JP2010190396A - Ball screw - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a ball screw capable of preventing generation of a large torque change when switching the operating direction from the normal direction to the reverse direction and capable of preventing an excessive preload in preload adjustment. <P>SOLUTION: This ball screw device includes: two nuts 1A and 1B; a screw shaft 2 passing through the inside of the nuts 1A and 1B in the axial direction; multiple balls 5 provided freely to roll between a nut side spiral groove 3 formed in the inner peripheral surface of the nuts 1A and 1B and a screw shaft side spiral groove 4 formed in the outer peripheral surface of the screw shaft 2; and spacers 6 as a preload giving member provided between the nut 1A and the nut 1B. In the state that the nuts 1A and 1B and the screw shaft 2 are not rotated, a gap Gs between the screw shaft side spiral groove 4 and the balls 5 is smaller than a gap Gn between the nut side spiral groove 3 and the balls 5. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a ball screw used in a machine tool or the like as a machine element that converts rotational motion into linear motion, and more particularly, to a ball screw of a double nut preloading method or an offset preloading method including a spring type double nut preloading method. .

  A double nut preload type ball screw generally has two nuts, a screw shaft that passes through the nut in the axial direction, a nut-side spiral groove formed on the inner peripheral surface of the nut, and an outer peripheral surface of the screw shaft. A plurality of balls rotatably provided between the formed screw shaft side spiral groove and a spacer or a spring as a preload applying member for applying preload to the balls between the two nuts. It is inserted.

As shown in FIG. 5, the ball screw contacts the nut-side spiral groove 3 and the screw shaft-side spiral groove 4 at a single point, as shown in FIG. On the other hand, the screw shaft can be rotated with a low torque (low friction) as compared with an oversized ball preload type ball screw in which the balls are in contact at two points.
However, since a double nut preload type ball screw has a Gothic arc shape as shown in FIG. 6, the nut-side spiral groove and the screw shaft-side spiral groove have a right-angle cross-sectional shape. When the ball 5 rolls, the ball 5 is displaced in the direction indicated by the arrow (perpendicular to the rolling direction), but bites into the nut side spiral groove 3 or the screw shaft side spiral groove 4. When the ball 5 bites into the nut-side spiral groove 3 or the screw shaft-side spiral groove 4, the contact form of the ball 5 with respect to the spiral grooves 3 and 4 changes from two-point contact to three-point contact during operation. This is the cause of the increase.

  Therefore, a double nut preload type ball screw is proposed in which the cross-sectional shape of the spiral groove perpendicular to the nut-side spiral groove and the screw shaft-side spiral groove is a circular arc shape, so that the contact form of the ball is always kept in two-point contact. (See Patent Document 1).

JP 2002-276765 A

  However, when the cross-sectional shape of the nut-side spiral groove and the screw shaft-side spiral groove is perpendicular to the circular arc shape, as shown in FIG. 7, the ball has a double nut preload type ball screw (Z preload) having three contact points. Compared to the system), the torque in the free zone region where the nut moving direction is switched from the forward direction to the reverse direction is significantly smaller than the torque during steady operation. For this reason, the ball screw disclosed in Patent Document 1 has a problem that a large torque fluctuation occurs when the moving direction of the nut is switched from the normal direction to the reverse direction.

Further, when the cross-sectional shape of the spiral groove perpendicular to the nut side spiral groove and the screw shaft side spiral groove is a circular arc shape, as shown in FIG. There was also a possibility.
The present invention has been made paying attention to the above-mentioned problems, and its purpose is to prevent large torque fluctuations when the operating direction is switched from the forward direction to the reverse direction, and to prevent excessive preload during preload adjustment. It is an object of the present invention to provide a ball screw that can be prevented from becoming.

  In order to solve the above-mentioned problem, a ball screw according to the invention described in claim 1 includes a nut, a screw shaft that passes through the nut in the axial direction, and a nut-side spiral groove formed on an inner peripheral surface of the nut. And a plurality of balls rotatably provided between the screw shaft side spiral groove formed on the outer peripheral surface of the screw shaft, and the balls form a spiral circuit of a plurality of turns, In a ball screw to which preload is applied by increasing the lead in the vicinity of the center in the axial direction by a preload amount, the contact point between the nut side spiral groove and the ball, and the contact point between the screw shaft side spiral groove and the ball The virtual straight line passing through the center of the ball is drawn substantially perpendicular to the straight line connecting the ball, and the virtual straight line and the spiral groove at the point where the virtual straight line intersects the spiral groove between the nut and the nut side spiral groove. Large gap in the virtual straight line direction Sato, the size of the virtual straight line direction of the gap between the ball and the screw shaft side spiral groove, in a state where the nut and the screw shaft is not rotating, characterized in that different.

  A ball screw according to a second aspect of the present invention is the ball screw according to the first aspect, wherein when the nut or the screw shaft is moved in the axial direction in a substantially no-load state, the nut-side spiral groove and the ball screw The sum of the number of contact points with the ball and the number of contact points between the screw shaft side spiral groove and the ball is axially separated from the axially central portion where the lead of the nut is increased by a preload amount. On the other hand, there are 2 points and 3 points on the other side in the axial direction.

A ball screw according to a third aspect of the invention is the ball screw according to the first or second aspect, wherein one of the screw shaft side spiral groove and the nut side spiral groove has a spiral groove perpendicular cross-sectional shape. It is a Gothic arc shape, and the spiral groove perpendicular cross-sectional shape of the other spiral groove is a circular arc shape.
A ball screw according to a fourth aspect of the present invention is the ball screw according to any one of the first to third aspects, wherein the helical circuit is configured as a multi-threaded screw, and a screw shaft side spiral groove between the threads. And changing the pitch of the nut side spiral groove.

A ball screw according to a fifth aspect of the present invention is the ball screw according to any one of the first to fourth aspects, wherein the screw shaft or the nut is composed of two divided parts.
A ball screw according to a sixth aspect of the present invention is the ball screw according to the fifth aspect, wherein the two divided parts are preloaded with a spring.
A ball screw according to a seventh aspect of the present invention is the ball screw according to any one of the first to sixth aspects, wherein a spacer ball made of a material softer than the ball and having a diameter smaller than the ball is used. It is characterized by having between balls.

  According to the ball screw according to the present invention, the nut moving direction from the positive direction, like a double nut preload type ball screw in which the spiral groove perpendicular cross-sectional shape of the nut side spiral groove and the screw shaft side spiral groove is a circular arc shape. Since the torque at the time of switching in the reverse direction is not significantly smaller than the torque at the time of steady operation, it is possible to prevent a large torque fluctuation from occurring when the operating direction is switched from the normal direction to the reverse direction.

  Moreover, since the rate of increase in torque with respect to the amount of preload does not become too small, it is possible to prevent an excessive preload during preload adjustment.

1 is an axial sectional view of a ball screw device according to a first embodiment of the present invention. It is sectional drawing which shows the clearance gap formed between a nut side spiral groove and a screw side spiral groove, and a ball | bowl. It is a figure which shows the 2nd Embodiment of this invention. It is a figure which shows the 3rd Embodiment of this invention. It is sectional drawing which shows a part of double nut preload type ball screw apparatus. It is a figure which shows the state of the ball | bowl at the time of the action | operation of a double nut preload type ball screw apparatus. It is a figure which shows the change of the dynamic torque in case the ball | bowl of a ball screw apparatus is 2 point contact, 3 point contact, and 4 point contact. It is a figure which shows the relationship between the preload torque and the amount of preload in case the ball | bowl of a ball screw apparatus is 2 point contact, 3 point contact, and 4 point contact.

FIG. 1 shows a schematic configuration of the ball screw according to the first embodiment of the present invention. In the figure, reference numerals 1A and 1B denote nuts, 2 denotes a screw shaft that passes through the nuts 1A and 1B in the axial direction, and a nut-side spiral groove 3 and a screw shaft 2 formed on the inner peripheral surfaces of the nuts 1A and 1B. A large number of balls 5 are provided so as to roll freely between the screw shaft side spiral groove 4 formed on the outer peripheral surface of the screw shaft.
The balls 5 form a helical circuit on the nut 1A side and the nut 1B side, respectively. The ball 5 rolls between the spiral grooves 3 and 4 as the nuts 1A and 1B move in the axial direction, and a preload is applied to the ball 5 between the nut 1A and the nut 1B. A spacer 6 is inserted as a preload applying member. Further, the balls 5 are made of a metal material such as alloy steel, for example, and spacer balls 7 made of a material softer than the balls 5 (for example, synthetic resin) and having a smaller diameter than the balls 5 are disposed between the balls 5. Is inserted.

The ball 5 rolling between the spiral grooves 3 and 4 passes through the ball return tube 8 as a ball circulation member assembled to the nuts 1A and 1B, and is returned to the original position. .
The nut-side spiral groove 3 is formed on the inner peripheral surfaces of the nuts 1A and 1B so that the cross-sectional shape perpendicular to the spiral groove has a circular arc shape having a radius of curvature Rn larger than the radius of the ball 5. Further, the screw shaft side spiral groove 4 is formed on the outer peripheral surface of the screw shaft 2 so that the right-angle cross-sectional shape of the spiral groove is a Gothic arc shape that is a substantially V shape combining two identical arcs having different curvature centers. Has been.

In a state where the nuts 1A and 1B and the screw shaft 2 are not rotating, as shown in FIG. 2A, the gap between the screw shaft side spiral groove 4 and the ball 5 (the nut side spiral groove 3 and the ball 5 When a virtual straight line that is substantially orthogonal to the straight line that connects the contact point Cn ₁ with the screw shaft side spiral groove 4 and the contact point Cs ₁ with the ball 5 and passes through the center of the ball 5 is drawn, The gap between the ball 5 and the screw shaft side spiral groove 4 in the imaginary straight line direction) Gs at the point where the screw shaft side spiral groove 4 and the screw shaft side spiral groove 4 intersect with each other is the gap between the nut side spiral groove 3 and the ball 5 ( It is smaller than the gap (Gn in the imaginary linear direction) between the ball 5 and the nut side spiral groove 3 at the point where the imaginary straight line and the nut side spiral groove 3 intersect.

  In this state, when the nuts 1A and 1B move in the direction of the arrow shown in FIG. 2 and an external load F smaller than the preload acts on the nuts 1A and 1B in the direction opposite to the moving direction, the nut-side spiral groove 3 of the nut 1A and the screw The ball 5 provided between the shaft side spiral groove 4 is slightly displaced in the direction in which the gap Gs increases, and the ball 5 provided between the nut side spiral groove 3 and the screw shaft side spiral groove 4 of the nut 1B. Is slightly displaced in the direction in which the gap Gs decreases. Accordingly, as shown in FIG. 2B, the number of contact points of the ball 5 with respect to the screw shaft side spiral groove 4 on the nut 1B side changes from one point to two points, and on the nut 1A side, the number of contact points with respect to the screw shaft side spiral groove 4 is changed. The number of contact points of the ball 5 is kept at one point.

  On the other hand, when the nuts 1A and 1B move in the direction opposite to the arrow direction shown in FIG. 2 and an external load F smaller than the preload is applied to the nuts 1A and 1B in the same direction as the moving direction, the nut-side spiral groove 3 of the nut 1A. And the ball 5 provided between the screw shaft side spiral groove 4 is slightly displaced in the direction in which the gap Gs is reduced, and is provided between the nut side spiral groove 3 and the screw shaft side spiral groove 4 of the nut 1B. The ball 5 is slightly displaced in the direction in which the gap Gs increases. As a result, as shown in FIG. 2C, the number of contact points of the ball 5 with respect to the screw shaft side spiral groove 4 on the nut 1A side changes from one point to two points, and on the nut 1B side, the number of contact points with respect to the screw shaft side spiral groove 4 is changed. The number of contact points of the ball 5 is kept at one point.

  Therefore, in the first embodiment described above, when the nuts 1A and 1B move in the direction of the arrow, the number of contact points of the ball 5 with respect to the screw shaft side spiral groove 4 changes from 1 to 2 on the nut 1B side. On the nut 1A side, the number of contact points of the balls 5 with respect to the screw shaft side spiral groove 4 is maintained at one point, and the cross section of the nut side spiral groove 3 and the screw shaft side spiral groove 4 is a circular arc shape. Like the double nut preload type ball screw, the torque when the movement direction of the nuts 1A and 1B is switched from the normal direction to the reverse direction is not significantly smaller than the torque at the normal operation, so the operation direction is the positive direction. Therefore, it is possible to prevent a large torque fluctuation from occurring when switching in the reverse direction.

Further, the rate of increase in torque with respect to the preload amount becomes too small as in a double nut preload type ball screw in which the spiral groove perpendicular cross-sectional shape of the nut side spiral groove 3 and the screw shaft side spiral groove 4 is a circular arc shape. Therefore, it is possible to prevent an excessive preload during preload adjustment.
The external load acting on the nuts 1A and 1B during the operation of the ball screw is preferably an external load smaller than the preload applied to the ball 5, and specifically, for example, the resistance of a seal attached to the ball screw, etc. It is desirable that the load including 1/100 or less of the preload or 1/1000 or less of the static load rating.

In the first embodiment shown in FIG. 1, the spacer 6 is illustrated as a preload imparting member inserted between the nut 1 </ b> A and the nut 1 </ b> B, but the present invention is not limited to this, and the space between the two nuts is not limited thereto. An elastic member such as a coil spring may be used as the preload application member inserted into the coil.
Further, in the first embodiment shown in FIG. 1, the ball return tube 8 is exemplified as a ball circulation member for infinite circulation of the ball 5, but an internal circulation type ball screw using, for example, an end deflector or the like as the ball circulation member. The present invention can also be applied to the above.

Moreover, in 1st Embodiment shown in FIG. 1, although the thread shaft side spiral groove 4 was formed in the outer peripheral surface of the screw shaft 2, the outer peripheral surface of the screw shaft and the inner peripheral surface of the nut were illustrated. The present invention can also be applied to a ball screw in which a plurality of spiral grooves are formed.
Further, in the first embodiment shown in FIG. 1, a ball screw in which the ball circulates through a ball return path formed on the nut side is exemplified, but for example, disclosed in JP-A-2005-344882. The present invention can also be applied to a type of ball screw, that is, a type of ball screw in which a ball circulates through a ball return path formed on the screw shaft side.

  Further, in the first embodiment shown in FIG. 1, the cross-sectional shape of the nut-side spiral groove 3 perpendicular to the spiral groove is a circular arc shape having a curvature radius Rn larger than the radius of the ball 5, and the screw shaft-side spiral groove 4 The cross-sectional shape perpendicular to the spiral groove is a Gothic arc shape having a radius of curvature Rs larger than the radius of the ball 5 and smaller than the radius of curvature Rn. However, the second embodiment shown in FIG. 3 and the third embodiment shown in FIG. As shown in the figure, the cross section shape of the nut shaft side spiral groove 3 is a Gothic arc shape having a radius of curvature Rn larger than the radius of the ball 5, and the screw groove side spiral groove 4 is A Gothic arc shape having a radius of curvature Rs that is larger and smaller than the radius of curvature Rn may be used. The curvature radii Rn and Rs may be the same.

  Further, in the first embodiment shown in FIG. 1, the case where the present invention is applied to a double nut preloading ball screw is shown, but the present invention is not limited to this. For example, a lead near the center of a nut is preloaded. The present invention can also be applied to an oaset preloading type ball screw that applies a preload by increasing the amount.

1A, 1B Nut 2 Screw shaft 3 Nut side spiral groove 4 Screw shaft side spiral groove 5 Ball 6 Spacer 7 Spacer ball 8 Ball return tube

Claims (7)

A nut, a screw shaft that passes through the nut in the axial direction, a nut-side spiral groove formed on the inner peripheral surface of the nut, and a screw-shaft side spiral groove formed on the outer peripheral surface of the screw shaft. A plurality of balls provided so as to be capable of rolling, and the balls form a multi-turn spiral circuit, and a preload is applied by increasing the lead in the vicinity of the axial center of the nut by a preload amount. In ball screw,
A virtual straight line that is substantially orthogonal to a straight line that connects the contact point between the nut-side spiral groove and the ball and the contact point between the screw shaft-side spiral groove and the ball is drawn through the center of the ball, and the virtual The size of the gap in the virtual linear direction between the ball and the nut-side spiral groove at the point where the straight line and the spiral grooves intersect, and the virtual between the ball and the screw shaft-side spiral groove A ball screw characterized in that the size of the gap in the linear direction differs when the nut and the screw shaft are not rotating.   2. The ball screw according to claim 1, wherein the number of contact points between the nut-side spiral groove and the ball and the screw shaft side when the nut or the screw shaft is moved in the axial direction in a substantially unloaded state. The total number of contact points between the spiral groove and the ball is 2 points on the one side in the axial direction and 3 points on the other side in the axial direction, with the nut lead being increased by a preload amount as a boundary. A ball screw characterized by that.   3. The ball screw according to claim 1, wherein a spiral groove perpendicular cross-sectional shape of one of the screw shaft side spiral groove and the nut side spiral groove is a Gothic arc shape, and the other spiral groove is a spiral. A ball screw characterized in that the cross-sectional shape perpendicular to the groove is a circular arc shape.   The ball screw according to any one of claims 1 to 3, wherein the spiral circuit is configured as a multi-threaded screw, and the pitch of the screw-side spiral groove and the nut-side spiral groove between the threads is changed. And ball screw.   The ball screw according to any one of claims 1 to 4, wherein the nut is composed of two divided parts.   6. The ball screw according to claim 5, wherein the two divided parts are spring preloaded.   The ball screw according to any one of claims 1 to 6, wherein a spacer ball made of a material softer than the ball and having a diameter smaller than that of the ball is interposed between the balls. .

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