JP2010190307A - Ball screw device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To cool a ball screw without using a pump. <P>SOLUTION: This ball screw device includes an axial hole 11 and a radial hole 12 formed through the inside of a ball screw shaft to structure holes of a flow passage inside a ball screw shaft for making a cooling fluid flow therein. The axial hole 11 is communicated with a flow-in pipe formed as a part, into which the cooling fluid flows, and structures one end of the hole of the flow passage inside the ball screw shaft arranged at the center of rotation of the ball screw shaft 10. The radial hole 12 is communicated with a flow-out pipe formed as a part, from which the cooling fluid flows out, and structures the other end of the hole of the flow passage inside the ball screw shaft arranged by displacing from the center of rotation of the ball screw shaft 10 in the radial direction. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a ball screw device including a round bar-shaped ball screw shaft and a ball screw nut screwed onto an outer peripheral surface of the ball screw shaft.

  As a conventional ball screw cooling method, there is a method of cooling the ball screw shaft by forcibly passing cooling water (oil) through the hollow ball screw shaft using an external pump (see, for example, Patent Document 1).

Japanese Patent Laid-Open No. 2000-24876

However, this method requires an external pump and cooling device and is expensive. Furthermore, depending on the cooling pump, the type of fluid used may be limited. In this case, for example, there is a problem that water having a large heat capacity cannot be used.
An object of the present invention is to cool a ball screw without using a pump.

  In order to solve the above-mentioned problem, the ball screw device according to claim 1 according to the present invention comprises a ball screw shaft having a round bar shape and a ball screw nut screwed onto an outer peripheral surface of the ball screw shaft. The apparatus includes a ball screw shaft passage hole formed through the inside of the ball screw shaft to flow a cooling fluid, and the ball screw shaft passage hole has one end portion into which the cooling fluid flows. The other end portion is a portion from which the cooling fluid flows out, and the other end portion is communicated with the outflow piping. The one end portion is disposed at the rotation center of the ball screw shaft, and the other The end portion is arranged so as to be displaced in the radial direction from the rotation center of the ball screw shaft.

The ball screw device according to claim 2 of the present invention is the ball screw device according to claim 1, wherein the other end of the ball screw shaft passage hole is formed from an outer peripheral surface of the ball screw shaft. It is provided in the protruding position.
A ball screw device according to a third aspect of the present invention is the ball screw device according to the first or second aspect, wherein the cooling fluid in the other end is disposed in the ball screw shaft passage hole. The centrifugal force increasing means for increasing the centrifugal force acting on is provided.

  According to a fourth aspect of the present invention, there is provided the ball screw device according to the third aspect, wherein the ball screw shaft passage hole is in the direction of the rotation axis of the ball screw shaft passage hole. The other end of the ball screw shaft passage hole extends in a radial direction toward the rotation center of the ball screw shaft, and is connected to the axial hole. Centrifugal force increasing means is a partition plate provided in a connecting portion with the other end portion in the axial hole, and partitioning the connecting portion of the axial hole in the circumferential direction.

  A ball screw device according to a fifth aspect of the present invention is the ball screw device according to any one of the first to fourth aspects, wherein the ball screw device communicates with one end of the ball screw shaft passage hole. An inflow pipe is connected, and an outflow pipe communicating with the other end of the ball screw shaft passage hole is connected, and the cooling fluid returned from the outflow pipe is stored and stored. Cooling fluid storage means for feeding the cooling fluid to the inflow pipe is provided.

According to the first aspect of the present invention, one end of the ball screw shaft passage hole is disposed at the rotation center of the ball screw shaft, while the other end of the ball screw shaft passage hole is formed on the ball screw shaft. By disposing in the radial direction from the center of rotation, a centrifugal force can be generated in the cooling fluid in the other end when the ball screw shaft rotates, and the cooling fluid can flow out to the outflow pipe.
As a result, the cooling fluid automatically flows through the flow passage hole in the ball screw shaft only by rotating the ball screw shaft, and the ball screw shaft can function as a pump. As a result, the ball screw can be cooled without using a pump.

Moreover, according to the invention which concerns on Claim 2, a big centrifugal force can be made to act on the cooling fluid in an other end part, and the cooling fluid can be circulated efficiently.
Moreover, according to the invention which concerns on Claim 3, a big centrifugal force can be made to act on the cooling fluid in an other end part, and the cooling fluid can be circulated efficiently.
Further, according to the invention of claim 4, the cooling fluid can be circulated efficiently with a simple configuration.
Moreover, according to the invention which concerns on Claim 5, a ball screw can be cooled only by providing a cooling fluid storage means, without using a pump.

It is a sectional side view which shows the structure of the ball screw of 1st Embodiment along a ball screw axis | shaft. It is a side view which shows the structure of the ball screw of 1st Embodiment. FIG. 3 is a cross-sectional view showing a cross-sectional structure of a ball screw shaft in the XX direction of FIG. 2. It is sectional drawing which shows the other sectional structure of the ball screw axis | shaft of the XX direction of FIG. It is sectional drawing which shows the shape of the seal unit for shaft ends. It is sectional drawing which shows the shape of the sealing unit for radial direction holes. It is a side view which shows the structure of the ball screw of 2nd Embodiment. It is a side view which shows the structure of the other ball screw of 2nd Embodiment. It is sectional drawing which shows the shape of a discharge unit. It is a side view which shows the structure of the ball screw of 3rd Embodiment.

A mode for carrying out the present invention will be described in detail with reference to the drawings.
(First embodiment)
(Constitution)
The first embodiment is a ball screw to which the present invention is applied. FIG. 1 is a side sectional view showing a ball screw along a ball screw axis.
As shown in FIG. 1, the ball screw has a ball screw shaft 10 and a ball screw nut 2.
The ball screw shaft 10 has a spiral ball rolling groove on the outer peripheral surface. The ball screw shaft 10 is supported by the housing 3 and the machine base. Specifically, ball screw brackets 3a and 3b are formed on the housing 3, and both ends of the ball screw shaft 10 are rotatably supported by ball bearings 4 and 5 on the ball screw brackets 3a and 3b, respectively. Yes.

A pair of seal units 20, 20 are attached to the ball screw shaft 10. That is, the shaft end seal unit 20 is attached to the end of the ball screw shaft 10 so as to be positioned outside the ball screw bracket 3a of the housing 3 (left bracket in FIG. 1). A radial hole seal unit 30 is attached to the inside of a ball screw bracket (right side bracket in FIG. 1) 3 b of the housing 3. The structures of the shaft end seal unit 20 and the radial hole seal unit 30 will be described in detail later.
The ball screw nut 2 is attached to the outer periphery of the ball screw shaft 10 and has a ball rolling groove corresponding to the ball rolling groove of the ball screw shaft 10 on the inner peripheral surface. In this embodiment, two ball screw nuts 2 a and 2 b are attached to the ball screw shaft 10. A ball (not shown) is interposed between the ball rolling groove of the ball screw shaft 10 and the ball rolling groove of the ball screw nut 2 so as to freely roll.

A moving body 6 is attached to the upper side of the ball screw nut 2. The moving body 6 is a column, a table, a saddle, or the like.
Further, the end of the ball screw shaft 10 on the mounting side of the radial hole seal unit 30 protrudes from the outer surface of the bracket 3b. A driving pulley 7 is attached to the end of the ball screw shaft 10. Driving means such as a motor for rotating the ball screw shaft 10 is attached to the driving pulley 7.
With such a configuration, the ball screw nut 2 is relatively moved in the axial direction of the ball screw shaft 10 while the ball screw shaft 10 rotates.

FIG. 2 shows a side view of the ball screw. FIG. 2 shows an example in which one ball screw nut 2 is attached to the ball screw shaft.
As shown in FIG. 2, the ball screw shaft 10 has an axial hole 11 and a radial hole 12 formed therein. The axial hole 11 is formed as a hole that is opened at the axial end surface of the ball screw shaft 10 and extends along the rotation axis center.
FIG. 3 shows a cross-sectional view of the ball screw shaft 10 in the XX direction of FIG. As shown in FIG. 3, the radial hole 12 is formed so as to penetrate the ball screw shaft 10 in the radial direction. Specifically, the radial hole 12 is formed by two orthogonal through holes. The radial hole 12 communicates with the axial hole 11 at the intersection (center portion) of the two through holes inside the ball screw shaft 10. As shown in FIG. 2, the radial hole 12 is formed closer to the other shaft end side, which is the opposite side of the ball screw shaft 10 from the opening of the axial hole 11.

As shown in FIG. 4, a partition plate 13 can also be disposed in the axial hole 11 at a communication site with the radial hole 12. The partition plate 13 divides the circumferential direction of the axial hole 11 into four parts and divides each compartment 11a, 11b, 11c, 11d into four holes 12a, 12b, 12c, 12d forming the radial holes 12. The shape is designed to communicate.
The axial hole 11 and the radial hole 12 as described above are sealed by the shaft end seal unit 20 and the radial hole seal unit 30.
FIG. 5 shows the shape of the shaft end seal unit 20. As shown in FIG. 5, the shaft end seal unit 20 is formed with a pipe attachment portion 21 and a ball screw shaft end portion attachment portion 22 on each side surface in the axial direction.

The pipe attachment portion 21 has a shape to which an inflow pipe 41 described later can be attached. Specifically, the pipe attachment portion 21 has a female screw shape so as to be screwed into the inflow pipe 41 (specifically, the nipple). The ball screw shaft end mounting portion 22 has a shape to which the end of the ball screw shaft 10 can be mounted.
The pipe attachment portion 21 and the ball screw shaft end portion attachment portion 22 communicate with each other in the shaft end seal unit 20. A seal 23 is provided on the inner peripheral surface of the communication portion. The seal 23 is disposed so as to seal on the outer periphery of the end face of the ball screw shaft 10.
Further, the shaft end seal unit 20 is formed with a drain hole 24 penetrating from the outer peripheral surface to the ball screw shaft end mounting portion 22. The shaft end seal unit 20 is formed with screw holes 25 and 26 for screwing to the shaft end portion of the ball screw shaft 10.

  FIG. 6 shows the shape of the radial hole seal unit 30. As shown in FIG. 6, the radial hole seal unit 30 penetrates in the axial direction. The radial hole seal unit 30 is provided with seals 31 and 32 on the inner peripheral surface of the through hole and on the side surfaces in the axial direction. The seals 31 and 32 are arranged so as to be sealed at the outer peripheral surface (screw surface) of the ball screw shaft 10. For example, a groove that is screwed with the ball screw shaft 10 is formed on the inner peripheral surface of the through hole of the radial hole seal unit 30. Seals 31 and 32 are provided in the screwing grooves. Thus, in the axial through hole of the radial hole seal unit 30, the gap 33 is formed between the two seals 31 and 32.

The radial hole seal unit 30 is formed with a pipe attachment portion 34 penetrating from the outer periphery to the shaft center (the gap portion 33) in the vicinity of the middle in the axial direction. The pipe mounting portion 34 is shaped so that a later-described outflow pipe 42 can be mounted. Specifically, the pipe attachment portion 34 has a female screw shape so as to be screwed into the outflow pipe 42 (specifically, the nipple).
The radial hole seal unit 30 is formed with a drain hole 35 penetrating from the outer peripheral surface. The radial hole seal unit 30 is formed with a screw hole 36 for fixing to the bracket 3b.

As shown in FIG. 1, the radial hole seal unit 30 is attached to the outer periphery of the ball screw shaft 10. In the state of being attached in this way, the radial hole 12 is positioned at an intermediate portion in the axial direction of the radial hole seal unit 30 (a portion where the gap portion 33 is formed). The radial hole seal unit 30 is fixed to the bracket 3b so as to maintain this state.
As shown in FIG. 1, a coolant tank 43 is connected to the ball screw configured as described above.

Specifically, one end (specifically, the nipple) of the inflow pipe 41 is attached to the pipe attachment portion 21 of the shaft end seal unit 20. One end (specifically, the nipple) of the outflow pipe 42 is attached to the pipe attachment portion 34 of the radial hole seal unit 30. A coolant tank (tank) 43 is connected to the other end of each of the inflow pipe 41 and the outflow pipe 42. That is, the shaft end seal unit 20 and the radial hole seal unit 30 communicate with each other through the coolant tank 43. Thus, the coolant tank 43, the inflow pipe 41, the axial hole 11, the radial hole 12, and the outflow pipe 42 are connected to form a flow path through which the cooling water can circulate.
Here, the coolant tank 43 is disposed at a position higher than the ball screw, more specifically, the axial hole 11 and the radial hole 12. The pipes 41 and 42 are, for example, metal pipes or rubber tubes.

(Operation and action)
When cooling water is supplied to the ball screw shaft 10 as a liquid from the cooling liquid tank 43 and the ball screw shaft 10 is rotated in a state where the axial holes 11 and the radial holes 12 are filled with the cooling water, the ball screw shaft 10 (particularly, Centrifugal force acts on the cooling water in the radial holes 12). As a result, the cooling water is discharged from the radial hole 12 and returned to the cooling liquid tank 43 via the outflow pipe 42. At this time, in the radial hole seal unit 30, the cooling water that has flowed out from the radial hole 12 flows out from the pipe mounting portion 34 to the outflow pipe 42 through the gap portion 33.
The amount of cooling water returned in this way flows from the coolant tank 43 into the axial hole 11 and the radial hole 12 through the inflow pipe 41.

As a result, the cooling water circulates through the flow path formed by the coolant tank 43, the inflow pipe 41, the axial hole 11, the radial hole 12, and the outflow pipe 42. As a result, the ball screw shaft 10 is cooled by the cooling water only by rotating the ball screw shaft 10. For example, the volume of the cooling water to be circulated is preferably at least three times the volume of the ball screw shaft 10.
As described above, only by rotating the ball screw shaft 10, the ball screw shaft 10 itself serves as a pump for circulating the cooling water.

(Effects of the first embodiment)
As described above, only by rotating the ball screw shaft 10, the ball screw shaft 10 itself serves as a pump for circulating the cooling water.
Thereby, a ball screw can be cooled with cooling water. As a result, the accuracy of these machines can be improved by applying this ball screw to a machine tool that does not like the extension of the shaft due to the heat generated by the ball screw or an injection molding machine that requires a long life of the ball screw.
Further, since the ball screw shaft 10 itself serves as a pump for circulating the cooling water, the ball screw can be cooled by itself without having a forced cooling device or a circulation unit. As a result, it is possible to provide a ball screw that is inexpensive and requires less equipment, power, and installation location.

Further, since the cooling water circulates only when the ball screw shaft 10 rotates (when heat is generated), it is possible to prevent the ball screw from being overcooled. That is, only the heat generated by the rotation of the ball screw shaft 10 can be appropriately removed.
It is also possible to use a fluid other than the cooling water as the cooling fluid. However, since a pump is not used, a fluid having a large heat capacity can be used as a cooling fluid if attention is paid only to rust of the ball screw shaft 10.

Further, the cooling water is only circulated through the flow path formed by the coolant tank 43, the inflow pipe 41, the axial hole 11, the radial hole 12, and the outflow pipe 42, and particularly in the circulation path. The cooling water is not forcibly cooled. However, since the cooling water has a large volume and a large heat capacity with respect to the ball screw shaft 10, a rapid temperature rise of the ball screw shaft 10 can be effectively prevented by using such cooling water. Although this does not change the size of the ball screw shaft 10, it is equivalent to an increase in the heat capacity of the ball screw shaft 10 itself.
Further, by adjusting the amount of cooling water stored in the cooling liquid tank 43 (for example, the capacity that can be stored in the cooling liquid tank 43), the temperature increase of the ball screw shaft 10 can be appropriately prevented without being excessive or insufficient.
Of course, the temperature control may be performed by a cooling device, and the temperature of the cooling water may be increased efficiently outside the ball screw shaft 10.

Further, by providing the partition plate 13 as shown in FIG. 4, the cooling water is easily rotated with the rotation of the ball screw shaft 10, so that a centrifugal force can be reliably generated in the cooling water. As a result, the cooling water can be efficiently discharged and circulated, and the cooling efficiency can be increased.
That is, even when the partition plate 13 is not provided as in FIG. 3, if the cooling water rotates together with the ball screw shaft 10 in the axial hole 11, centrifugal force acts on the cooling water. become. However, in the case where slippage occurs between the cooling water and the inner peripheral surface of the axial hole 11 due to the viscosity of the cooling water, the centrifugal force hardly acts on the cooling water. On the other hand, by providing the partition plate 13, the cooling water can be easily rotated together with the ball screw shaft 10, and the centrifugal force can be reliably generated in the cooling water.

  In this embodiment, a ball screw device including a round bar-shaped ball screw shaft and a ball screw nut screwed onto the outer peripheral surface of the ball screw shaft is realized. Further, the axial hole 11 and the radial hole 12 are formed so as to penetrate the inside of the ball screw shaft, thereby realizing a ball screw shaft flow passage hole through which a cooling fluid flows. The axial hole 11 is a part into which the cooling fluid flows and communicates with the inflow pipe to realize one end of a ball screw shaft passage hole disposed at the rotation center of the ball screw shaft. Further, the radial hole 12 is a part through which the cooling fluid flows out, communicates with the outflow pipe, and is arranged in addition to the flow path hole in the ball screw shaft that is arranged to be displaced in the radial direction from the rotation center of the ball screw shaft. Realize the end.

(Second Embodiment)
(Constitution)
In the second embodiment, the cooling water discharge efficiency from the ball screw shaft 10 is increased.
As shown in FIG. 7, in the second embodiment, a portion 14 of the ball screw shaft 10 where the radial hole 12 is formed is enlarged in the circumferential direction. Specifically, the part 14 has a flange shape. Thereby, the radial distance of the radial hole 12 is lengthened. Alternatively, the radial hole 12 is disposed at a position protruding from the outer peripheral surface of the ball screw shaft 10.
In this case, the shape of the radial hole seal unit 30 is also changed. That is, for example, the gap 33 of the radial hole seal unit 30 also expands in the radial direction.

(Operation and action)
When the cooling water is supplied from the cooling liquid tank 43 to the ball screw shaft 10 and the ball screw shaft 10 is rotated in a state where the axial hole 11 and the radial hole 12 are filled with the cooling water, the cooling liquid tank 43 and the inflow piping are provided. 41, the cooling water circulates through a flow path formed by the axial hole 11, the radial hole 12, and the outflow pipe 42. In this way, the ball screw shaft 10 itself plays the role of a pump for circulating the cooling water only by rotating the ball screw shaft 10.

(Effect of 2nd Embodiment)
Also in the second embodiment, as in the first embodiment, the ball screw shaft 10 itself plays the role of a pump for circulating the cooling water only by rotating the ball screw shaft 10.
In the second embodiment, by increasing the radial distance of the radial hole 12, the peripheral speed (rotational angular velocity) of the portion extended by the radial hole 12 when the ball screw shaft 10 is rotated is increased. Yes. Thereby, the centrifugal force which acts on cooling water can be enlarged. As a result, the cooling water discharge efficiency from the ball screw shaft 10 can be increased, and the cooling water can be circulated efficiently.

(Modification of the second embodiment)
In the second embodiment, the ball screw shaft 10 and the ball screw shaft 10 are enlarged in the radial direction. On the other hand, the radially enlarged portion can be provided as an individual component. 8 and 9 show a configuration of a ball screw provided with a radially enlarged portion as the discharge unit 50. FIG. FIG. 8 shows a side view of the ball screw. 9 shows a cross-sectional view in the YY direction of FIG.
As shown in FIGS. 8 and 9, a discharge unit 50 is attached to the ball screw shaft 10 on the outer peripheral surface of the portion where the radial hole 12 is formed.

The discharge unit 50 is formed in a hollow flange shape. Inside the discharge unit 50, a partition plate 53 is provided so as to divide the circumferential direction into four parts and form four compartments 51a, 51b, 51c, 51d. On the peripheral wall of the discharge unit 50, discharge holes 52a, 52b, 52c, and 52d are formed so as to penetrate the compartments 51a, 51b, 51c, and 51d. The discharge unit 50 rotates integrally with the ball screw shaft 10.
Further, the shape of the radial hole seal unit 30 is also changed in correspondence with the provision of the discharge unit 50 in this way. That is, for example, the gap 33 of the radial hole seal unit 30 also expands in the radial direction so as to match the outer shape of the discharge unit 50.

(Third embodiment)
(Constitution)
In the third embodiment, the ball screw shaft 10 is configured to be cantilevered.
FIG. 10 shows a configuration of the ball screw shaft 10 of the third embodiment.
As shown in FIG. 10, a fluid circulation unit 60 is attached to the ball screw shaft 10. The fluid circulation unit 60 has a shape that allows the cooling water to flow into and out of the axial hole 11 of the ball screw shaft 10. The fluid circulation unit 60 is attached to the axial end surface of the ball screw shaft 10 and discharges the cooling water in the axial hole 11 attached to the inflow portion 70 for feeding the cooling water from the inflow pipe 41 to the axial hole 11. Part (rotating part) 80.

The discharge part 80 is hollow and formed in a flange shape. A ball screw shaft coupling hole 81 is formed in the discharge portion 80 on the side wall on the shaft end surface side of the ball screw shaft 10. The ball screw shaft coupling hole 81 is formed to have the same diameter as the axial hole 11 so as to communicate with the axial hole 11 of the ball screw shaft 10. A seal 82 is provided on the side wall (outer periphery of the ball screw shaft connection hole 81) of the discharge portion 80 where the ball screw shaft connection hole 81 is formed. Thereby, leakage of the cooling water from between the side wall and the shaft end surface of the ball screw shaft 10 is prevented.
An outflow hole 84 is formed on the outer peripheral surface of the discharge portion 80. In the present embodiment, a plurality of outflow holes 84 are formed.

  The inflow portion 70 has a thin pipe shape. The inflow portion 70 is inserted into the axial hole 11 of the ball screw shaft 10, and one end portion 70 a thereof is inserted into the ball screw shaft connection hole 81 of the discharge portion 80. And the one end part 70a is connected to the side wall facing the side wall in which the ball screw shaft coupling hole 81 is formed. On the other hand, an inflow pipe 41 is connected from the outside to a portion of the side wall to which one end portion 70a of the inflow portion 70 is connected. Thereby, the hole 70b of the inflow part 70 and the inflow piping 41 are connected. Therefore, a seal 83 is provided on the side wall of the discharge portion 80 at the connection site of the inflow pipe 41. Thereby, leakage of the cooling water from between the hole 70b of the inflow portion 70 and the inflow pipe 41 is prevented.

Further, the inflow portion 70 has the other end portion 70 c extending to the vicinity of the closed end portion side of the axial hole 11 of the ball screw shaft 10. In the third embodiment, the radial hole 12 as in the first and second embodiments is not provided. Therefore, only the axial hole 11 extending in the axial direction is formed in the ball screw shaft 10. In the third embodiment, a gap 15 is formed between the inner peripheral surface of the axial hole 11 and the outer peripheral surface of the inflow portion 70, and the hole 70 b of the inflow portion 70 and the discharge portion are interposed via the gap 15. The interior 85 of the 80 is communicated.
The fluid circulation unit 60 configured as described above is fixed to the ball screw shaft 10. Thereby, the fluid circulation unit 60 rotates integrally with the ball screw shaft 10.

By providing such a fluid circulation unit 60, the coolant tank 53, the inflow pipe 51, the hole 70 b of the inflow part 70, and the outer peripheral surface of the inflow part 70 and the inner peripheral surface of the axial hole 11 are provided. A passage through which cooling water circulates is formed by the gap 15, the inside 85 of the discharge portion 80, and the outflow pipe 42.
Although not shown, a seal unit for returning the cooling water flowing out from the outflow hole 84 to the outflow pipe 42 without leakage is provided. That is, a seal unit having a structure capable of preventing leakage between the outer peripheral surface (outflow hole 84) of the discharge portion 80 of the fluid circulation unit 60 that rotates integrally with the ball screw shaft 10 and the outflow pipe 42 is provided.

(Operation and action)
When cooling water is supplied from the coolant tank 53 to the ball screw shaft 10 to rotate the ball screw shaft 10, the coolant tank 53, the inflow pipe 51, the hole 70 b of the inflow portion 70, the outer peripheral surface of the inflow portion 70 and the shaft The cooling water circulates through the flow path formed by the gap 15 between the inner surface of the direction hole 11, the inside 85 of the discharge portion 80, and the outflow pipe 42. In this way, the ball screw shaft 10 itself plays the role of a pump for circulating the cooling water only by rotating the ball screw shaft 10.

(Effect of the third embodiment)
Also in the third embodiment, as in the first and second embodiments, the ball screw shaft 10 itself plays the role of a pump for circulating the cooling water only by rotating the ball screw shaft 10.
Also in the third embodiment, similarly to the second embodiment, by providing the discharge portion 80 having a shape extending in the radial direction, the peripheral speed (rotational angular velocity) of the discharge portion 80 when the ball screw shaft 10 rotates. ) Can be increased. Thereby, the centrifugal force which acts on cooling water can be enlarged. As a result, the cooling water discharge efficiency from the ball screw shaft 10 can be increased, and the cooling water can be circulated efficiently.
Furthermore, in the third embodiment, even when the ball screw shaft 10 is cantilevered, it is possible to form a flow path, circulate cooling water, and cool the ball screw shaft 10.

  2 Ball screw nut, 10 Ball screw shaft, 11 axial hole, 12 radial hole

Claims (5)

A plurality of balls are interposed between the outer peripheral surface of the round ball-shaped ball screw shaft and the inner peripheral surface of the ball screw nut, the ball screw shaft is rotated, and the ball screw nut is moved in the axial direction of the ball screw shaft. In the ball screw device for relative movement,
The ball screw shaft is formed through the inside of the ball screw shaft, and has a flow passage hole in the ball screw shaft for flowing a cooling fluid,
The flow path hole in the ball screw shaft has one end portion as a portion into which the cooling fluid flows in and communicates with the inflow piping, and the other end portion as a portion through which the cooling fluid flows out and communicates with the outflow piping.
The ball screw device is characterized in that the one end portion is arranged at a rotation center of the ball screw shaft, and the other end portion is arranged to be shifted in a radial direction from the rotation center of the ball screw shaft.   The ball screw device according to claim 1, wherein the other end of the ball screw shaft passage hole is provided at a position protruding from an outer peripheral surface of the ball screw shaft.   The ball screw according to claim 1 or 2, further comprising a centrifugal force increasing means for increasing a centrifugal force acting on the cooling fluid in the other end portion in the ball screw shaft passage hole. apparatus. The ball screw shaft channel hole has an axial hole extending in the rotation axis direction of the ball screw shaft channel hole, and the other end of the ball screw shaft channel hole is formed by the ball screw shaft. Extending radially toward the center of rotation and connected to the axial hole,
The said centrifugal force increase means is a partition plate provided in the connection part with the said other end part by the said axial direction hole, and divides the connection part of the said axial direction hole in the circumferential direction. The ball screw device described.   An inflow pipe that communicates with one end of the ball screw shaft passage hole is connected, and an outflow pipe that communicates with the other end of the ball screw shaft passage hole is connected to the outflow pipe. The ball screw device according to any one of claims 1 to 4, further comprising cooling fluid storage means for storing the returned cooling fluid and feeding the stored cooling fluid to the inflow pipe. .

Images