wheel of described set-up spring or rotating part produces rotational resistance.

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