Rotation support device, and support mechanism position adjustment mechanism of shaft support device

Abstract

Provided is a support mechanism (30) for rotatably supporting both ends of a screw shaft (21) in an axial direction, the support mechanism (30) comprising: a bearing unit (41) having a moving-side bearing housing (51), and a pair of angular ball bearings (33B) that fit inside the moving-side bearing housing (51); a support base (43) through which the screw shaft (21) passes, the support base (43) being disposed closer to the center in the axial direction relative to the bearing unit (41); and a housing position adjustment mechanism (44) disposed between the bearing unit (41) and the support base (43). The housing position adjustment mechanism (44) comprises: a support base-side member (61) provided on the support base (43) side; a bearing housing-side member (62) provided on the bearing housing (51) side, and movable in the axial direction relative to the support base-side member (61); a working fluid that fills in a pressure chamber (66) formed between the support base-side member (61) and the bearing housing-side member (62); and a disc spring (80) disposed in a compressed state between facing axial end surfaces of the support base-side member (61) and bearing housing-side member (62) in the pressure chamber (66). Consequently, even when the length of a rotating shaft in the axial direction changes due to influence of heat, it is possible to continuously and stably maintain the support stiffness in the axial direction.

Description

Rotation support device and support mechanism position adjustment mechanism for shaft support device

[0001] The present invention relates to a rotation support device that supports a rotation shaft such as a ball screw feed device or a spindle device, and to a support mechanism position adjustment mechanism for a shaft support device that supports a shaft.

[0002] Ball screw feed devices require high axial rigidity to maintain the feed accuracy of the screw shaft. Conventionally, a common method for providing rigidity to the screw shaft of a ball screw device is to combine and preload multiple angular bearings, place them at one or both ends of the screw shaft, and support the screw shaft in the axial direction. In addition, when thermal expansion of the screw shaft is taken into consideration, a method is used in which axial tension is applied to the screw shaft in advance to elongate it by a predetermined amount. Patent Document 1 describes a method in which tension is applied to the feed screw (screw shaft) in advance by adjusting the axial dimension of a spacer, and further includes a pretensioning mechanism that uses a disc spring or fluid pressure to move the bearing axially and apply tension to the feed screw when the feed screw elongates beyond the pretension due to temperature rise.

[0003] Japanese Utility Model Registration No. 2573982

[0004] However, excessive loads, such as pretension or pretension, applied to the feed screw can place a heavy load on the bearing, potentially damaging it. For this reason, a disc spring or an externally supplied fluid, as seen in the pretension mechanism described in Patent Document 1, is typically used to prevent excessive axial loads from being applied to the bearing. However, disc springs, as seen in the pretension mechanism described in Patent Document 1, weaken the load as the shaft elongates, and can only accommodate a temperature rise of 3 to 4 degrees. In machining centers, ball screws often experience temperature rises of more than 4 degrees, which prevents the disc springs from applying sufficient load, resulting in a decrease in axial support rigidity. Furthermore, hydraulic systems that apply loads hydraulically by supplying fluid from an external source require external devices such as a hydraulic pump, increase the size of the ball screw feed device, and result in increased costs and additional energy consumption. Furthermore, these issues exist not only in ball screw feed devices but also in rotation support devices, such as spindle devices, in which both axial ends of a rotating shaft are rotatably supported by a pair of support mechanisms.

[0005] The present invention has been made in consideration of the above-mentioned problems, and its purpose is to provide a rotation support device and a support mechanism position adjustment mechanism for a shaft support device that can continuously and stably maintain axial support rigidity even if the axial length of the rotating shaft changes due to the effects of heat.

[0006] The above object of the present invention can be achieved by the following configuration. [1] A rotary support device comprising: a rotating shaft and a pair of support mechanisms rotatably supporting both axial ends of the rotating shaft, one of the pair of support mechanisms comprising: a bearing unit comprising a bearing housing and a bearing that rotatably supports the rotating shaft relative to the bearing housing and is capable of supporting an axial load; a support base through which the rotating shaft passes or is arranged around the rotation axis; and a housing position adjustment mechanism arranged between the bearing unit and the support base, wherein the housing position adjustment mechanism comprises: a support base side member provided on the support base side and through which the rotating shaft passes or is arranged around the rotation axis; a bearing housing side member provided on the bearing housing side and through which the rotating shaft passes or is arranged around the rotation axis, and which is movable axially relative to the support base side member; a working fluid filled in a pressure chamber formed between the support base side member and the bearing housing side member; and an elastic member arranged in a compressed state within the pressure chamber between opposing axial end faces of the support base side member and the bearing housing side member. [2] A support mechanism position adjustment mechanism for a shaft support device including a shaft and a pair of support mechanisms provided at both axial ends of the shaft to support the shaft, the support mechanism position adjustment mechanism for the shaft support device being provided on one of the pair of support mechanisms, wherein one of the pair of support mechanisms has a support through which the shaft passes or is arranged around the axis, the support mechanism comprising: a first member provided on one of the shaft side and the support side, and through which the shaft can pass or be arranged around the axis; a second member provided on the other of the shaft side and the support side, and through which the shaft can pass or be arranged around the axis, movable axially relative to the first member, and forming an accommodation space between itself and the first member; a working fluid filled in the accommodation space; and an elastic member arranged in a compressed state within the accommodation space between the opposing axial end faces of the first member and the second member.

[0007] According to the rotary support device of the present invention, even if the axial length of the rotary shaft changes due to the influence of heat, the support rigidity in the axial direction can be continuously and stably maintained.

[0008] Furthermore, the support mechanism position adjustment mechanism for the shaft support device of the present invention can continuously and stably maintain axial support rigidity even if the axial length of the shaft changes due to the influence of heat.

[0009] 6 is a cross-sectional view of a table feed system of a machine tool to which the ball screw feed device according to the first embodiment of the present invention is applied. FIG. 7 is an enlarged cross-sectional view of a support mechanism equipped with the housing position adjustment mechanism shown in FIG. 1. FIG. 8 is a view taken along arrow A in FIG. 2. FIG. 9 is a cross-sectional view showing a modified disc spring. FIG. 10 is a view corresponding to FIG. 2 of the ball screw feed device according to the second embodiment of the present invention. FIG. 11 is a view corresponding to FIG. 2 of the ball screw feed device according to the third embodiment of the present invention. FIG. 12 is an enlarged view of part VII in FIG. 6. (a) to (c) are enlarged cross-sectional views of essential parts showing an example in which a wear-resistant member is applied to the seal groove of a ball screw feed device according to a modified embodiment of the third embodiment. FIG. 13 is a view corresponding to FIG. 2 of the ball screw feed device according to the fourth embodiment of the present invention. FIG. 14 is a view corresponding to FIG. 2 of the ball screw feed device according to the fifth embodiment of the present invention. FIG. 15 is a view corresponding to FIG. 2 of a modified bearing unit in which a pair of angular contact ball bearings are combined back to back in the first to fifth embodiments. FIG. 16 is a view corresponding to FIG. 2 of another modified bearing unit in which a pair of angular contact ball bearings are combined in parallel in the first to fifth embodiments. 14(a) is a schematic side view showing a first example in which the housing position adjustment mechanism is constituted by a plurality of pressure chambers, and FIG. 14(b) is a schematic side view showing a second example in which the housing position adjustment mechanism is constituted by a plurality of pressure chambers. 14(a) is a schematic side view showing a third example in which the housing position adjustment mechanism is constituted by a plurality of pressure chambers, and FIG. 14(b) is a schematic side view showing a fourth example in which the housing position adjustment mechanism is constituted by a plurality of pressure chambers. 14(b) is a schematic side view showing a fifth example in which the housing position adjustment mechanism is constituted by a plurality of pressure chambers. 14(a) is a cross-sectional view taken along line XVI-XVI of FIG. 14(a). 14(a) is a view corresponding to FIG. 2 of a ball screw feed device according to a sixth embodiment of the present invention. 14(b) is a view corresponding to FIG. 2 of a ball screw feed device according to a first modified example of the sixth embodiment. 14(b) is a view corresponding to FIG. 2 of a ball screw feed device according to a second modified example of the sixth embodiment. 14(b) is a view corresponding to FIG. 2 of a ball screw feed device according to a third ... an enlarged view of portion XVIII of FIG. 14(a). 22A and 22B are views of a ball screw feed device according to a fourth modified example of the sixth embodiment, and corresponding to FIG. 2; and FIG. 23A and FIG. 23B are views of a ball screw feed device according to a fifth modified example of the sixth embodiment, and corresponding to FIG.25(a) is an enlarged cross-sectional view corresponding to FIG. 2 in a phase where an oil supply passage formed in a bearing housing side member is provided to fill a pressure chamber with working fluid, and FIG. 25(b) is a cross-sectional view showing a modified example of the locking plug bolt of FIG. 25(a). FIG. 25(a) is a cross-sectional view of a locking plug plug used in place of the locking plug bolt of FIG. 25(a), and FIG. 25(b) is a cross-sectional view showing an example in which the locking plug of FIG. 25(a) is combined with a disk-shaped member, and FIG. 25(c) is a cross-sectional view showing a modified example of the disk-shaped member of FIG. 25(b), and FIG. 25(d) is a cross-sectional view showing another modified example of the disk-shaped member of FIG. 25(b). FIG. 25(b) is a cross-sectional view of a table feed system of a machine tool to which a ball screw feed device according to a modified example of the present invention is applied. FIG. 25(c) is a cross-sectional view showing a first example of a housing position adjustment mechanism in which a support base is disposed at an axial end side with respect to a bearing unit. FIG. 25(d) is a cross-sectional view showing a third example of a housing position adjustment mechanism in which a support base is disposed at an axial end side with respect to a bearing unit. 34 is a cross-sectional view showing a fourth example of a housing position adjustment mechanism in which a support base is disposed on the axial end side with respect to a bearing unit. FIG. 35 is a cross-sectional view showing a rotation support device according to the present invention. FIG. 36 is a cross-sectional view showing another rotation support device according to the present invention. FIG. 37 is a cross-sectional view showing a shaft support device to which the support mechanism position adjustment mechanism according to the present invention is applied. FIG. 38 is an enlarged view of a portion XXXV of FIG. 34.

[0010] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of a ball screw feed device, which is an example of a rotation support device or a shaft support device according to the present invention, will be described in detail with reference to the drawings.

[0011] (First Embodiment) Fig. 1 shows a table feed system of a machine tool to which a ball screw feed device of the first embodiment is applied. With reference to Figs. 1 to 3, the axial direction of a screw shaft 21 of a ball screw feed device 20 (the left-right direction in Fig. 1) is defined as the X direction, the direction parallel to the mounting surface 1a of a base 1 and perpendicular to the axial direction of the screw shaft 21 (the direction perpendicular to the plane of the paper in Fig. 1) is defined as the Y direction, and the direction perpendicular to the mounting surface 1a of the base 1 (the up-down direction in Fig. 1) is defined as the Z direction. In Fig. 2 and corresponding figures, dotted lines indicate bolt fastening locations.

[0012] The table feed system 10 includes a moving table 11 fixed to a nut 23 of a ball screw feed device 20. The moving table 11 is configured to be movable in the X direction by driving a screw shaft 21 of the ball screw feed device 20 with a drive motor 12. The moving table 11 is provided with a pair of linear guides 13 (only one of which is shown in FIG. 1 ) on both sides of the ball screw feed device 20 in the Y direction. Each linear guide 13 includes a guide rail 15 disposed on the base 1 via a rail mounting base 14 in parallel to the screw shaft 21, and two sliders 16 fixed to the underside of the moving table 11 and mounted across the guide rails 15. When the drive motor 12 rotates the screw shaft 21, the moving table 11 is guided by the pair of linear guides 13 and moves back and forth linearly together with the nut 23.

[0013] The ball screw feed device 20 comprises a screw shaft 21 having a spiral screw groove 21b formed on its outer peripheral surface, a nut 23 arranged around the screw shaft 21, having a spiral screw groove (not shown) formed on its inner peripheral surface, and fitted into a nut housing 22 fixed to the underside of the moving table 11, and a plurality of balls (not shown) arranged so as to roll freely between the screw groove of the nut 23 and the screw groove 21b of the screw shaft 21.

[0014] The screw shaft 21 includes a large-diameter portion 24 formed in the axial center and having a screw groove 21b, and small-diameter portions 25 formed at both axial ends of the large-diameter portion 24. A male thread 25a is formed on the outer peripheral surface of the tip end of the small-diameter portion 25, and a small-diameter shaft portion 27 is provided at the tip end of one side (the right side in the figure) of the screw shaft 21. The small-diameter shaft portion 27 is connected to the rotating shaft 12a of the drive motor 12 via a coupling 28.

[0015] In addition, one side of the screw shaft 21, to which the drive motor 12 is connected, is rotatably supported by a first support mechanism 30, and the other side of the screw shaft 21 (the left side in the figure) is rotatably supported by a second support mechanism 40.

[0016] The first support mechanism 30 includes a fixed-side bearing housing 31 fixed to the base 1, and a pair of angular contact ball bearings 33, 33 arranged in a face-to-face combination to rotatably support the screw shaft 21 relative to the fixed-side bearing housing 31. Each of the pair of angular contact ball bearings 33, 33 includes an outer ring 34 fitted inside the fixed-side bearing housing 31, an inner ring 35 fitted outside the small diameter portion 25 of the screw shaft 21, and a plurality of balls 36 rollably disposed between the outer ring 34 and the inner ring 35 with a contact angle therebetween.

[0017] The pair of angular contact ball bearings 33, 33 has an outer ring 34 of the axially inner angular contact ball bearing 33 abutting against the inward flange 31a of the fixed-side bearing housing 31, and the outer ring 34 of the axially outer angular contact ball bearing 33 fixed by an outer ring holder 37 fastened to the fixed-side bearing housing 31. The inner ring 35 of the axially inner angular contact ball bearing 33 abuts against the step 21a between the large-diameter portion 24 and the small-diameter portion 25 of the screw shaft 21, and the inner ring 35 of the axially outer angular contact ball bearing 33 is fastened by a fastening nut 38a that screws onto the male threads 25a. Therefore, the first support mechanism 30 supports the screw shaft 21 with the axial position of the screw shaft 21 fixed.

[0018] 2 and 3, the second support mechanism 40 includes a bearing unit 41 disposed at the other end of the screw shaft 21, a support base 43 fixed to the base 1 axially centrally of the bearing unit 41, and a housing position adjustment mechanism 60 disposed between the bearing unit 41 and the support base 43. The support base 43 is provided with a through-hole 43a through which the screw shaft 21 passes.

[0019] The bearing unit 41 includes a moving-side bearing housing 51 and a pair of angular contact ball bearings 53, 53 that rotatably support the screw shaft 21 relative to the moving-side bearing housing 51. The pair of angular contact ball bearings 53, 53 include an outer ring 54 that fits inside the moving-side bearing housing 51, an inner ring 55 that fits outside the small diameter portion 25 of the screw shaft 21, and a plurality of balls 56 that are rotatably disposed between the outer ring 54 and the inner ring 55 with a contact angle therebetween.

[0020] In the pair of angular contact ball bearings 53, 53, the outer ring 54 of the axially inner angular contact ball bearing 53 abuts against the inward flange 51 a of the moving-side bearing housing 51, and the outer ring 54 of the axially outer angular contact ball bearing 53 is fastened by an outer ring holder 47 fastened and fixed to the moving-side bearing housing 51, so that each outer ring 54, 54 is positioned axially with respect to the moving-side bearing housing 51. Also, the inner ring 55 of the angular contact ball bearing 53 arranged axially outward is fastened by a fastening nut 38 b that threads onto the male thread 25 a via a spacer 48. In other words, the pair of angular contact ball bearings 53, 53, the moving-side bearing housing 51, and the outer ring holder 47 can be unitized as a bearing unit 41 with a predetermined preload applied to the pair of angular contact ball bearings 53, 53 arranged face-to-face, and this bearing unit 41 can be easily attached to the screw shaft 21 and the housing position adjustment mechanism 60, respectively. In this configuration, the moving-side bearing housing 51 can be integrated with the bearing housing side member 62 as needed.

[0021] The housing position adjustment mechanism 60 is provided on the support base 43 side and includes a support base side member 61 through which the screw shaft 21 passes, and a bearing housing side member 62 provided on the movable-side bearing housing 51 side and movable in the axial direction relative to the support base side member 61. The support base side member 61 and the bearing housing side member 62 face each other in the axial direction.

[0022] The support base side member 61 has an annular portion 61a protruding toward the support base 43 side, which fits into a through hole 43a of the support base 43, and is fixed to the support base 43 with a plurality of bolts (not shown). The bearing housing side member 62 has an annular portion 62a protruding toward the moving-side bearing housing 51 side, which fits into the inward flange 51a, and is fixed to the moving-side bearing housing 51 with a plurality of bolts 63 (see FIG. 3).

[0023] Furthermore, a bottomed annular recess 64 that opens toward the support base side member 61 (one axial side) is provided on the side surface of the bearing housing side member 62 that faces the support base side member 61. Meanwhile, an annular protrusion 65 that protrudes into the annular recess 64 toward the bearing housing side member 62 (the other axial side) is provided on the side surface of the support base side member 61 that faces the bearing housing side member 62. The annular recess 64 and the annular protrusion 65 are slidably fitted together in the axial direction, and an annular pressure chamber 66 is formed between the bottom surface, inward surface 64a, and outward surface 64b of the annular recess 64 and the tip surface of the annular protrusion 65.

[0024] The pressure chamber 66 is filled with a working fluid, for example, hydraulic oil 70, in a compressed state, and a plurality of disc springs 80, which are elastic members, are arranged in a compressed state between the opposing axial end faces of the support base side member 61 and the bearing housing side member 62, i.e., between the bottom surface of the annular recess 64 and the tip surface of the annular protrusion 65.

[0025] The hydraulic oil 70 is a hydraulic fluid that has an elastic effect when an external force is applied, and whose rigidity has been industrially confirmed, and is given rigidity when compressed.

[0026] Specifically, it is known that the bulk modulus of hydraulic oil is affected by the inclusion of gas, etc. (see non-patent document (Deshimaru Junichi and Tanaka Hirohisa, "Measurement of the Bulk Modulus of Hydraulic Oil," Hydraulics and Pneumatics, Vol. 19, No. 7, 1988, pp. 580-583)). In this embodiment, even if the temperature rises by more than 4 degrees, when the pressure chamber 66 expands in the axial direction in response to the axial elongation of the screw shaft 21, the type of hydraulic oil and gas are appropriately selected so that the desired axial stiffness is imparted to the screw shaft by the pressure acting on the bearing housing side member 62.

[0027] The working fluid is not limited to oil, and may be any liquid, such as water, or gas, as long as it has an elastic effect and exhibits rigidity when compressed. Furthermore, the magnitude of the axial load applied to the screw shaft 21 by the working fluid may be set by the tightening amount of the fastening nut 38b, and may also be set taking into consideration volumetric expansion of the working fluid due to temperature rise caused by temperature rises in the angular contact ball bearings 53 and the screw shaft 21 during operation of the ball screw feed device 20. Additionally, the magnitude of the axial load applied to the screw shaft 21 by the working fluid may also be set taking into consideration volumetric expansion of the working fluid due to temperature rises caused by environmental changes around the ball screw feed device 20 during operation of the ball screw feed device 20.

[0028] When the plurality of disc springs 80 function as series springs, they are arranged so that the convex surfaces of adjacent disc springs 80 face each other and the concave surfaces of adjacent disc springs 80 face each other, as shown in Fig. 2. When the plurality of disc springs 80 function as parallel springs, they are arranged so that the disc springs 80 face each other and face each other in the same direction in the axial direction, although this is not shown.

[0029] Furthermore, O-rings 67 are fitted between the outward surface 65a of the annular convex portion 65 and the inward surface 64a of the annular recessed portion 64, and between the inward surface 65b of the annular convex portion 65 and the outward surface 64b of the annular recessed portion 64. Specifically, the O-rings 67 are arranged in annular seal grooves 68 formed on the outward surface 65a and the inward surface 65b of the annular convex portion 65 and come into sliding contact with the opposing inward surface 64a and the outward surface 64b of the annular recessed portion 64 to seal the radial gap between the outward surface 65a of the annular convex portion 65 and the inward surface 64a of the annular recessed portion 64, and the radial gap between the inward surface 65b of the annular convex portion 65 and the outward surface 64b of the annular recessed portion 64. Note that the seal grooves 68 may also be formed on the inward surface 64a and the outward surface 64b of the annular recessed portion 64. Furthermore, one O-ring 67 and one seal groove 68 are respectively arranged between the opposing surfaces, but multiple O-rings 67 and multiple seal grooves 68 may also be arranged. As a result, the O-ring 67 prevents leakage of the hydraulic oil 70 filled in the pressure chamber 66. From the viewpoint of preventing wear, the O-ring 67 may be subjected to a surface treatment that provides wear resistance or the like.

[0030] An anti-rotation mechanism 75 is provided between the support base side member 61 and the bearing housing side member 62 to prevent relative rotation therebetween. Specifically, for example, the bearing housing side member 62 has a through-hole 77 formed in at least one location in the circumferential direction, which penetrates radially so that the tip of a positioning pin 76 protrudes from the inward surface 64a of the annular recess 64. The tip of the positioning pin 76 is inserted into an elongated hole 78 formed along the axial direction in the outward surface 65a of the annular protrusion 65 of the support base side member 61 so that the bearing housing side member 62 can move in the axial direction. Note that the positioning pin 76 may be replaced by a rotational positioning key (not shown) having a similar anti-rotation function, which is inserted into the elongated hole 78 so that the bearing housing side member 62 can move in the axial direction.

[0031] In this housing position adjustment mechanism 60, after the hydraulic oil 70 and the plurality of disc springs 80 are accommodated in the pressure chamber 66, the fastening nut 38b is tightened to press the bearing housing side member 62 toward the support base side member 61 via the pair of angular ball bearings 53, 53 and the movable-side bearing housing 51. As a result, the hydraulic oil 70 is compressed, and pressure in the screw axis direction is applied to the hydraulic oil 70, and the plurality of disc springs 80 are compressed, and pressure in the screw axis direction is applied to the plurality of disc springs 80.

[0032] On the other hand, since the support base side member 61 is fixed to the base 1 via the support base 43, the bearing housing side member 62 and the movable side bearing housing 51 are pressed leftward in the figure by the pressure of the hydraulic oil 70 contained in the pressure chamber 66 in a compressed state and the pressure of the multiple disc springs 80. This brings about a state in which tension is applied to the screw shaft 21 in advance to the left in Figures 1 and 2.

[0033] Furthermore, the pressure of the hydraulic oil 70 contained in the pressure chamber 66 and the pressure of the plurality of disc springs 80 can be controlled to any desired magnitude by adjusting the amount of tightening of the fastening nut 38b. That is, the magnitude of the axial load applied to the screw shaft 21 by the fastening nut 38b can be set to any desired magnitude.

[0034] Furthermore, the magnitude of the axial load applied to the screw shaft 21 by the hydraulic oil 70 can be set not only by the amount of tightening of the fastening nut 38b, as described above, but also by taking into account the volume expansion of the hydraulic oil 70 due to the temperature rise when the ball screw feed device 20 is in operation.

[0035] Next, we will explain the operation of the ball screw feed device 20 of this embodiment. In the ball screw feed device 20, when the screw shaft 21 is rotationally driven by the drive motor 12 and the moving table 11 fixed to the nut 23 is caused to move linearly back and forth, the drive motor 12, angular contact ball bearings 33, 53, nut 23, etc. generate heat in association with this movement, the temperature of the ball screw feed device 20 gradually rises, and the screw shaft 21 extends in the axial direction due to thermal expansion.

[0036] 1, when the screw shaft 21 expands in the axial direction due to thermal expansion, it extends leftward because the right end of the screw shaft 21 is fixed to the fixed-side bearing housing 31 via the angular contact ball bearings 33, 33. When the screw shaft 21 expands in the axial direction (leftward) due to the influence of heat, the bearing unit 41 and the bearing housing side member 62 move in the same direction, following the axial expansion of the screw shaft 21 due to thermal expansion, due to the pressure of the hydraulic oil 70 contained in the pressure chamber 66 and the multiple disc springs 80.

[0037] In this embodiment, the hydraulic oil 70 and the plurality of disc springs 80 are designed to continue to press the bearing unit 41 and the bearing housing side member 62 to the left even when the screw shaft 21 extends in the axial direction. The hydraulic oil 70 and the pressure chamber 66 have a high degree of design freedom, and by appropriately selecting the physical properties of the hydraulic fluid filled in the pressure chamber and the size and shape of the pressure chamber, the pressure of the hydraulic oil 70 can be exerted in addition to the pressure of the plurality of disc springs 80, thereby applying a sufficient and appropriate load in response to greater axial extension. Therefore, even if the temperature of the ball screw feed device 20 rises above 4 degrees, the pair of angular contact ball bearings 53, 53 can be moved axially to maintain axial support rigidity, and the axial rigidity of the ball screw feed device 20 is stabilized.

[0038] In particular, since the pressure of the hydraulic oil 70 can change in response to the axial elongation of the screw shaft 21 even if the temperature rises by more than 4 degrees, the pair of angular contact ball bearings 33, 33 are maintained as fixed supports while the axial rigidity of the ball screw feed device 20 is stabilized while the screw shaft 21 is elongating in the axial direction. Furthermore, the multiple disc springs 80 used in this embodiment have an elastic coefficient that can share the load with the hydraulic oil 70 and maintain a compressed state between the bottom surface of the annular recess 64 and the tip surface of the annular protrusion 65 overall over a long axial distance, even if the temperature of the ball screw feed device 20 rises by more than 4 degrees.

[0039] In the case of this embodiment, an excessive load is not applied to the pair of angular ball bearings 33, 33 and 53, 53, so there is no risk of excessive wear or seizure due to poor lubrication, and the life of the pair of angular ball bearings 33, 33 and 53, 53 is extended. That is, in this embodiment, there is no need to apply to the screw shaft 21 a pretension of the magnitude that is applied by the spacer in the ball screw described in Patent Document 1, so an excessive load is not applied to the pair of angular ball bearings 33, 33 and 53, 53 either.

[0040] Furthermore, in the ball screw feed device 20 of this embodiment, it is not necessary to install an external device such as an accumulator or pump for supplying the hydraulic oil 70 to the pressure chamber 66, thereby simplifying the housing position adjustment mechanism 60. As a result, the pressure in the pressure chamber 66 can be maintained with as little change as possible without consuming energy supplied from the outside.

[0041] The O-ring 67 in this embodiment also functions as a damping mechanism. That is, when a workpiece placed on the movable table 11 is machined, vibrations generated in the movable table 11 tend to vibrate the screw shaft 21, which has a relatively low rigidity. The vibrations of the screw shaft 21 are propagated to the bearing housing side member 62 via the pair of angular contact ball bearings 33 and the movable-side bearing housing 51. However, the O-ring 67 between the bearing housing side member 62 and the support base side member 61 damps the vibrations of the bearing housing side member 62. Therefore, the vibrations of the screw shaft 21 can also be damped, suppressing disturbances in the quality of the machined surface of the workpiece placed on the movable table 11. In this case, the O-ring 67 disposed between the bearing housing side member 62 and the support base side member 61 damps not only the axial vibrations of the screw shaft 21 but also the radial vibrations of the screw shaft 21.

[0042] Furthermore, the hydraulic oil 70 of the housing position adjustment mechanism 60 is stored not only in the pressure chamber 66 but also in the gaps between the outward surface 65 a of the annular convex portion 65 and the inward surface 64 a of the annular recessed portion 64, and between the inward surface 65 b of the annular convex portion 65 and the outward surface 64 b of the annular recessed portion 64, and in each gap closer to the pressure chamber 66 than the O-ring 67. Therefore, when the hydraulic oil 70 is compressed, pressure acts on the hydraulic oil 70 not only in the axial direction but also in the radial direction. This allows the bearing housing side member 62 to be supported by the support base side member 61 with a sufficient and appropriate radial load. As a result, the housing position adjustment mechanism 60 can provide radial support rigidity to the screw shaft 21 via the pair of angular contact ball bearings 53 and the bearing housing 51, and can also provide an aligning function for the screw shaft 21.

[0043] Furthermore, when the axial elongation of the screw shaft 21 described above occurs, even if vibration occurs due to elastic deformation when the disc spring 80 returns from a compressed state, the O-ring 67 can damp this vibration.

[0044] Furthermore, the hydraulic oil 70 in the pressure chamber 66 exerts an orifice effect when passing through the tiny gaps that form at the contact points between the disc springs 80 or between the disc springs 80 and the inner surface of the pressure chamber 66, thereby damping the vibrations of the screw shaft 21 and the multiple disc springs 80 mentioned above.

[0045] Therefore, in the ball screw feed device 20 of this embodiment, by accommodating hydraulic oil 70 and multiple disc springs 80 in the pressure chamber 66, even if the axial length of the screw shaft 21 changes due to the influence of heat, the axial support rigidity can be continuously and stably maintained, and vibrations in the axial and radial directions can be damped.

[0046] 4, the disc-shaped disc spring 80 may have a plurality of through holes 80a penetrating the conical plate portion in the axial direction, or may have a plurality of slits (not shown). This allows the disc spring 80 to function as an orifice, and the hydraulic oil 70 flows through the plurality of through holes 80a and slits, thereby achieving an even greater damping effect.

[0047] Although not shown, the support base side member 61 may be configured integrally with the support base 43 , and the bearing housing side member 62 may be configured integrally with the moving side bearing housing 51 .

[0048] Second Embodiment Next, a ball screw feed device according to a second embodiment of the present invention will be described with reference to Fig. 5. In this embodiment, the configuration of the housing position adjustment mechanism 60 of the second support mechanism 40 is different from that of the first embodiment.

[0049] In the housing position adjustment mechanism 60 of the second embodiment, a storage chamber 71 is formed within the annular convex portion 65, and an orifice 72 is formed along the axial direction at at least one location (two locations in Figure 5) in the circumferential direction to connect the storage chamber 71 and the pressure chamber 66.

[0050] The reservoir chamber 71 is formed in a disk groove shape, opening onto the outward surface 65 a of the annular protrusion 65 closer to the tip surface of the annular protrusion 65 than the groove in which the O-ring 67 is disposed. Therefore, in this embodiment, the hydraulic oil 70 is stored not only in the pressure chamber 66 but also in the reservoir chamber 71 and the orifice 72.

[0051] As a result, in this embodiment, vibration of the screw shaft 21 causes the bearing housing side member 62 to vibrate together with the moving-side bearing housing 51 and the pair of angular contact ball bearings 33, 33, and the hydraulic oil 70 in the pressure chamber 66 and the reservoir chamber 71 passes through the orifice 72 and the gap g between the outward surface 65 a of the annular convex portion 65 and the inward surface 64 a of the annular recess 64, thereby damping the vibration. Therefore, similar to the O-ring 67 described above, when a workpiece placed on the moving table 11 is machined, the vibration transmitted to the screw shaft 21 is damped, and disturbances in the machined surface quality of the workpiece can be further improved.

[0052] In the above embodiment, the reservoir chamber 71 is formed on the outer diameter side so as to open to the outward surface 65a of the annular convex portion 65, but it may also be formed on the inner diameter side so as to open to the inward surface 65b of the annular convex portion 65. The cross-sectional shape and length of the orifice 72 may be arbitrarily formed as long as they provide a damping function. The other configurations and functions are the same as those of the first embodiment.

[0053] Third Embodiment Next, a ball screw feed device according to a third embodiment of the present invention will be described with reference to Figures 6 and 7. In this embodiment, the configuration of the housing position adjustment mechanism 60 of the second support mechanism 40 is different from that of the first embodiment.

[0054] In the housing position adjustment mechanism 60 of the third embodiment, the seal groove 68 formed on the outward surface 65a and the inward surface 65b of the annular protrusion 65 is composed of a tapered surface 69a whose groove depth becomes shallower as it moves away from the pressure chamber 66 side, and circular ring-shaped axial side surfaces 69b, 69c extending radially from both axial end edges of the tapered surface 69a.

[0055] Furthermore, the axial distance between both axial side surfaces 69b, 69c is wider than the axial width of the O-ring 67 when it is elastically deformed and attached to the seal groove 68. As a result, the hydraulic oil 70 that has passed through the gap g from the pressure chamber 66 flows around to the vicinity of the boundary between the axial side surface 69b, which has a deep groove, and the tapered surface 69a.

[0056] Therefore, as the pressure of the hydraulic oil 70 in the pressure chamber 66 increases and the O-ring 67 is pushed toward the atmospheric pressure side by the hydraulic oil 70, the O-ring 67 further improves the sealing performance due to the wedge structure between the tapered surface 69a of the seal groove 68 and the inward surface 64a and outward surface 64b of the opposing annular recess 64. As a result, even if relative movement occurs between the support base side member 61 and the bearing housing side member 62, leakage of the hydraulic oil 70 toward the atmospheric pressure side can be prevented, and the axial rigidity of the ball screw feed device 20 can be continuously maintained.

[0057] As a modification of this embodiment, as shown in Figures 8(a) to (c), a wear-resistant member 59 may be interposed between the O-ring 67 and at least one of the inward surface 64a of the annular recess 64 and the outward surface 65a of the annular protrusion 65 (in this embodiment, the tapered surface 69a of the seal groove 68 formed on the outward surface 65a).

[0058] Specifically, as shown in FIG. 8( a), the wear-resistant member 59 may be formed as an annular member having a U-shaped cross section so as to be positioned between the outer peripheral surface of the O-ring 67 and the inward surface 64 a of the annular recess 64, and between the inner peripheral surface of the O-ring 67 and the tapered surface 69 a of the seal groove 68 formed on the outward surface 65 a of the annular protrusion 65.

[0059] 8(b), the wear-resistant member 59 may be formed as an annular member having a straight cross section so as to be positioned between the inner peripheral surface of the O-ring 67 and the tapered surface 69a of the seal groove 68 formed in the outward surface 65a of the annular protrusion 65. Furthermore, as shown in FIG. 8(c), the wear-resistant member 59 may be formed as an annular member having a straight cross section so as to be positioned between the outer peripheral surface of the O-ring 67 and the inward surface 64a of the annular recess 64.

[0060] The wear-resistant member 59 may be made of, for example, a resin material such as a fluorine-based resin, or a metal material that has been subjected to an appropriate surface treatment.

[0061] In any of the embodiments shown in Figures 8(a) to (c), the use of the wear-resistant member 59 can disperse the stress concentration on the O-ring 67, thereby suppressing damage such as wear to the O-ring 67 and the contact surface with the O-ring 67.

[0062] The wear-resistant member 59 may also be interposed between the O-ring 67 and at least one of the outward surface 64b of the annular recess 64 and the inward surface 65b of the annular protrusion 65 (in FIG. 7, the tapered surface 69a of the seal groove 68 formed on the inward surface 65b), as shown in FIG.

[0063] 8(a) to 8(c), the wear-resistant member 59 is interposed between the O-ring 67 and the opposing surface of the O-ring 67 in the seal groove 68 having a tapered surface 69a. On the other hand, the above effect can also be achieved by interposing the wear-resistant member 59 between the O-ring 67 and the opposing surface of the O-ring 67 in the seal groove 68 having a uniform groove depth as shown in Fig. 2. The other configurations and operations are the same as those of the first embodiment.

[0064] Fourth Embodiment Next, a ball screw feed device according to a fourth embodiment of the present invention will be described with reference to Fig. 9. Note that in this embodiment, the configuration of the housing position adjustment mechanism 60 of the second support mechanism 40 is different from that of the first embodiment.

[0065] In the housing position adjustment mechanism 60 of the fourth embodiment, heating elements 180, 181, such as heating wires or rubber heaters, serving as working fluid volume change parts, are arranged in a ring shape or discretely on the outer circumferential surfaces of the support base side member 61 and the bearing housing side member 62.

[0066] As a result, heat from the heating elements 180, 181 is transferred from the support base side member 61 and the bearing housing side member 62 to the hydraulic oil 70 in the pressure chamber 66, and by heating the hydraulic oil 70, the volume of the hydraulic oil 70 can be expanded. As a result, even if the screw shaft 21 extends in the axial direction, a load is excited in the pressure chamber 66 due to the volume expansion of the hydraulic oil 70, and therefore, the support rigidity in the axial direction can be maintained.

[0067] In this embodiment, heating elements 180, 181 are attached to the outer peripheral surfaces of the support base side member 61 and the bearing housing side member 62 as working fluid volume change units, but cooling media 182, 183 such as a cooling jacket or a cooling element may be attached instead.

[0068] By using the cooling media 182, 183, even if the load excited in the pressure chamber 66 becomes excessive due to the volume expansion of the hydraulic oil 70, it is possible to cool the hydraulic oil 70 and contract the volume of the hydraulic oil 70. This prevents the axial support stiffness of the ball screw feed device 20 from becoming excessively large, and makes it possible to continuously maintain the axial support stiffness in a stable state.

[0069] In addition, in this embodiment, since the temperature of the hydraulic oil 70 is affected by the components, installation environment, operating cycle, etc. of the ball screw feed device 20, the hydraulic oil 70 may be controlled to a target temperature by forming a feedback loop for the temperatures of the components and the hydraulic oil 70 using the heating elements 180, 181 and the cooling media 182, 183. Furthermore, in this embodiment, the operation of the heating elements 180, 181 and the cooling media 182, 183 may be feedback-controlled by taking into consideration the volume change of the hydraulic oil 70, the pressure state in the pressure chamber 66, the relative axial displacement between the support base side member 61 and the bearing housing side member 62, etc.

[0070] In addition, in this embodiment, the working fluid volume change unit is attached to both the support base side member 61 and the bearing housing side member 62, but it may also be attached to either the support base side member 61 or the bearing housing side member 62.

[0071] Furthermore, in this embodiment, the working fluid volume change unit is provided on the outer peripheral surface of the support base side member 61 and the outer peripheral surface of the bearing housing side member 62, but it can be attached at any position, such as the axial side, inner peripheral surface, or interior, as long as it is a location where the volume of the working oil 70 in the pressure chamber 66 can be expanded or contracted.

[0072] In addition, a heating element may be attached to either the support base side member 61 or the bearing housing side member 62, and a cooling medium may be attached to the other. Also, the heating element and the cooling medium may be arranged so as to coexist in either the support base side member 61 or the bearing housing side member 62. The other configurations and operations are the same as those of the first embodiment.

[0073] Fifth Embodiment Next, a ball screw feed device according to a fifth embodiment of the present invention will be described with reference to Fig. 10. This embodiment differs from the first embodiment in that the second support mechanism 40 further includes another housing position adjustment mechanism 160.

[0074] That is, the second support mechanism 40 of the fifth embodiment further includes another housing position adjustment mechanism 160 disposed adjacent to the housing position adjustment mechanism 60 between the bearing unit 41 and the support base 43. The other housing position adjustment mechanism 160 includes: another support base side member 161 provided on the support base 43 side and through which the screw shaft 21 passes; another bearing housing side member 162 provided on the bearing housing 51 side and through which the screw shaft 21 passes and which is movable in the axial direction relative to the other support base side member 161; hydraulic oil 70 as another working fluid filled in a compressed state in a pressure chamber 166 formed between the other support base side member 161 and the other bearing housing side member 162; and a disc spring 80 as another elastic member disposed in a compressed state in the pressure chamber 166 between the opposing axial end faces of the other support base side member 161 and the other bearing housing side member 162. That is, the second support mechanism 40 includes two housing position adjustment mechanisms 60, 160 in a tandem configuration arranged in series in the axial direction.

[0075] As shown in Figure 10, in another housing position adjustment mechanism 160, another bearing housing side member 162 has an annular recess 164, and another support base side member 161 has an annular protrusion 165 that fits axially within the annular recess 164 so as to be able to slide, and the hydraulic oil 70 is filled in a compressed state in a pressure chamber 166 formed between the annular recess 164 and the annular protrusion 165.

[0076] In this embodiment, the other support base side member 161 has an annular portion 161a protruding toward the support base 43 and fitted into a through hole 43a of the support base 43, and is fixed to the support base 43 with a plurality of bolts (not shown). Furthermore, the support base side member 61 of the housing position adjustment mechanism 60 and the other bearing housing side member 162 of the other housing position adjustment mechanism 160 are integrally configured as a single member or by connecting the two.

[0077] In this way, by arranging the two housing position adjustment mechanisms 60, 160 in series in the axial direction, it is possible to stably maintain the axial rigidity of the ball screw feed device 20 even when the extension of the screw shaft is even greater, and it is also possible to improve axial alignment and coaxiality.

[0078] The other housing position adjustment mechanism 160 is not limited to the same configuration as the housing position adjustment mechanism 60 shown in FIG. 10 , and may have any other configuration as long as it has a pressure generating means accommodated in a compressed state in a pressure chamber 166 formed between the other support base side member 161 and the other bearing housing side member 162. For example, the pressure generating means may be arranged in the pressure chamber 166 using only hydraulic oil or only an elastic member. Furthermore, the second support mechanism 40 may have two housing position adjustment mechanisms 60, 160, or may have three or more housing position adjustment mechanisms, as long as multiple housing position adjustment mechanisms are arranged in series in the axial direction. The other configurations and operations are the same as those of the first embodiment.

[0079] In the first to fifth embodiments, the pair of angular contact ball bearings used in the bearing unit of the second support mechanism are arranged in a face-to-face configuration, but the arrangement is not limited to this. That is, the pair of angular contact ball bearings 53, 53 may be arranged in various support configurations, such as a back-to-back configuration as shown in FIG. 11 or a parallel configuration as shown in FIG. 12. When the pair of angular contact ball bearings 53, 53 are arranged in a back-to-back configuration as shown in FIG. 11, an inner ring spacer 49 may be disposed between the step between the large-diameter portion 24 and the small-diameter portion 25 of the screw shaft 21 and the inner ring 55 of the angular contact ball bearing 53 on the axially inner side. Furthermore, the pair of angular contact ball bearings 33, 33 of the first support mechanism are also arranged in a face-to-face configuration, but may be arranged in various support configurations, such as a back-to-face configuration or a parallel configuration. Furthermore, although not shown, the angular contact ball bearings 33, 53 do not necessarily have to be composed of two angular contact ball bearings, but may also be composed of three or more angular contact ball bearings.

[0080] Furthermore, in the above embodiment, the other housing position adjustment mechanism 160 is disposed adjacent to the housing position adjustment mechanism 60 in the axial direction, but this is not limiting, and the other housing position adjustment mechanism 160 may be disposed adjacent to the housing position adjustment mechanism 60 in parallel in the radial direction. This makes it possible to maintain the axial rigidity of the ball screw feed device 20 while suppressing the axial dimension of the ball screw feed device 20 and in a state in which a larger axial load is generated than when a single housing position adjustment mechanism is disposed.

[0081] Furthermore, in the above embodiment, the annular recess is provided on the bearing housing side member and the annular protrusion is provided on the support base side member, but the present invention is not limited to this, and the annular recess may be provided on the support base side member and the annular protrusion may be provided on the bearing housing side member.

[0082] Furthermore, in the above embodiment, the pressure chamber 66 is formed in an annular shape by the annular recess 64 and the annular protrusion 65, but multiple recesses and protrusions may be formed in the circumferential direction to form multiple pressure chambers. In this case, hydraulic oil and an elastic member may be disposed in each of the multiple pressure chambers, and an O-ring may be disposed between the inner peripheral surface of the recess and the outer peripheral surface of the protrusion to provide a configuration that prevents hydraulic oil leakage and damping functions. Also, a storage chamber that opens to the outer peripheral surface of the protrusion and an orifice that communicates the storage chamber with the pressure chamber may be provided to provide an additional damping function.

[0083] For example, as shown in FIG. 13( a), four pressure chambers 66 may be arranged around the screw shaft 21 in the circumferential direction, or as shown in FIG. 13( b), two pressure chambers 66 arranged side by side and adjacent to each other in the radial direction may be arranged at four circumferential positions, i.e., a total of eight pressure chambers 66 may be arranged around the screw shaft 21. Alternatively, as shown in FIG. 14( a), two pressure chambers 66 may be arranged around the screw shaft 21 in the circumferential direction, i.e., the pressure chambers 66 on both sides in the width direction (Y direction) of the screw shaft 21. Alternatively, as shown in FIG. 14( b), three pressure chambers 66 arranged side by side and adjacent to each other in the radial direction (width direction in this example) may be arranged at two circumferential positions, i.e., a total of six pressure chambers 66 may be arranged around the screw shaft 21. In this case, the height dimensions of the support base side member 61 and the bearing housing side member 62 can be reduced.

[0084] 15, two pressure chambers 66 may be arranged around the screw shaft 21, i.e., pressure chambers 66 on both sides in the upper and lower directions relative to the screw shaft 21. In this case, the width dimensions of the support base side member 61 and the bearing housing side member 62 can be reduced.

[0085] 16 is a schematic cross-sectional view taken along line XVI-XVI in FIG. 14(a). In this case, the two pressure chambers 66 are each formed of a recess 64x and a protrusion 65x. In the drawing, the protrusion 65x is formed integrally with the base of the support base member 61, but it may also be formed separately from the base and then joined.

[0086] The multiple pressure chambers 66 can be arranged arbitrarily as long as the bearing unit 41 and the bearing housing side member 62 can move stably in the same direction following the axial extension of the screw shaft 21 due to thermal expansion, and specifically, they are preferably arranged point-symmetrically or line-symmetrically on a plane perpendicular to the screw shaft 21. The multiple pressure chambers 66 may also be arranged offset in the axial direction.

[0087] Furthermore, adjacent pressure chambers 66 may be communicated with each other via a communication passage as necessary for the purpose of equalizing pressure, and the working fluid inside may flow through adjacent pressure chambers 66. For example, in Figures 14(b) and 15, adjacent pressure chambers 66 are communicated with each other via a communication passage 66x.

[0088] Furthermore, the support base side member 61 and the bearing housing side member 62 are not limited to being formed as a single member, but may be configured as separate members arranged around the screw shaft 21 according to the layout of the pressure chamber 66. Furthermore, the support base side member 61 and the bearing housing side member 62, which are single members, may also be configured with a portion of the circumferential direction being open or divided so as to be arranged around the screw shaft 21. For example, in Figure 14 (b) , two support base side members 61 and two bearing housing side members 62 are configured as separate members in the width direction of the screw shaft 21.

[0089] In addition, similar to the other housing position adjustment mechanisms 160 described above, the pressure generating means in the multiple pressure chambers 66 are not limited to all having the same configuration, i.e., a configuration having a working fluid and an elastic member, and the pressure generating means in any of the pressure chambers 66 may have another configuration, such as using only a working fluid or only an elastic member.

[0090] Furthermore, the recesses and protrusions that make up the pressure chambers 66 are not limited to being circular in cross section, but may be any shape, such as rectangular. Furthermore, the cross-sectional dimensions and axial dimensions of the multiple pressure chambers 66 can each be configured as desired.

[0091] Sixth Embodiment In the housing position adjustment mechanism 60 of the above-described embodiment and modified example, when the screw shaft 21 extends in the axial direction, the volume of the pressure chamber 66 increases, and the compressed hydraulic oil 70 and the disc spring 80 gradually reduce their pressure while pressing the bearing unit 41 and the bearing housing side member 62 to the left. This causes the pair of angular contact ball bearings 53 to move in the axial direction, maintaining the axial support rigidity of the screw shaft 21.

[0092] However, in the sixth embodiment, the axial support rigidity of the screw shaft 21 is maintained by using a housing position adjustment mechanism 60 as shown in Fig. 17. Specifically, when the screw shaft 21 extends in the axial direction, the bearing unit 41 and the bearing housing side member 62 move to the left via the pair of angular contact ball bearings 53, 53 that move together with the screw shaft 21, and the volume of the pressure chamber 66 decreases. On the other hand, as the pressure of the hydraulic oil 70 and the disc spring 80 gradually increases, the bearing unit 41 and the bearing housing side member 62 are pressed to the right. Therefore, by adjusting the volume of the pressure chamber 66 so as to allow the screw shaft 21 to extend in the axial direction, the axial support rigidity of the screw shaft 21 can be maintained.

[0093] In this case, the support base side member 61 has a small-diameter cylindrical portion 61c extending from the small-diameter portion of the annular base portion 61b attached to the support base 43 toward the bearing housing 51, and an outward flange portion 61d extending from the tip of the small-diameter cylindrical portion 61c toward the outer diameter side. The bearing housing side member 62 has a large-diameter cylindrical portion 62c extending from the large-diameter portion of the annular base portion 62b attached to the moving-side bearing housing 51 toward the support base 43, and an inward flange portion 62d extending from the tip of the large-diameter cylindrical portion 62c toward the inner diameter side.

[0094] The outward flange portion 61d of the support base side member 61 is movable axially relative to the annular base portion 62b and the inward flange portion 62d of the bearing housing side member 62, and its outer peripheral surface is in sliding contact with the inner peripheral surface of the large-diameter cylindrical portion 62c via an O-ring 67. The inward flange portion 62d of the bearing housing side member 62 is movable axially relative to the annular base portion 61b and the outward flange portion 61d of the support base side member 61, and its inner peripheral surface is in sliding contact with the outer peripheral surface of the small-diameter cylindrical portion 61c via an O-ring 67. Therefore, the pressure chamber 66 is formed by an annular space partitioned by the small-diameter cylindrical portion 61c and the outward flange portion 61d of the support base side member 61 and the large-diameter cylindrical portion 62c and the inward flange portion 62d of the bearing housing side member 62, and this pressure chamber 66 is filled with hydraulic oil 70 and a disc spring 80 in a slightly compressed state.

[0095] Also in this case, the hydraulic oil 70 is appropriately selected so that, even if the temperature rises above 4 degrees, when the pressure chamber 66 narrows in the axial direction in response to the axial elongation of the screw shaft 21, the pressure acting on the bearing housing side member 62 will impart the desired axial rigidity to the screw shaft 21. Furthermore, the multiple disc springs 80 that are used have an elastic coefficient that will provide the desired axial rigidity to the screw shaft 21 overall over a long axial distance while sharing the load with the hydraulic oil 70, even if the temperature of the ball screw feed device 20 rises above 4 degrees and the springs are compressed.

[0096] By forming the pressure chamber 66 in this manner, when the screw shaft 21 stretches axially due to thermal expansion, the pair of angular ball bearings 53, 53, the bearing housing 51, and the bearing housing side member 62 move to the left in the figure while compressing the hydraulic oil 70 and the disc spring 80 in the pressure chamber 66, thereby maintaining the axial support rigidity of the screw shaft 21.

[0097] In addition, by installing the O-ring 67 between the inner surface of the inward flange portion 62d and the outer surface of the small diameter cylindrical portion 61c, and between the outer surface of the outward flange portion 61d and the inner surface of the large diameter cylindrical portion 62c, leakage of the hydraulic oil 70 filled in the pressure chamber 66 can be prevented, and the O-ring 67 also functions as a damping mechanism to damp vibrations occurring in the screw shaft 21.

[0098] Furthermore, compressed hydraulic oil 70 is stored in each gap between the inner circumferential surface of the inward flange portion 62d and the outer circumferential surface of the small-diameter cylindrical portion 61c, and between the outer circumferential surface of the outward flange portion 61d and the inner circumferential surface of the large-diameter cylindrical portion 62c. Therefore, the radial pressure of the hydraulic oil 70 acting on each gap can increase the radial support rigidity and alignment ability between the bearing housing side member 62 and the support base side member 61. As a result, the housing position adjustment mechanism 60 can provide radial support rigidity to the screw shaft 21 and can also have an alignment function for the screw shaft 21.

[0099] The support base side member 61 and the bearing housing side member 62 may each be formed from a single member, but in consideration of ease of assembly, they may each be formed with an O-ring 67 sandwiched between two members 91, 92, 93, 94, as shown in Figure 17. Also, one O-ring 67 and one seal groove 68 are disposed between each opposing surface, but multiple O-rings 67 and multiple seal grooves 68 may be disposed.

[0100] Also, instead of Figure 17, the support base side member 61 may have a large diameter cylindrical portion and an inward flange portion, and the bearing housing side member 62 may have a small diameter cylindrical portion and an outward flange portion to form a pressure chamber.

[0101] 18, such a housing position adjustment mechanism 60 may be provided with a storage chamber 71 and an orifice 72 in the outward flange portion 61d, and similarly to the second embodiment, the working fluid in the pressure chamber 66 and the storage chamber 71 may pass through the orifice 72 and the gap between the inner circumferential surface of the large-diameter cylindrical portion 62c and the outer circumferential surface of the outward flange portion 61d, thereby providing a function of damping vibration of the screw shaft 21. Note that the storage chamber and the orifice may be formed in the inward flange portion 62d, and the storage chamber may be open to the outer circumferential surface of the small-diameter cylindrical portion 61c.

[0102] Also in this housing position adjustment mechanism 60, the pair of angular contact ball bearings 53, 53 may be arranged in a face-to-face configuration as shown in Figures 17 and 18, or in a back-to-back configuration as shown in Figures 19 and 20, or may be arranged in various other support configurations such as a parallel configuration. In addition, although not shown, the pair of angular contact ball bearings does not necessarily have to be made up of two angular contact ball bearings, but may also be made up of three or more ball bearings.

[0103] Furthermore, as shown in Figures 21 and 22, in the housing position adjustment mechanism 60 of the sixth embodiment, similar to the third embodiment, the seal groove 68 formed on the inner surface of the inward flange portion 62d and the outer surface of the outward flange portion 61d may be composed of a tapered surface 69a whose groove depth becomes shallower as it moves away from the pressure chamber side, and circular axial side surfaces 69b, 69c extending radially from both axial end edges of the tapered surface 69a.

[0104] Therefore, as the pressure of the hydraulic oil 70 in the pressure chamber 66 increases and the O-ring 67 is pushed toward the atmospheric pressure side, the O-ring 67 further improves the sealing performance due to the wedge structure between the tapered surface 69a of the seal groove 68 and the outer peripheral surface of the opposing small-diameter cylindrical portion 61c and the inner peripheral surface of the opposing large-diameter cylindrical portion 62c. As a result, even if relative movement occurs between the support base side member 61 and the bearing housing side member 62, leakage of the hydraulic oil 70 toward the atmospheric pressure side can be prevented, and the axial rigidity of the ball screw feed device 20 can be continuously maintained.

[0105] In this modified example, as shown in Figure 22, the seal groove 68 formed on either of the opposing surfaces of the two members 91, 92 that make up the support base side member 61, and the seal groove 68 formed on either of the opposing surfaces of the two members 93, 94 that make up the bearing housing side member 62 may also have a tapered surface 69a in which the groove depth becomes shallower as it moves away from the pressure chamber side.

[0106] Also, in this modified example, a wear-resistant member may be interposed between the O-ring 67 and at least one of the inner surface of the inward flange portion 62d and the outer surface of the small-diameter cylindrical portion 61c, and between the O-ring 67 and at least one of the outer surface of the outward flange portion 61d and the inner surface of the large-diameter cylindrical portion 62c.

[0107] In this case, the wear-resistant member 59 may be interposed between the O-ring 67 and the opposing surface of the O-ring 67 in a seal groove 68 having a tapered surface 69a as shown in FIG. 22, or may be interposed between the O-ring 67 and the opposing surface of the O-ring 67 in a seal groove 68 having a uniform groove depth as shown in FIG. 17.

[0108] Furthermore, as shown in FIG. 23, the housing position adjustment mechanism 60 of the sixth embodiment may be configured so that the support base side member 61 and the bearing housing side member 62 are provided with working fluid volume change units such as heating elements 180, 181 and cooling media 182, 183, as in the fourth embodiment.

[0109] As a result, as described in the fourth embodiment, depending on the state of the ball screw feed device 20 being used, the volume of the hydraulic oil 70 in the pressure chamber 66 can be expanded by the heating elements 180, 181, or the volume of the hydraulic oil 70 in the pressure chamber 66 can be contracted by the cooling media 182, 183, thereby making it possible to continuously maintain the axial support rigidity in a stable state.

[0110] Furthermore, in the housing position adjustment mechanism 60 of the sixth embodiment, as shown in FIG. 24, similar to the fifth embodiment, the second support mechanism 40 may have a tandem configuration in which the housing position adjustment mechanism 60 and another housing position adjustment mechanism 160 are arranged in series in the axial direction between the bearing unit 41 and the support base 43.

[0111] In this case, the other support base side member 161 of the other housing position adjustment mechanism 160 has an annular base portion 161b, a small-diameter cylindrical portion 161c, and an outward flange portion 161d, and the other bearing housing side member 162 has an annular base portion 162b, a large-diameter cylindrical portion 162c, and an inward flange portion 162d. The other support base side member 161 and the other bearing housing side member 162 of the other housing position adjustment mechanism 160 are each composed of two members 191, 192, 193, and 194. The support base side member 61 of the housing position adjustment mechanism 60 and the other bearing housing side member 162 of the other housing position adjustment mechanism 160 are connected to each other and configured as a single unit.

[0112] Furthermore, similar to the fifth embodiment, the second support mechanism 40 may be configured such that a plurality of housing position adjustment mechanisms are arranged in series in the axial direction, or may be configured such that they are arranged in parallel in the radial direction.

[0113] The present invention is not limited to the above-described embodiment, and modifications, improvements, and the like are possible. Furthermore, the embodiments and modifications described in this specification can be combined and applied within a practicable range. For example, an auxiliary accumulator or an external pump that supplies hydraulic oil can be connected to the pressure chamber as needed. Furthermore, the state of the ball screw feed device may be diagnosed or corrected by monitoring the pressure of the hydraulic oil in the pressure chamber and the load applied to the pair of angular bearings 53, 53. Furthermore, in the above-described embodiment, a disc spring is used as the elastic member, but this is not limiting and a coil spring may also be used.

[0114] Furthermore, in the first to fifth embodiments, O-rings 67 are fitted between the outward surface 65a of the annular convex portion 65 and the inward surface 64a of the annular recessed portion 64, and between the inward surface 65b of the annular convex portion 65 and the outward surface 64b of the annular recessed portion 64. However, this is not limited to this, and any seal members may be arranged to prevent leakage of the hydraulic oil 70 from the pressure chamber 66. Similarly, in the sixth embodiment, O-rings 67 are fitted between the outer peripheral surface of the outward flange portion 61d and the inner peripheral surface of the large-diameter cylindrical portion 62c, and between the inner peripheral surface of the inward flange portion 62d and the outer peripheral surface of the small-diameter cylindrical portion 61c. However, this is not limited to this, and any seal members may be arranged to prevent leakage of the hydraulic oil 70 from the pressure chamber 66. Furthermore, it is more preferable that the seal members not only prevent leakage of the hydraulic oil 70 from the pressure chamber 66 but also damp vibrations of the screw shaft 21, similar to the O-ring 67.

[0115] In any embodiment, the hydraulic oil 70 needs to be sealed from the outside after being filled into the pressure chamber 66. In this case, for example, in the housing position adjustment mechanism 60 shown in Fig. 2, an oil supply passage 109 for filling the pressure chamber 66 with the hydraulic oil 70 may be formed in the bearing housing side member 62, as shown in Fig. 25(a), so as to penetrate radially between the inward surface 64a of the annular recess 64 and the outer peripheral surface of the bearing housing side member 62.

[0116] A stopper bolt 110 may be attached to the outer peripheral surface of the bearing housing side member 62, threadedly engaging with a female thread portion 109a formed in the oil supply passage 109 to close the oil supply passage 109. The male thread portion of the stopper bolt 110 may be wrapped with sealing tape (not shown) or coated or filled with a leak prevention agent to fill the gap between the male thread and the female thread portion 109a, thereby more reliably preventing leakage of the hydraulic oil 70 filled in a compressed state.

[0117] An annular seal groove 110a may be formed in the surface of the head of the stopper bolt 110 that faces the outer circumferential surface of the bearing housing side member 62. An O-ring 111 may then be attached to the seal groove 110a to improve the sealing performance of the stopper bolt 110. As shown in Figure 26(b), the bottom surface of the seal groove 110a of the stopper bolt 110 may be tapered to further improve the sealing performance.

[0118] Furthermore, the member blocking the oil supply passage 109 may be a stopper plug instead of the stopper bolt 110. For example, the oil supply passage 109 may be blocked by a tapered stopper plug 112 as shown in FIG. 26( a). In this case, the stopper plug 112 is threaded into a female thread portion 109a formed on the outer diameter side of the oil supply passage 109 and fixed to the oil supply passage 109. Furthermore, as shown in FIG. 26( b), the oil supply passage 109 has a tapered female thread portion 109a on the outer diameter side, and a straight portion 109b without a female thread portion is continuous with the female thread portion 109a via a stepped hole 109c. In this case, the stopper plug 112 may be fastened to the female thread portion 109a with a disk-shaped member 113 accommodated in the stepped hole 109c. In this case, the stopper plug 112 is fastened to the female thread portion 109a while deforming the disk-shaped member 113, thereby ensuring a tight seal between the contact surface of the disk-shaped member 113 and the stepped hole 109c. In addition, the male thread portion of the stopper plug 112 may also be wrapped with sealing tape (not shown) or coated or filled with a leak prevention agent to fill the gap between the male thread and the female thread portion 109a, thereby providing a good seal.

[0119] 26(c), the disk-shaped member 113 may be integrated with an elastically deformable member 114 that forms the contact surface with the stepped hole 109c. Alternatively, as shown in FIG. 26(d), the disk-shaped member 113 may have an annular seal groove 113a formed in the contact surface with the stepped hole 109c, and an O-ring 115 may be disposed therein.

[0120] Furthermore, the oil supply passage 109 communicating with the pressure chamber 66 is not limited to a configuration in which it is formed so as to penetrate in the radial direction, but may be formed so as to penetrate in the axial direction through any of the members that constitute the pressure chamber 66 .

[0121] Furthermore, the support base may be configured to directly or indirectly support the support base side member of the housing position adjustment mechanism, and is not limited to a configuration in which the rotation axis passes through it as in the above embodiment, but may also be configured to be arranged around the rotation axis, and can be designed into any shape.

[0122] (Application to Other Ball Screw Feeding Devices) In the ball screw feeding device 20 of Fig. 1, the drive motor 12 is coupled to one side (the right side in Fig. 1) of the screw shaft 21 supported by the first support mechanism 30, but the present invention is not limited to this. That is, as in the ball screw feeding device 20 of Fig. 27, the drive motor 12 may be coupled to the other side (the left side in Fig. 27) of the screw shaft 21 supported by the second support mechanism 40. In this case, the drive motor 12 is fixed to the base 1 and supported by another support base 85 through which the screw shaft 21 passes. In addition, the tip of the small diameter shaft portion 27 is disposed within the coupling 28 away from the rotating shaft 12a of the drive motor 12 so that the small diameter shaft portion 27 can move in the axial direction when the screw shaft 21 expands axially due to thermal expansion.

[0123] Therefore, the present invention can be used with a high degree of freedom as a ball screw feed device for positioning devices that perform high-precision processing and measurement, such as machine tools (machining centers, lathes, grinding machines, etc.), measuring machines (three-dimensional measuring devices), semiconductor manufacturing equipment (tables for exposure devices, inspection probes, etc.), inspection equipment, etc., and for use in semiconductor manufacturing, etc.

[0124] Furthermore, in the above embodiment, the support base 43 is disposed on the axial center side relative to the bearing unit 41, but the present invention is not limited to this, and the support base 43 may be disposed on the axial end side relative to the bearing unit 41. That is, the support base 43 may be disposed on the axial center side relative to the bearing unit 41 or on the axial end side depending on the configuration and function of the housing position adjustment mechanism 60.

[0125] 28 and 29 , for example, the support base 43 is provided closer to the axial end than the bearing unit 41. In this case, the support base side member 61 may be attached directly or indirectly to the support base 43, and the bearing housing side member 62 may be attached directly or indirectly to the bearing housing 51. In addition, the spacer 48a, which is disposed between the inner ring 55 and the fastening nut 38b, passes through the through hole 43a of the support base 43 and the inside of the support base side member 61 and the bearing housing side member 62.

[0126] 30 and 31 , the support base 43 is disposed closer to the axial end than the bearing unit 41, and is fixed to a support base side member 61 disposed closer to the axial center than the bearing unit 41 by an outer cylinder portion 43b that extends axially from a main body portion having a through hole 43a and surrounds the periphery of the housing position adjustment mechanism 60. In this case, too, the support base side member 61 may be attached directly or indirectly to the support base 43, and the bearing housing side member 62 may be attached directly or indirectly to the bearing housing 51. In addition, a spacer 48a disposed between the inner ring 55 and the fastening nut 38b passes through the through hole 43a of the support base 43.

[0127] (Applications Other Than Ball Screw Feeder Devices) Although the above-described embodiment describes a ball screw feeder device, the present invention can also be applied to a rotation support device in which both axial ends of a rotating shaft are rotatably supported by a pair of support mechanisms. That is, when the axial length of the rotating shaft changes due to the influence of heat, a configuration can be made in which the axial support rigidity of the rotating shaft is continuously and stably maintained using a housing position adjustment mechanism such as that of the above embodiment. Furthermore, by using the housing position adjustment mechanism of the above embodiment, vibrations in the axial and radial directions can be damped.

[0128] 32, a rotation support device 120 includes a rotating shaft 121 and a pair of support mechanisms 30, 40 that rotatably support both axial ends of the rotating shaft 121. The support mechanism 30 includes a bearing housing 31 fixed to the base 1, and bearings 33, 33 that rotatably support the rotating shaft 121 relative to the bearing housing 31, i.e., a pair of angular contact ball bearings 33, 33 arranged in a face-to-face combination.

[0129] The support mechanism 40 also includes a bearing housing 51, a bearing unit 41 that supports the rotating shaft 121 rotatably relative to the bearing housing 51 and is equipped with bearings 53, 53 that can support axial loads, i.e., a pair of angular ball bearings 53, 53 arranged in a face-to-face combination, a support base 43 that is arranged axially toward the center of the bearing unit 41 and through which the rotating shaft 121 passes, and a housing position adjustment mechanism 60 that is arranged between the bearing unit 41 and the support base 43.

[0130] The housing position adjustment mechanism 60 includes a support base side member 61 provided on the support base 43 side and through which the rotating shaft 121 passes, a bearing housing side member 62 provided on the bearing housing 51 side and through which the rotating shaft 121 passes and which is movable in the axial direction relative to the support base side member 61, hydraulic oil (a working fluid having compressible properties) 70 filled in a pressure chamber 66 formed between the support base side member 61 and the bearing housing side member 62, and a disc spring (elastic member) 80 disposed in a compressed state between the opposing axial end faces of the support base side member 61 and the bearing housing side member 62 within the pressure chamber 66. Note that in FIG. 32 , components designated by the same reference numerals as those in the above embodiment are considered to be substantially the same, and their description will be omitted or simplified. The various structures described in the ball screw feed device 20 can also be applied to the rotation support device, and similar effects will be achieved.

[0131] Furthermore, the bearings 33, 53 of the support mechanisms 30, 40 of the rotation support device 120 may be angular contact ball bearings as in the above embodiment, but are not limited to these and may also be roller bearings or plain bearings capable of supporting axial loads. By using such bearings capable of supporting axial loads, the hydraulic oil 70 and the elastic member 80 can be compressed via the bearings, particularly in the support mechanism 40, by tightening the fastening nut 38b as in the above embodiment.

[0132] In addition, in Figure 32, the second support mechanism 40 having the housing position adjustment mechanism 60 is configured to support the end of the rotating shaft 121, but as shown in Figure 33, the second support mechanism 40 having the housing position adjustment mechanism 60 may be configured to support the rotating shaft 121 at a position closer to another support base 85 that supports the drive motor 12.

[0133] For example, when a rotary support device 120 such as that shown in FIG. 33 is applied to a spindle device that rotates a tool in a machine tool, by attaching a tool to the end of the rotating shaft 121 supported by the support mechanism 30, the axial support rigidity of the rotating shaft 121 is continuously and stably maintained while the axial positioning of the tool is reliably performed, thereby enabling high-precision machining.

[0134] In the rotary support device 120 shown in Figures 32 and 33, the drive motor 12 does not necessarily have to be arranged coaxially with the rotating shaft 121, and the power of the drive motor may be transmitted to the rotating shaft 121 via, for example, a pulley or a gear train.

[0135] In addition, the drive motor 12 is not necessarily limited to a separate motor arranged coaxially with the rotary shaft 121, and may be, for example, a built-in motor directly configured on the rotary shaft 121. Furthermore, the rotation support device 120 may be a housing case in which the bearing housing 31 of the first support mechanism 30 and the support base 43 of the second support mechanism 40 are integrated as a support body.

[0136] In addition, in a rotation support device other than a ball screw feed device, the support base may be disposed on the axial end side of the bearing unit as shown in FIGS.

[0137] Furthermore, in the above embodiment, the housing position adjustment mechanism is described as a mechanism for adjusting the axial position of the bearing housing of the bearing that supports the rotating shaft, but the present invention is not limited to this and can be applied as a support mechanism position adjustment mechanism for a shaft support device. That is, the shaft is not limited to a rotating shaft, and the support mechanism is not limited to a configuration including a bearing. The shaft support device may be configured to include a shaft and a pair of support mechanisms provided at both axial ends of the shaft to support the shaft, one of the pair of support mechanisms including a support body (e.g., support base 43 in the above embodiment) through which the shaft passes or around which the shaft is disposed.

[0138] Therefore, the support mechanism position adjustment mechanism of the shaft support device may include a first member (e.g., support base member 61 in the above embodiment) provided on one of the shaft side and the support side, through which the shaft passes or which can be arranged around the shaft, a second member (e.g., bearing housing member 62 in the above embodiment) provided on the other of the shaft side and the support side, through which the shaft passes or which can be arranged around the shaft, movable axially relative to the first member, and forming an accommodation space (e.g., pressure chamber 66 in the above embodiment) between the first member and the second member, a working fluid filled in the accommodation space, and an elastic member arranged in a compressed state between the opposing axial end faces of the first member and the second member within the accommodation space. The support mechanism position adjustment mechanism of such a shaft support device can be configured to employ the structure of the housing position adjustment mechanism described in connection with the ball screw feed device 20, and achieves similar effects.

[0139] 34 and 35 show a rigid-jointed structure 200 as a shaft support device in which a support mechanism position adjustment mechanism is provided on one of a pair of support mechanisms that support a shaft. The rigid-jointed structure 200 includes two parallel steel supports 231, 243 that are fixed vertically to a base 1. Concentric through-holes 231a, 243a are formed in the supports 231, 243, and a shaft 221 that constitutes a beam member is inserted through these through-holes. The supports 231, 243 may be pillars, beams, support plates, or the like, and may be made of members of any shape and material that can support a shaft.

[0140] In this example, the flange portion 226 on one axial end of the shaft 221 abuts against the small diameter step portion 231b of the through hole 231a of the support body 231, and one end of the shaft 221 is positioned and fixed to the support body 231 by the other support mechanism that attaches the pressing lid 232 to the large diameter step portion 231c of the through hole 231a.

[0141] The other axial end of shaft 221 passes through a through-hole 243a of support 243, protrudes to the opposite side from support 231, and is supported by support 243 via a shaft guide member 250, a housing 251, and a support mechanism position adjustment mechanism 260, which constitute one of the support mechanisms. The cross-sectional shape of the central part of shaft 221 is arbitrary, and may be made of a square steel pipe, an H-shaped steel, or the like.

[0142] The shaft guide member 250 is a member configured to surround the shaft 221, guides the small diameter portion 225 of the shaft 221, and has both outer diameter ends sandwiched and integrated between the housing 251 and a pressing member 247 fixed to the housing 251.

[0143] As in the above embodiment, the housing 251 is attached to the support body 243 via a support mechanism position adjustment mechanism 260. That is, a first member 261 corresponding to the support base side member 61 in the above embodiment is fitted into a through hole 243a of the support body 243 and fixed to the support body 243, and a second member 262 corresponding to the bearing housing side member 62 in the above embodiment is fitted into an inward flange 251a of the housing 251 and fixed to the housing 251.

[0144] Therefore, when the shaft guide member 250 is tightened by the fastening nut 38b that is threaded onto the male screw 225a via the spacer 48, a reaction force acts on the shaft guide member 250, and the shaft guide member 250 is subjected to an axial load. Therefore, a predetermined rigidity is provided between the supports 231, 243 and the shaft 221.

[0145] Furthermore, in such a rigid-jointed structure 200, even if axial elongation occurs in the shaft 221, the support mechanism position adjustment mechanism 260 operates to move the shaft guide member 250 and the housing 251 in the same direction in response to the axial elongation of the shaft 221. Therefore, the axial force acting on the shaft 221 can be maintained, and the rigidity of the rigid-jointed structure 200 can be maintained.

[0146] In this example, the housing 251 and the second member 262 of the support mechanism position adjustment mechanism 260 may be integrally configured, and the shaft guide member 250 may be disposed on the integrated member. Alternatively, the housing 251 may be omitted, and the shaft guide member 250 may be directly fixed to the second member 262 of the support mechanism position adjustment mechanism 260. The shaft support device is not limited to a rigid joint structure as in this example, and may have a brace structure in which the support mechanisms on the shaft side and the support body side are pin-jointed. In this case, the shaft 221 may be disposed at an angle depending on the configuration of the brace structure. Furthermore, in a shaft support device such as a rigid structure, both support mechanisms may have a support mechanism position adjustment mechanism.

[0147] As described above, the present specification discloses the following: (A1) A ball screw feed device comprising: a screw shaft having a helical thread groove formed on its outer peripheral surface; a nut having a helical thread groove formed on its inner peripheral surface; a plurality of balls arranged to roll freely between the thread groove of the screw shaft and the thread groove of the nut; and a pair of support mechanisms rotatably supporting both axial end portions of the screw shaft, one of the pair of support mechanisms comprising: a bearing unit including a bearing housing and an angular contact ball bearing each including an outer ring fitted inside the bearing housing, an inner ring fitted outside an axial end portion of the screw shaft, and balls arranged to roll freely between the outer ring and the inner ring; a support base arranged axially centrally from the bearing unit and through which the screw shaft passes; and a housing position adjustment mechanism arranged between the bearing unit and the support base, the housing position adjustment mechanism comprising: a support base side member arranged on the support base side and through which the screw shaft passes; a bearing housing side member arranged on the bearing housing side and through which the screw shaft passes and which is movable axially relative to the support base side member. a pressure chamber formed between the support base member and the bearing housing member, and a pressure chamber formed between the support base member and the bearing housing member, the pressure chamber being compressed to form an elastic member ...

[0148] (A2) The ball screw feed device according to (A1), wherein one of the support base member and the bearing housing member has an annular recess that opens to one axial side, and the other of the support base member and the bearing housing member has an annular protrusion that protrudes toward the other axial side and is axially slidably fitted within the annular recess, and the pressure chamber is formed between the annular recess and the annular protrusion. With this configuration, the pressure chamber is formed between the annular recess and the annular protrusion, allowing the housing position adjustment mechanism to be configured compactly around the screw shaft.

[0149] (A3) The ball screw feed device according to (A2), wherein at least one seal member is attached between the inward surface of the annular recess and the outward surface of the annular protrusion, and between the outward surface of the annular recess and the inward surface of the annular protrusion, respectively. With this configuration, the seal members can prevent leakage of the working fluid filled in the pressure chamber, and the function of the housing position adjustment mechanism can be maintained for a long period of time.

[0150] (A4) The ball screw feed device according to (A2) or (A3), wherein the working fluid is stored in each gap between the inward surface of the annular recess and the outward surface of the annular protrusion, and between the outward surface of the annular recess and the inward surface of the annular protrusion. With this configuration, the housing position adjustment mechanism can provide radial support rigidity to the screw shaft and can also have an aligning function with respect to the screw shaft.

[0151] (A5) The ball screw feed device according to (A2) or (A3), wherein the housing position adjustment mechanism includes: a reservoir chamber formed in the annular convex portion so as to open to an outward or inward surface of the annular convex portion and configured to store the working fluid; and an orifice formed in the annular convex portion so as to communicate the reservoir chamber with the pressure chamber. With this configuration, the working fluid in the pressure chamber and the reservoir chamber passes through the orifice and a gap between the outward surface of the annular convex portion and the inward surface of the annular recess, thereby damping the vibration.

[0152] (A6) The ball screw feed device according to any one of (A1) to (A5), wherein the elastic member is a disc spring having a plurality of through holes or a plurality of slits penetrating in the axial direction in a conical plate portion. With this configuration, the working fluid flows through the plurality of through holes or the plurality of slits, thereby exhibiting a damping effect.

[0153] (A7) The ball screw feed device according to (A3), wherein the seal member is an O-ring, and a seal groove in which the O-ring is disposed is formed on the inward surface of the annular recess or the outward surface of the annular protrusion, and on the outward surface of the annular recess or the inward surface of the annular protrusion, respectively, and the seal groove has a tapered surface whose depth decreases with increasing distance from the pressure chamber. With this configuration, by using an O-ring as the seal member, the O-ring also functions as a damping mechanism to damp vibrations occurring in the screw shaft. Furthermore, even when relative movement occurs between the support base side member and the bearing housing side member, leakage of hydraulic oil to the atmospheric pressure side can be prevented, thereby continuously maintaining the axial rigidity of the ball screw feed device.

[0154] (A8) The ball screw feed device according to (A3) or (A7), wherein the sealing member is an O-ring, and a wear-resistant member is interposed between the O-ring and at least one of the inward surface of the annular recess and the outward surface of the annular protrusion, and between the O-ring and at least one of the outward surface of the annular recess and the inward surface of the annular protrusion. According to this configuration, by using an O-ring as the sealing member, the O-ring also functions as a damping mechanism, damping vibrations generated in the screw shaft. Furthermore, stress concentration on the O-ring can be dispersed, suppressing damage such as wear to the O-ring and the contact surface with the O-ring.

[0155] (A9) The ball screw feed device according to (A1), wherein one of the support base member and the bearing housing member has a small-diameter cylindrical portion extending toward one axial direction and an outward flange portion extending from a tip of the small-diameter cylindrical portion toward an outer diameter side, and the other of the support base member and the bearing housing member has a large-diameter cylindrical portion extending toward the other axial direction and having an inner circumferential surface against which the outer circumferential surface of the outward flange portion slides, and an inward flange portion extending from a tip of the large-diameter cylindrical portion toward an inner diameter side and having an inner circumferential surface against which the outer circumferential surface of the small-diameter cylindrical portion slides, and the pressure chamber is formed in an annular space partitioned by the small-diameter cylindrical portion, the outward flange portion, the large-diameter cylindrical portion, and the inward flange portion. With this configuration, axial support rigidity can be continuously and stably maintained even if the axial length of the screw shaft changes due to the influence of heat.

[0156] (A10) The ball screw feed device according to (A9), wherein at least one seal member for preventing leakage of the working fluid filled in the pressure chamber is attached between the inner peripheral surface of the inward flange portion and the outer peripheral surface of the small diameter cylindrical portion, and between the outer peripheral surface of the outward flange portion and the inner peripheral surface of the large diameter cylindrical portion, respectively. With this configuration, the seal member can prevent leakage of the working fluid filled in the pressure chamber, and the function of the housing position adjustment mechanism can be maintained for a long period of time.

[0157] (A11) The ball screw feed device according to (A9) or (A10), wherein the working fluid is stored in each gap between the inner peripheral surface of the inward flange portion and the outer peripheral surface of the small diameter cylindrical portion, and between the outer peripheral surface of the outward flange portion and the inner peripheral surface of the large diameter cylindrical portion. With this configuration, the housing position adjustment mechanism can provide radial support rigidity to the screw shaft and can also have an aligning function with respect to the screw shaft.

[0158] (A12) The ball screw feed device according to (A9) or (A10), wherein the housing position adjustment mechanism comprises: a reservoir chamber formed in the outward flange portion or the inward flange portion so as to open to the inner circumferential surface of the large-diameter cylindrical portion or the outer circumferential surface of the small-diameter cylindrical portion, for storing the working fluid; and an orifice formed in the outward flange portion or the inward flange portion so as to communicate the reservoir chamber with the pressure chamber. With this configuration, the working fluid in the pressure chamber and the reservoir chamber passes through the orifice and a gap between the inner circumferential surface of the large-diameter cylindrical portion and the outer circumferential surface of the outward flange portion, or between the outer circumferential surface of the small-diameter cylindrical portion and the inner circumferential surface of the inward flange portion, thereby damping the vibration.

[0159] (A13) The ball screw feed device according to (A10), wherein the seal member is an O-ring, and a seal groove in which the O-ring is disposed is formed on the inner peripheral surface of the inward flange portion or the outer peripheral surface of the small-diameter cylindrical portion, and on the outer peripheral surface of the outward flange portion or the inner peripheral surface of the large-diameter cylindrical portion, and the seal groove has a tapered surface whose groove depth decreases with increasing distance from the pressure chamber. With this configuration, by using an O-ring as the seal member, the O-ring also functions as a damping mechanism to damp vibrations occurring in the screw shaft. Furthermore, even when relative movement occurs between the support base side member and the bearing housing side member, leakage of hydraulic oil to the atmospheric pressure side can be prevented, thereby continuously maintaining the axial rigidity of the ball screw feed device.

[0160] (A14) The ball screw feed device according to (A10), wherein the sealing member is an O-ring, and a wear-resistant member is interposed between the O-ring and at least one of the inner circumferential surface of the inward flange portion and the outer circumferential surface of the small-diameter cylindrical portion, and between the O-ring and at least one of the outer circumferential surface of the outward flange portion and the inner circumferential surface of the large-diameter cylindrical portion. With this configuration, the O-ring serves as a damping mechanism to attenuate vibrations occurring in the screw shaft. Furthermore, stress concentration on the O-ring can be dispersed, suppressing damage such as wear to the O-ring and the contact surface with the O-ring.

[0161] (A15) The ball screw feed device according to (A1), wherein a working fluid volume change unit that changes the volume of the working fluid by heating or cooling the working fluid is attached to at least one of the support base side member and the bearing housing side member. With this configuration, the axial support rigidity can be continuously kept stable by heating or cooling the working fluid to expand or contract the volume of the working fluid.

[0162] (A16) The ball screw feed device according to (A1), wherein one of the pair of support mechanisms further includes another housing position adjustment mechanism arranged adjacent to the housing position adjustment mechanism in series or parallel between the bearing unit and the support base, the other housing position adjustment mechanism including: another support base side member provided on the support base side and through which the screw shaft passes; another bearing housing side member provided on the bearing housing side and through which the screw shaft passes and which is axially movable relative to the other support base side member; and a pressure generating means accommodated in a compressed state in a pressure chamber formed between the other support base side member and the other bearing housing side member. With this configuration, in the case of a series arrangement, the axial rigidity of the ball screw feed device can be maintained even when the screw shaft elongates more significantly, and the centering and coaxiality of the screw shaft can be improved. Furthermore, in the case of a parallel arrangement, a larger axial load can be generated and axial rigidity can be maintained compared to when a single housing position adjustment mechanism is provided.

[0163] (A17) A ball screw feed device comprising: a screw shaft having a helical thread groove formed on its outer peripheral surface; a nut having a helical thread groove formed on its inner peripheral surface; a plurality of balls arranged to roll freely between the thread groove of the screw shaft and the thread groove of the nut; and a pair of support mechanisms rotatably supporting both axial end portions of the screw shaft, one of the pair of support mechanisms comprising: a bearing unit including a bearing housing and an angular contact ball bearing each including an outer ring fitted in the bearing housing, an inner ring fitted around an axial end portion of the screw shaft, and balls arranged to roll freely between the outer ring and the inner ring; a support base through which the screw shaft passes; and a housing position adjustment mechanism attached to the bearing unit and the support base, wherein the housing position adjustment mechanism comprises: a support base side member attached to the support base and through which the screw shaft passes; a bearing housing side member attached to the bearing housing and through which the screw shaft passes and which is movable axially relative to the support base side member. a pressure chamber formed between the support base member and the bearing housing member, and a pressure chamber formed between the support base member and the bearing housing member, the pressure chamber being compressed to form an elastic member ...

[0164] (A18) A rotary support device comprising: a rotating shaft; and a pair of support mechanisms rotatably supporting both axial ends of the rotating shaft, one of the pair of support mechanisms comprising: a bearing unit comprising a bearing housing and a bearing that rotatably supports the rotating shaft relative to the bearing housing and is capable of supporting an axial load; a support base disposed axially centrally from the bearing unit and through which the rotating shaft passes; and a housing position adjustment mechanism disposed between the bearing unit and the support base, wherein the housing position adjustment mechanism comprises: a support base side member disposed on the support base side and through which the rotating shaft passes; a bearing housing side member disposed on the bearing housing side and through which the rotating shaft passes and which is movable axially relative to the support base side member; a working fluid filled in a pressure chamber formed between the support base side member and the bearing housing side member; and an elastic member disposed in a compressed state within the pressure chamber between the opposing axial end faces of the support base side member and the bearing housing side member. With this configuration, even if the axial length of the rotating shaft changes due to the effects of heat, the axial support rigidity can be continuously and stably maintained, and vibrations in the axial and radial directions can be damped.

[0165] (A19) A rotary support device comprising a rotating shaft and a pair of support mechanisms rotatably supporting both axial ends of the rotating shaft, one of the pair of support mechanisms comprising: a bearing unit comprising a bearing housing and a bearing that rotatably supports the rotating shaft relative to the bearing housing and is capable of supporting an axial load; a support base through which the rotating shaft passes; and a housing position adjustment mechanism attached to the bearing unit and the support base, wherein the housing position adjustment mechanism comprises: a support base side member attached to the support base and through which the rotating shaft passes; a bearing housing side member attached to the bearing housing and through which the rotating shaft passes and which is movable axially relative to the support base side member; a working fluid filled in a pressure chamber formed between the support base side member and the bearing housing side member; and an elastic member arranged in a compressed state within the pressure chamber between the opposing axial end faces of the support base side member and the bearing housing side member. With this configuration, even if the axial length of the rotating shaft changes due to the effects of heat, the axial support rigidity can be continuously and stably maintained, and vibrations in the axial and radial directions can be damped.

[0166] (A20) In a shaft support device including a shaft and a pair of support mechanisms provided at both axial ends of the shaft to support the shaft on a base, a support mechanism position adjustment mechanism for the shaft support device provided on one of the pair of support mechanisms, comprising: a first member provided on one of the support mechanism side and the base side, and through which the shaft can pass, a second member provided on the other of the support mechanism side and the base side, and through which the shaft can pass, movable axially relative to the first member, and forming an accommodation space between the first member and the second member, a working fluid filled in the accommodation space, and an elastic member disposed in a compressed state within the accommodation space between opposing axial end faces of the first member and the second member. With this configuration, even if the axial length of the shaft changes due to the influence of heat, it is possible to continuously and stably maintain axial support rigidity and to damp vibrations in both the axial and radial directions.

[0167] (A21) In a shaft support device including a shaft and a pair of support mechanisms provided at both axial ends of the shaft to support the shaft on a base, a support mechanism position adjustment mechanism for the shaft support device provided on one of the pair of support mechanisms, comprising: a first member attached to one of the support mechanism and the base, and through which the shaft can pass; a second member attached to the other of the support mechanism and the base, and through which the shaft can pass, movable axially relative to the first member, and forming an accommodation space between the first member and the second member; a working fluid filled in the accommodation space; and an elastic member disposed in a compressed state within the accommodation space between opposing axial end faces of the first member and the second member. With this configuration, even if the axial length of the shaft changes due to the influence of heat, axial support rigidity can be continuously and stably maintained, and vibrations in both the axial and radial directions can be damped.

[0168] (A22) A rotary support device comprising a rotating shaft and a pair of support mechanisms rotatably supporting both axial ends of the rotating shaft, one of the pair of support mechanisms comprising: a bearing unit comprising a bearing housing and a bearing that rotatably supports the rotating shaft relative to the bearing housing and is capable of supporting an axial load; a support base through which the rotating shaft passes; and a housing position adjustment mechanism arranged between the bearing unit and the support base, wherein the housing position adjustment mechanism comprises: a support base side member provided on the support base side and through which the rotating shaft passes or is arranged around the rotation axis; a bearing housing side member provided on the bearing housing side and through which the rotating shaft passes or is arranged around the rotation axis, and which is movable axially relative to the support base side member; a working fluid filled in a pressure chamber formed between the support base side member and the bearing housing side member; and an elastic member arranged in a compressed state within the pressure chamber between the opposing axial end faces of the support base side member and the bearing housing side member. With this configuration, even if the axial length of the rotating shaft changes due to the effects of heat, the axial support rigidity can be continuously and stably maintained, and vibrations in the axial and radial directions can be damped.

[0169] (A23) A rotation support device according to (A22), wherein one of the support base side member and the bearing housing side member has a plurality of recesses opening to one axial side, and the other of the support base side member and the bearing housing side member has a plurality of protrusions protruding toward the other axial side and respectively fitting within the plurality of recesses so as to be slidable in the axial direction, and a plurality of the pressure chambers are respectively formed between the plurality of recesses and the plurality of protrusions. With this configuration, the layout of the housing position adjustment mechanism can be freely configured using the plurality of pressure chambers.

[0170] (A24) The rotation support device according to (A23), wherein the plurality of pressure chambers are arranged on both sides of the rotation shaft in the width direction. With this configuration, the height dimension of the housing position adjustment mechanism can be reduced.

[0171] (A25) The rotation support device according to (A23), wherein the working fluid and the elastic member are respectively disposed in the plurality of pressure chambers. With this configuration, the plurality of pressure chambers can be configured in common.

[0172] (A26) The rotation support device according to (A22), which is a ball screw feed device, further includes: a rotating shaft that is a threaded shaft having a helical thread groove formed on its outer peripheral surface; a nut having a helical thread groove formed on its inner peripheral surface; and a plurality of balls disposed so as to roll between the thread groove of the threaded shaft and the thread groove of the nut. With this configuration, a ball screw feed device can be configured that can continuously and stably maintain axial support rigidity even if the axial length of the rotating shaft changes due to the influence of heat.

[0173] (A27) In a shaft support device including a shaft and a pair of support mechanisms provided at both axial ends of the shaft to support the shaft on a base, a support mechanism position adjustment mechanism for the shaft support device provided on one of the pair of support mechanisms, comprising: a first member provided on one of the support mechanism side and the base side, through which the shaft can pass or which can be arranged around the axis, a second member provided on the other of the support mechanism side and the base side, through which the shaft can pass or which can be arranged around the axis, movable axially relative to the first member, and forming an accommodation space between itself and the first member, a working fluid filled in the accommodation space, and an elastic member arranged in a compressed state within the accommodation space between the opposing axial end faces of the first member and the second member. With this configuration, even if the axial length of the shaft changes due to the influence of heat, it is possible to continuously and stably maintain axial support rigidity and to damp vibrations in both the axial and radial directions.

[0174] (B1) A rotary support device comprising: a rotating shaft and a pair of support mechanisms rotatably supporting both axial ends of the rotating shaft, one of the pair of support mechanisms comprising: a bearing unit comprising a bearing housing and a bearing that rotatably supports the rotating shaft relative to the bearing housing and is capable of supporting an axial load; a support base through which the rotating shaft passes or is arranged around the rotation axis; and a housing position adjustment mechanism arranged between the bearing unit and the support base, wherein the housing position adjustment mechanism comprises: a support base side member provided on the support base side and through which the rotating shaft passes or is arranged around the rotation axis; a bearing housing side member provided on the bearing housing side and through which the rotating shaft passes or is arranged around the rotation axis, and which is movable axially relative to the support base side member; a working fluid filled in a pressure chamber formed between the support base side member and the bearing housing side member; and an elastic member arranged in a compressed state within the pressure chamber between the opposing axial end faces of the support base side member and the bearing housing side member. With this configuration, even if the axial length of the rotating shaft changes due to the effects of heat, the axial support rigidity can be continuously and stably maintained, and vibrations in the axial and radial directions can be damped.

[0175] (B2) The rotation support device according to (B1), wherein one of the support base member and the bearing housing member has an annular recess that opens to one axial side, and the other of the support base member and the bearing housing member has an annular protrusion that protrudes toward the other axial side and is axially slidably fitted within the annular recess, and the pressure chamber is formed between the annular recess and the annular protrusion. With this configuration, the pressure chamber is formed between the annular recess and the annular protrusion, allowing the housing position adjustment mechanism to be configured compactly around the rotation shaft.

[0176] (B3) The rotation support device according to (B2), wherein at least one seal member is attached between the inward surface of the annular recess and the outward surface of the annular protrusion, and between the outward surface of the annular recess and the inward surface of the annular protrusion, respectively. With this configuration, the seal members can prevent leakage of the working fluid filled in the pressure chamber, and the function of the housing position adjustment mechanism can be maintained for a long period of time.

[0177] (B4) The rotation support device according to (B2) or (B3), wherein the working fluid is stored in each gap between the inward surface of the annular recess and the outward surface of the annular protrusion, and between the outward surface of the annular recess and the inward surface of the annular protrusion. With this configuration, the housing position adjustment mechanism can provide radial support rigidity to the rotating shaft and can also have an alignment function with respect to the rotating shaft.

[0178] (B5) The rotation support device according to (B2) or (B3), wherein the housing position adjustment mechanism includes: a reservoir chamber formed in the annular convex portion so as to open to an outward or inward surface of the annular convex portion and configured to store the working fluid; and an orifice formed in the annular convex portion so as to communicate the reservoir chamber with the pressure chamber. With this configuration, the working fluid in the pressure chamber and the reservoir chamber passes through the orifice and the gap between the outward surface of the annular convex portion and the inward surface of the annular recess, thereby damping the vibration.

[0179] (B6) The rotation support device according to any one of (B1) to (B5), wherein the elastic member is a disc spring having a plurality of through holes or a plurality of slits penetrating in the axial direction in a conical plate portion. With this configuration, the working fluid flows through the plurality of through holes or the plurality of slits, thereby achieving a damping effect.

[0180] (B7) The rotation support device according to (B3), wherein the seal member is an O-ring, and a seal groove in which the O-ring is disposed is formed on the inward surface of the annular recess or the outward surface of the annular protrusion, and on the outward surface of the annular recess or the inward surface of the annular protrusion, respectively, and the seal groove has a tapered surface whose groove depth decreases with increasing distance from the pressure chamber. With this configuration, by using an O-ring as the seal member, the O-ring also functions as a damping mechanism, damping vibrations occurring in the rotating shaft. Furthermore, even if relative movement occurs between the support base side member and the bearing housing side member, leakage of hydraulic oil to the atmospheric pressure side can be prevented, thereby continuously maintaining the axial rigidity of the rotation support device.

[0181] (B8) The rotation support device according to (B3) or (B7), wherein the sealing member is an O-ring, and a wear-resistant member is interposed between the O-ring and at least one of the inward surface of the annular recess and the outward surface of the annular protrusion, and between the O-ring and at least one of the outward surface of the annular recess and the inward surface of the annular protrusion. With this configuration, the O-ring serves as a damping mechanism to attenuate vibrations occurring in the rotating shaft. Furthermore, stress concentration on the O-ring can be dispersed, suppressing damage such as wear to the O-ring and the contact surface with the O-ring.

[0182] (B9) The rotation support device according to (B1), wherein one of the support base member and the bearing housing member has a small-diameter cylindrical portion extending toward one axial direction and an outward flange portion extending from a tip of the small-diameter cylindrical portion toward an outer diameter side, and the other of the support base member and the bearing housing member has a large-diameter cylindrical portion extending toward the other axial direction and having an inner circumferential surface against which the outer circumferential surface of the outward flange portion slides, and an inward flange portion extending from a tip of the large-diameter cylindrical portion toward an inner diameter side and having an inner circumferential surface against which the outer circumferential surface of the small-diameter cylindrical portion slides, and the pressure chamber is formed in an annular space partitioned by the small-diameter cylindrical portion, the outward flange portion, the large-diameter cylindrical portion, and the inward flange portion. With this configuration, axial support rigidity can be continuously and stably maintained even if the axial length of the rotating shaft changes due to the influence of heat.

[0183] (B10) The rotation support device according to (B9), wherein at least one seal member that prevents leakage of the working fluid filled in the pressure chamber is attached between the inner peripheral surface of the inward flange portion and the outer peripheral surface of the small diameter cylindrical portion, and between the outer peripheral surface of the outward flange portion and the inner peripheral surface of the large diameter cylindrical portion. With this configuration, the seal member can prevent leakage of the working fluid filled in the pressure chamber, and the function of the housing position adjustment mechanism can be maintained for a long period of time.

[0184] (B11) The rotation support device according to (B9) or (B10), wherein the working fluid is stored in each gap between the inner peripheral surface of the inward flange portion and the outer peripheral surface of the small diameter cylindrical portion, and between the outer peripheral surface of the outward flange portion and the inner peripheral surface of the large diameter cylindrical portion. With this configuration, the housing position adjustment mechanism can provide radial support rigidity to the rotating shaft and can also have an alignment function with respect to the rotating shaft.

[0185] (B12) The rotation support device according to (B9) or (B10), wherein the housing position adjustment mechanism comprises: a reservoir chamber formed in the outward flange portion or the inward flange portion so as to open to the inner circumferential surface of the large-diameter cylindrical portion or the outer circumferential surface of the small-diameter cylindrical portion, for storing the working fluid; and an orifice formed in the outward flange portion or the inward flange portion so as to communicate the reservoir chamber with the pressure chamber. With this configuration, the working fluid in the pressure chamber and the reservoir chamber passes through the orifice and a gap between the inner circumferential surface of the large-diameter cylindrical portion and the outer circumferential surface of the outward flange portion, or between the outer circumferential surface of the small-diameter cylindrical portion and the inner circumferential surface of the inward flange portion, thereby damping the vibration.

[0186] (B13) The rotation support device according to (B10), wherein the seal member is an O-ring, and a seal groove in which the O-ring is disposed is formed on the inner circumferential surface of the inward flange portion or the outer circumferential surface of the small-diameter cylindrical portion, and on the outer circumferential surface of the outward flange portion or the inner circumferential surface of the large-diameter cylindrical portion, and the seal groove has a tapered surface whose groove depth decreases with increasing distance from the pressure chamber side. With this configuration, by using an O-ring as the seal member, the O-ring also functions as a damping mechanism, damping vibrations occurring in the rotating shaft. Furthermore, even if relative movement occurs between the support base side member and the bearing housing side member, leakage of hydraulic oil to the atmospheric pressure side can be prevented, thereby continuously maintaining the axial rigidity of the rotation support device.

[0187] (B14) The rotation support device according to (B10), wherein the sealing member is an O-ring, and a wear-resistant member is interposed between the O-ring and at least one of the inner circumferential surface of the inward flange portion and the outer circumferential surface of the small-diameter cylindrical portion, and between the O-ring and at least one of the outer circumferential surface of the outward flange portion and the inner circumferential surface of the large-diameter cylindrical portion. With this configuration, the O-ring serves as a damping mechanism to attenuate vibrations occurring in the rotating shaft. Furthermore, stress concentration on the O-ring can be dispersed, suppressing damage such as wear to the O-ring and the contact surface with the O-ring.

[0188] (B15) The rotation support device according to (B1), wherein a working fluid volume change unit that changes the volume of the working fluid by heating or cooling the working fluid is attached to at least one of the support base side member and the bearing housing side member. With this configuration, the working fluid can be heated or cooled to expand or contract its volume, thereby continuously maintaining a stable axial support rigidity.

[0189] (B16) The rotary support device according to (B1), wherein one of the pair of support mechanisms further includes another housing position adjustment mechanism arranged adjacent to the housing position adjustment mechanism in series or parallel between the bearing unit and the support base, the other housing position adjustment mechanism including: another support base side member provided on the support base side and through which the rotation shaft passes or around which the rotation shaft is arranged; another bearing housing side member provided on the bearing housing side and through which the rotation shaft passes or around which the rotation shaft is arranged, and which is movable axially relative to the other support base side member; and pressure generating means accommodated in a compressed state in a pressure chamber formed between the other support base side member and the other bearing housing side member. With this configuration, in the case of a series arrangement, the axial rigidity of the rotary support device can be maintained even when the extension of the rotation shaft is greater, and the alignment and coaxiality of the rotation shaft can be improved. Furthermore, in the case of a parallel arrangement, a larger axial load can be generated and axial rigidity can be maintained compared to when a single housing position adjustment mechanism is arranged.

[0190] (B17) The rotation support device according to (B1), wherein one of the support base side member and the bearing housing side member has a plurality of recesses opening to one axial side, and the other of the support base side member and the bearing housing side member has a plurality of protrusions protruding toward the other axial side and respectively fitting within the plurality of recesses so as to be slidable in the axial direction, and the plurality of pressure chambers are respectively formed between the plurality of recesses and the plurality of protrusions. With this configuration, the layout of the housing position adjustment mechanism can be freely configured using the plurality of pressure chambers.

[0191] (B18) The rotation support device according to (B17), wherein the plurality of pressure chambers are arranged on both sides of the rotation shaft in the width direction. With this configuration, the height dimension of the housing position adjustment mechanism can be reduced.

[0192] (B19) The rotation support device according to (B17), wherein the working fluid and the elastic member are respectively disposed in the plurality of pressure chambers. With this configuration, the plurality of pressure chambers can be configured in common.

[0193] (B20) The rotation support device according to any one of (B1) to (B19), wherein the bearing of the bearing unit includes a pair of angular contact ball bearings each including an outer ring fitted inside the bearing housing, an inner ring fitted around an axial end of the rotating shaft, and balls disposed so as to roll between the outer ring and the inner ring. With this configuration, when the bearing unit has a pair of angular contact ball bearings, it is possible to continuously and stably maintain axial support rigidity even if the axial length of the rotating shaft changes due to the influence of heat.

[0194] (B21) The rotation support device according to any one of (B1) to (B20), which is a ball screw feed device, further comprising: a rotating shaft that is a threaded shaft having a helical thread groove formed on its outer peripheral surface, a nut having a helical thread groove formed on its inner peripheral surface, and a plurality of balls disposed so as to roll between the thread groove of the threaded shaft and the thread groove of the nut. With this configuration, a ball screw feed device can be configured that can continuously and stably maintain axial support rigidity even if the axial length of the rotating shaft changes due to the influence of heat.

[0195] (B22) A shaft support device including a shaft and a pair of support mechanisms provided at both axial ends of the shaft to support the shaft, a support mechanism position adjustment mechanism for the shaft support device provided on one of the pair of support mechanisms, wherein one of the pair of support mechanisms has a support through which the shaft passes or is arranged around the shaft, the support mechanism comprising: a first member provided on one of the shaft side and the support side, through which the shaft can pass or be arranged around the axis, a second member provided on the other of the shaft side and the support side, through which the shaft can pass or be arranged around the axis, movable axially relative to the first member, and forming an accommodation space between itself and the first member, a working fluid filled in the accommodation space, and an elastic member arranged in a compressed state within the accommodation space between the opposing axial end faces of the first member and the second member. With this configuration, even if the axial length of the shaft changes due to the influence of heat, axial support rigidity can be continuously and stably maintained, and vibrations in both the axial and radial directions can be damped.

[0196] (B23) The support mechanism position adjustment mechanism for a shaft support device described in (B22), wherein the shaft is a rotating shaft, one of the pair of support mechanisms further includes a bearing unit including a bearing housing and a bearing that rotatably supports the rotating shaft relative to the bearing housing and is capable of supporting an axial load, the support mechanism position adjustment mechanism is a housing position adjustment mechanism disposed between the bearing unit and the support, the first member is a support side member provided on the support side and through which the rotating shaft can pass or which can be arranged around the rotating shaft, and the second member is a bearing housing side member provided on the bearing housing side and through which the rotating shaft can pass or which can be arranged around the rotating shaft, movable in the axial direction relative to the support side member, and which forms the accommodation space between itself and the support side member. With this configuration, axial support rigidity can be continuously and stably maintained even if the axial length of the shaft changes due to the influence of heat.

[0197] (B24) A support mechanism position adjustment mechanism for a shaft support device according to (B22) or (B23), wherein one of the first member and the second member has an annular recess that opens to one axial side, and the other of the first member and the second member has an annular protrusion that protrudes toward the other axial side and is axially slidably fitted within the annular recess, and the pressure chamber is formed between the annular recess and the annular protrusion. With this configuration, the pressure chamber is formed between the annular recess and the annular protrusion, allowing the support mechanism position adjustment mechanism to be configured compactly around the shaft.

[0198] (B25) The support mechanism position adjustment mechanism for a shaft support device according to (B24), wherein at least one seal member is attached between the inward surface of the annular recess and the outward surface of the annular protrusion, and between the outward surface of the annular recess and the inward surface of the annular protrusion. With this configuration, the seal members can prevent leakage of the working fluid filled in the pressure chamber, and the function of the support mechanism position adjustment mechanism can be maintained for a long period of time.

[0199] (B26) The support mechanism position adjustment mechanism for a shaft support device according to (B24) or (B25), wherein the working fluid is stored in each gap between the inward surface of the annular recess and the outward surface of the annular protrusion, and between the outward surface of the annular recess and the inward surface of the annular protrusion. With this configuration, the support mechanism position adjustment mechanism can provide radial support rigidity to the shaft and can also have an aligning function with respect to the shaft.

[0200] (B27) The support mechanism position adjustment mechanism for a shaft support device according to (B24) or (B25), wherein the support mechanism position adjustment mechanism comprises: a reservoir chamber formed in the annular convex portion so as to open to an outward or inward surface of the annular convex portion and configured to store the working fluid; and an orifice formed in the annular convex portion so as to communicate the reservoir chamber with the pressure chamber. With this configuration, the working fluid in the pressure chamber and the reservoir chamber passes through the orifice and the gap between the outward surface of the annular convex portion and the inward surface of the annular recess, thereby damping the vibration.

[0201] (B28) The support mechanism position adjustment mechanism for a shaft support device according to any one of (B22) to (B27), wherein the elastic member is a disc spring having a plurality of through holes or a plurality of slits penetrating in the axial direction in a conical plate portion. With this configuration, a damping effect can be achieved by the working fluid flowing through the plurality of through holes or the plurality of slits.

[0202] (B29) The support mechanism position adjustment mechanism for a shaft support device described in (B25), wherein the seal member is an O-ring, and a seal groove in which the O-ring is disposed is formed on the inward surface of the annular recess or the outward surface of the annular protrusion, and on the outward surface of the annular recess or the inward surface of the annular protrusion, respectively, and the seal groove has a tapered surface whose groove depth decreases with increasing distance from the pressure chamber. With this configuration, by using an O-ring as the seal member, the O-ring also functions as a damping mechanism to damp vibrations occurring in the shaft. Furthermore, even if relative movement occurs between the first member and the second member, leakage of hydraulic oil to the atmospheric pressure side can be prevented, thereby continuously maintaining the axial rigidity of the shaft support device.

[0203] (B30) The support mechanism position adjustment mechanism for a shaft support device described in (B25) or (B29) is characterized in that the sealing member is an O-ring, and a wear-resistant member is interposed between the O-ring and at least one of the inward surface of the annular recess and the outward surface of the annular protrusion, and between the O-ring and at least one of the outward surface of the annular recess and the inward surface of the annular protrusion. With this configuration, by using an O-ring as the sealing member, the O-ring also functions as a damping mechanism, damping vibrations occurring in the shaft. Furthermore, stress concentration on the O-ring can be dispersed, suppressing damage such as wear to the O-ring and the contact surface with the O-ring.

[0204] (B31) The support mechanism position adjustment mechanism for a shaft support device described in (B22), wherein one of the first member and the second member has a small-diameter cylindrical portion extending toward one side in the axial direction and an outward flange portion extending from a tip of the small-diameter cylindrical portion toward an outer diameter side, and the other of the first member and the second member has a large-diameter cylindrical portion extending toward the other side in the axial direction and having an inner circumferential surface with which the outer circumferential surface of the outward flange portion slides, and an inward flange portion extending from the tip of the large-diameter cylindrical portion toward an inner diameter side and having an inner circumferential surface that slides against the outer circumferential surface of the small-diameter cylindrical portion, and the pressure chamber is formed in an annular space partitioned by the small-diameter cylindrical portion, the outward flange portion, the large-diameter cylindrical portion, and the inward flange portion. With this configuration, axial support rigidity can be continuously and stably maintained even if the axial length of the shaft changes due to the influence of heat.

[0205] (B32) The support mechanism position adjustment mechanism for a shaft support device according to (B31), wherein at least one seal member that prevents leakage of the working fluid filled in the pressure chamber is attached between the inner peripheral surface of the inward flange portion and the outer peripheral surface of the small-diameter cylindrical portion, and between the outer peripheral surface of the outward flange portion and the inner peripheral surface of the large-diameter cylindrical portion. With this configuration, the seal member can prevent leakage of the working fluid filled in the pressure chamber, and the function of the support mechanism position adjustment mechanism can be maintained for a long period of time.

[0206] (B33) A support mechanism position adjustment mechanism for a shaft support device according to (B31) or (B32), wherein the working fluid is stored in each gap between the inner peripheral surface of the inward flange portion and the outer peripheral surface of the small diameter cylindrical portion, and between the outer peripheral surface of the outward flange portion and the inner peripheral surface of the large diameter cylindrical portion. With this configuration, the support mechanism position adjustment mechanism can provide radial support rigidity to the shaft and can also have an aligning function with respect to the shaft.

[0207] (B34) The support mechanism position adjustment mechanism for a shaft support device according to (B31) or (B32), wherein the support mechanism position adjustment mechanism comprises: a reservoir chamber formed in the outward flange portion or the inward flange portion so as to open to the inner circumferential surface of the large-diameter cylindrical portion or the outer circumferential surface of the small-diameter cylindrical portion, for storing the working fluid; and an orifice formed in the outward flange portion or the inward flange portion so as to communicate the reservoir chamber with the pressure chamber. With this configuration, the working fluid in the pressure chamber and the reservoir chamber passes through the orifice and the gap between the inner circumferential surface of the large-diameter cylindrical portion and the outer circumferential surface of the outward flange portion, or between the outer circumferential surface of the small-diameter cylindrical portion and the inner circumferential surface of the inward flange portion, thereby damping the vibration.

[0208] (B35) The support mechanism position adjustment mechanism for a shaft support device described in (B32), wherein the seal member is an O-ring, and a seal groove in which the O-ring is disposed is formed on the inner circumferential surface of the inward flange portion or the outer circumferential surface of the small-diameter cylindrical portion, and on the outer circumferential surface of the outward flange portion or the inner circumferential surface of the large-diameter cylindrical portion, and the seal groove has a tapered surface whose groove depth becomes shallower with increasing distance from the pressure chamber. With this configuration, by using an O-ring as the seal member, the O-ring also functions as a damping mechanism to damp vibrations occurring in the shaft. Furthermore, even if relative movement occurs between the first member and the second member, leakage of hydraulic oil to the atmospheric pressure side can be prevented, thereby continuously maintaining the axial rigidity of the shaft support device.

[0209] (B36) The support mechanism position adjustment mechanism for a shaft support device described in (B32) is characterized in that the sealing member is an O-ring, and a wear-resistant member is interposed between the O-ring and at least one of the inner circumferential surface of the inward flange portion and the outer circumferential surface of the small-diameter cylindrical portion, and between the O-ring and at least one of the outer circumferential surface of the outward flange portion and the inner circumferential surface of the large-diameter cylindrical portion. With this configuration, by using an O-ring as the sealing member, the O-ring also functions as a damping mechanism, damping vibrations occurring in the shaft. Furthermore, stress concentration on the O-ring can be dispersed, suppressing damage such as wear to the O-ring and the contact surface with the O-ring.

[0210] (B37) The support mechanism position adjustment mechanism for a shaft support device according to (B22), wherein a working fluid volume changer that changes the volume of the working fluid by heating or cooling the working fluid is attached to at least one of the first member and the second member. With this configuration, the working fluid is heated or cooled to expand or contract its volume, thereby making it possible to continuously maintain a stable axial support rigidity.

[0211] (B38) The support mechanism position adjustment mechanism for a shaft support device described in (B22), wherein one of the pair of support mechanisms further includes another support mechanism position adjustment mechanism arranged adjacent to the support mechanism position adjustment mechanism in series or parallel between the bearing unit and the support base, the other support mechanism position adjustment mechanism including: an other first member provided on the support base side and through which the shaft passes or around which the shaft is arranged; an other second member provided on the bearing housing side and through which the shaft passes or around which the shaft is arranged, and which is movable axially relative to the other first member; and pressure generating means accommodated in a compressed state in a pressure chamber formed between the other first member and the other second member. With this configuration, in the case of a series arrangement, the axial rigidity of the shaft support device can be maintained even when the shaft elongates even more, and the shaft alignment and coaxiality can be improved. Furthermore, in the case of a parallel arrangement, a larger axial load can be generated and axial rigidity can be maintained compared to when a single support mechanism position adjustment mechanism is arranged.

[0212] (B39) A support mechanism position adjustment mechanism for a shaft support device according to (B22), wherein one of the first member and the second member has a plurality of recesses that open to one axial side, and the other of the first member and the second member has a plurality of protrusions that protrude toward the other axial side and are axially slidably fitted within the plurality of recesses, and the plurality of pressure chambers are formed between the plurality of recesses and the plurality of protrusions, respectively. With this configuration, the layout of the support mechanism position adjustment mechanism can be freely configured using the plurality of pressure chambers.

[0213] (B40) The support mechanism position adjustment mechanism for a shaft support device according to (B39), wherein the plurality of pressure chambers are arranged on both sides of the shaft in the width direction. With this configuration, the height dimension of the support mechanism position adjustment mechanism can be reduced.

[0214] (B41) The support mechanism position adjustment mechanism for a shaft support device according to (B39), wherein the working fluid and the elastic member are respectively disposed in the plurality of pressure chambers. With this configuration, the plurality of pressure chambers can be configured in common.

[0215] In addition, this application is a Japanese patent application filed on October 28, 2022 (Patent Application No. 2022-173761), a Japanese patent application filed on July 21, 2023 (Patent Application No. 2023-118995), and a Japanese patent application filed on August 22, 2023 (Patent Application No. 2023-134635), the contents of which are incorporated by reference into this application.

[0216] DESCRIPTION OF SYMBOLS 20 Ball screw feed device (shaft support device, rotation support device) 21 Screw shaft (shaft, rotating shaft) 23 Nut 30 First support mechanism (support mechanism) 31 Fixed side bearing housing 33, 53 Angular contact ball bearing (bearing) 34, 54 Outer ring 35, 55 Inner ring 36, 56 Balls 38a, 38b Fastening nut 40 Second support mechanism (support mechanism) 41 Bearing unit 43 Support base (support member) 51 Moving side bearing housing (bearing housing) 51a Inward flange 59 Wear-resistant member 60 Housing position adjustment mechanism (support mechanism position adjustment mechanism) 61 Support base side member (first member) 62 Bearing housing side member (second member) 64 Annular recess 65 Annular protrusion 66 Pressure chamber (accommodation space) 67 O-ring (seal member) 68 Seal groove 69a Tapered surface 70 Hydraulic oil (working fluid) 80 Disc spring (elastic member) 120 Rotation support device 121 Rotating shaft 160 Other housing position adjustment mechanism (other support mechanism position adjustment mechanism) 161 Other support base side member (other support body side member) 162 Other bearing housing side member 180, 181 Heat generating element (working fluid volume change unit) 182, 183 Cooling medium (working fluid volume change unit)

Claims

1. A rotary support device comprising a rotary shaft and a pair of support mechanisms that rotatably support both axial ends of the rotary shaft, wherein one of the pair of support mechanisms includes a bearing unit including a bearing housing and a bearing that rotatably supports the rotary shaft with respect to the bearing housing and is capable of supporting an axial load, a support base through which the rotary shaft passes or disposed around the rotary shaft, a housing position adjustment mechanism disposed between the bearing unit and the support base, and wherein the housing position adjustment mechanism includes a support base side member provided on the support base side, through which the rotary shaft passes or disposed around the rotary shaft, a bearing housing side member provided on the bearing housing side, through which the rotary shaft passes or disposed around the rotary shaft, and axially relatively movable with respect to the support base side member, a working fluid filled in a pressure chamber formed between the support base side member and the bearing housing side member, and an elastic member disposed in a compressed state between opposing axial end faces of the support base side member and the bearing housing side member within the pressure chamber, and wherein the pressure chamber is sealed from the outside. A rotary support device.

2. One of the support base side member and the bearing housing side member has an annular recess opening axially on one side, and the other of the support base side member and the bearing housing side member has an annular protrusion protruding axially toward the other side and slidably fitted axially within the annular recess, and wherein the pressure chamber is formed between the annular recess and the annular protrusion. The rotary support device according to Claim 1.

3. At least one seal member is respectively mounted between the inner facing surface of the annular recess and the outer facing surface of the annular protrusion, and between the outer facing surface of the annular recess and the inner facing surface of the annular protrusion. The rotary support device according to Claim 2.

4. The working fluid is stored in each gap between the inner facing surface of the annular recess and the outer facing surface of the annular protrusion, and between the outer facing surface of the annular recess and the inner facing surface of the annular protrusion. The rotary support device according to Claim 2 or 3.

5. The housing position adjustment mechanism includes a storage chamber formed within the annular protrusion so as to open to the outer or inner facing surface of the annular protrusion and storing the working fluid, and an orifice formed within the annular protrusion so as to communicate the storage chamber and the pressure chamber. The rotary support device according to Claim 2 or 3.

6. ​ The rotary support device according to claim 1, wherein the elastic member is a disc spring having a plurality of through holes or a plurality of slits penetrating in the axial direction in a conical plate portion.

7. The seal member is an O-ring, seal grooves in which the O-ring is disposed are respectively formed on an inner surface of the annular recess or an outer surface of the annular protrusion, and on an outer surface of the annular recess or an inner surface of the annular protrusion, The rotary support device according to claim 3, wherein the seal groove has a tapered surface whose groove depth becomes shallower as it moves away from the pressure chamber side.

8. The seal member is an O-ring, A wear-resistant member is interposed between the O-ring and at least one of an inner surface of the annular recess and an outer surface of the annular protrusion, and between the O-ring and at least one of an outer surface of the annular recess and an inner surface of the annular protrusion. The rotary support device according to claim 3.

9. One of the support base side member and the bearing housing side member has a small-diameter cylindrical portion extending axially on one side, and an outward flange portion extending from the tip of the small-diameter cylindrical portion toward the outer diameter side, The other of the support base side member and the bearing housing side member has a large-diameter cylindrical portion extending axially toward the other side and having an inner peripheral surface in sliding contact with the outer peripheral surface of the outward flange portion, and an inward flange portion extending from the tip of the large-diameter cylindrical portion toward the inner diameter side and having an inner peripheral surface in sliding contact with the outer peripheral surface of the small-diameter cylindrical portion, The rotary support device according to claim 1, wherein the pressure chamber is formed in an annular space partitioned by the small-diameter cylindrical portion, the outward flange portion, the large-diameter cylindrical portion, and the inward flange portion.

10. At least one seal member for preventing leakage of the working fluid filled in the pressure chamber is respectively mounted between the inner peripheral surface of the inward flange portion and the outer peripheral surface of the small-diameter cylindrical portion, and between the outer peripheral surface of the outward flange portion and the inner peripheral surface of the large-diameter cylindrical portion. The rotary support device according to claim 9.

11. The working fluid is stored in each gap between the inner peripheral surface of the inward flange portion and the outer peripheral surface of the small-diameter cylindrical portion, and between the outer peripheral surface of the outward flange portion and the inner peripheral surface of the large-diameter cylindrical portion. The rotary support device according to claim 9 or 10.

12. The housing position adjustment mechanism is formed in the outward flange portion or the inward flange portion so as to open to the inner peripheral surface of the large-diameter cylindrical portion or the outer peripheral surface of the small-diameter cylindrical portion, and includes a storage chamber for storing the working fluid, and an orifice formed in the outward flange portion or the inward flange portion so as to communicate the storage chamber with the pressure chamber. The rotary support device according to claim 9 or 10.

13. The seal member is an O-ring, Seal grooves in which the O-ring is disposed are respectively formed on the inner peripheral surface of the inward flange portion or the outer peripheral surface of the small-diameter cylindrical portion, and on the outer peripheral surface of the outward flange portion or the inner peripheral surface of the large-diameter cylindrical portion, The seal groove has a tapered surface whose groove depth becomes shallower as it moves away from the pressure chamber side. The rotary support device according to claim 10.

14. The seal member is an O-ring, A wear-resistant member is interposed between the O-ring and at least one of the inner peripheral surface of the inward flange portion and the outer peripheral surface of the small-diameter cylindrical portion, and between the O-ring and at least one of the outer peripheral surface of the outward flange portion and the inner peripheral surface of the large-diameter cylindrical portion. The rotary support device according to claim 10.

15. An operating fluid volume change portion for changing the volume of the operating fluid by heating or cooling the operating fluid is attached to at least one of the support base side member and the bearing housing side member. The rotary support device according to claim 1.

16. One of the pair of support mechanisms, Further includes another housing position adjustment mechanism disposed in series or in parallel adjacent to the housing position adjustment mechanism between the bearing unit and the support base, The other housing position adjustment mechanism, Another support base side member provided on the support base side, through which the rotary shaft passes, or disposed around the rotary shaft, Another bearing housing side member provided on the bearing housing side, through which the rotary shaft passes, or disposed around the rotary shaft, and axially relatively movable with respect to the other support base side member, And pressure generating means housed in a compressed state in a pressure chamber formed between the other support base side member and the other bearing housing side member. The rotary support device according to claim 1.

17. One of the support base side member and the bearing housing side member has a plurality of recesses opening on one side in the axial direction, ​ The other of the support base side member and the bearing housing side member has a plurality of convex portions that project toward the other axial direction and are respectively fitted slidably in the axial direction within the plurality of concave portions. The plurality of pressure chambers are respectively formed between the plurality of concave portions and the plurality of convex portions. The rotary support device according to claim 1.

18. The rotary support device according to claim 17, wherein the plurality of pressure chambers are arranged on both sides in the width direction with respect to the rotary shaft.

19. The rotary support device according to claim 17, wherein the working fluid and the elastic member are respectively arranged in the plurality of pressure chambers.

20. The bearing of the bearing unit includes a pair of angular ball bearings each having an outer ring fitted inside the bearing housing, an inner ring fitted outside an axial end of the rotary shaft, and balls arranged to be rotatable between the outer ring and the inner ring, the rotary support device according to claim 1.

21. The rotary support device further includes a screw shaft having a spiral screw groove formed on an outer peripheral surface, a nut having a spiral screw groove formed on an inner peripheral surface, and a plurality of balls arranged to be rotatable between the screw groove of the screw shaft and the screw groove of the nut. The rotary support device according to claim 1, which is a ball screw feed device.

22. In a shaft support device including a shaft and a pair of support mechanisms provided at both axial ends of the shaft to support the shaft, a support mechanism position adjustment mechanism of the shaft support device provided on one of the pair of support mechanisms, One of the pair of support mechanisms has a support body through which the shaft passes or is arranged around the shaft. A first member provided on one of the shaft side and the support body side, through which the shaft can pass or be arranged around the shaft. A second member provided on the other of the shaft side and the support body side, through which the shaft can pass or be arranged around the shaft, relatively movable in the axial direction with respect to the first member, and forming an accommodation space between the first member and the second member. A working fluid filled in the accommodation space. An elastic member arranged in a compressed state between opposing axial end faces of the first member and the second member within the accommodation space. comprising The pressure chamber is sealed from the outside, a support mechanism position adjustment mechanism of the shaft support device.

23. The shaft is a rotary shaft. One of the pair of support mechanisms further includes a bearing unit including a bearing housing and a bearing that rotatably supports the rotating shaft with respect to the bearing housing and can support an axial load. The support mechanism position adjustment mechanism is a housing position adjustment mechanism disposed between the bearing unit and the support. The first member is a support-side member provided on the support side, through which the rotating shaft can pass or which can be disposed around the rotating shaft. The second member is a bearing housing-side member provided on the bearing housing side, through which the rotating shaft can pass or which can be disposed around the rotating shaft, axially movable relative to the support-side member, and forming the accommodation space with the support-side member. The support mechanism position adjustment mechanism of the shaft support device according to claim 22.